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Justia Patents US Patent Application for Shaft sealing mechanism, structure for mounting shaft sealing mechanism on stator, and turbine Patent Application (Application #20060033285)
Shaft sealing mechanism, structure for mounting shaft sealing mechanism on stator, and turbine
A shaft sealing mechanism of an annular shape having at least one divided portion, which is installed in an annular space between a rotor and a stator, includes a group of thin plates. Outer peripheral ends of the thin plates are joined, and inner peripheral free ends come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap near the divided portion is set to be larger than a low-pressure gap in a circumferential direction other than near the divided portion.
The present invention relates to a shaft sealing mechanism, a structure for mounting the shaft sealing mechanism on a stator, and a turbine including the shaft sealing mechanism and the structure for mounting the shaft sealing mechanism on a stator.
In general, a turbine is provided around a rotor thereof with static blades and dynamic blades, and has a shaft sealing mechanism around the rotor in order to reduce a leakage amount of working fluid flowing from a high pressure side to a low pressure side. As one example of such a shaft sealing mechanism, there are leaf seals disclosed in Japanese Patent Application Laid-Open Nos. 2002-013647, 2003-113945, and the like.
The turbine includes a gas turbine and a steam turbine, and an entire structure of the gas turbine is shown, as one example, in FIG. 8. Air compressed by a compressor 1 is mixed with fuel to be combusted in a combustor 2. Combustion gas, as working fluid, generated in the combustor 2 expands so that thermal energy of the combustion gas is converted to rotational energy in the courses of passing through static blades 6 and dynamic blades 7, which are provided alternatively around a rotor 4. The thus converted rotational energy is taken out as electric power. A shaft sealing mechanism 11 is provided between each static blade 6 and the rotor 4 in order to reduce a leakage amount of the combustion gas from a high pressure side to a low pressure side, and a leaf seal is used as an example of the shaft sealing mechanism.
One example of a conventional shaft sealing mechanism including the leaf seals is shown in FIG. 9. The shaft sealing mechanism 11 has a structure in which many thin plates 121, having a fixed width in an axial line direction of the rotor 4, are arranged in a multi-layered manner. The shaft sealing mechanism 11 includes a thin plate group 12 where the thin plates are arranged annularly in a circumferential direction of the rotor 4 and are disposed with fine spacing along the circumferential direction thereof. The thin plate group 12 is joined at an outer peripheral proximal end 122 thereof, and an inner peripheral free end 123 thereof comes in sliding contact with a rotor outer peripheral face 4a to form an acute angle to the rotor 4 without being joined. Thus, an annular space 8, which is provided between the rotor 4 and a stator 5 to allow working fluid to flow, is partitioned into a high-pressure region and a low-pressure region.
The thin plate group 12 is fixed to a leaf seal ring 14 obtained by combining a pair of divided seal rings 14a and 14b, and each thin plate 121 has a T-shape cross section, including a rotor axial line. The leaf seal ring 14 also includes a high-pressure-side plate 15 provided on a side adjacent to the high-pressure region through the thin plate group 12, and a low-pressure-side plate 16 provided on a side adjacent to the low-pressure region as guide plates for working fluid. A length of the low-pressure-side plate 16 is shorter than that of the high-pressure-side plate 15 in a sectional view including the rotor axial line, in order to generate a floating force by a gas pressure distribution acting on upper and lower faces of the thin plates 121. Therefore, a gap defined between a stator inner wall 5a adjacent to the low-pressure region and a thin plate edge 125 (hereinafter, "low-pressure gap Y1") is larger than a gap defined between the high-pressure-side plate 15 provided adjacent to the high-pressure region and a thin plate edge 124 (hereinafter, "high-pressure gap X") (X<Y1).
The shaft sealing mechanism 11 with the above configuration is fittingly inserted into a recessed groove 31 provided on the stator 5. The inner peripheral free end 123 of each thin plate 121 is floated from the outer peripheral face 4a of the rotor 4 by a floating force due to working fluid acting on the thin plate 121 and a dynamic pressure effect of working fluid due to rotation of the rotor 4 to achieve a non-contacting state between the inner peripheral free end 123 and the outer peripheral face 4a. Thus, each thin plate is prevented from wearing and generating heat.
Conventionally, the shaft sealing mechanism with such a leaf seal has a divided portion in a radial direction to the rotor axial center in order to facilitate assembling. A plurality of pieces of the divided leaf seal are sequentially assembled to the stator to integrally exhibit a sealing function. However, even if the assembled and integrated annular seal is formed, since it has at least one (usually, plural) divided portion in a radial direction to the rotor axial center, high pressure working fluid eventually flows into the leaf seal via a gap formed by the divided portions. FIG. 10 schematically depicts a flow of working fluid around the divided portion of the leaf seal. An actual leaf seal has a head of the thin plate 121 formed in a wide T-shape in cross section, including the rotor axial center, but it is schematically simplified as a rectangular shape in FIG. 10. Working fluid that has flowed in the shaft sealing mechanism 11 from a divided portion 19 flows into the inside from a gap (a high-pressure gap) between the high-pressure-side plate 15 and the thin plate edge 124 of the thin plate 121 along the high-pressure-side plate 16 in a circumferential direction, to flow down on a surface of the thin plate 121 along upper and lower faces of the thin plate 121. As disclosed in Japanese Patent Application Laid-Open No. 2002-013647, the working fluid passes through a gap between the lower end of the high-pressure-side plate 15 and the rotor outer peripheral face 4a at any point in the circumferential direction on the leaf seal, except for around the divided portion of the leaf seal, to flow on the upper and the lower faces of the thin plate 121 from the side of the inner peripheral free end 123 of the thin plate 121 toward the side of the outer peripheral proximal end 122.
Around the divided portion, however, the working fluid flows from the divided portion 19 into the shaft sealing mechanism 11 while maintaining the same pressure over the entire length of the high-pressure-side plate 15 in a sectional view including the rotor axial line. Therefore, the same pressure acts on the side of the outer peripheral proximal end 122 and the side of the inner peripheral free end 123 around the thin plate edge 124 of the thin plate 121. This technique is different from the conventional example in this point. However, a pressing force acts on the thin plate due to fluctuation over a gas pressure distribution, and the inner peripheral free end 123 comes in contact with the rotor outer-surface 4a so that wearing and heat generation of the thin plate occurs.
It is an object of the present invention to at least solve the problems in the conventional technology.
A shaft sealing mechanism of an annular shape having at least one divided portion according to one aspect of the present invention, which is installed in an annular space between a rotor and a stator, includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap near the divided portion is set to be larger than a low-pressure gap in a circumferential direction other than near the divided portion.
A shaft sealing mechanism of an annular shape having at least one divided portion according to another aspect of the present invention, which is installed in an annular space between a rotor and a stator, includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap near the divided portion is set to be larger than a gap between an inner wall of the stator or a mounting piece inner wall and edges of the thin plates.
A shaft sealing mechanism of an annular shape having at least one divided portion according to still another aspect of the present invention, which is installed in an annular space between a rotor and a stator, includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap is set near the divided portion in such a manner that a pressing force acting on the thin plates is not generated by working fluid flowing downward on surfaces of the thin plates.
A structure according to still another aspect of the present invention is for mounting a shaft sealing mechanism of an annular shape on a stator. The shaft sealing mechanism is installed in an annular space between a rotor and the stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. A recessed groove that can accommodate the shaft sealing mechanism is formed on the stator. A mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove. An annular recess is provided on a surface of the mounting piece opposite to a low-pressure-side plate.
A shaft sealing mechanism of an annular shape according to still another aspect of the present invention, which is installed between a rotor and a stator, includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. The shaft sealing mechanism is formed integrally without including a divided portion so that a pressing force acting on the thin plates is not generated by working fluid.
A structure according to still another aspect of the present invention is for mounting a shaft sealing mechanism of an annular shape on a stator. The shaft sealing mechanism is installed in an annular space between a rotor and the stator. The shaft sealing mechanism is formed integrally without including a divided portion. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. A recessed groove that can accommodate the shaft sealing mechanism is formed on the stator. A mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove.
A turbine according to still another aspect of the present invention includes a shaft sealing mechanism of an annular shape having at least one divided portion. The shaft sealing mechanism is installed in an annular space between a rotor and a stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap near the divided portion is set to be larger than a low-pressure gap in a circumferential direction other than near the divided portion.
A turbine according to still another aspect of the present invention includes a shaft sealing mechanism of an annular shape having at least one divided portion. The shaft sealing mechanism is installed in an annular space between a rotor and a stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap near the divided portion is set to be larger than a gap between an inner wall of the stator or a mounting piece inner wall and edges of the thin plates.
A turbine according to still another aspect of the present invention includes a shaft sealing mechanism of an annular shape having at least one divided portion. The shaft sealing mechanism is installed in an annular space between a rotor and a stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. At least a low-pressure gap is set near the divided portion in such a manner that a pressing force acting on the thin plates is not generated by working fluid flowing downward on surfaces of the thin plates.
A turbine according to still another aspect of the present invention includes a structure for mounting a shaft sealing mechanism of an annular shape on a stator. The shaft sealing mechanism is installed in an annular space between a rotor and the stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. A recessed groove that can accommodate the shaft sealing mechanism is formed on the stator. A mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove. An annular recess is provided on a surface of the mounting piece opposite to a low-pressure-side plate.
A turbine according to still another aspect of the present invention includes a shaft sealing mechanism of an annular shape that is installed between a rotor and a stator. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. The shaft sealing mechanism is formed integrally without including a divided portion so that a pressing force acting on the thin plates is not generated by working fluid.
A turbine according to still another aspect of the present invention includes a structure for mounting a shaft sealing mechanism of an annular shape on a stator. The shaft sealing mechanism is installed in an annular space between a rotor and the stator. The shaft sealing mechanism is formed integrally without including a divided portion. The shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates. Outer peripheral ends of the thin plates are joined. Inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined. A recessed groove that can accommodate the shaft sealing mechanism is formed on the stator. A mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove.
The above and other objects, features, advantages and technical and industrial significance of this invention will be better understood by reading the following detailed description of presently preferred embodiments of the invention, when considered in connection with the accompanying drawings.
FIG. 1 is a cross section of a divided-type leaf seal according to the present invention and a structure for mounting the divided-type leaf seal on a stator;
FIGS. 2A and 2B are schematics for illustrating a principle of an operation of a conventional leaf seal;
FIGS. 3A and 3B are schematics for illustrating a principle of an operation around a divided portion of a divided-type leaf seal;
FIGS. 4A and 4B are schematics for illustrating a principle of an operation around a divided portion of a divided-type leaf seal according to the present invention;
FIG. 5 is a perspective view of an integral leaf seal according to the present invention;
FIG. 6 is a cross section of a structure for mounting the integral leaf seal according to the present invention on a stator;
FIGS. 7A to 7C are schematics for illustrating a manufacturing method of the leaf seal according to the present invention;
FIG. 8 is a perspective view of a gas turbine;
FIG. 9 is a cross section of the conventional leaf seal; and
FIG. 10 is a perspective view around the divided portion of a divided-type leaf seal.
Exemplary embodiments of the present invention will be explained in detail below with reference to the accompanying drawings. These embodiments are only illustrative, and the present invention is not limited to the embodiments as far as functions and structures of the shaft sealing mechanism constituting the feature of the present invention are provided. A gas turbine is taken as an example of the embodiments, but the present invention is also applicable to steam turbines.
According to a first embodiment of the present invention, a shaft sealing mechanism (hereinafter, "divided-type leaf seal") including leaf seal having at least one divided portion 1, and a structure for mounting the shaft sealing mechanism on a stator will be explained with reference to FIG. 1.
FIG. 1 is a cross section of a shaft sealing mechanism including a leaf seal, and a mounting structure of the shaft sealing mechanism on a stator, including a rotor axial line. The shaft sealing mechanism including a leaf seal will be explained first. A shaft sealing mechanism 11 includes a thin plate group 12, a pair of thin-plate holding rings 13a, 13b, a high-pressure-side plate 15, a low-pressure-side plate 16, and a spacer 17. The shaft sealing mechanism 11 is provided in an annular space 8 between a rotor 4 and a stator 5 and is disposed around the rotor 4 to partition the annular space into a high-pressure region and a low-pressure region, thereby forming an annular seal at a face perpendicular to a rotor axial line. The shaft sealing mechanism 11 includes the thin plate group 12 having a T-shaped fixed width to a direction of the rotor axial line, where many thin plates 121 are stacked with fine spaces to one another in a circumferential direction of the rotor to form the annular seal. The thin plate 121 is fixed at an outer peripheral proximal end 122 by welding or the like, but it is not joined at its inner peripheral free end 123. The thin plate 121 comes in sliding contact with a rotor outer peripheral face 4a to form an acute angle to the rotor 4.
In order to prevent working fluid from blowing out, a high-pressure-side plate 15 and a low-pressure-side plate 16 serving as guide plates are disposed on an upstream side and a downstream side of working fluid flowing on respective thin plates 121. The high-pressure-side plate 15 is an annular plate and is arranged to be opposed to a thin plate edge 124 adjacent to the high-pressure region of the thin plate 121. The high-pressure-side plate 15 is fixed to the thin plate 121 by a receiving groove 126 provided on the thin plate 121 to keep a fixed gap (high-pressure gap X) between the high-pressure-side plate 15 and the thin plate edge 124. On the other hand, the low-pressure-side plate 16 is similarly an annular plate and is arranged to be opposed to the thin plate edge 125 adjacent to the low-pressure region of the thin plate 121. The low-pressure-side plate 16 is fixed to the thin plate 121 by the receiving groove 126 provided on the thin plate 121 to keep a fixed gap between the low-pressure-side plate 16 and the thin plate edge 125. A length of the low-pressure-side plate 16 is made shorter than that of the high-pressure-side plate 15 in a sectional view including the rotor axial line, so that a gap enlarged as compared with the gap between the low-pressure-side plate 16 and the thin plate edge 125 is provided. That is, such a gap is provided at any point except for around the divided portion of the shaft sealing mechanism, as a gap (low-pressure gap Y1) defined between a mounting piece inner wall 21a and the thin plate edge 125. As a result, more stable pressure distributions of working fluid can be obtained on upper and lower faces of the thin plate 121. A spacer 17 for constraining movement of the thin plate group 12 in a radial direction is arranged between the thin plate group 12 and the thin-plate holding rings 13a, 13b.
The stator 5 is formed, around the rotor axial center, with an annular recessed groove 31 that can receive the shaft sealing mechanism 11 easily in a sectional view including the rotor axial line. The recessed groove 31 is wider than a full width of the shaft sealing mechanism 11 in a direction of the rotor axial line, so that the shaft sealing mechanism 11 is fixed to the stator 5 by inserting the shaft sealing mechanism 11 into the recessed groove 31 and further fittingly inserting a mounting piece 21 into the remaining gap. A biasing member (for example, a leaf spring) 18 is provided between outer peripheral ends of the pair of thin-plate holding rings 13a, 13b and the stator 5 to press the thin-plate holding rings 13a, 13b in a direction of the axial center of the rotor 4. Thus, movement of the shaft sealing mechanism 11 in the radial direction is constrained. The mounting structure of the shaft sealing mechanism is realized by the shaft sealing mechanism 11, the recessed groove 31, the mounting piece 21, and the biasing member 18.
An annular recess 22 around the rotor axial center is formed on a face of the mounting piece 21 opposed to the low-pressure-side plate 16 around the divided portion of the shaft sealing mechanism. A gap (low-pressure gap Y2) is provided between the thin plate edge 125 and an annular recess inner wall 22a forming the annular recess 22.
A pressure distribution of working fluid is disturbed around the divided portion of the shaft sealing mechanism due to leakage of high pressure working fluid from the dividing portion, and the disturbance of the pressure distribution can not be absorbed by a gap with a size of about the low-pressure gap (Y1), so that downward pressing force acts on each thin plate 121. Therefore, the low-pressure gap (Y2) further larger than the low-pressure gap (Y1) is secured by providing the annular recess 22, so that the gas pressure distribution acting on the thin plate can be improved and the pressing force can be reduced (a concept of an improvement in pressure distribution is described later). The annular recess 22 can be provided to extend from a height equal to the lower end of the low-pressure-side plate 16 to a lower end of the mounting piece 21. FIG. 1 depicts the annular recess 22 provided by a fixed length from the divided face in a circumferential direction, but the annular recess 22 can be provided over an entire circumference of the mounting piece 21. When the annular recess is limited to a fixed length instead of the entire circumference, loss due to leakage of working fluid is reduced. The term "around the divided portion" is not limited to the divided face, but includes a range from the divided face to a point entering therefrom by about 100 millimeters in the circumferential direction.
A fundamental concept of a function and an operation of the present invention will be explained in comparison with the conventional shaft sealing mechanism including a leaf seal. An aspect of the conventional leaf seal is defined as Case 1. An aspect of the similar structure to Case 1 around the divided portion of a divided-type leaf seal is defined as Case 2. An aspect of the portion around the divided portion according to the first embodiment of the invention is defined as Case 3.
The concept of Case 1 will be explained with reference to FIGS. 2A and 2B, while taking a gas turbine as an example. As shown in FIG. 1, an actual leaf seal has substantially a T-shape cross section, including rotor axial line, but it is schematically shown to have a rectangular cross section in FIG. 2A. In FIG. 2A, a length of the low-pressure-side plate 16 is shorter than that of the high-pressure-side plate 15 in a sectional view including a rotor axial line. It is assumed herein that combustion gas pressure is applied to the thin plate 121 due to flowing of the combustion gas serving as working fluid from the high-pressure region to the low-pressure region. When the gap (the low-pressure gap Y1) between the low-pressure-side plate 16 and the stator inner wall 5a opposed thereto is set to be larger than the gap (the high-pressure gap X) between the high-pressure-side plate 15 and the thin plate edge 124 opposed thereto, a stable pressure distribution can be obtained. That is, a substantially triangular gas pressure distribution can be formed where the maximum gas pressure is obtained at a corner r1 positioned at the inner peripheral free end 123 on the thin plate edge 124, and gas pressure gradually lowers toward a diagonal corner r2 regarding upper and lower faces of the thin plate 121. That is, when a corner positioned on the inner peripheral free end 123 at the thin plate edge 125 is represented as r3, a relationship of r1>r3>r2 is satisfied in gas pressure comparison at the respective corners.
As shown in FIG. 2B, gas pressure applied on a lower face 121b of the thin plate becomes higher than gas pressure applied on an upper face 121a thereof according to formation of such a pressure distribution in a sectional view orthogonal to the rotor axial line in a widthwise direction of the thin plate 121. That is, as shown in FIG. 2B, the gas pressure distributions applied on the upper face 121a and the lower face 121b of the thin plate takes a triangular distribution shape showing a pressure distribution that is small at the outer peripheral proximal end 122, and is the largest at the inner peripheral free end 123. As a result, when gas pressures that are respectively applied on the upper face 121a and the lower face 121b at any point P in a lengthwise direction of the thin plate 121 are represented as Fa and Fb, and a pressure that floats a distal end of the inner peripheral free end 123 due to dynamic pressure of working fluid flowing between the rotor outer peripheral face 4a and the inner peripheral free end 123 of the thin plate 121 is represented as Fc, a relationship of Fb+Fc>Fa is satisfied.
When Fx=Fb+Fc-Fa is assumed, a criterion on whether a floating force acts on the thin plate 121 or a pressing force acts thereon can be set according to Fx>0 or Fx<0. That is, when Fx>0 is satisfied, a floating force acts on the thin plate, while a pressing force acts on the thin plate when Fe<0 is satisfied. When Fx=0 is satisfied, neither a floating force nor a pressing force acts on the thin plate. In Case 1, a floating force acts on the thin plate 121 and the thin plate floats because of Fx>0, as described above, so that the inner peripheral free end 123 and the rotor outer peripheral face 4a are kept in a non-contacting state therebetween.
In Case 2, a pressure distribution of working fluid is disturbed due to flowing of working fluid from a section of the divided portion into the leaf seal, as explained with reference to FIG. 10, concerning the problems of the conventional technique. This state will be explained with reference to FIGS. 3A and 3B. As shown in FIG. 3A, first, working fluid that has flowed inside the leaf seal 11 flows from the divided portion into the gap (the high-pressure gap X) between the high-pressure-side plate 15 and the thin plate edge 124 to enter along the high-pressure-side plate 15 in a circumferential direction. The working fluid that has entered to the inside forms a flow parallel to the rotor axial line a long the upper and lower faces of the thin plate 121 over an entire length of the thin plate 121, from the outer peripheral proximal end 122 of the thin plate edge 124 to the inner peripheral free end 123, to flow into fine gaps in the thin plate group 12 obtained by stacking the thin plates. In the conventional leaf seal explained with reference to FIG. 2A, working fluid flows in from the lower end of the high-pressure-side plate 15 to flow on the upper and lower faces of each thin plate while diffusing from the inner peripheral free end 123 to the outer peripheral proximal end. Therefore, a substantially triangular gas pressure distribution where gas pressure is the highest at the corner r1 and gradually lowers toward the diagonal corner r2 is formed, so that an upward floating force is generated. However, in Case 2 concerning a portion around the divided portion of the divided-type leaf seal, a gas pressure distribution similar to the above cannot be obtained.
That is, as shown in FIG. 3A, working fluid, forming a flow parallel to the rotor axial line along upper and lower faces of the thin plate 121 to flow into fine gaps in the thin plate group 12 obtained by stacking the thin plates, flows downward as a flow parallel to the rotor axial line along the upper and lower faces of the thin plate 121. However, when spacing on an outlet side of working fluid, namely, a spacing of the low-pressure gap adjacent to the low-pressure region is not sufficient, working fluid forms downward flow inside the thin plates due to an outlet side resistance, to flow out to the low-pressure region. That is, working fluid necessarily flows from the lower end of the high-pressure-side plate 15 to inside of the leaf seal 11 at a seal portion where no divided portion is provided in the circumferential direction. Therefore, if the gap (the low-pressure gap Y1) defined between the stator inner wall 5a and the thin plate edge 125 is secured, upward flow of working fluid is necessarily generated inside the respective thin plates, so that floating force is necessarily generated.
In the case of the divided-type leaf seal and around the divided portion, however, leakage of working fluid from a section of the divided portion cannot be suppressed. Therefore, upward flow of working fluid can not be generated or rather downward flow thereof is generated inside the thin plates. As a result, pressure becomes the highest at both the corner (r1) positioned at the outer peripheral proximal end 122 and the corner (r1) positioned at the inner peripheral free end 123 on the thin plate edge 124 adjacent to the high-pressure region. Although working fluid flows downward inside the thin plates and pressure lowers, downward flow is generated inside the thin plates. Therefore, when a gas pressure at the corner (r2) positioned on the outer peripheral proximal end 122 at the thin plate edge 125 facing the low-pressure region of the thin plate is compared with a gas pressure at the corner (r3) positioned at the inner peripheral free end 123 at the thin plate edge 125 facing the low-pressure region nearest to the outlet side, relationship of r1>r2>r3 can be obtained. Accordingly, as shown in FIG. 3B, a gas pressure distribution on the upper and lower faces of the thin plate 121 shows a substantially inverted triangular pressure distribution where pressure becomes the maximum at the outer peripheral proximal end 122 and becomes the minimum at the inner peripheral free end 123.
When working fluid shows such an inverted triangular pressure distribution, when gas pressures acting on the upper face 121a and the lower face 121b of the thin plate are represented as Fa and Fb, Fa<Fb is obtained. That is, assuming the relationship of Fx=Fa−Fb, Fx<0 is obtained so that a downward pressing force acts on the thin plate 121. In Case 1, since upward gas flow is generated on each thin plate 121, an upward force Fc acts on a distal end of the inner peripheral free end 123 due to gas pressure of combustion gas flowing between the rotor outer-surface 4a and the inner peripheral free end 123 of the thin plate 121. In the present Case, however, the downward pressing force Fx acts on each thin plate 121, as described above. Therefore, the distal end of the inner peripheral free end 123 comes in contact with the rotor outer-surface 4a, so that dynamic effect owing to working fluid between the rotor outer-surface 4a and the inner peripheral free end 123 cannot be expected. That is, in Case 2, since gas pressure acting on each thin plate 121 is generated by only Fa and Fb, assuming Fx=Fa−Fb, Fx<0 can be obtained. That is, a floating force is not generated on each thin plate 121, but a downward pressing force is generated thereon, so that the inner peripheral free end 123 of each thin plate is pressed on the rotor outer-surface 4a.
In Case 3, in order to solve the problems arising around the divided portion of the conventional leaf seal, the low-pressure gap in the low-pressure region around the divided portion is further enlarged to reduce the pressing force. Specifically, as shown in FIG. 4A, the annular recess 22 is provided on a face of the stator 5 opposed to the low-pressure-side plate 16, and the low-pressure gap (Y1) is expanded. As shown in FIG. 4A, when the low-pressure gap after expansion is represented as Y2, and when the low-pressure gap in the conventional leaf seal, in other words, between the stator inner wall 5a in the other seal portion in the circumferential direction, except for around the divided portion of the leaf seal, and the thin plate edge 125 is represented as Y1, the annular recess 22 is provided on the stator inner wall 5 to satisfy Y2>Y1>X. In FIG. 4A, the mounting piece is not assembled. However, when the mounting piece 21 is assembled, a substantially same concept can be applied by regarding the stator 5 and the stator inner wall 5a as the mounting piece 21 and the mounting piece inner wall 21a respectively.
At a portion around the divided portion of the leaf seal, by adopting the low-pressure gap (Y2) larger than the low-pressure gap (Y1) in the circumferential direction except for around the divided portion in this manner, working fluid flowing in from a section of the divided portion via the high-pressure gap (X) forms a flow approximately parallel to the rotor axial line, to flow downward on each thin plate in the low-pressure region. Therefore, downward flow is hardly generated inside the thin plates. That is, as shown in FIG. 4A, a flow line of working fluid becomes parallel to the rotor axial line. As shown in FIG. 4B, a gas pressure distribution on the upper and lower faces of each thin plate in this Case shows a substantially rectangular pressure distribution in sectional view orthogonal to the rotor axial line. That is, the fact that the flow line of working fluid forms the parallel flow means that pressure lowering of working fluid, from the thin plate edge 124 facing the high-pressure-side plate 15, becomes approximately equal at any point in any sectional view perpendicular to the rotor axial line of each thin plate. Therefore it can be said that a substantially constant pressure distribution is obtained from the outer peripheral proximal end 122 of the thin plate to the inner peripheral free end 123.
That is, around the divided portion of the leaf seal, when the low-pressure gap is set so that a flow line of working fluid on the upper and lower faces of the thin plate forms a parallel flow to the rotor axial line, and gas pressures acting on the upper face 121a and the lower face 121b of the thin plate are represented as Fa and Fb, both Fa and Fb are approximately equal pressures in a range from the outer peripheral proximal end 122 to the inner peripheral free end 123, thereby establishing a relationship of Fa=Fb. That is, neither floating force nor pressing force is generated on the thin plate 121. On the other hand, since dynamic pressure of working fluid following rotation acts on the lower end of the inner peripheral free end 123 upwardly, along with increase in the number of revolutions of the rotor 4, the thin plate 121 receives the floating force to be floated slightly. Therefore, neither a contact resistance between the rotor outer peripheral face 4a and the inner peripheral free end 123 nor a frictional resistance is generated.
A concept of an action and a function of the sealing mechanism in the seal portion except for around the divided portion can be considered the same as Case 1.
In order to exhibit the effect securely around the divided portion of the leaf seal, it is desirable that a width of the low-pressure gap (Y2) around the divided portion is at least 1.5 times a width of the low-pressure gap (Y1) in the circumferential direction except for around the divided portion. When a low-pressure gap of five times or more is provided, a leakage amount of working fluid from the low-pressure gap increases, which is undesirable regarding running cost. The present embodiment relates to the divided-type leaf seal, where the divided face can be provided in a plane including the rotor axial line or the divided face can have an inclination angle to the plane. The divided face is not necessarily flat, but may be curved.
A second embodiment of the present invention will be explained with reference to FIGS. 5 and 6. FIG. 5 is a perspective view of a shaft sealing mechanism including an integral leaf seal and not including any divided portions. In FIG. 5, a divided section is shown in order to show an internal structure, but an actual leaf seal is formed integrally, to have no divided portion. FIG. 6 depicts a structure for mounting the shaft sealing mechanism, including the integral leaf seal, on a stator. The second embodiment is different from the first embodiment in that the shaft sealing mechanism 11 does not have any divided portions and is formed integrally, but other constitutions are the same for the both embodiments. Regarding the structure for mounting the shaft sealing mechanism on the stator, the second embodiment is different from the first embodiment in that the annular recess 22 is not provided on the mounting piece 21, but other constitutions are the same for the both embodiments. Accordingly, explanation of a detailed constitution of this embodiment is omitted.
In the shaft sealing mechanism including such integral leaf seal, since there is no divided portion, leakage of working fluid from a section of the divided portion does not occur, a gas pressure distribution acting on each thin plate is stable, and an upward floating force always acts over the entire circumference of the shaft sealing mechanism. Therefore, since neither a contact resistance between the inner peripheral free end of the thin plate and the rotor outer peripheral face nor a frictional resistance is generated, the seal is prevented from wearing. Since mounting of the shaft sealing mechanism on the stator is completed by providing the recessed groove on the stator, fittingly inserting the shaft sealing mechanism into the recessed groove, and thereafter fitting the mounting piece in the remaining gap, assembling is facilitated.
A manufacturing method of the shaft sealing mechanism including a leaf seal will be explained next. The method is only one example and the present invention is not limited to this example. As shown in FIG. 7A, respective thin plates, produced by punching steel plates in a T-shape, are superimposed obliquely in a multi-layered manner, and outer peripheral proximal ends 122 thereof are joined together by welding. Specifically, as shown in FIG. 7B, outer peripheral proximal ends 122, and side ends 127a and 127b positioned on wider portions of the respective thin plates 121 are welded, and the joined thin plates are bent such that they can be easily inserted in the thin-plate holding ring. Next, as shown in FIG. 1, heads of the high-pressure-side plate 15 and the low-pressure-side plate 16 are inserted into a pair of receiving grooves 126 provided on both side edges of the respective thin plates, the thin plate group 12 is sandwiched by a pair of thin-plate holding rings 13a and 13b via a spacer 17, and the thin-plate holding rings 13a and 13b are welded to the spacer 17, so that the shaft sealing mechanism is completed. According to this method, since the high-pressure-side plate and the low-pressure-side plate are mounted precisely, adjustment of the high-pressure gap and the low-pressure gap is easy.
According to the present invention, at a portion around the divided portion of the shaft sealing mechanism having at least one divided portion, even when gas pressure distributions on the upper and lower faces of the thin plate is disturbed due to leakage of high pressure working fluid from a section of the divided portion, since the low-pressure gap at least around the divided portion of the shaft sealing mechanism is set to be larger than the remaining low-pressure gap in the circumferential direction except for the portion around the divided portion, a gas pressure distribution is improved around the divided portion. Therefore, there is no pressing force acting on the thin plate around the divided portion, and the thin plate is floated from the rotor outer-surface. Thus, the seal wearing and heat generation due to contact between the thin plate and the rotor outer-surface are prevented.
Furthermore, according to the present invention, at a portion around the divided portion of the shaft sealing mechanism having at least one divided portion, even when gas pressure distributions on the upper and lower faces of the thin plate is disturbed due to leakage of high pressure working fluid from a section of the divided portion, since the low-pressure gap at least around the divided portion of the shaft sealing mechanism is set to be larger than the low-pressure gap formed between the stator inner wall or the mounting piece inner wall and the thin plate edge opposed thereto, a gas pressure distribution is prevented from being disturbed even around the divided portion. Therefore, there is no pressing force acting on the thin plate group over a front periphery of the shaft sealing mechanism including the portion around the divided portion, so that the seal wearing can be prevented.
Moreover, according to the present invention, at a portion around the divided portion of the shaft sealing mechanism having at least one divided portion, even when gas pressure distributions on the upper and lower faces of the thin plate is disturbed due to leakage of high pressure working fluid from a section of the divided portion, since the low-pressure gap is set such that a pressing force does not act on the thin plate owing to a gas pressure distribution of the working fluid flowing downward on a surface of the thin plate around the divided portion of the shaft sealing mechanism, an upward floating force acts on the inner peripheral free end of the thin plate. That is, the low-pressure gap around the divided portion of the shaft sealing mechanism is set to be larger than the remaining low-pressure gap except for at least the portion around the divided portion. Therefore, a flowing line of working fluid flowing downward on the thin plate becomes parallel to the rotor axial line, so that a pressing force acting on the thin plate is not generated from the working fluid. Therefore, the thin plate is floated from the rotor outer-surface owing to a dynamic pressure effect at the inner peripheral free end of the thin plate, so that the seal wearing and heat generation due to contact between the seal and the rotor outer-surface are prevented.
Furthermore, according to the present invention, even when the shaft sealing mechanism has at least one divided portion, the low-pressure gap is further enlarged by providing the annular recess in the mounting piece so that a gas pressure distribution acting on the thin plate is improved. Therefore, there is no pressing force acting on the thin plate from working fluid, and a contact resistance generated between the inner peripheral free end of each thin plate and the rotor outer peripheral face is reduced, so that the seal wearing can be prevented. Heat generation due to the contact between the thin plate and the rotor, and generation of vibrations are prevented. After the shaft sealing mechanism is inserted in the recessed groove of the stator, the mounting piece is fittingly inserted into the gap of the stator to be fixed. Thus, the shaft sealing mechanism can be mounted easily.
Moreover, according to the present invention, the low-pressure gap can be set more efficiently by providing the recess extending from a height equal to the lower end of the low-pressure-side plate to the lower end of the mounting piece. Therefore, a stable pressure distribution can be obtained over the entire periphery of the shaft sealing mechanism. Since a range in which the low-pressure gap can be provided is limited, loss due to leakage of working fluid can be reduced.
Furthermore, according to the present invention, since the shaft sealing mechanism does not have any divided portion and is formed in an integral seal, high pressure wording fluid does not leak into the shaft sealing mechanism from a section of the divided portion. Therefore, pressure distributions of working fluid formed on the upper and the lower faces of each thin plate are stabilized over the entire periphery of the shaft sealing mechanism so that floating force always acts on the thin plate. Accordingly, a contact resistance between the rotor outer peripheral face and the inner peripheral free end of the thin plate is not generated so that the seal wearing is prevented.
Moreover, according to the present invention, the integral seal is adopted as the shaft sealing mechanism, and high pressure wording fluid does not leak into the shaft sealing mechanism from a section of the divided portion. Therefore, stable pressure distributions are obtained on the upper and lower faces of each thin plate over the entire periphery of the shaft sealing mechanism. Accordingly, a contact resistance between the rotor outer peripheral face and the inner peripheral free end of the thin plate is not generated. Since the mounting piece is fittingly inserted into the gap of the stator to be fixed to the stator, after the shaft sealing mechanism is inserted into the recessed groove of the stator, the shaft sealing mechanism can be mounted easily.
Furthermore, according to the present invention, since leakage of working fluid from the high-pressure region to the low-pressure region is reduced, the turbine can be stably operated for a long period, and running cost of the turbine can reduced.
Although the invention has been described with respect to a specific embodiment for a complete and clear disclosure, the appended claims are not to be thus limited but are to be construed as embodying all modifications and alternative constructions that may occur to one skilled in the art that fairly fall within the basic teaching herein set forth.
1. A shaft sealing mechanism of an annular shape having at least one divided portion, the shaft sealing mechanism being installed in an annular space between a rotor and a stator, the shaft sealing mechanism comprising a group of thin plates obtained by stacking a plurality of thin plates, wherein
outer peripheral ends of the thin plates are joined,
inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined, and
at least a low-pressure gap near the divided portion is set to be larger than a low-pressure gap in a circumferential direction other than near the divided portion.
at least a low-pressure gap near the divided portion is set to be larger than a gap between an inner wall of the stator or a mounting piece inner wall and edges of the thin plates.
at least a low-pressure gap is set near the divided portion in such a manner that a pressing force acting on the thin plates is not generated by working fluid flowing downward on surfaces of the thin plates.
4. A structure for mounting a shaft sealing mechanism of an annular shape on a stator, the shaft sealing mechanism being installed in an annular space between a rotor and the stator, wherein
the shaft sealing mechanism includes a group of thin plates obtained by stacking a plurality of thin plates,
inner peripheral free ends of the thin plates come in contact with the rotor in a sliding manner so that a surface of the rotor and the thin plates form an acute angle to partition the annular space into a high-pressure region and a low-pressure region without being joined,
a recessed groove that can accommodate the shaft sealing mechanism is formed on the stator,
a mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove, and
an annular recess is provided on a surface of the mounting piece opposite to a low-pressure-side plate.
5. The structure according to claim 4, wherein the annular recess is provided extending from a height equal to a lower end of the low-pressure-side plate to a lower end of the mounting piece.
6. A shaft sealing mechanism of an annular shape that is installed between a rotor and a stator, the shaft sealing mechanism comprising a group of thin plates obtained by stacking a plurality of thin plates, wherein
the shaft sealing mechanism is formed integrally without including a divided portion so that a pressing force acting on the thin plates is not generated by working fluid.
the shaft sealing mechanism is formed integrally without including a divided portion,
a recessed groove that can accommodate the shaft sealing mechanism is formed on the stator, and
a mounting piece is fittingly inserted into a gap generated after the shaft sealing mechanism is assembled to the recessed groove.
8. A turbine comprising a shaft sealing mechanism of an annular shape having at least one divided portion, wherein
the shaft sealing mechanism is installed in an annular space between a rotor and a stator,
10. A turbine comprising a shaft sealing mechanism of an annular shape having at least one divided portion, wherein
11. A turbine comprising a structure for mounting a shaft sealing mechanism of an annular shape on a stator, wherein
the shaft sealing mechanism is installed in an annular space between a rotor and the stator,
12. A turbine comprising a shaft sealing mechanism of an annular shape that is installed between a rotor and a stator, wherein
Filed: Aug 10, 2005
Inventors: Shin Nishimoto (Hyogo-ken), Tanehiro Shinohara (Hyogo-ken), Hidekazu Uehara (Hyogo-ken), Takashi Nakano (Hyogo-ken)
Current U.S. Class: 277/355.000
International Classification: F16J 15/44 (20060101);


text:
Q: How to copy a mysql table to another in cakephp? Can any one guide me for how can i copy one mysql table to another table in same database using cakephp please give me example query if possible.

A: create table new_table like your_table;
insert into new_table select * from your_table;

The above will keep index for new_table
create table new_table select * from your_table;

The above will not keep index.
There is nothing to do with cakephp, you just need the correct sql syntax,
plus relevant connection setting to allow php connect to mysql

A: If it's a quick and dirty one time copy, I'd just loop over the source table records and create new target records:
$source = $this->Source->find('all');
foreach($source as $sRec)
{
    $this->Target->create();
    $targetData = array();
    $target['Target']['field1'] = $sRec['Source']['field1'];
    $target['Target']['field2'] = $sRec['Source']['field2'];
    //etc
    $this->Target->save($targetData);
}

Apologies if it's buggy, I've just splurged it.
Edited to show row selection conditional. Something along the lines of:
$toCopy = array(1,32,71,72,73);
foreach($toCopy as $anId)
{
    $sRec = $this->Source->read(null,$anId);
    $this->Target->create();
    $targetData = array();
    $target['Target']['field1'] = $sRec['Source']['field1'];
    $target['Target']['field2'] = $sRec['Source']['field2'];
    //etc
    $this->Target->save($targetData);
}

redpajama_set_name: RedPajamaStackExchange


text:
Aport-212PG: Programmable platform for device networks
The new programmable device server Artila Aport-212PG from Acceed is well-equipped for the special communication tasks within future device networks. The energy-saving ARM Cortex M3 processor is the motor of the Ethernet serial converter. Its special feature is the integrated operating system FreeRTOS which supports 34 architectures and various compilation environments. FreeRTOS is perfectly geared to embedded microcontrollers and has proved its worth as a professionally developed and robust system in industrial and commercial environments.
Current developments under the keywords M2M, ZigBee or Industry 4.0 focus on network communication between devices. The so-called IoT (Internet of Things) incorporates a whole host of specialised end devices such as sensors, actors and controllers which are used equally in modern building management as in industrial plants, large-scale living environments and outdoor installations. End devices for light controls, thermostats, motion detectors, security sensors, switches, locks, pumps, meters and a lot more form a network within which the individual components should intercommunicate trouble-free and safely. The initial step is the transfer and concentration of serial data from the sensor via the TCP/IP protocol. Serial Ethernet converters such as the new Aport-212PG act as device servers here.
The Aport-212 has a Cortex-M3 processor with 100 MHz and is equipped with 64KB SRAM, 512KB flash, an 10/100 Mbps Ethernet interface as well as two RS-232/485 connections. The new converter supports lightweight IP (lwIP) and flexible and comfortable programming with the BSD Socket Library. A compact Web server for the customer's own Web-based applications is integrated. Sample programs for data communication, Web configuration and EEPROM routines are incorporated in the development kit, making starting-up fast easier. A special Windows Management utility for the functional overview, the configuration of the Aport-212PG and the transfer of firmware developed by the customer is also included in the scope of delivery.
Its development options alongside the energy-saving and low-service hardware make the Aport-212PG an ideal platform for the Internet of Devices and the communication of serial data in TCP/IP networks.

redpajama_set_name: RedPajamaCommonCrawl


text:
Harriett Baldwin welcomes co-operation between UK and Ukraine on defence
Harriett Baldwin welcomes the defence memorandum of implementation between the UK and Ukraine and urges the Government not to be deterred by Russia's recent attempts at intimidation in the Black sea.
I welcome the defence memorandum of implementation signed between the UK and Ukraine, which will see our two countries working together on new Ukrainian naval bases and eight fast missile warships. Can the Secretary of State confirm that we will not be deterred, and the Royal Navy will not be deterred, by Russia's recent attempts at intimidation in the Black sea? (902231)
Mr Wallace (The Secretary of State for Defence)
My hon. Friend is right to highlight the real importance that we attach to Ukraine as a friend and a partner, and to reiterate the fact that the Royal Navy will always uphold international law and will not be deterred by bullying. The transit by HMS Defender was through Ukrainian waters; we do not recognise Russia's claim on Crimea. Our Navy will continue to uphold the rule of law wherever she sails.


text:
Q: How to make Visual Studio debug session launch a cmd.exe replacement? Can I somehow setup visual studio to launch a cmd.exe replacement (on this case TCC/LE, from JP Software) console when debugging console applications?
I have it setup on the Tools Menu as an External tool with a start directory pointing to the project debug bin folder. But I'd like a more immediate access, just so hitting the F5 key (Start Debugging) would launch the application in this cmd.exe replacement instead.

A: In the project properties for your console project select the debug tab. There are 3 radiobuttons there that specify how the project is started when you hit 'F5'. The default value is 'start project' in your case I assume you need to select 'start external program' and specify your cmd replacement with any arguments to get the debug app launched from it.
For cmd.exe it would be the /c or /k option to launch something else from the command shell.

A: I use Clink.
It doesn't replace cmd.exe, but makes it something I can very much live with. By using Clink, I don't need to worry about injecting an alternative. Instead, cmd.exe works mostly as I'd like it to.


text:
Executive Vice President and Chief Business Strategy Officer
As executive vice president and chief business strategy officer, Richard Miller evaluates Northwell Health's business strategy and organizational decision-making. He oversees revenue optimization and commercial investments, as well as ensures that financial strategies align with organizational strategies.
Mr. Miller was previously deputy chief financial officer, business strategy, and senior vice president, payer relations and contract development, where he oversaw contracting and business development strategies, payer relations and contract negotiations, health care economics and analytics, and value-based contracting.
Mr. Miller serves as a chairman of the Northwell Health Plans Holding Company and on external boards and advisory committees, such as the Nassau Queens Performing Provider System, Optum 360 and Healthfirst Finance Committee.
Mr. Miller joined Northwell in 2008 as vice president, financial planning before assuming his the position of senior vice president in 2013. Prior to Northwell, Mr. Miller was CFO for NYU Hospitals Center from 2001-2008. He previously was vice president, finance for NYU Hospitals Center and the Hospital For Joint Diseases.
Holding an MBA from the Stern School of Business of New York University and a BBA from Bernard Baruch College, Mr. Miller is on the faculty of St. Joseph's College, New York, where he teaches a graduate course on health care finance.
The latest news for Richard Miller
From cost-cutting to solid margins
Modern Healthcare covers a panel featuring Richard Miller, who talks about fighting insurance denials.
Translate hospital price list into plain English (commentary)
Rich Miller tells the Staten Island Advance the federal government's transparent pricing wasn't intended to be a price list for procedures.
Northwell offers financial support during federal shutdown
Northwell Health will work with government employees feeling the financial effects of the federal shutdown by offering payment flexibility for patient billing.
Hospitals federally required to post full prices on their websites
Rich Miller, EVP and chief business strategy officer at Northwell, discusses how online costs don't tell the whole story in a report by AARP.


Come May, Meghan Markle is reportedly planning to break with the tradition for royal brides by making a Speech at her own wedding reception.
A YouGov poll from 2016 found that only 16% of those surveyed thought the bride should give a speech at her wedding.
Make that 16% plus one.


text:
Samuelsson scores 2, Osgood stops 19 in Wings win
IRA PODELL
DETROIT - It's no surprise the Detroit Red Wings have a Swede to thank for a prime-time performance, but Mikael Samuelsson?
The demoted forward busted out of a slump with two goals, and Chris Osgood stifled the Pittsburgh Penguins' young and talented stable of forwards with 19 saves to lift the Red Wings to a 4-0 victory in the opening game of the Stanley Cup finals on Saturday night.
Samuelsson doubled his playoff goal total with two in the biggest game of his five-season NHL career. He had been dropped to Detroit's third line earlier in the playoffs and had posted only two assists since his two-goal outburst on May 1.
"I just live in the moment," said Samuelsson, who scored two goals in 22 games during the 2002-03 season with the Penguins. "We played good as a team. I'm lucky to be the one who scored a couple of goals."
Detroit overpowered goalie Marc-Andre Fleury with a 36-shot barrage. Osgood has two postseason shutouts this season and 12 in his playoff career.
Game 2 is Monday night in Detroit.
The Red Wings are led by a collection of seven Swedes, most notably captain Nicklas Lidstrom on defense and key forwards Henrik Zetterberg and Johan Franzen.
With Samuelsson finding his scoring touch, it didn't matter that Franzen - tied with Zetterberg for the NHL lead with 12 postseason goals - missed his sixth straight game due to recurring headaches. He seems close to returning, and that could pose big problems for the Penguins, who fell to 12-3 in the playoffs.
Pittsburgh raced out to 3-0 leads in each of the first three rounds - all started in the Steel City - and didn't drop more than one game to any opponent. Detroit, however, kept Penguins captain Sidney Crosby in check along with the rest of Pittsburgh's 20-somethings and under.
In a series billed as a matchup between Penguins' youth and Red Wings' experience, Detroit claimed the first strike. The Presidents' Trophy-winning Red Wings are 13-4 in the playoffs and three wins away from their third Stanley Cup title in 11 seasons.
Samuelsson needed no help as both of his goals were unassisted. He bailed out fellow Swede Tomas Holmstrom, who was whistled for interference on Fleury that negated a goal by Lidstrom that would have been the game's first score.
Samuelsson broke the tie in the second period, picking off an errant pass on the far side of center ice and taking it all the way with 6:59 left in the first.
It was Samuelsson's first goal in seven games, dating to the series-clinching Game 4 win over Colorado.
"He didn't score here lately, but he got an assist his last game," Red Wings coach Mike Babcock said. "Sammy is kind of a streak guy. When he scores he feels good about himself."
Samuelsson netted his second 2:16 into the third when Pittsburgh's Rob Scuderi and Evgeni Malkin took turns fumbling the puck. Samuelsson got it and was alone at the top of the crease for the goal. Dan Cleary added a short-handed goal with 2:42 left and Fleury's rough night got worse when he was beaten by Zetterberg for a power-play goal with 12 seconds remaining.
Osgood withstood a 12-shot first period from the Penguins, who generated eight shots in the frame during four fruitless power plays. At even strength, Pittsburgh managed only eight shots through two periods.
Detroit clamped down in the second and held a 16-4 shots advantage during the frame and 27-16 through 40 minutes.
"We just have to be a little smarter and a little more disciplined and move the puck quicker and play in their end more and we'll be all right," Penguins defenseman Hal Gill said.
The Red Wings had already been whistled for three penalties in the entertaining first period when Holmstrom was sent to the box for a second time and wiped out Lidstrom's goal.
Lidstrom ripped a drive from Fleury's left as Holmstrom cut across the top of the crease and smacked the goalie's feet with his stick with 4:40 left in the first. The puck sailed into the net, drawing a huge roar from the crowd that didn't see referee Dan O'Halloran emphatically waving off the first goal of the highly anticipated series.
Babcock demanded an explanation at the bench during the ensuing commercial break and then cursed at O'Halloran once he heard it. The call was reminiscent of one against Holmstrom in Game 4 of the Western Conference finals that also cost the Red Wings a goal in a loss to Dallas.
"That's the rule, you can't put your stick in the crease now?" Babcock said. "Did they change that when I wasn't watching? Did he touch his pads in any way or interfere with him in any way?
"They've got to decide. I just coach the game. I don't get to referee it."
Osgood stopped a five-shot flurry during a first-period power play, lunged with his arm to knock the puck off the stick of Marian Hossa, and turned aside a partial breakaway by Pascal Dupuis.
Osgood, who backstopped Detroit's Stanley Cup run in 1998, is 11-2 since taking over from Dominik Hasek in the first round and has allowed only 20 goals in 14 games.
Notes: Pittsburgh has been shut out in two of its three playoff losses. ... Detroit leads the all-time series 60-57 with 16 ties. This is the clubs' first postseason meeting. ... The Penguins haven't won in Detroit since Dec. 10, 2000. ... Each team's captain was whistled for rare penalties. Lidstrom went off for holding in the first period and interference in the third, giving him 14 penalty minutes in these playoffs and 64 overall in 209 career postseason games. Crosby's slashing infraction in the second gave him 10 minutes in 15 playoff games this year.


text:
The main repository have been moved to [wsdl2phpgenerator/wsdl2phpgenerator](https://github.com/wsdl2phpgenerator/wsdl2phpgenerator)

[![Build Status](https://travis-ci.org/reload/wsdl2phpgenerator.png?branch=master)](https://travis-ci.org/reload/wsdl2phpgenerator)
[![Coverage Status](https://coveralls.io/repos/reload/wsdl2phpgenerator/badge.png?branch=code-coverage-coveralls)](https://coveralls.io/r/reload/wsdl2phpgenerator?branch=code-coverage-coveralls)

Simple WSDL to PHP classes converter. Takes a WSDL file and outputs class files ready to use.

Uses the [MIT licence](http://www.opensource.org/licenses/mit-license.php)

## Contributors
Originally developed by Fredrik Wallgren, https://github.com/walle/wsdl2phpgenerator

Includes bugfixes and improvements from:

* Vardan Akopian, https://github.com/vakopian/wsdl2phpgenerator
* http://www.statik.be, https://github.com/statikbe/wsdl2phpgenerator
* Eric Colinet, https://github.com/ecolinet/wsdl2phpgenerator
* Nuth, https://github.com/nuth/wsdl2phpgenerator
* Kasper Garnæs, https://github.com/kasperg/wsdl2phpgenerator

This fork has been created in an attempt to merge changes in forks of wsdl2phpgenerator which has never made it back into the original repository.

Pull requests are very welcome.

## Usage
Use the executable or the Generator class directly.

### Executable
`./wsdl2php -i input.wsdl -o /tmp/my/directory/wsdl`

The directory is created if possible.

usage listed under `./wsdl2php -h`

### Code

```php
<?php
require_once __DIR__."/path/here/Generator.php";

$generator = Generator::instance();
$generator->setDisplayCallback( function( $msg ) {
	echo "{$msg}\n";
});
$generator->generate(
	new Config( SOAPSERVICE, SOAPDIR )
);
?>
```

redpajama_set_name: RedPajamaGithub


text:
No Trespass Claim Where Unmanned Truck Rolled Into House
Where defendants' truck rolled into a duplex owned by plaintiff causing real property damage, a directed verdict for defendants on all but plaintiff's negligence claim as well as a jury verdict for diminution in value to the property was affirmed.
In Twenty Holdings, LLC v. Land South LLC and Brandon Majors, No. M2018-01903-COA-R3-CV (Tenn. Ct. App. Sept. 5, 2019), plaintiff owned a duplex in Nashville, and defendant Majors lived nearby. Majors drove a tractor trailer truck for defendant Land South, and on the day of the incident, he "parked the truck, with an attached 53 foot trailer…, near his residence at the top of a steep hill with the front of the truck pointing toward the drop off of the hill and toward Plaintiff's property." Within hours of the truck being parked, it rolled down the hill. The trailer detached from the truck, but the truck portion struck the duplex and stopped in one of the living rooms, causing significant damage to the building. According to Majors, he had parked the truck on a safe area and "took various precautions in securing the tractor-trailer, including engaging the parking brake, placing garden timbers under the wheels, letting the trailer down, and placing the tractor-trailer in reverse."
Plaintiff filed a complaint against defendant driver and his employer for negligence, gross negligence, recklessness, trespass, negligent hiring, negligent entrustment, and punitive damages. After several evidentiary disputes and motions in limine, this case proceeded to a jury trial. At the close of plaintiff's proof, the trial court directed a verdict for defendant on all claims except the negligence claim. Later, the jury returned a verdict for plaintiff for $185,000 for the diminution in value to the real property. On appeal, the Court of Appeals affirmed all the rulings.
In a lengthy opinion, the Court analyzed several issues raised by the parties. First, the Court addressed plaintiff's argument that the trial court erred by failing to determine whether the truck was a commercial or farm vehicle and excluding evidence about whether defendant kept appropriate records for a commercial vehicle. The background on this issue was extensive—the trial court had initially made a spoliation ruling based on the sale of the truck, but had later modified that ruling. Plaintiff asserted that it should have been allowed to introduce evidence regarding defendant's record keeping after the modification of the spoliation ruling, but the transcript revealed that when plaintiff made this argument during the trial and was faced with the prospect of either getting to go to trial and not present evidence about record keeping or take a mistrial, plaintiff chose to go to trial. The Court stated that "where a party could have nullified an error by taking an offered mistrial, the party [is] not entitled to appellate relief." (internal citation omitted). Because plaintiff declined the mistrial and chose to move forward with the trial, no relief could be granted on this issue.
Next, plaintiff asserted that the trial court wrongly directed a verdict for defendants on the trespass claim. While plaintiff presented evidence from an investigating police officer that Majors did not engage the brakes when parking the truck, the trial court found that such a conclusion was beyond the officer's expertise and specifically did not accept his opinion. Accordingly, the trial court found, and the Court of Appeals agreed, that there were no facts upon which to base a trespass claim. Trespass is an intentional tort, and while the tortfeasor does not have to have the intent to specifically trespass, such a claim "requires the intentional entry onto the land of another." (internal citation and quotation omitted). "Here, defendants did not drive the tractor-trailer onto plaintiff's property, but the truck rolled down the hill unmanned. Whether by simple negligence or more reckless nonfeasance, the intrusion on plaintiff's property was not a voluntary act by defendants." The Court noted that there was no precedent to hold a defendant liable for trespass "where an object enters the property of the plaintiff without an intent on the part of the object's owner/operator to perform the physical act that results in the invasion," and the ruling for defendants was affirmed.
The next issue raised by plaintiff was that the trial court erred in its ruling regarding spoliation of evidence. In its brief, however, plaintiff failed to cite to any legal authority on this issue (other than to the applicable standard of review). "In the absence of appropriate legal authority to support this argument," it was deemed waived on appeal.
The Court next analyzed plaintiff's assertion that the trial court erred by directing a verdict on its claims for recklessness and gross negligence. As an initial matter, the Court noted that the trial court's rulings on these claims was "rather deficient," but that "the trial court is not required under Rule 50.01 to make specific findings to support its directed verdict ruling," and that plaintiff made no objection to the rulings during the trial. As to the whether the rulings were correct, the Court found that "even taking the cited evidence in the light most favorable to plaintiff, we cannot conclude that Defendants' conduct meets the high standard required of either gross negligence or recklessness." Majors testified about several precautions he took when parking the truck, and though the police officer speculated that the brakes may not have actually been set, "the evidence supporting the plaintiff's verdict must be more than mere speculation or a glimmer of evidence." (internal citation omitted). The Court ruled that, "given the multiple steps taken by Mr. Majors to secure the tractor-trailer, it cannot be said that he consciously disregarded a substantial and unjustifiable risk."
Plaintiff also took issue with the trial court's directed verdict on its claims of negligent hiring and negligent entrustment. The Court of Appeals noted, though, that while plaintiff spent "considerable time it its brief on the question of whether Land South engaged in a sufficient investigation of Mr. Majors at the time of his hiring and when he was entrusted with the tractor-trailer, Plaintiff points to no evidence in the record to show that at the time of hiring or entrustment, Mr. Majors was in fact unfit for his job, posed an unreasonable risk to others, or was in any way incompetent to operate the tractor-trailer." (internal citation omitted). The only evidence presented regarding his fitness was that his CDL license was suspended for unpaid speeding tickets, but this occurred after the incident in question and thus could not be the basis for these claims.
Plaintiff likewise took issue with the directed verdict for punitive damages, but because the Court affirmed the rulings on trespass, recklessness, and gross negligence, this ruling was also affirmed, as "simple negligence is generally held insufficient to support an award of punitive damages." (internal citation omitted).
The next issue addressed by the Court of Appeals was the method by which damages were determined. In a case involving damages to real property, the measure of damages varies depending on whether the damages are permanent or temporary. Whether the damage is permanent or temporary is a question of fact. (internal citations omitted). In this case, the trial court gave the jury multiple instructions, including one about calculating damages for a permanent injury to real property and one about calculating damages for a temporary injury to real property. In addition, the instructions also included a Tennessee Pattern Jury Instruction stating that the "measure of damage to real property is the lesser of the following: 1) The reasonable cost of repairing the damage to the property; or 2) the difference between the fair market value of the premises immediately prior to and immediately after the damage." Plaintiff argued that these instructions were conflicting, but the Court of Appeals disagreed. The Court found that "the instructions were appropriate as they contain a substantially accurate statement of Tennessee law on this subject and were not misleading to the jury." The Court stated that "the instructions clearly indicated that the jury was required to make a determination as to whether the injury to the property was permanent or temporary, and reflected Tennessee law that the jury should also consider whether the cost of repairing the injury was more than the difference in value to the property as a result of the injury." Further, the Court found that the jury's verdict, which was between the amount requested by plaintiff and the evidence of diminution in value presented by defendant, was "well within the range of values submitted at trial."
Finally, plaintiff argued that rather than 5% prejudgment interest, the trial court should have awarded the maximum allowed (10%). The Court of Appeals noted, though, that prejudgment interest is in the discretion of the trial court. Here, "though it was certain that the defendant could be liable for some amount of compensatory damages, the amount was uncertain and both sides had reputable experts on the issue of damages." The Court ruled that based on all the facts at play here, including the fact that defendant did not admit liability until the day before the trial but also that there was a reasonable dispute as to the amount of damages in this case, the trial court did not abuse its discretion by awarding 5% instead of 10%.
Having concluded that the trial court did not err on any of the issues being appealed, the verdict was affirmed.
This opinion covered lots of issues, but a few big takeaways are: 1) trespass requires some intentional act, 2) a plaintiff can't refuse a mistrial over an issue then later seek appellate relief for that same issue, and 3) an appellant must cite authority in its brief for each issue that it seeks to raise on appeal.
NOTE: To aid lawyers in giving clients guidance about how long it takes to receive an opinion after oral argument in the appellate courts, we are going to start sharing that information with readers. Please understand that the length of time that elapses between oral argument and the date the opinion is released is dependent on a multitude of factors, not the least of which is the complexity of the issues presented. In this case, the opinion was released less than eight weeks after oral argument.
Posted in: Miscellaneous and Uncategorized
Updated: September 23, 2019 7:12 am


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7th Rangers: Slow Joe Biden Urges Downplaying the Jihad Threat and Enabling Stealth Jihadis
Slow Joe Biden Urges Downplaying the Jihad Threat and Enabling Stealth Jihadis
Slow Joe Biden with the Nigga Berak Obummer
Jihad Watch : President Trump has a very clear idea of what a Joe Biden presidency would mean for America's security in the face of of the Islamic jihad terror threat.
"Biden," Trump said at a rally in Tampa on Thursday, "wants to terminate our travel bans and surge refugees from the most dangerous places in the world. He will open the floodgate to radical Islamic terrorism – and you saw three days ago what happened the beheading in France, and today it happened again." Trump was referring to the beheading of French teacher Samuel Paty for showing a Muhammad cartoon, and the beheading Thursday of a woman in a Lyons church in yet another jihad attack.
"Under the Biden plan," Trump warned, "the horrifying attacks in France will come to our cities and our towns….These Radical Islamic terrorist attacks must stop immediately. No country, France or otherwise, can long put up with it!"
Trump had a point. After the latest attack in France, Biden said Friday: "A Biden-Harris administration will work with our allies and partners to prevent extremist violence in all forms." The fact that he did not name jihad violence specifically was portentous. On October 15, Biden released a video message to Muslim Advocates, the association of Muslim lawyers that bears the primary responsibility for demanding, back in 2010, that the Obama administration remove all mention of Islam and jihad from counterterror training and refer to an undefined "extremism" rather than to jihad terrorism. Obama, of course, immediately complied, despite the fact that this would hamstring the ability of law enforcement and intelligence agencies to understand, and defeat, jihadists.
Biden also declared: "As president, I'll work with you to rip the poison of hate from our society, honor your contributions and seek your ideas. My administration will look like America, Muslim Americans serving at every level."
This was not reassuring, but ominous in light another Biden engagement with Muslims last summer. Biden stated last July: "One of the things I think is important, I wish we taught more in our schools about the Islamic faith." He clearly mean apologetic information, not accurate discussion of Islamic jihad activity. Even worse, Biden's call for this came as he addressed the "Million Muslim Votes Summit," a call hosted by Emgage Action, which says it is the largest Muslim PAC in the United States. According to the Washington Free Beacon, it is also "a George Soros-backed Muslim group" that serves as an "official cohost of Islamic Society of North America (ISNA) conferences. ISNA was previously revealed to be part of the Muslim Brotherhood network—though it claims it is no longer associated with the group."
Would Emgage or groups like it be tasked with choosing the Muslims who would staff Biden's administration? Almost certainly.
Biden made a promise that Trump referred to on Thursday: "If I have the honor of being president, I will end the Muslim ban on day one, day one." There is no "Muslim ban," but Islamic supremacists and their Leftist allies insist on calling the Trump administration's travel bans on nationals from 13 countries a "Muslim ban," even though five of those countries, Burma, Eritrea, Tanzania, North Korea, and Venezuela, are not Muslim countries, and there are 49 other Muslim countries upon which there is no ban at all.
The ban exists because these countries cannot or will not provide accurate information about prospective immigrants. The list of countries was devised during the Obama administration, while Biden was vice president. But that didn't stop Biden from casting it in racial terms, declaring: "Muslim communities were the first to feel Donald Trump's assault on black and brown communities in this country with his vile Muslim ban."
It's a peculiar "assault on black and brown communities" that leaves untouched scores of countries inhabited by "black and brown communities," but the Left is working on the gut level of rage and hatred, not rational consideration. This kind of language from Biden is also extraordinarily irresponsible, stoking racial resentment at a time when racial tensions are high.
Internationally, Palestinian leaders have repeatedly expressed their preference for Biden, hoping that if he is elected, the Trump-brokered peace deals between Israel and several Muslim Arab states will be repudiated, and their jihad against Israel will gain a renewed impetus.
Biden appears to accept the post-9/11 contention of Leftists and Islamic supremacists alike: that opposition to jihad violence and Sharia oppression of women is "hate." As a result, a Biden/Harris administration would almost certainly leave America more vulnerable to jihad attacks, and do nothing to halt the expanding influence of Sharia in the workplace and the educational system.
As Palestinian leaders have shown, Biden presidency would be welcomed by jihadis worldwide.
posted by Major D Swami (Retired) @ 12:56 PM
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Patrick Schmidt grew up in Los Angeles. He studied psychology at California State University and French literature at L'Université de Strasbourg. His professional international career started in Germany. He then moved to Malaysia. Later, he lived in Canada, then in Austria and currently he has settled in Strasbourg.
Before Patrick Schmidt became self-employed as a trainer, which also makes him part of the CONTUR GmbH network, he designed and conducted numerous international trainings at the Institute of Technology in Karlsruhe. He has also taught international negotiation and sales management at the Ecole de Management in Strasbourg and at the Vienna University of Economics and Business Administration.
As a freelance trainer, he works for many well-known companies and has already gained many years of experience in his field. As a freelance trainer at CONTUR GmbH, Patrick Schmidt primarily conducts trainings on team development and U.S.-German business relations. He also gives intercultural coaching sessions.
Based on his many professional experiences and knowledge, Patrick Schmidt has written three books: "Understanding American and German Business Cultures", "In Search of Intercultural Understanding", "Dancing to a Different Tune". He is also an active member of SIETAR (The society for intercultural education, training and research) for many years.