Our unique integration of world-class curriculum, innovative performance technology, and field application tools create a continuous improvement life-cycle for sales teams.
Over 1.5 million people and hundreds of global organizations have used SPI's Solution Selling® based sales performance programs to effectively apply a buyer-aligned sales process, diagnose customer needs, and position new insights and solutions for greatest customer value.
We empower organizations to market and sell high-value solutions. Our comprehensive programs include essential processes, methods, and tools for organizational sales transformation.
The SPI-1 Sales Performance Platform is a complete, closed-loop system that provides a precise, data-driven approach to continual sales improvement.
Our expert services are designed to help align the investment in sales development with goals of the organization, and to integrate new practices into the fabric of the business.
Our extensive sales training content spans all key planning, execution, and management disciplines through multiple modalities of delivery. Due to our world-class curriculum, SPI is regularly recognized as one of the top training companies in the world by Selling Power, Training Industry, and others.
We have educated more than 1.5 million sales professionals in more than 50 countries across 14 languages and can truly meet the needs of global enterprises. Our exclusive, 100+ module mobile micro-learning library is available in seven major languages to further support our global customer base.
Our Performance Development Platform provides a ground-breaking closed-loop system for aligning professional development with specific sales goals, and provides an individualized learn- practice-apply experience for developing mastery that drives sales outcomes.
Multi-year, independent research demonstrates that our customers attain significant, year-over-year improvement in key sales metrics, including quota attainment, deal size, and time-to-productivity.
All aspects of our approach are adapted to align with your business and best practices to create a unique selling edge. We align development priorities to your sales strategy and goals, adapt learning to critical competencies, and focus enablement on high value capabilities.
Discover how you can begin your journey toward sales excellence and outperform your competition with SPI's world-class Solution Selling® programs. See why more than 1.5 million participants use Solution Selling® to demonstrate value, build business relationships, and provide solutions to their customers around the world.
For 29 years, SPI has effectively driven revenue and sales growth, reduced sales and marketing costs, and increased win rates for clients around the world. We operate in over 50 countries across 17 languages and have served more than 600 global clients and over 1.5 million participants. Contact us today to find out how we can help you today!


WritePass is committed to ensuring that your privacy is protected. Should we ask you to provide certain information by which you can be identified when using this website, then you can be assured that it will only be used in accordance with this privacy statement.
WritePass may change this policy from time to time by updating this page. You should check this page from time to time to ensure that you are happy with any changes. This policy is effective from 23/06/2011.
We may periodically send e-mails regarding blog updates, essay advice, special offers or other information which we think you may find interesting.
WritePass is committed to ensuring that your information is secure. In order to prevent unauthorised access or disclosure, we have put in place suitable physical, electronic and managerial procedures to safeguard and secure the information we collect online. We will not sell, distribute or lease your personal information to third parties.


It's with regret that we will have to inform our readers A War Between Spies is being placed on hiatus. Management had decided to move the team to other projects in the pipeline. Chapter 124 will be the end of the current arc and hopefully we can reactivate this novel again in the future. Again,we thanks all our readers for the support to date.


text:
F04D 17/12(2006.01)
F04D 29/057(2006.01)
Turbomachine
TURBOMASCHINE
(73) Proprietor: Panasonic Intellectual Property Management Co., Ltd.
Osaka 540-6207 (JP)
(72) Inventor:
SHOYAMA, Tadayoshi
Osaka, 540-6207 (JP)
(74) Representative: Eisenführ Speiser
Patentanwälte Rechtsanwälte PartGmbB Postfach 10 60 78
28060 Bremen (DE)
US-A1- 2006 083 642
1. Technical Field
[0001] The present disclosure relates to a turbomachine.
[0002] Conventionally known turbomachines include a thrust bearing, which supports an axial load (thrust load) resulting from differences in pressure between the surfaces of an impeller thereof, and a radial bearing, which supports a radial load. Some turbomachines include an angular bearing, which supports the thrust load and the radial load. As a bearing for a rotation shaft, a bearing having a tapered shape is known.
[0003] A self-aligning rotor-hydrostatic bearing system and method of bearing operation are provided in US 5,449,235. A rotor includes a surface defining a portion of a sphere. A bearing having a concave spherical surface adjacent the rotor spherical surface is movable with respect to the rotor. Movement, in one embodiment, is controlled by a piston which also provides pressurized lubrication fluid to a recess formed in the bearing spherical surface. Centrifugal deformation of the rotor is accommodated by axial movement of the bearing and/or contouring of a portion of the rotor. A pivoting bearing pad can be provided to accommodate centrifugal, thermal or other deformation. The rotor surface and the pivoting pad surface can be spherical or conical. A slotted bearing ring permits pivoting while maintaining a continuous seal surface.
[0004] As illustrated in Fig. 12, Japanese Unexamined Patent Application Publication No. 62-13816 discloses a turbocharger 300 including a turbine 302, a rotation shaft 303, a compressor wheel 304, a collar 306, a bearing 307a, and another bearing 307b. The rotation shaft 303 includes a tapered portion 305 gradually increasing in diameter from a middle section of the rotation shaft 303 toward the turbine 302. The collar 306 has a tapered shape gradually increasing in diameter from the middle section of the rotation shaft 303 toward the compressor wheel 304. The collar 306 is fixed to the rotation shaft 303. The bearing 307a has a tapered shape corresponding to the shape of the tapered portion 305 and having a slightly larger diameter than the tapered portion 305. The bearing 307b has a tapered shape corresponding to the shape of the collar 306 and having a slightly larger diameter than the collar 306.
[0005] The bearing 307a and the bearing 307b are aerostatic bearings. Pressurized air is supplied around the tapered portion 305 and the collar 306. This lifts the tapered portion 305 and the collar 306 above the bearing 307a and the bearing 307b, respectively, and thus the rotation shaft 303 rotates without generating friction with the bearings 307a, 307b. The gas pressure acts on the tapered surface of the tapered portion 305 and the tapered surface of the collar 306 in a perpendicular direction. The gas pressure acts not only in the radial direction but also in the thrust direction. Thus, the turbocharger 300 does not require a thrust bearing.
[0006] As illustrated in Fig. 13, Japanese Unexamined Patent Application Publication No. 58-196319 discloses an air bearing apparatus 500 including a rotation shaft 501, a bearing 503, another bearing 504, an air bearing 506, another air bearing 507, a flow passage 508, and another flow passage 509. The air bearing 506 is disposed between the rotation shaft 501 and the bearing 503. The air bearing 507 is disposed between the rotation shaft 501 and the bearing 504. The bearings 503 and 504 include the flow passages 508 and 509, respectively. Pressurized air is supplied to the air bearings 506 and 507 through the flow passages 508 and 509, respectively. The air bearings 506 and 507 each have a tapered shape and are disposed such that a larger-diameter portion of the air bearing 506 is placed opposite to a larger-diameter portion of the air bearing 507. Japanese Unexamined Patent Application Publication No. 58-196319 does not disclose the positional relationship between the air bearing apparatus 500 and an impeller to be attached to the rotation shaft 501.
[0007] One non-limiting and exemplary embodiment provides a turbomachine having good vibration characteristics, since the turbocharger 300 described in Japanese Unexamined Patent Application Publication No. 62-13816 leaves room for improvement in the vibration characteristics of the turbocharger 300 during rotation of the rotation shaft 303.
[0008] In one general aspect, the techniques disclosed here feature a turbomachine for a refrigeration cycle apparatus as defined in claim 1.
[0009] The above-described turbomachine has good vibration characteristics.
[0010] Additional benefits and advantages of the disclosed embodiments will become apparent from the specification and drawings. The benefits and/or advantages may be individually obtained by the various embodiments and features of the specification and drawings, which need not all be provided in order to obtain one or more of such benefits and/or advantages.
Fig. 1 is a cross-sectional view of a turbomachine according to one example of a first embodiment;
Fig. 2 is a cross-sectional view of a turbomachine according to another example of the first embodiment; The embodiments related to figg. 1 and 2 do not fall within the scope of protection of the claims.
Fig. 3 is a cross-sectional view of a turbomachine according to one example of a second embodiment;
Fig. 4 is a cross-sectional view of a turbomachine according to another example of the second embodiment;
Fig. 5 is a cross-sectional view of a first tapered portion and a first bearing according to a first modification;
Fig. 6 is a cross-sectional view of a second tapered portion and a second bearing according to a first modification;
Fig. 7 is a graph showing an advantage of the first modification;
Fig. 8 is a cross-sectional view of a first tapered portion and a first bearing according to a second modification;
Fig. 9 is cross-sectional view of a second tapered portion and a second bearing according to a second modification;
Fig. 10 is a cross-sectional view of a first tapered portion and a first bearing according to a third modification;
Fig. 11 is a cross-sectional view of a second tapered portion and a second bearing according to a third modification;
Fig. 12 is a cross-sectional view illustrating a conventional turbocharger; and
Fig. 13 is a cross-sectional view of a conventional air bearing apparatus.
Findings Forming Basis of the Present Disclosure
[0012] The inventors of the present disclosure studied turbomachines that use a working fluid having a negative (lower than the atmospheric pressure in terms of absolute pressure) saturated vapor pressure at a normal temperature (20°C ± 15°C defined in JIS Z8703 (Japanese Industrial Standard)) and discharges the working fluid having a negative pressure. As a result of the study, the following findings were obtained.
[0013] In a refrigeration cycle apparatus using a refrigerant as a working fluid having a negative saturated vapor pressure at a normal temperature, the turbomachine thereof is required to have a high pressure ratio compared to that of a refrigeration cycle apparatus that uses a refrigerant as a working fluid having a positive saturated vapor pressure at a normal temperature. To satisfy the requirement, the rotation body of the turbomachine needs to have an extremely high rotational speed, which is likely to cause abnormal vibration in the turbomachine as a result of resonance. The inventors of the present disclosure conducted a comprehensive study and found that the abnormal vibration as a result of resonance is reduced by making the natural frequency of the rotation shaft higher than a rated rotational speed. This is achieved by concentrating the axial mass distribution of the rotation body at a position close to the center of gravity of the rotation body to increase the bending natural frequency of the rotation body. Based on the above findings, the inventors developed the techniques including the following aspects.
[0014] The present invention is defined in claim 1 and refers to a turbomachine comprising, in combination, the first and the second aspects of this disclosure, which are defined as follows. A turbomachine according to a first aspect of this disclosure is a turbomachine for a refrigeration cycle apparatus using a refrigerant as a working fluid having a negative saturated vapor pressure at a normal temperature. The turbomachine includes a rotation shaft, a first impeller fixed to the rotation shaft and including a low-pressure-side surface subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft, and including a high-pressure-side surface subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft, a first bearing disposed on the low-pressure-side surface of the first impeller and supporting the rotation shaft, and a second bearing disposed on the high-pressure-side surface of the first impeller from the first bearing and supporting the rotation shaft. The rotation shaft includes a first tapered portion at least within an area supported by the first bearing. The first tapered portion gradually increases in diameter toward the low-pressure-side surface of the first impeller. The first bearing includes a first support surface gradually increasing in diameter toward the low-pressure-side surface of the first impeller. The first support surface supports the first tapered portion. The first bearing, the first impeller, and the second bearing are disposed in this order in a longitudinal direction of the rotation shaft.
[0015] According to the first aspect, the first impeller having a relatively large mass is disposed between the first bearing and the second bearing. With this configuration, the mass distribution of the rotation body including the rotation shaft is unlikely to be concentrated at a position away from the center of the gravity. Thus, the natural frequency of the rotation body including the rotation shaft is relatively high, and high-speed rotation of the rotation shaft is unlikely to cause resonance and consequently abnormal vibration. As a result, the turbomachine according to the first aspect has good vibration characteristics.
[0016] According to the first aspect, the first bearing includes the first support surface supporting the first tapered portion, and the first bearing is disposed adjacent to the low-pressure-side surface of the first impeller. The first tapered portion gradually increases in diameter toward the first impeller. With this configuration, a middle section of the rotation shaft has a relatively large cross-sectional area. Thus, the bending natural frequency of the rotation body including the rotation shaft is relatively high, and high-speed rotation of the rotation shaft is unlikely to cause resonance and consequently abnormal vibration. In addition, according to the first aspect, since the first bearing is adjacent to the low-pressure-side surface of the first impeller, the thrust load applied in the direction from the first impeller to the first bearing is supported by the first bearing.
[0017] According to the first aspect, the refrigerant having a negative saturated vapor pressure at the normal temperature is used as the working fluid. As described above, if the refrigerant having a negative saturated vapor pressure at the normal temperature is used as the working fluid, the impeller of the turbomachine is required to have a high rotational speed, which is likely to cause abnormal vibration in the turbomachine as a result of resonance. However, in the turbomachine according to the first aspect, the abnormal vibration as a result of resonance is reduced even though the refrigerant having negative saturated vapor pressure at the normal temperature is used as the working fluid.
[0018] In addition, when the refrigerant having a negative saturated vapor pressure at the normal temperature is used as the working fluid, the thrust load to be generated in a turbomachine is very low, even if the turbomachine is a turbocompressor having a high pressure ratio (e.g., pressure ratio of 2 or more), for example. Therefore, according to the first aspect, the thrust load generated by the rotation is supported by the first bearing (e.g., tapered plain bearing) alone, which includes the first support surface for supporting the first tapered portion. The turbomachine according to the first aspect has a simple configuration compared to a turbomachine that includes a thrust bearing and a radial bearing as separate members.
[0019] The turbomachine according to the first aspect of this disclosure is superior to the turbocharger disclosed in Japanese Unexamined Patent Application Publication No. 62-13816 in terms of the following points. In the turbocharger 500 disclosed in Japanese Unexamined Patent Application Publication No. 62-13816, the rotation shaft 303 has the smallest diameter at the middle section thereof and the compressor wheel 304 is fixed to the front end of the rotation shaft 303. In this configuration, the bending natural frequency of the rotation body including the rotation shaft 303 and the compressor wheel 304 is low, and abnormal vibration may be generated at the rotation shaft 303 by the resonance that develops during high-speed rotation of the rotation shaft 303. However, as described above, in the turbomachine disclosed in this disclosure, the first tapered portion increases in diameter toward the first impeller. With this configuration, the middle section of the rotation shaft has a relatively large cross-sectional area. Thus, the bending natural frequency of the rotation body including the rotation shaft is relatively high, and high-speed rotation of the rotation shaft is unlikely to cause resonance and consequently abnormal vibration. In addition, in the turbocharger 500 disclosed in Japanese Unexamined Patent Application Publication No. 62-13816, the rotation shaft 303 or the casing should be formed of at least two pieces because of its structure. This may cause problems such as insufficient rigidity and vibration generation. The turbomachine according to the first aspect is free from such problems.
[0020] According to a second aspect of this disclosure, the turbomachine of the first aspect may further include a second impeller fixed to the rotation shaft, for example. The first bearing, the first impeller, the second impeller, and the second bearing may be disposed in this order in the longitudinal direction of the rotation shaft. According to the second aspect, when the turbomachine is a turbocompressor, for example, compression efficiency is improved by the two-stage compression, and a high compression ratio is achieved.
[0021] According to a third aspect of this disclosure, in the turbomachine of the second aspect, a surface of the second impeller subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft (a low-pressure-side surface of the second impeller) may be closer to the second bearing than a surface of the second impeller subjected to a relatively high pressure by the working fluid during rotation of the rotation shaft (a high-pressure-side surface of the second impeller). According to the third aspect, the direction of the thrust load generated by the first impeller and the direction of the thrust load generated by the second impeller are opposite, and thus the thrust loads cancel each other out. With this configuration, when the turbomachine is a turbocompressor, for example, the range of the pressure ratio where the turbomachine is operational is broadened.
[0022] According to a fourth aspect of this disclosure, in the turbomachine of the second aspect, a surface of the second impeller subjected to a relatively high pressure by the working fluid during rotation of the rotation shaft (a high-pressure-side surface of the second impeller) may be closer to the second bearing than a surface of the second impeller subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft (a low-pressure-side surface of the second impeller). According to the fourth aspect, the flow passage for the working fluid between the first impeller and the second impeller is shortened. As a result, the size of the turbomachine can be reduced.
[0023] According to a fifth aspect of this disclosure, in the turbomachine of any one of the first aspect to the fourth aspect, an inclination angle of the first support surface with respect to a center axial line of a tapered hole defined by the first support surface may be larger than an inclination angle of the first tapered portion with respect to a center axial line of the rotation shaft. According to the fifth aspect, in the axial direction of the rotation shaft, variation in the pressure applied to the lubricant between the first support surface and the first tapered portion is reduced. As a result, spatial variation in the bearing load is reduced and the bearing load capacity is increased.
[0024] According to a sixth aspect of this disclosure, in the turbomachine of any one of the first aspect to the fifth aspect, the first bearing may include a first supply hole through which a lubricant is supplied to the first support surface. According to the sixth aspect, the lubricant is supplied to the first support surface, and thus galling due to an insufficient amount e of the lubricant is reduced.
[0025] According to the seventh aspect of this disclosure, in the turbomachine of the sixth aspect, the first supply hole may be disposed closer to a smallest-diameter end of the first tapered portion than to a largest-diameter end of the first tapered portion. According to the seventh aspect, the hydrostatic effect due to the lubricant is preferentially applied to a smaller-diameter portion of the first tapered portion where a pressure of the lubricant is relatively low. As a result, the entire bearing load capacity of the first bearing is increased.
[0026] According to an eighth aspect of this disclosure, in the turbomachine of one of the sixth aspect and the seventh aspect, the first bearing may include a first porous member constituting at least a part of the first support surface. According to the eighth aspect, spatial variation in temperature or pressure is reduced in the first bearing.
[0027] According to a ninth aspect of this disclosure, in the turbomachine of any one of the first aspect to the eighth aspect, the rotation shaft may extend in the gravity direction, and the low-pressure-side surface of the first impeller may be disposed in the gravity direction above a surface of the first impeller that is subjected to a relatively large pressure by the working fluid during rotation of the rotation shaft. According to the ninth aspect, the thrust load generated by the rotation of the rotating shaft is cancelled out by gravity acting on the rotation body, which includes the rotation shaft and the first impeller. With this configuration, when the turbomachine is a turbocompressor, for example, the range of the pressure ratio where the turbomachine is operational is broadened.
[0028] According to a tenth aspect of this disclosure, in the turbomachine of any one of the first aspect to the ninth aspect, the rotation shaft may include a second tapered portion at a position corresponding to the second bearing. The second tapered portion gradually increases in diameter toward the first impeller. The second bearing may include a second support surface gradually increasing in diameter toward the first impeller. The second bearing supports the second tapered portion. According to the tenth aspect, the thrust load acting in the direction opposite to the direction from the first impeller toward the first bearing is supported by the second bearing.
[0029] According to an eleventh aspect of this disclosure, in the turbomachine of the tenth aspect, an inclination angle of the second support surface with respect to a center axial line of a tapered hole defined by the second support surface may be larger than an inclination angle of the second tapered portion with respect to a center axial line of the rotation shaft. According to the eleventh aspect, in the axial direction of the rotation shaft, variation in pressure applied to the lubricant contained between the second support surface and the second tapered surface is reduced. As a result, spatial variation in the bearing load is reduced and the bearing load capacity is increased.
[0030] According to a twelfth aspect of this disclosure, in the turbomachine of one of the tenth aspect and the eleventh aspect, the second bearing may include a second supply hole through which a lubricant is supplied to the second support surface. According to the twelfth aspect, the lubricant is supplied to the second support surface, and thus galling due to an insufficient amount of the lubricant is reduced.
[0031] According to a thirteenth aspect of this disclosure, in the turbomachine of the twelfth aspect, the second supply hole may be disposed closer to a smallest-diameter end of the second tapered portion than to a largest-diameter end of the second tapered portion. According to the thirteenth aspect, the hydrostatic effect due to the lubricant is preferentially applied to a smaller-diameter portion of the second tapered portion where a pressure of the lubricant is relatively low. As a result, the entire bearing load capacity of the second bearing is increased.
[0032] According to a fourteenth aspect of this disclosure, in the turbomachine of one of the twelfth aspect and the thirteenth aspect, the second bearing may include a second porous member constituting at least a part of the second support surface. According to the fourteenth aspect, spatial variation in temperature or pressure of the lubricant is reduced in the second bearing.
[0033] A turbomachine according to a fifteenth aspect of this disclosure is a turbomachine for a refrigeration cycle apparatus using a refrigerant as a working fluid having a negative saturated vapor pressure at a normal temperature. The turbomachine includes a rotation shaft, a first impeller including a low-pressure-side surface subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft and a high-pressure-side surface opposite the low-pressure-side surface, the first impeller generating a force by creating a difference in pressure between the low-pressure-side surface and the high-pressure-side surface from the high-pressure-side surface toward the low-pressure-side surface, and a first bearing adjacent to the low-pressure-side surface of the first impeller and supporting the rotation shaft. A rotation body including the first impeller and the rotation shaft has a center of gravity at a position adjacent to the high-pressure-side surface of the first impeller. The rotation shaft includes a first tapered portion adjacent to the low-pressure-side surface of the first impeller. The first tapered portion gradually increases in diameter toward the low-pressure-side surface of the first impeller. The first bearing includes a first support surface gradually increasing in diameter toward the low-pressure-side surface of the first impeller and supporting the first tapered portion.
[0034] Hereinafter, embodiments of this disclosure will be described with reference to the drawings. The following description is merely an example of this disclosure, and this disclosure is not limited to the description.
First Embodiment
[0035] As illustrated in Fig. 1, a turbomachine 100a includes a rotation shaft 4, a first impeller 3a, a first bearing 1, and a second bearing 2. The turbomachine 100a is a turbocompressor, for example. The first impeller 3a is fixed to the rotation shaft 4. The first impeller 3a includes a low-pressure-side surface 31 and a high-pressure-side surface 32. The low-pressure-side surface 31 is one of a surface of the first impeller 3a in the axial direction which is subjected to a relatively low pressure by a working fluid during rotation of the rotation shaft 4. The high-pressure-side surface 32 is one of a surface of the first impeller 3a in the axial direction which is subjected to a relatively high pressure by a working fluid during rotation of the rotation shaft 4. The first bearing 1 is adjacent to the low-pressure-side surface 31 of the first impeller 3a. The first bearing 1 is formed to support the rotation shaft 4. The first bearing 1 supports a front end of the rotation shaft 4 in an area between an inlet of the working fluid and the first impeller 3a. The second bearing 2 is disposed such that the first impeller 3a is disposed between the second bearing 2 and the first bearing 1. The second bearing 2 is formed to support the rotation shaft 4. The second bearing 2 is disposed on an opposite side of the first impeller 3a from the low-pressure-side surface 31. The rotation shaft 4 includes a first tapered portion 41 gradually increasing in diameter toward the first impeller 3a. The first tapered portion 41 is adjacent to the low-pressure-side surface 31 of the first impeller 3a. The first bearing 1 includes a first support surface 11 supporting the first tapered portion 41.
[0036] The turbomachine 100a further includes a casing 5 and a motor 6. The first impeller 3a and the motor 6 are connected through the rotation shaft 4. The second bearing 2 is disposed farther from the first impeller 3a than the motor 6. The casing 5 defines an ejection passage 71 at a position close to an outer periphery of the first impeller 3a. Driving of the motor 6 rotates the first impeller 3a with the rotation shaft 4 at a high speed. The rotation allows the working fluid to flow from the front side of the first impeller 3a (left side of the first impeller 3a in Fig. 1) to the first impeller 3a. The working fluid is accelerated and pressurized by the rotating first impeller 3a and then ejected from the turbomachine 100a through the ejection passage 71. At this time, the left surface of the first impeller 3a in Fig. 1 is subjected to an inlet pressure of the working fluid and the right surface of the first impeller 3a is subjected to the pressure substantially equal to a discharge pressure. In other words, the low-pressure-side surface 31 is subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft 4. A pressure difference exists between two surfaces of the first impeller 3a in the axial direction, and the pressure difference generates a thrust load acting on a rotation body including the rotation shaft 4 and the first impeller 3a in the leftward direction in Fig. 1. The first bearing 1 is a plain bearing, for example, and a lubricant is applied between the first support surface 11 and the first tapered portion 41. The first support surface 11 defines a tapered hole which has a diameter slightly larger than that of the first tapered portion 41. In other words, the tapered hole gradually increasing in diameter toward the first impeller 3a is defined by the first support surface 11. The tapered hole supports the generated thrust load.
[0037] In the turbomachine 100a, the first impeller 3a having a relatively large mass is disposed between the first bearing 1 and the second bearing 2. With this configuration, a mass distribution of the rotation body, which includes the rotation shaft 4 and the first impeller 3a, is unlikely to be concentrated at a position away from the center of the gravity, and thus the bending natural frequency of the rotation body is unlikely to be reduced. This enables the bending natural frequency of the rotation body, which includes the rotation shaft 4 and the first impeller 3a, to be sufficiently higher than the rotational speed of the rotation body. With this configuration, the rotational speed of the rotation body is not close to the bending natural frequency of the rotation body, and thus high-speed rotation of the rotation shaft 4 is unlikely to cause resonance and consequently abnormal vibration. As a result, the turbomachine 100a has good vibration characteristics.
[0038] The bending natural frequency of the rotation body increases with an increase in the cross-sectional area of the rotation body. Particularly, the bending natural frequency of the rotation body is largely affected by the cross-sectional area of the middle section of the rotation shaft in a first bending vibration mode. The first bearing 1 includes the first support surface 11 supporting the first tapered portion 41, and the first bearing 1 is adjacent to the low-pressure-side surface 31 of the first impeller 3a. The first tapered portion 41 gradually increases in diameter toward the first impeller 3a. The rotation shaft 4 has a relatively large cross-sectional area at the middle section thereof. With this configuration, high-speed rotation of the rotation shaft 4 is unlikely to cause resonance and consequently abnormal vibration. As a result, the turbomachine 100a has good vibration characteristics.
[0039] The rotation shaft 4 and the second bearing 2 may be configured as illustrated in Fig. 2. A turbomachine 100b has the same configuration as the turbomachine 100a except that the rotation shaft 4 and the second bearing 2 have the configuration as illustrated in Fig. 2. In the turbomachine 100b, the rotation shaft 4 includes a second tapered portion 42. The second tapered portion 42 gradually increases in diameter toward the first impeller 3a. The second bearing 2 includes a second support surface 21 supporting the second tapered surface 21. The second bearing 2 is a plain bearing, for example. The second support surface 21 defines a tapered hole having a diameter slightly larger than that of the second tapered portion 42. A lubricant is applied between the second support surface 21 and the second tapered portion 42.
[0040] During high-speed rotation of the rotation body, which includes the rotation shaft 4 and the first impeller 3a, a vibration load may be generated by an imbalance of mass properties of the rotation body or by an asymmetric hydrodynamic force of the working fluid. A large vibration load in the axial direction may allow the thrust load of the rotation body, which includes the rotation shaft 4 and the first impeller 3a, to act in the direction opposite to the direction from the first impeller 3a toward the first bearing 1. Such a thrust load is supported by the second bearing 2.
[0041] In the turbomachine 100b, the second bearing 2 is disposed such that the center of the rotation shaft 4 in the axial direction is disposed between the first bearing 1 and the second bearing 2. With this configuration, the cross-sectional area of the middle section of the rotation shaft 4 is not reduced. The rotation shaft 4 may be connected to a different rotation shaft by a universal joint, for example. However, in such a case, the bending vibration frequency of the rotation body, which includes the rotation shaft 4, is hardly affected by the different rotation shaft. Therefore, the different rotating shaft connected to the rotation shaft 4 is ignored when the center of the rotation shaft 4 in the axial direction is determined.
Second Embodiment
[0042] Next, a turbomachine 100c and a turbomachine 100d according to a second embodiment will be described. The turbomachine 100c and the turbomachine 100d according to the second embodiment have the same configuration as the turbomachine 100a unless otherwise specified. Components of the turbomachine 100c and components of the turbomachine 100d same as or similar to those of the turbomachine 100a are assigned the same reference numerals as the turbomachine 100a and will not be described in detail. The description about the first embodiment may also be applied to this embodiment unless a contradiction is recognized.
[0043] The turbomachine 100c further includes a second impeller 3b. The second impeller 3b is fixed to the rotation shaft 4. The first impeller 3a and the second impeller 3b are disposed between the first bearing 1 and the second bearing 2. Since the second bearing 2 of the turbomachine 100c has the same configuration as the second bearing 2 of the turbomachine 100b, the rotation shaft 4 includes the second tapered portion 42. The second impeller 3b includes a low-pressure-side surface 131 and a high-pressure-side surface 132. The low-pressure-side surface 131 is a surface of the second impeller 3b which is subjected to a relatively low pressure by the working fluid during rotation of the rotation shaft 4. The high-pressure-side surface 132 is disposed opposite the low-pressure-side surface 131. The casing 5 defines an ejection passage 73 at a position close to an outer periphery of the second impeller 3b. The turbomachine 100c further includes a connection passage 72 that allows communication between the ejection passage 71 and a space adjacent to the low-pressure-side surface 131 of the second impeller 3b. The turbomachine 100c is a turbocompressor, for example. The working fluid pressurized by the first impeller 3a is drawn to the second impeller 3b through the ejection passage 71 and the connection passage 72. The working fluid is accelerated and pressurized by the rotating second impeller 3b, and then ejected from the turbomachine 100c through the ejection passage 73. As described above, the working fluid is pressurized in two stages by the first impeller 3a and the second impeller 3b. Thus, compression efficiency is improved, and a high-pressure ratio is achieved.
[0044] The second impeller 3b is fixed to the rotation shaft 4 such that the surface (high-pressure-side surface 132) which is opposite to the low-pressure-side surface 131 faces the first impeller 3a. During rotation of the second impeller 3b, the right surface of the second impeller 3b in Fig. 3 is subjected to the inlet pressure of the working fluid, and the left surface of the first impeller 3a is subjected to the pressure substantially equal to the discharge pressure of the working fluid. Thus, the thrust load acting in the rightward direction in Fig. 3 is generated by the rotation of the second impeller 3b. The direction of the thrust load generated by the rotation of the first impeller 3a and the direction of the thrust load generated by the rotation of the second impeller 3b are opposite, and thus the thrust loads cancel each other out. With this configuration, the range of the pressure ratio where the turbomachine 100c is operational is broad.
[0045] As a turbomachine 100d illustrated in Fig. 4, the second impeller 3b may be fixed to the rotation shaft 4 such that the low-pressure-side surface 131 faces the first impeller 3a. In such a case, a distance of the flow passage (connection passage 72) for the working fluid between the first impeller 3a and the second impeller 3b is shortened. As a result, the turbomachine 100d has a smaller size than the turbomachine 100c.
[0046] The turbomachine 100a and the turbomachine 100b according to the first embodiment and the turbomachine 100c and the turbomachine 100d according to the second embodiment may be modified from various viewpoints. Hereinafter, modifications of the turbomachines 100a to 100d will be described. Components of the following modifications same as or similar to those of the turbomachines 100a to 100d are assigned the same reference numerals as the turbomachines 100a to 100d and will not be described in detail.
First Modification
[0047] The support surface 11 of the first bearing 1 and the support surface 21 of the second bearing 2 may be configured as illustrated in Fig. 5 and Fig. 6, respectively. The first support surface 11 is configured such that an inclination angle θ2 of the first support surface 11 with respect to a center axial line Q1 of the tapered hole, which is defined by the first support surface 11, is larger than an inclination angle θ1 of the first tapered portion 41 with respect to a center axial line P of the rotation shaft 4. The second support surface 21 is configured such that an inclination angle θ4 of the second support surface 21 with respect to a center axial line Q2 of the tapered hole, which is defined by the second support surface 21, is larger than an inclination angle θ3 of the second tapered portion 42 with respect to the center axial line P of the rotation shaft 4. In the above cases, a ratio (θ2/θ1) between the inclination angle θ2 and the inclination angle θ1 is 1.0001 to 1.01, for example, and a ratio (θ4/θ3) between the inclination angle θ4 and the inclination angle θ3 is 1.0001 to 1.01, for example.
[0048] The lubrication condition between the bearing and the shaft, which are lubricated by the lubricant, may be evaluated by the following sommerfeld number:
where µ denotes a viscosity coefficient [Pa·s], N denotes a rotation speed of the shaft [s-1], P denotes a load surface pressure (applied load/meridional cross-sectional area) [Pa], R denotes a radius [m] of the shaft, and c denotes a radial clearance [m] between the bearing and the shaft.
[0049] Fig. 7 indicates a relationship between the pressure of the lubricant, which is contained between the first support surface 11 and the first tapered surface 41, and the axial distance from the end portion of the first support surface 11 having the smallest diameter, where the diameter of the tapered hole defined by the first support surface 11 is the smallest. The smaller the sommerfeld number, the smaller the pressure applied to the lubricant. When the inclination angle θ1 is equal to the inclination angle θ2, as indicated by the broken line in Fig. 7, the pressure of the lubricant is larger at a portion of the first tapered portion 41 having a larger diameter since the radius of a large-diameter portion of the first tapered portion 41 is larger than that of a small-diameter portion of the first tapered portion 41. This results in concentration of the bearing load on the large-diameter portion of the first tapered portion 41. On the other hand, when the relationship between the inclination angle θ1 and the inclination angle θ2 is set as described above, the axial variations in the sommerfeld number in the first tapered portion 41 is reduced. This results in reduction in the axial variations in the pressure distribution of the lubricant in the first tapered portion 41 as indicated by the solid line in Fig. 7. Thus, the bearing load capacity increases. The same is applicable to the relationship between the inclination angle θ3 and the inclination angle θ4.
[0050] In a cross section of the first bearing 1 taken along the center axial line Q1, an imaginary intersection of two lines extending from ridgelines along the first support surface 11 is defined as an intersection point 1. In addition, in a cross section of the first tapered portion 41 taken along the center axial line P, an imaginary intersection of two lines extending from ridgelines of the first tapered portion 41 is defined as an intersection point 2. The first support surface 11 is preferably formed such that the intersection 1 meets the intersection 2 to reduce the axial variations in the sommerfeld number in the first tapered portion 41. The same is applicable to the relationship between the second support surface 21 and the second tapered portion 42.
Second Modification
[0051] As illustrated in Fig. 8, the first bearing 1 may include a first supply hole 12 for supplying a lubricant to the first support surface 11. With this configuration, the lubricant is supplied to the first support surface 11, and thus galling due to an insufficient amount of the lubricant is reduced. In addition, the supply of the high-pressure lubricant through the first supply hole 12 provides the rotation body, which includes the rotation shaft 4, with bearing force by a hydrostatic effect. In addition to the bearing force by a hydrodynamic effect generated by the rotation of the rotation shaft 4, the bearing force by the hydrostatic effect is obtained. This enables the rotation shaft 4 to float even when the rotation of the rotation shaft 4 is suspended. As a result, wear of the bearing surface of the first bearing 1 and the rotation shaft 4 that may be caused during the suspension of the rotation of the rotation shaft 4 is remarkably reduced. Since the bearing force by the hydrostatic effect acts perpendicular onto the first support surface 11, not only a radial component of the bearing force, but also an axial component of the bearing force is obtained. Therefore, an axial bearing load capacity is increased.
[0052] As illustrated in Fig. 8, the first supply hole 12 is preferably disposed closer to the end of the first tapered portion 41 having the smallest diameter than to the other end of the first tapered portion 41 having the largest diameter. With this configuration, the hydrostatic effect due to the lubricant is preferentially-applied to a smaller-diameter portion of the first tapered portion 41 where a pressure of the lubricant is relatively low. Therefore, the entire bearing load capacity of the first bearing 1 is increased.
[0053] As illustrated in Fig. 9, the second bearing 2 may include a second supply hole 22 for supplying a lubricant to the second support surface 21. The second supply hole 22 is preferably disposed closer to the end of the second tapered portion 42 having the smallest diameter than to the other end portion of the second tapered portion 42 having the largest diameter. With this configuration, the second bearing 2 also has the above-described advantage.
Third Modification
[0054] As illustrated in Fig. 10, in addition to the first supply hole 12, the first bearing 1 may include a first porous member 13 constituting at least a part of the first support surface 11. Furthermore, as illustrated in Fig. 11, in addition to the second supply hole 22, the second bearing 2 may include a second porous member 23 constituting at least a part of the second support surface 21. The first porous member 13 and the second porous member 23 are made of a porous material such as a sintered metal, a grown cast iron, and a synthetic resin. If the first bearing 1 includes one or a few first supply holes 12, a temperature or a pressure of the lubricant at a position close to the first supply hole 12 may differ from those of the lubricant at a position away from the first supply hole 12. This may result in unstable rotation of the rotation shaft 4. The same is applicable to the second bearing 2 including one or a few second supply holes 22. In the first bearing 1, spatial variation in temperature or pressure of the lubricant is reduced by the first porous member 13 constituting at least a part of the first support surface 11. Furthermore, in the second bearing 2, spatial variations in temperature or pressure of the lubricant are reduced by the second porous member 23 constituting at least a part of the second support surface 21.
[0055] The rotation shaft 4 may extend in a horizontal direction or a vertical direction. In a case where the rotation shaft 4 extends in the vertical direction, the first impeller 3a is preferably fixed to the rotation shaft 4 such that the thrust load caused by the rotation of the rotation shaft 4 acts in the direction opposite to the gravity direction. In this configuration, the thrust load generated by the rotation of the rotation shaft 4 is cancelled out by the gravity acting on the rotation body, which includes the rotation shaft 4 and the first impeller 3a. Thus, the range of the pressure ratio where the turbomachine is operational is broadened.
[0056] The present disclosure is advantageously used in compressors for refrigeration cycle apparatuses applicable to centrifugal chiller air conditioners such as industrial air conditioners.
1. A turbomachine (100a, 100b, 100c, 100d) for a refrigeration cycle apparatus using a refrigerant as a working fluid having saturated vapor pressure being at a temperature of 20°C ± 15°C lower than the atmospheric pressure in terms of absolute pressure, the turbomachine (100a) comprising:
a rotation shaft (4);
a first impeller (3a) fixed to the rotation shaft (4), the first impeller (3a) including a low-pressure-side surface and a high-pressure-side surface;
a first bearing (1) disposed on a low-pressure-side of the first impeller (3a), the first bearing (1) supporting the rotation shaft (4); and
a second bearing (2) disposed on a high-pressure-side of the first impeller (3a), the second bearing (2) supporting the rotation shaft (4), wherein
the rotation shaft (4) includes a first tapered portion (41) at least within an area supported by the first bearing (1), characterised in that the first tapered portion (41) gradually increasing in diameter toward the low-pressure-side surface of the first impeller (3a),
the first bearing (1) includes a first support surface (11) gradually increasing in diameter toward the low-pressure-side surface of the first impeller (3a), the first support surface (11) supporting the first tapered portion (41), and
a second impeller (3b) fixed to the rotation shaft (4), wherein
the first bearing (1), the first impeller (3a), the second impeller (3b), and the second bearing (2) are disposed in this order in a longitudinal direction of the rotation shaft (4).
2. The turbomachine (100a, 100b, 100c, 100d)according to claim 1, wherein
the second impeller (3b) includes a low-pressure-side surface and a high-pressure-side surface, and
the low-pressure-side surface of the second impeller (3b) is closer to the second bearing (2) than the high-pressure-side surface of the second impeller (3b).
the high-pressure-side surface of the second impeller (3b) is closer to the second bearing (2) than the low-pressure-side surface of the second impeller (3b).
an inclination angle of the first support surface (11) with respect to a center axial line of a tapered hole defined by the first support surface (11) is larger than an inclination angle of the first tapered portion (41) with respect to a center axial line of the rotation shaft (4).
5. The turbomachine (100a, 100b, 100c, 100d) according to claim 1, wherein
the first bearing (1) includes a first supply hole through which a lubricant is supplied to the first support surface (11).
the first supply hole is disposed closer to a smallest-diameter end of the first tapered portion (41) than to a largest-diameter end of the first tapered portion (41).
the first bearing (1) includes a first porous member constituting at least a part of the first support surface (11).
8. The turbomachine (100a, 100b, 100c, 100d) according to claim 1, wherein when in use the rotation shaft (4) extends in the gravity direction, and
the low-pressure-side surface of the first impeller (3a) is disposed in the gravity direction above the high-pressure-side surface of the first impeller (3a).
9. The turbomachine (100a, 100b, 100c, 100d)) according to claim 1, wherein
the rotation shaft (4) includes a second tapered portion (42) at a position corresponding to the second bearing (2), the second tapered portion (42) gradually increasing in diameter toward the first impeller (3a), and
the second bearing (2) includes a second support surface (11) gradually increasing in diameter toward the first impeller (3a), the second bearing (2) supporting the second tapered portion (42).
10. The turbomachine (100a, 100b, 100c, 100d) according to claim 9, wherein
an inclination angle of the second support surface (11) with respect to a center axial line of a tapered hole defined by the second support surface (11) is larger than an inclination angle of the second tapered portion (42) with respect to a center axial line of the rotation shaft (4).
the second bearing (2) includes a second supply hole through which a lubricant is supplied to the second support surface (11).
12. The turbomachine (100a, 100b, 100c, 100d) according to claim 11, wherein
the second supply hole is disposed closer to a smallest-diameter end of the second tapered portion (42) than to a largest-diameter end of the second tapered portion (42).
the second bearing (2) includes a second porous member constituting at least a part of the second support surface (11).
1. Turbomaschine (100a, 100b, 100c, 100d) für eine Kältekreislaufvorrichtung, bei der ein Kältemittel als Arbeitsfluid verwendet wird, das einen Sättigungsdampfdruck aufweist, der bei einer Temperatur von 20°C ± 15°C niedriger als der Atmosphärendruck, angegeben als absoluter Druck, ist, wobei die Turbomaschine (100a) umfasst:
eine Drehwelle (4);
ein erstes Laufrad (3a), das an der Drehwelle (4) befestigt ist, wobei das erste Laufrad (3a) eine niederdruckseitige Oberfläche und eine hochdruckseitige Oberfläche umfasst;
ein erstes Lager (1), das auf einer Niederdruckseite des ersten Laufrads (3a) angeordnet ist, wobei das erste Lager (1) die Drehwelle (4) trägt; und
ein zweites Lager (2), das auf einer Hochdruckseite des ersten Laufrads (3a) angeordnet ist, wobei das zweite Lager (2) die Drehwelle (4) trägt, wobei
die Drehwelle (4) zumindest in einem Bereich, der von dem ersten Lager (1) getragen wird, einen ersten konischen Abschnitt (41) umfasst, dadurch gekennzeichnet, dass
der erste konische Abschnitt (41) in Richtung der niederdruckseitigen Oberfläche des ersten Laufrads (3a) graduell im Durchmesser zunimmt,
das erste Lager (1) eine erste Auflagefläche (11) umfasst, die in Richtung der niederdruckseitigen Oberfläche des ersten Laufrads (3a) graduell im Durchmesser zunimmt, wobei die erste Auflagefläche (11) den ersten konischen Abschnitt (41) trägt, und
ein zweites Laufrad (3b), das an der Drehwelle (4) befestigt ist, wobei
das erste Lager (1), das erste Laufrad (3a), das zweite Laufrad (3b) und das zweite Lager (2) in dieser Reihenfolge in einer Längsrichtung der Drehwelle (4) angeordnet sind.
2. Turbomaschine (100a, 100b, 100c, 100d) nach Anspruch 1, wobei
das zweite Laufrad (3b) eine niederdruckseitige Oberfläche und eine hochdruckseitige Oberfläche umfasst, und
die niederdruckseitige Oberfläche des zweiten Laufrads (3b) näher beim zweiten Lager (2) ist als die hochdruckseitige Oberfläche des zweiten Laufrads (3b).
die hochdruckseitige Oberfläche des zweiten Laufrads (3b) näher beim zweiten Lager (2) ist als die niederdruckseitige Oberfläche des zweiten Laufrads (3b).
ein Neigungswinkel der ersten Auflagefläche (11) zu einer Mittelachslinie eines konischen Lochs, das von der ersten Auflagefläche (11) definiert wird, größer ist als ein Neigungswinkel des ersten konischen Abschnitts (41) zu einer Mittelachslinie der Drehwelle (4).
das erste Lager (1) eine erste Zuführbohrung umfasst, durch die der ersten Auflagefläche (11) ein Schmiermittel zugeführt wird.
die erste Zuführbohrung näher bei einem Ende mit dem kleinsten Durchmesser des ersten konischen Abschnitts (41) als bei einem Ende mit dem größten Durchmesser des ersten konischen Abschnitts (41) angeordnet ist.
das erste Lager (1) ein erstes poröses Element umfasst, das zumindest einen Teil der ersten Auflagefläche (11) bildet.
8. Turbomaschine (100a, 100b, 100c, 100d) nach Anspruch 1, wobei sich die Drehwelle (4) beim Gebrauch in der Schwerkraftrichtung erstreckt, und
die niederdruckseitige Oberfläche des ersten Laufrads (3a) in der Schwerkraftrichtung über der hochdruckseitigen Oberfläche des ersten Laufrads (3a) angeordnet ist.
die Drehwelle (4) einen zweiten konischen Abschnitt (42) in einer Position umfasst, die dem zweiten Lager (2) entspricht, wobei der zweite konische Abschnitt (42) in Richtung des ersten Laufrads (3a) graduell im Durchmesser zunimmt, und
das zweite Lager (2) eine zweite Auflagefläche (11) umfasst, die in Richtung des ersten Laufrads (3a) graduell im Durchmesser zunimmt, wobei das zweite Lager (2) den zweiten konischen Abschnitt (42) trägt.
10. Turbomaschine (100a, 100b, 100c, 100d) nach Anspruch 9, wobei
ein Neigungswinkel der zweiten Auflagefläche (11) zu einer Mittelachslinie eines konischen Lochs, das von der zweiten Auflagefläche (11) definiert wird, größer ist als ein Neigungswinkel des zweiten konischen Abschnitts (42) zu einer Mittelachslinie der Drehwelle (4).
das zweite Lager (2) eine zweite Zuführbohrung umfasst, durch die der zweiten Auflagefläche (11) ein Schmiermittel zugeführt wird.
12. Turbomaschine (100a, 100b, 100c, 100d) nach Anspruch 11, wobei
die zweite Zuführbohrung näher bei einem Ende mit dem kleinsten Durchmesser des zweiten konischen Abschnitts (42) als bei einem Ende mit dem größten Durchmesser des zweiten konischen Abschnitts (42) angeordnet ist.
das zweite Lager (2) ein zweites poröses Element umfasst, das zumindest einen Teil der zweiten Auflagefläche (11) bildet.
1. Turbomachine (100a, 100b, 100c, 100d) pour un appareil à cycle de réfrigération utilisant un fluide frigorigène en tant que fluide de travail possédant une pression de vapeur saturée qui est, à une température de 20°C ± 15°C, inférieure à la pression atmosphérique en termes de pression absolue, la turbomachine (100a) comprenant :
un arbre rotatif (4) ;
une première roue à aubes (3a) fixée à l'arbre rotatif (4), la première roue à aubes (3a) comprenant une surface côté basse pression et une surface côté haute pression ;
un premier palier (1) disposé sur un côté basse pression de la première roue à aubes (3a), le premier palier (1) supportant l'arbre rotatif (4) ; et
un deuxième palier (2) disposé sur un côté haute pression de la première roue à aubes (3a), le deuxième palier (2) supportant l'arbre rotatif (4),
l'arbre rotatif (4) comprenant une première partie conique (41) au moins au sein d'une zone supportée par le premier palier (1),
caractérisée en ce que
la première partie conique (41) augmente progressivement en diamètre vers la surface côté basse pression de la première roue à aubes (3a),
le premier palier (1) comprend une première surface de support (11) augmentant progressivement en diamètre vers la surface côté basse pression de la première roue à aubes (3a), la première surface de support (11) supportant la première partie conique (41) et
une deuxième roue à aubes (3b) est fixée à l'arbre rotatif (4),
le premier palier (1), la première roue à aubes (3a), la deuxième roue à aubes (3b) et le deuxième palier (2) étant disposés dans cet ordre dans une direction longitudinale de l'arbre rotatif (4).
2. Turbomachine (100a, 100b, 100c, 100d) selon la revendication 1,
la deuxième roue à aubes (3b) comprenant une surface côté basse pression et une surface côté haute pression et
la surface côté basse pression de la deuxième roue à aubes (3b) étant plus proche du deuxième palier (2) que la surface côté haute pression de la deuxième roue à aubes (3b).
la surface côté haute pression de la deuxième roue à aubes (3b) étant plus proche du deuxième palier (2) que la surface côté basse pression de la deuxième roue à aubes (3b).
un angle d'inclinaison de la première surface de support (11) par rapport à une ligne axiale centrale d'un trou conique défini par la première surface de support (11) étant supérieur à un angle d'inclinaison de la première partie conique (41) par rapport à une ligne axiale centrale de l'arbre rotatif (4).
le premier palier (1) comprenant un premier trou d'alimentation à travers lequel un lubrifiant est fourni à la première surface de support (11).
le premier trou d'alimentation étant disposé plus près d'une extrémité de plus petit diamètre de la première partie conique (41) que d'une extrémité de plus grand diamètre de la première partie conique (41).
le premier palier (1) comprenant un premier élément poreux constituant au moins une partie de la première surface de support (11).
l'arbre rotatif (4) s'étendant, lors de l'utilisation, dans la direction de la gravité et
la surface côté basse pression de la première roue à aubes (3a) étant disposée, dans la direction de la gravité, au-dessus de la surface côté haute pression de la première roue à aubes (3a).
l'arbre rotatif (4) comprenant une deuxième partie conique (42) en une position correspondant au deuxième palier (2), la deuxième partie conique (42) augmentant progressivement en diamètre vers la première roue à aubes (3a) et
le deuxième palier (2) comprenant une deuxième surface de support (11) augmentant progressivement en diamètre vers la première roue à aubes (3a), le deuxième palier (2) supportant la deuxième partie conique (42).
10. Turbomachine (100a, 100b, 100c, 100d) selon la revendication 9,
un angle d'inclinaison de la deuxième surface de support (11) par rapport à une ligne axiale centrale d'un trou conique défini par la deuxième surface de support (11) étant supérieur à un angle d'inclinaison de la deuxième partie conique (42) par rapport à une ligne axiale centrale de l'arbre rotatif (4).
le deuxième palier (2) comprenant un deuxième trou d'alimentation à travers lequel un lubrifiant est fourni à la deuxième surface de support (11).
12. Turbomachine (100a, 100b, 100c, 100d) selon la revendication 11,
le deuxième trou d'alimentation étant disposé plus près d'une extrémité de plus petit diamètre de la deuxième partie conique (42) que d'une extrémité de plus grand diamètre de la deuxième partie conique (42).
le deuxième palier (2) comprenant un deuxième élément poreux constituant au moins une partie de la deuxième surface de support (11).
JP62013816A [0004] [0007] [0019] [0019] [0019]
JP58196319A [0006] [0006]

redpajama_set_name: RedPajamaCommonCrawl


text:
Lords: 5 February 2019
NHS: Accident and Emergency Departments
Lord Hunt of Kings Heath
To ask Her Majesty's Government what is their response to the assessment of the President of the Royal College of Emergency Medicine that removing the four-hour accident and emergency treatment target would have a "near-catastrophic impact" on patient safety in many emergency departments.
Baroness Manzoor
(Con)
My Lords, I note the concerns of the Royal College of Emergency Medicine and assure it, and the House, that patient safety remains paramount in any NHS care setting. As I mentioned in the excellent debate that the noble Lord, Lord Hunt, introduced last week, the NHS long-term plan will reform urgent and emergency care, and NHS England's clinical review of standards will report its interim findings in spring 2019. Until then, we are clear that existing core access standards will remain in place.
My Lords, I am grateful to the Minister. She will know that, before the four-hour target was introduced, we had dangerously overcrowded A&E departments, very long waiting times and unsafe care generally. It is clear from the evidence that the chief executive of the NHS recently gave to a parliamentary committee that he wants the clinical standards review to get rid of the four-hour target under the guise of giving greater priority to the most urgent treatments. The problem with that is that most urgent treatments get priority already. There is a real risk that, if you let the four-hour target go, many patients will have to wait longer and longer. The royal college is concerned about patient safety. Is the answer not to invest in more beds and adult social care for frail, older patients and then get a more effective flow of patients through hospitals? In that way, the target could be met.
My Lords, the noble Lord is absolutely right: performance targets are important. However, we must ensure that the NHS is focusing on clinically appropriate targets. The clinical review of standards is considering standards for both physical and mental health. Following its interim findings, any recommended changes will be carefully field-tested across the NHS before they are implemented. An impact assessment will be published and changes to the NHS constitution will be consulted on, as is legally required.
Lord Warner
My Lords, I remind the Minister that 12 years ago, when I was the ministerial enforcer of the four-hour A&E target, the royal college came to plead with me not to abandon it. Its arguments were not only the ones made by the noble Lord, Lord Hunt, but that this target had caused acute hospitals to reorganise their affairs much more efficiently. How will getting rid of the four-hour target impact on the Government's drive to improve the efficiency of the NHS?
My Lords, I have already said that performance targets are important. The Academy of Medical Royal Colleges released a statement on 30 January, which said:
"Reviewing, updating and improving the clinical standards to ensure that they remain relevant and appropriate is sensible and overdue. We support an evidence based review that is driven by clinical considerations as to what is appropriate, that informs and promotes changes in service delivery where needed and involves wide input from all relevant parties … any review may suggest change or reinforce current measures".
I could not have put it better myself.
Lord O'Shaughnessy
My Lords, the acid test for any waiting-time targets is the clinical outcomes they deliver. In 2017, NHS England recommended—and the department subsequently accepted—reforms to the ambulance waiting-time targets, but that took place only after a two-year clinical trial and an independent assessment by the University of Sheffield of the impact on patients of all kinds of severity. I suggest that, if there is to be movement in this area, it should proceed cautiously and only after following a similarly robust and objective process.
My Lords, of course I entirely agree with my noble friend. As I have said, there will be robust evaluation, monitoring and assessment before any targets are put in place.
Baroness Jolly
My Lords, there is no doubt that emergency departments are currently working at full tilt to care for their patients. I recently visited one that had totally reconfigured its workspace. By so doing, it had been able to operate much more efficiently, saving precious time. I believe that it had received grant funding to do this. How many emergency departments have done the same, with or without a grant?
My Lords, forgive me, I do not know the answer in relation to grants and will have to write to the noble Baroness, but she is right that NHS A&E admissions have been quite significant. Demand has increased. To put this into context, the NHS addressed just under 2,500 more attendances per day on average within the four-hour standard in 2017-18 compared with 2009-10, and 86.4% of patients admitted were transferred or discharged within four hours. Performance has improved since last year but we recognise that we have not hit the standard.
Baroness Symons of Vernham Dean
My Lords, is not the simple Answer to this Question that we need more nurses and doctors in our accident and emergency units? The real problem is that there are simply not enough there. I do not know when the Minister was last in an accident and emergency unit, but over the past 18 months or so I have been to three different hospitals six times and waited for hours with somebody who was extraordinarily ill and might well have suffered the ultimate consequence of his illness. It is simply not good enough to answer my noble friend's Question in the way the Minister has done. This is a real issue and people are in great difficulty because we simply do not have enough nurses and doctors.
My Lords, I am very sorry to hear of the noble Baroness's experience of A&E. Just to reassure her, I went to an A&E department not very long ago, so I know and understand the pressures on A&E departments. Indeed, I have worked in A&E departments, so I understand the pressures on staff too. I reassure her that we are doing everything we can to ensure that there are more nurses, doctors and consultants working in A&E. I do not have the figures at hand, but we have more NHS consultants working in A&E than we have ever had.


text:
Q: Load photo from gallery I have an NSURL of a photo from the camera roll and I'd like to load the image or the NSData from it.
I try this:
NSData *imageDataTemp = [NSData dataWithContentsOfURL:path];

but it return half of the size of the image.

A: Here is how to load an image having the ALAsset URL.
Using ALAssetLibrary (deprecated in iOS 9.0 )
ALAssetsLibraryAssetForURLResultBlock resultBlock = ^(ALAsset *asset)
{
    ALAssetRepresentation *representation = [asset defaultRepresentation];
    CGImageRef image = [representation fullResolutionImage];

    if (image)
    {
        yourImageView.image = [UIImage imageWithCGImage:image];
    }
};

ALAssetsLibraryAccessFailureBlock failureBlock  = ^(NSError *error)
{
    NSLog(@"Error %@", [error localizedDescription]);
};

ALAssetsLibrary *library = [[ALAssetsLibrary alloc] init];

[library assetForURL:assetURL
         resultBlock:resultBlock
        failureBlock:failureBlock];

Using PHPhotoLibrary
    NSURL *yourALAssetURL;
    PHFetchResult *result = [PHAsset fetchAssetsWithALAssetURLs:@[yourALAssetURL] options:nil];
    PHAsset *asset = result.firstObject;

    if (asset)
    {
        PHCachingImageManager *imageManager = [[PHCachingImageManager alloc] init];

        // Request an image for the asset from the PHCachingImageManager.
        [imageManager requestImageForAsset:asset
                                targetSize:CGSizeMake(100.0f, 100.0f)
                               contentMode:PHImageContentModeAspectFill
                                   options:nil
                             resultHandler:^(UIImage *image,
                                             NSDictionary *info)
         {
             NSLog(@"IMAGE: %@", image);
         }];
    }

Apple created a sample app that uses PHPhotoLibrary. It's available here.

redpajama_set_name: RedPajamaStackExchange


We are a well-established manufacturer who dedicated USB-C accessories as well as owning exclusive design. In addition to creating the state of the technology, we pride ourselves on ensuring customer experience.
Our business model has enabled us to decrease on cost that allows our premium quality products to be marketed at a competitive price. We strive for customer service and the quality of our products, so we have LIFETIME WARRANTY & easy-to-reach support.
If there's any questions or concerns, please contact us at any time.
【BEST IN CLASS DESIGN】 Durable nylon braided design with premium aluminium housing and gold-plated connectors which gives it a stylish appearance and delivers optimal signal transfer with lower distortion at the point of contact,90 degree design + insert indicator light. It's more convenient to use.
If you have any questions about this product by NIROLLE, contact us by completing and submitting the form below. If you are looking for a specif part number, please include it with your message.


The following are a list of resources that help ensure the inclusion and success of all faculty at our institution (i.e., create a supportive academic culture that focuses on empowerment and success). They address specific features of academic environments (structures, cultures, practices, etc.) that have been associated with increased hiring, retention, and promotion of underrepresented faculty.
Looking for a group of male faculty engaged in building, promoting and sustaining an equitable university for people of all genders?
The list includes a variety of child care options in Morgantown, a financial assistance program for child care costs, lists of local events/programs and support groups as well as a virtual parental networking system.
See a sample document that utilizes "best practices" for evaluating faculty engaged in interdisciplinary work.
NCFDD is an independent faculty development center that provides training, mentoring, and supportive communities for faculty, graduate students, and post-docs across the institution. Check out their resources including professional development training focused on increasing productivity, an intense and reliable support network of highly trained and successful mentors, and a number of other informative webcasts.
The Faculty Family Travel Fund was designed to remove travel-related barriers to the professional advancement of faculty and postdoctoral scholars who have substantial childcare, eldercare, or other dependent care responsibilities.
The Women's Leadership Initiative is housed under the ADVANCE Center and was created to address the underrepresentation of women in faculty and leadership positions. The Center also offers workshops for leadership development, professional network building, and other career skills. Check out our campus wide program for empowering and engaging women.
Members of our ADVANCE team are engaged in creating and disseminating policies that provide support for work-life fit for all faculty. These policies are intimately linked with faculty satisfaction and retention. Most of the initiatives focus on promoting departmental and institutional flexibility and include a procedure for parental work assignment after the birth/adoption/guardianship of a child, expanding dual career opportunities, child care resources, lactation support, etc.


constructed by that process. In fields frequently affected by the gatekeeping practices of the traditional publishing industry, professionals in fields such as the science of spectroscopy are turning to online community learning spaces or collaborative document holders such as wikis. Knowledge seekers in cutting-edge fields are increasingly finding that ongoing appraisal of new developments is most effectively achieved through the participatory kraft and negotiated experience of rhizomatic community engagement. For instance, a researcher exploring social software use must rely at least in part on online knowledge repositories because current information on the terminology used in these areas is simply not available in any exhaustive or definitive form in books or peer-reviewed articles (Nichol 2007. This community acts as the curriculum, spontaneously shaping, constructing, and reconstructing itself and the subject of its learning in the same way that the rhizome responds to changing environmental conditions: The rhizome is an antigenealogy. Exhibit 1 as Horton and Freire (1990) argue, "If the act of knowing has historicity, then todays knowledge about something is not necessarily the same tomorrow. Educational technology is one such field. Ml (accessed May 27, 2008). Changing Knowledge, new communication technologies and the speeds at which they allow the dissemination of information and the conversion of information to knowledge have forced us to reexamine what constitutes knowledge; moreover, it has encouraged us to take a critical look at where it can. Minds on fire: Open education, the long tail, and Learning.0. Collaborative the knowledge construction is also being taken up in fields that are more traditionally coded as learning environments. Copyright and Citation Information for this Article This article may be reproduced and distributed for educational purposes if the following attribution is included in the document: Note: This article was originally published in Innovate ( fo/ ) as: Cormier,. The originals are still available at archive. Wikis and similar tools offer a participatory medium that can allow for communal negotiation of knowledge. (Deleuze and Guattari 1987, 21) With this model, a community can construct a model of education flexible enough for the way knowledge develops and changes today by producing a map of contextual knowledge. A botanical metaphor, first posited by Deleuze and Guattari. With the help of partners in education, business and industry, and trade associations, each program includes the academic and technical skills required to be successful in todays economy. Thus the foundations upon which we are working are changing as well as the speed at which new information must be integrated into those foundations. London: University of Minnesota Press. Knowledge represents positions from which people make sense of their worlds and their place in them, and from which they construct their concepts of agency, the possible, and their own capacities to do (Stewart 2002, 20). Read more about Math. Rhizomatic education : Community as curriculum. Conclusion In a sense, the rhizomatic viewpoint returns the concept of knowledge to its earliest roots. Suggesting that a distributed negotiation of knowledge can allow a community of people to legitimize the work they are doing among themselves and for each member of the group, the rhizomatic model dispenses with the need for external validation of knowledge, either by an expert. Information is the foundation of knowledge. Weblog entry, March. The ephemeral nature of the Web and the rate at which cutting-edge knowledge about it and on it becomes obsolete disrupts the painstaking process by which knowledge has traditionally been codified. In the meantime, learners are left without a canonical source of accepted knowledge, forcing a reliance on new avenues for knowledge creation. There is an assumption in both theories that the learning process should happen organically but that knowledge, or what is to be learned, is still something independently verifiable with a definitive beginning and end goal determined by curriculum.
One has been to attack these new sources as flawed as has been the pagination case in the history department at Middlebury College Jaschik 2007. Open Habitat Project collate the work of a variety of professionals to create snapshots of the knowledge of a particular field kierkegaard as it is seen at a given time Cormier 2008. Rather, weblog entry, tru" edtechtalk, mnews20070126wiki accessed May 27, horton.
A comprehensive, coeducational Catholic High school Diocese of Wollongong - Albion Park Act Justly, love tenderly and walk humbly with your God Micah 6:8.At first I thought, I could do my own dissertation but couldn't handle after getting stuck on it for almost a year.It took me days going through all the reviews of paper writing services and finally came across SpeedyPaper.
Modifiable, see Whats Covered in Our Integrated Math Series. See SpringBoard in Action, unlike the graphic arts, individual experts translate information into knowledge through the application of checks and balances involving peer review and rigorous. Is its ability to support and expand the various aspects of social learnin" In a nonrhizomatic model, then, the existing educational model with its expertcentered pedagogical planning and publishing cycle is too static and prescribed to accommodate the kind of fluid. Drawing or photography, transitory conception of knowledge that is necessary to understand the simplest of Webbased concepts 18, the community, we make the road by walking. Constructed, has the power to create knowledge within a given context and leave that knowledge as a new node connected to the rest of the network. Such as may be found in the technical reference manuals of learning. However, reversible, information is coming too fast for our traditional methods of expert verification to adapt. Debating the merits of various Creative Commons licenses and trying to determine the means by which content creators intellectual property curriculum analysis paper rights can be protected even.


text:
%REAL2RGB  Converts a real-valued matrix into a truecolor image
%
% Examples:
%   B = real2rgb(A, cmap);
%   B = real2rgb(A, cmap, lims);
%   [B lims map] = real2rgb(...);
%
% This function converts a real-valued matrix into a truecolor image (i.e.
% double array with values between 0 and 1) using the colormap specified
% (either user-defined or the name of a colormap function). The output
% image is suitable for display using IMAGE or IMSHOW, exporting using
% IMWRITE, texture mapping a surface etc.
%
% Colormaps specified by name, e.g. 'hot', can be reversed ('-hot'), made
% to convert linearly to grayscale when printed on a black & white printer
% ('hot*'), or both ('-hot*').
%
% Value limits and a colormap table can be output, for use generating the
% correct colorbar, e.g.:
%   [B lims map] = real2rgb(peaks(256), '-hot*');
%   hIm = imshow(B);
%   set(gcf, 'Colormap', map);
%   set(gca, 'CLim', lims);
%   set(hIm, 'CDataMapping', 'scaled');
%   colorbar;
%
% IN:
%   A - MxN real matrix.
%   cmap - JxK user-defined colormap, or a string indicating the name
%          of the colormap to be used. K = 3 or 4. If K == 4 then
%          cmap(1:end-1,4) contains the relative widths of the bins between
%          colors. If cmap is a colormap function name then the prefix '-'
%          indicates that the colormap is to be reversed, while the suffix
%          '*' indicates that the colormap bins are to be rescaled so that
%          each bin produces the same change in gray level, such that the
%          colormap converts linearly to grayscale when printed in black
%          and white.
%   lims - 1x2 array of saturation limits to be used on A. Default:
%          [min(A(:)) max(A(:))].
%
% OUT:
%   B - MxNx3 truecolor image.
%   lims - 1x2 array of saturation limits used on A. Same as input lims, if
%          given.
%   map - 256x3 colormap similar to that used to generate B.

% Copyright: Oliver Woodford, 2009-2011

% Thank you to Peter Nave for reporting a bug whereby colormaps larger than
% 256 entries long are returned.

function [B, lims, map] = real2rgb(A, cmap, lims)
% Don't do much if A is wrong size
[y, x, c] = size(A);
if c > 1
    error('A can only have 2 dimensions');
end
if y*x*c == 0
    % Create an empty array with the correct dimensions
    B = zeros(y, x, (c~=0)*3);
    return
end

% Generate the colormap
if ischar(cmap)
    % If map starts with a '-' sign, invert the colormap
    reverseMap = cmap(1) == '-';
    % If the map ends with a '*', attempt to make map convert linearly to
    % grayscale
    grayMap = cmap(end) == '*';
    % Extract the map name
    cmap = lower(cmap(reverseMap+1:end-grayMap));
    % Load the map
    try
        % Check for a concise table first
        map = feval(cmap, Inf);
    catch
        map = [];
    end
    if invalid_map(map)
        try
            % Just load a large table
            map = feval(cmap, 256);
        catch
            error('Colormap ''%s'' not found', cmap);
        end
        if invalid_map(map)
            error('Invalid colormap');
        end
    end
    if reverseMap
        % Reverse the map
        map = map(end:-1:1,:);
        if size(map, 2) == 4
            % Shift up the bin lengths
            map(1:end-1,4) = map(2:end,4);
        end
    end
    if grayMap && size(map, 1) > 2
        % Ensure the map converts linearly to grayscale
        map(1:end-1,4) = abs(diff(map(:,1:3) * [0.299; 0.587; 0.114]));
    end
else
    % Table-based colormap given
    map = cmap;
end

% Only work with real doubles
B = reshape(double(real(A)), y*x, c);

% Compute limits and scaled values
maxInd = 1 + (size(map, 1) - 2) * (size(map, 2) ~= 4);
if nargin < 3
    lims = [];
end
[B, lims] = rescale(B, lims, [0 maxInd]);

% Compute indices and offsets
if size(map, 2) == 4
    % Non-linear colormap
    bins = map(1:end-1,4);
    cbins = cumsum(bins);
    bins(bins==0) = 1;
    bins = cbins(end) ./ bins;
    cbins = [0; cbins(1:end-1) ./ cbins(end); 1+eps];
    [ind, ind] = histc(B, cbins);
    B = (B - cbins(ind)) .* bins(ind);
    clear bins cbins
else
    % Linear colormap
    ind = min(floor(B), maxInd-1);
    B = B - ind;
    ind = ind + 1;
end

% Compute the output image
try
    B = bsxfun(@times, map(ind,1:3), 1 - B) + bsxfun(@times, map(ind+1,1:3), B);
catch
    % If no bsxfun
    B = B(:,[1 1 1]);
    B = map(ind,1:3) .* (1 - B) + map(ind+1,1:3) .* B;
end
B = min(max(B, 0), 1); % Rounding errors can make values slip outside bounds
B = reshape(B, y, x, 3);

if nargout > 2 && (size(map, 1) ~= 256 || size(map, 2) == 4)
    % Generate the colormap (for creating a colorbar with)
    map = reshape(real2rgb(0:255, map, [0 255]), 256, 3);
end
return

function notmap = invalid_map(map)
notmap = isempty(map) || ndims(map) ~= 2 || size(map, 1) < 1 || size(map, 2) < 3 || size(map, 2) > 4 || ~all(reshape(map(:,1:3) >= 0 & map(:,1:3) <= 1, [], 1));

redpajama_set_name: RedPajamaGithub


category John Morris , Urban Outfitters, Inc/ , Urban Outfitters Inc/ (Philadelphia PA) , and 5 more.
category Analyst Ratings , Rishi Jaluria , Market News , and 13 more.
category Fox Business News , tech jobs , Analyst Color , and 12 more.
category Nautilus Group, Inc/ (The) , John Fread , Retailing , and 3 more.
category morningstar , D/A/ Davidson , Earnings , and 16 more.
category COLM , Christopher Svezia , D/A/ Davidson , and 12 more.
category Market News , Benzinga , Analyst Ratings , and 5 more.
category Retailing , Michael Kawamoto , Nautilus Group, Inc/ (The) , and 3 more.
category Reiteration , Market News , Benzinga , and 8 more.
category Tim Boyle , D/A/ Davidson , Columbia Sportswear Company , and 4 more.
category Red Dead Redemption , PUBG , Tom Forte , and 13 more.
category Nomura , Jefferies , iPad , and 19 more.
category Tom Forte , D/A/ Davidson , Market News , and 6 more.
category Analyst Color , ORCL , Price Target , and 7 more.
category Risk Management , Mark Kelleher , D/A/ Davidson , and 13 more.
category Reiteration , Media , D/A/ Davidson , and 13 more.
category D/A/ Davidson , Wedbush , video games , and 18 more.
category PRTY , Downgrades , D/A/ Davidson , and 7 more.
category John Bunch , Adam Bold , Financial Planning , and 11 more.
category Benzinga , TGT , Reiteration , and 11 more.
category Upgrades , Thomas Diffely , Analyst Ratings , and 4 more.
category Deborah Weinswig , Analyst Ratings , Benzinga , and 5 more.
category Price Target , Analyst Color , Analyst Ratings , and 5 more.


text:
The return of Dylan
Lisa Napoli Sep 8, 2006
https://www.marketplace.org/2006/09/08/return-dylan/
MARK AUSTIN THOMAS: Guess who's back on top of the record charts? Bob Dylan. Marketplace's Lisa Napoli says the new album features his trademark vocals and poetic lyrics.
LISA NAPOLI: Bob Dylan may not look like he did 30 years ago, but he still sounds the same. And that sound is serving him well on the charts. For the first time since 1976, he's topping them. His "Modern Times" is the number one seller. Geoff Mayfield of Billboard is not terribly surprised:
GEOFF MAYFIELD: But if you look, his last two studio albums also made the top 10.
But this new one has sold more than 190,000 copies in just the last week. That's thanks in part to a modern marketing campaign on that virtual record store known as iTunes.
In Los Angeles, I'm Lisa Napoli for Marketplace.
How Billboard's charting formula has changed over the decades
The Nobel Committee can't find Bob Dylan
Why Bob Dylan may have sold his entire catalog of music
Bob Dylan hands over his archives
Bob Dylan should respond to the Nobel Prize committee if he wants that prize money
Can art triumph over developers in this coastal city?


Let James Quan and Winnie Chan of Bynd Artisan take you across the various artists' enclaves in Singapore.
Singapore's museums and galleries abound with keepsakes that encapsulate the nation's unique culture and heritage.
Take a walk around Singapore, and discover a city where art comes alive on the streets.
Paint the town red—or other colours of the rainbow—at these art jamming studios.


FORT WORTH, Texas (Jan. 31, 2017) In keeping with its commitment to excellence in the arts, Tarrant County College offers a variety of opportunities to enjoy dance, drama and music events and visual arts exhibits during the spring semester.
Those Before Me opens Feb. 16 and runs through Feb. 18 at the Joe B. Rushing Center for Performing Arts at the South Campus, 5301 Campus Drive. Researched and performed by TCC students, the drama honors women's history. TCC students, faculty and staff attend free of charge. General admission is $5. Show times are 7:30 p.m. nightly.
The Festival of New Plays features three award-winning, 10-minute plays written by students who submitted their work in a playwriting competition last fall. Opening on February 22 and running through Feb. 24 at the C.A. Roberson Theatre at the Southeast Campus, 2100 Southeast Parkway, Arlington, festival performances are 7:30 p.m. nightly. A matinee at 1:30 p.m. on Feb. 24 will highlight an expanded version of MetAMORfosis, by Carlos Romero, last year's first-place winner in the competition. The play will be performed at the Region 6 Kennedy Center American College Theater Festival in March. Tickets for the Festival of New Plays are free to TCC students, faculty and staff, $3 for non-TCC students and senior citizens and $6 general admission.
Students have a mystery to solve when MISS NELSON IS MISSING! premieres March 1 at the Northwest Campus, 4801 Marine Creek Parkway. The play, which continues through March 5, features Miss Nelson, a teacher who is just too nice and cannot seem to control her classroom. When she suddenly disappears, her hard-as-nails substitute, Viola Swamp, has her students ready to do anything to bring Miss Nelson back. General admission is $3. Show times are 7:30 nightly and 2 p.m. on Saturday.
A diverse cross-section of music, ranging from the Middle Ages to the contemporary era, will be performed March 28 at the Northeast Campus, 828 Harwood Road, Hurst. During the concert, audience members move through four rooms, each featuring a different era's music. The concert, which is free of charge, begins at 7 p.m.
On March 29, the Southeast Campus will host a Swing Dance and Music Benefit, which features the TCC SE Jazz Ensemble playing traditional big band swing music. Dance instructors will be available to teach basic swing dance steps. An auction of art by TCC instructors and students will take place. Additionally, art will be available for sale. Guests are encouraged to dress in the style of the 1920s. Tickets are $5 for TCC students and $10 general admission. All proceeds will go toward scholarships for SE Campus Fine Arts students studying Art, Dance and Music.
Starting April 3, the Northwest Campus presents DADA Week, a celebration of the unlimited potential of human expression. The art exhibit shows how DADA connects all areas of study, including the rational and irrational. It is an example of thinking outside of what is expected and challenges students to invent new directions of their own. The exhibit will be available in the Lakeview Gallery through April 7.
Next story: TCC Board of Trustees Governance Committee Meeting February 9 at 2 p.m.


text:
Choose Charitable Bequests Carefully
When helping wealthy clients design their legacies, be mindful of how charitable designations fit into the mix.
Lifetime charitable contributions of appreciated assets often are tax-efficient while donations from IRAs can pose problems. In estate planning, though, tactics can be reversed. Charitable bequests may come from tax-deferred accounts, so human beneficiaries will have fewer taxable withdrawals from inherited retirement plans. Meanwhile, appreciated assets can be left to individual heirs.
"In working with estate planning attorneys, I have found it advantageous in some cases to list private family foundations, donor-advised funds or direct charitable organizations as beneficiaries of IRAs, 401(k)s, and so on," says Robert Cron, senior portfolio manager in the Minneapolis office of Bronfman E.L. Rothschild, an investment advisory and consulting firm.
"This planning strategy provides a way to reduce an individual's taxable estate and pass assets that will receive a step-up in cost basis to the heirs." With cost basis increased to current value at death, a subsequent sale may avoid income tax on lifetime appreciation or real estate depreciation.
Cron tells of a client who owns shares of a large financial institution as well as a great deal of real estate with a very low cost basis. "We have assigned a family foundation as the beneficiary for his IRA and 401(k) plan assets," says Cron. "The heirs will receive a rather large inheritance from the financial institution stock and potentially from the sale of the real estate. This client will continue to hold the company stock in his revocable trust until death, or until a change in tax law."
Different Designations
Similarly, Jen Dawson, a wealth manager with Balasa Dinverno Foltz, an independent private wealth management firm based in Itasca, IL, has a client who wants to leave assets to charity rather than to the government. "She has significant IRA assets," says Dawson, "but her trust originally named charities as beneficiaries, which makes things complicated. If a trust is a beneficiary of an IRA and the trust names a charity as ultimate beneficiary, then it is likely that the beneficiaries would be forced to take a full distribution of the IRA within five years, which is not ideal from an income tax perspective. It is better to leave IRA assets directly to charity and individuals."
Dawson reports that her client is carefully targeting a portion of her IRAs to go to charity. "She revised the IRA beneficiary designations so that 33% goes to one charity, 33% goes to another charity and the remainder is split between two family members," says Dawson. "We review the account values at least annually, to ensure that this plan is roughly accomplishing her goals of leaving IRA assets to charity and avoiding federal estate taxes. Her children will inherit primarily taxable, non-retirement assets."
—Donald Jay Korn
Donald Jay Korn is a Financial Planning contributing writer in New York. He also writes regularly for On Wall Street.
On the iPad
Download our Perspectives app, "Practice Management: Navigating the Seas of Change."
Estate Planning When Tax Laws Are Uncertain
There's no point in waiting on new policy to initiate preparation that is protective and vital, no matter what the ultimate law may be.
Time to Plan for the Death of the "Death Tax"?
Advisors are already prepping clients for sweeping changes coming under President-elect Trump's administration next year.
Does Planning Software Go Too Far, or Not Far Enough?
Too much of it is designed to sell products rather than to enable advisors to actually provide the guidance clients are seeking.


Here's the What's On listing for July! It's an eclectic mix of all sorts of events that come to my attention and I'll update it through the the month so do check back when you can.
1st 1pm The Choir of Trinity College. Lunchtime concert, a recital of music from the forthcoming tour to Germany. Trinity College Chapel. Free admission.
14th 5.30pm Summer Choral Concert. Choir of King's College. Elgar, Bernstein, Vaughan Williams and Dvorak. King's College Chapel. Tickets from King's College Visitor Centre.


His Imperial Majesty, Ooni Adeyeye Ogunwusi, the ooni of Ife, says if Nigerian youth are not happy with President Muhammadu Buhari, they should vote him out in the next election.
Speaking in an interview aired on The Osasu Show, the king said the youth were yet to fathom how powerful they are in the scheme of things., admonishing them to quit complaining about the misdeeds of government.
He admonished them to stop complaining about the misdeeds of government.
When asked what government must do to better the lot of the Nigerian youth, the monarch said: "Why must it be government, government? Who is government? It is the people that are behind the government.
The ooni also advised against hate speech, division and projection of negative energy among countrymen.
"Truth be told, the youth don't know their power yet. Fortunately, power belongs to the youth of Nigeria. Once they can get themselves together, that power belongs to them," he said.
"So my advice to them is to stop hate speeches. They should stop being not focused. I understand the frustrations, I understand absolutely. I live all my life for the youth –every day of my life, I live it for the youth.
Ooni also spoke on his relationship with Rilwan Akiolu, the oba of Lagos, saying he has no rift with the king but the media only "over-celebrated the situation".
Some months back, a video of the Lagos monarch refusing to exchange pleasantries with his Ife counterpart went viral, and it elicited different reactions.


This book aims at researchers in academia and industry looking for a state-of-the-art overview of the use of semantic and Web 2.0 technologies for knowledge management and personal productivity. Practitioners in industry will also benefit, in particular from the case studies which highlight cutting-edge applications in these fields.
Awareness systems can be broadly defined as those systems that help people construct and maintain awareness of each others' activities, context or status, even if the participants are not co-located. Providing an overview of the current state-of-the-art this book provides a theoretical foundation for the design and development of Awareness Systems.
The new digital media offers us an unprecedented memory capacity, an ubiquitous communication channel and a growing computing power. How can we exploit this medium to augment our personal and social cognitive processes at the service of human development? Combining a deep knowledge of humanities and social sciences as well as a real familiarity with computer science issues, this book explains the collaborative construction of a global hypercortex coordinated by a computable metalanguage.
Marshalling an impressive array of data, the authors discuss where and how IT is contributing to our unemployment crisis and increasingly uneven wealth distribution. More importantly, they provide a roadmap that will help us to turn this challenge into an opportunity.


sir plz plz reply i want to ask that aapke integration and definite integration kke course ki video sune ke baaad aur kya keru ...? i mean to say that agar aapke course achae se samjh lu so au practice kerne ki jarurat hai ya phir aapke course ke questions sufficent hai..? plz read my full question plz !!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!!