JP2004270523A - Rotary fluid-machinery - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure sealing properties by allowing a valve-plate on a fixed side to follow up runouts of the sliding face of a rotary valve of a rotary fluid-machinery. <P>SOLUTION: A rotary valve 71 performs switching between supply paths P1, P2 and discharge paths P5-P8 of high temperature, high pressure steam to a rotor rotatably supported on a casing. In the valve 71, a fixed-side valve-plate 73 and a moving-side valve plate 74 are brought into contact with each other at a sliding surface 77. A pressure chamber 84 is made open on the contact face 83 to the fixed-side valve plate 73 of a valve body 72 so as to conduct high temperature, high pressure steam from the supply path P1. In order to bring the sliding surface 77 into intimate contact, the fixed-side valve plate 73 supported floatingly is brought into press-contact with the moving-side valve-plate 74 by the press load generated in the pressure chamber 84. Escape of high temperature, high pressure steam from the pressure chamber 84 is prevented by placing a V-packing 88 in the inside of the pressure chamber 84. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a casing, a rotor rotatably supported by the casing, an operating portion provided on the rotor, and a rotary valve provided between the casing and the rotor to control supply and discharge of a working medium to and from the operating portion. And a rotary fluid machine having the same.
[0002]
[Prior art]
In a rotary fluid machine that supplies combustion gas generated in a combustor to an axial piston cylinder group via a distribution mechanism (rotary valve), the combustion gas is generated in order to ensure the sealing performance of the sliding surface (valve seat) of the distribution mechanism. When not supplied, the pressing member is pressed by a spring to adhere to the sliding surface, and when the combustion gas is supplied, the pressure member presses the pressing member via the free piston through the free piston to adhere to the sliding surface. These are known from the following patent documents.
[0003]
[Patent Document]
Japanese Utility Model Publication No. 61-155610
[0004]
[Problems to be solved by the invention]
By the way, since the rotor supported by the ball bearing in the casing generates a slight run-out when rotating, it is inevitable that the run-out also occurs on the sliding surface of the rotary valve. At this time, simply pressing the pressing member with the spring force of the spring, the pressure of the combustion gas, the pressure of the high-temperature and high-pressure supply gas or the pressure of the steam to bring the pressing member into close contact with the sliding surface will cause the deflection of the pressing member. It is difficult to ensure the sealing performance by following the above.
[0005]
The present invention has been made in view of the above-described circumstances, and has as its object to ensure the sealing performance by causing a fixed-side valve plate to follow a runout of a sliding surface of a rotary valve of a rotary fluid machine.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, according to the invention described in claim 1, a casing, a rotor rotatably supported by the casing, an operating portion provided on the rotor, and a casing provided between the casing and the rotor are provided. A rotary valve for switching a supply passage and a discharge passage of the working medium to the operating portion.The rotary valve is non-rotatably floating supported by a movable valve plate provided on the rotor and a valve body fixed to the casing. In the rotary fluid machine having the fixed side valve plate and the fixed side valve plate in contact with each other on a sliding surface orthogonal to the axis, the supply passage and the discharge passage of the working medium are provided on the mating surface of the valve body with the fixed side valve plate. A pressure chamber for introducing the working medium is opened from the passage on the high pressure side of the pressure chamber. A rotary fluid machine is proposed, which seals leakage of the working medium from the chamber to the mating surface and presses the fixed-side valve plate toward the sliding surface with the pressure of the working medium acting on the pressure chamber. You.
[0007]
According to the above configuration, the fixed-side valve plate is non-rotatably floatingly supported on the valve body fixed to the casing, and the high-pressure chamber is formed in the valve body so as to open at the mating surface with the fixed-side valve plate. Since the working medium is supplied and the mating surface is sealed by the seal member to receive the high pressure of the working medium, the fixed side valve plate is pressed against the sliding surface with the movable side valve plate by the pressure of the working medium in the pressure chamber. A pressing load is generated, and the sliding surfaces thereof are brought into close contact to prevent leakage of the working medium. In addition, the floating valve supports the fixed-side valve plate to follow the runout of the sliding surface, so that the followability of the pressing load to the sliding surface is enhanced, and the sealing performance of the sliding surface can be ensured.
[0008]
In particular, when leakage from the sliding surface is likely to occur due to high pressure of the working medium, the pressing load generated by the pressure chamber increases accordingly, so that even if the pressure of the working medium fluctuates, the sliding surface While preventing the leakage of the working medium by always generating the optimum surface pressure, it is possible to prevent the surface pressure from excessively increasing and minimize the frictional resistance of the sliding surface.
[0009]
Moreover, since the seal between the fixed side valve plate floatingly supported by the valve body and the pressure chamber is sealed by a sealing member to prevent leakage of the working medium, the pressing load generated by the pressure chamber can be stabilized, and Since the fixed-side valve plate can move in the axial direction and the radial direction, it can follow the inclination of the sliding surface by oscillating while securing the sealing performance.
[0010]
According to the second aspect of the present invention, in addition to the configuration of the first aspect, the seal member has a seal lip that can be elastically deformed by softening due to pressure and heat of the working medium. A machine is proposed.
[0011]
According to the above configuration, since the seal member has the seal lip which is elastically deformed by softening due to the pressure and heat of the working medium, the seal lip is deformed in accordance with an increase in the pressure of the working medium and an increase in the temperature to further improve the sealing property. And can move axially with low friction due to the shape of the seal lip.
[0012]
According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, an elastic urging means for urging the seal member toward the mating surface is provided. Rotary fluid machine is proposed.
[0013]
According to the above configuration, since the seal member is urged toward the mating surface with the fixed side valve plate by the elastic urging means, the seal member is urged when the pressure of the working medium has not risen to achieve the sealing property. In addition, the vibration of the fixed side valve plate accompanying the runout of the sliding surface is attenuated by the elastic force of the elastic urging means in accordance with the damping characteristics of the seal member, and the adhesion of the sliding surface is improved. Can be secured.
[0014]
According to a fourth aspect of the invention, in addition to the configuration of the third aspect, there is proposed a rotary fluid machine characterized in that the resilient biasing means is a tapered coil spring tapering toward the seal member. Is done.
[0015]
According to the above configuration, since the resilient urging means is constituted by the tapered coil spring tapering toward the seal member, the alignment of the tapered coil spring reduces the deflection of the sliding surface generated by the movable valve plate. The fixed-side valve plate swings around the axis to follow the swinging motion of the fixed-side valve plate, which is different from that of the fixed-side valve plate. It can be secured effectively.
[0016]
According to the invention described in claim 5, in addition to the configuration according to any one of claims 1 to 4, a low-temperature side passage among the supply passage and the discharge passage of the working medium is provided in the valve body. And an annular pressure chamber is formed so as to surround the periphery of the low-temperature side passage.
[0017]
According to the above configuration, since the annular pressure chamber is formed so as to surround the periphery of the passage of the low-temperature side working medium provided in the center of the valve body, the temperature rise of the sealing member housed in the pressure chamber is suppressed and the sealing is performed. Sex can be maintained. In addition, the fixed-side valve plate and the movable-side valve plate can be effectively cooled with the low-temperature side working medium, so that the smoothness and wear resistance of the sliding surface can be maintained.
[0018]
According to the invention described in claim 6, in addition to the configuration according to any one of claims 1 to 4, the high pressure side passage among the supply passage and the discharge passage for the working medium is provided in the valve body. A rotary fluid machine is provided, which is provided in the center of a rotary fluid machine and has an annular pressure chamber surrounding the periphery of the high-pressure side passage.
[0019]
According to the above configuration, since the annular pressure chamber is formed so as to surround the passage of the high-pressure side working medium provided at the center of the valve body, the pressing load generated in the pressure chamber is uniformly applied to the sliding surface. Can work. Thus, even if the pressure chamber is downsized and the pressing load is set to be small, it is possible to secure the adhesion of the sliding surface and prevent uneven wear, and to appropriately minimize the pressing load on the sliding surface. Therefore, the frictional resistance generated on the sliding surface can be reduced, and the loss torque of the rotary fluid machine can be reduced.
[0020]
According to the seventh aspect of the present invention, in addition to the configuration of any one of the first to fourth aspects, the seal member seals the space between the fixed side valve plate and the first side. And a second seal lip for sealing between the seal lip and the inner peripheral surface of the pressure chamber.
[0021]
According to the above configuration, the first seal lip of the seal member seals between the mating surface of the fixed-side valve plate and the second seal lip seals with the inner peripheral surface of the pressure chamber. The sealing of the chamber can be maintained, and in particular, the second sealing lip can be configured such that the second sealing lip has an inner circumferential surface of the pressure chamber against the fluctuation of the pressure of the working medium and the axial and radial displacement of the fixed-side valve plate due to its lip structure. The sealing property can be enhanced by closely following the surface with good followability.
[0022]
According to the invention described in claim 8, in addition to the configuration according to any one of claims 1 to 4, the first sealing member seals a gap between the fixed member and the mating surface of the valve plate. And a second seal lip for sealing between the seal lip of the above and the outer peripheral surface of the working medium pipe inserted into the pressure chamber.
[0023]
According to the above configuration, the first seal lip of the seal member seals between the mating surface of the fixed valve plate and the second seal lip of the working medium pipe inserted into the pressure chamber from the lip structure. It can follow the radial thermal elongation caused by the high temperature working medium, seal the space between the working medium pipe and the outer peripheral surface, and maintain the tightness of the pressure chamber. Seals the outer peripheral surface of the working medium pipe, which has a smaller diameter than the inner peripheral surface, so that the seal lip is in line contact in the radial direction, reducing the frictional resistance of the seal and smoothly following the thermal expansion of the working medium pipe Further, the fixed valve plate can follow the axial and radial swinging movement of the sliding surface about the seal member.
[0024]
According to the ninth aspect of the present invention, in addition to the configuration of any one of the first to fourth aspects, in addition to the area of the sliding surface, the area of the pressure chamber pressure acting on the mating surface with respect to the area of the sliding surface. A rotary fluid machine characterized by setting the surface pressure of a sliding surface by a ratio is proposed.
[0025]
According to the above configuration, the surface pressure of the sliding surface is set by the ratio of the area of the pressure chamber acting on the mating surface to the area of the sliding surface. An optimal surface pressure that can reduce the frictional resistance of the moving surface can be obtained.
[0026]
The axial piston cylinder group 56 of the embodiment corresponds to the operating portion of the present invention, the coil spring 86 of the embodiment corresponds to the elastic biasing means of the present invention, and the V-packing 88 of the embodiment corresponds to the seal of the present invention. The steam supply pipe 8 of the embodiment corresponding to the member 5 is The first and second steam passages P1 and P2 of the embodiment correspond to the supply passage of the present invention, and the fifth to eighth steam passages P5 to P8 of the embodiment correspond to the working medium pipe of the present invention. The first and second seal lips S1 and S2 of the present invention correspond to the discharge passage, and correspond to the seal lips of the present invention.
[0027]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described based on examples of the present invention shown in the accompanying drawings.
[0028]
1 to 15 show a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an expander, FIG. 2 is a sectional view taken along line 2-2 in FIG. 1, and FIG. 3 is 3-3 in FIG. 4 is an enlarged view of a part 4 of FIG. 1, FIG. 5 is an enlarged view of a part 5 of FIG. 1, FIG. 6 is an exploded perspective view of the rotor, FIG. 7 is a sectional view taken along the line 7-7 of FIG. 8 is a sectional view taken along line 8-8 of FIG. 4, FIG. 9 is an enlarged view of 9 part of FIG. 4, FIG. 10 is an enlarged view of 10 part of FIG. 5, FIG. 11 is a view taken along line 11-11 of FIG. 13 is a sectional view taken along line 12-12 of FIG. 10, FIG. 13 is a sectional view taken along line 13-13 of FIG. 5, FIG. 14 is a sectional view taken along line 14-14 of FIG. 5, and FIG. 15 is a view of the coil spring, the packing retainer and the V-packing. It is a perspective view.
[0029]
As shown in FIGS. 1 to 9, the expander E of this embodiment is used in, for example, a Rankine cycle device, and converts heat energy and pressure energy of a high-temperature high-pressure steam as a working medium into mechanical energy and outputs the mechanical energy. I do. The casing 11 of the expander E includes a casing body 12, a front cover 15 connected to a front opening of the casing body 12 by a plurality of bolts 14 via a sealing member 13, and a rear opening of the casing body 12. A rear cover 18 connected to the casing body 12 with a plurality of bolts 17 via a sealing member 16 and an oil pan 21 connected to an opening on the lower surface of the casing body 12 via a sealing member 19 with a plurality of bolts 20. It consists of.
[0030]
A rotor 22 rotatably arranged around an axis L extending in the front-rear direction at the center of the casing 11 is supported by combined angular bearings 23f, 23r having a front portion provided on the front cover 15, and a rear portion of the casing body 12 is provided. And is supported by a radial bearing 24 provided at the bottom. A swash plate holder 28 is integrally formed on the rear surface of the front cover 15, and a swash plate 31 is rotatably supported by the swash plate holder 28 via an angular bearing 30. The axis of the swash plate 31 is inclined with respect to the axis L of the rotor 22, and the angle of inclination is fixed.
[0031]
The rotor 22 includes an output shaft 32 supported on the front cover 15 by combined angular bearings 23f and 23r, and cutouts 57 and 58 (see FIGS. 4 and 9) having predetermined widths at the rear of the output shaft 32. The three integrally formed sleeve support flanges 33, 34, 35 are connected to the rear sleeve support flange 35 by a plurality of bolts 37 via a metal gasket 36. And a heat insulating cover 40 which is fitted to the three sleeve support flanges 33, 34, 35 from the front and is connected to the front sleeve support flange 33 by a plurality of bolts 39. .
[0032]
Each of the three sleeve support flanges 33, 34, 35 is formed with five sleeve support holes 33a,..., 34a, 35a at intervals of 72 ° around the axis L. The sleeve support holes 33a,. Five cylinder sleeves 41 are fitted into 34a, 35a from behind. A flange 41a is formed at the rear end of each cylinder sleeve 41. The flange 41a is fitted to the metal gasket 36 in a state where the flange 41a is fitted to a step 35b formed in the sleeve support hole 35a of the rear sleeve support flange 35. It is positioned in the axial direction by contact (see FIG. 9). A piston 42 is slidably fitted inside each of the cylinder sleeves 41. A front end of the piston 42 abuts a dimple 31a formed on the swash plate 31, and a piston 42 and a rotor head 38 A steam expansion chamber 43 is defined therebetween.
[0033]
A plate-shaped bearing holder 92 is superimposed on the front surface of the front cover 15 via a sealing member 91 and fixed with bolts 93. A pump body 95 is superimposed on the front surface of the bearing holder 92 via a sealing member 94. It is fixed with bolts 96. The combined angular bearings 23f and 23r are fixed between the stepped portion of the front cover 15 and the bearing holder 92 in the direction of the axis L.
[0034]
A shim 97 having a predetermined thickness is sandwiched between a flange 32d formed on the output shaft 32 supporting the combined angular bearings 23f and 23r and an inner race of the combined angular bearings 23f and 23r, and screwed to the outer periphery of the output shaft 32. The inner race of the combined angular bearings 23f and 23r is tightened by the nut 98. As a result, the output shaft 32 is positioned in the direction of the axis L with respect to the combined angular bearings 23f and 23r, that is, with respect to the casing 11.
[0035]
The combined angular bearings 23f and 23r are mounted in opposite directions, and not only support the output shaft 32 in the radial direction but also support the output shaft 32 so as not to be movable in the axis L direction. That is, one combination angular bearing 23f restricts the output shaft 32 from moving forward, and the other combination angular bearing 23r restricts the output shaft 32 from moving rearward.
[0036]
Since the combined angular bearings 23f and 23r are used for the bearing that supports the front part of the rotor 22, the load generated on the both sides in the direction of the axis L generated in the expansion chambers 43 in the predetermined operating state of the expander E is one of the rotors. 22 is transmitted to the inner race of the combined angular bearings 23f, 23r, and the other is transmitted to the outer race of the combined angular bearings 23f, 23r via the swash plate 31 and the swash plate holder 28 of the front cover 15. These two loads compress the swash plate holder 28 of the front cover 15 sandwiched between the angular bearing 30 that supports the swash plate 31 and the combined angular bearings 23f and 23r that support the rotor 22. The rigidity is high. In addition, as in the present embodiment, by forming the swash plate holder 28 integrally with the front cover 15, a simple structure having higher rigidity is obtained.
[0037]
Further, by incorporating the angular bearings 30 for supporting the swash plate 31 and the combined angular bearings 23f and 23r for supporting the rotor 22 into the front cover 15, the “rotor 22 and pistons 42. , "Pump body 95" can be assembled, and the efficiency of operations such as rearrangement of pistons 42 and replacement of oil pump 49 is improved.
[0038]
The radial bear 24 supporting the rotor head 38 constituting the rear end portion of the rotor 22 is a normal ball bearing that supports only a radial load, and the rotor head 38 moves in the direction of the axis L with respect to the radial bearing 24. A gap α (see FIG. 5) is formed between the rotor head 38 and the inner race of the radial bearing 24 so that the rotor head 38 can slide.
[0039]
An oil passage 32a extending on the axis L is formed inside the output shaft 32 integrated with the rotor 22, and the front end of the oil passage 32a branches radially and communicates with an annular groove 32b on the outer periphery of the output shaft 32. An oil passage closing member 45 is screwed into the inner periphery of the oil passage 32a via a seal member 44 at a position radially inward of the sleeve support flange 34 at the center of the rotor 22. A plurality of oil holes 32c extending outward in the direction open in the outer peripheral surface of the output shaft 32.
[0040]
A trochoid-type oil pump 49 disposed between a concave portion 95a formed on the front surface of the pump body 95 and a pump cover 48 fixed to the front surface of the pump body 95 with a plurality of bolts 47 via a seal member 46 is provided. An outer rotor 50 rotatably fitted in the recess 95a, and an inner rotor 51 fixed to the outer periphery of the output shaft 32 and meshing with the outer rotor 50. The internal space of the oil pan 21 communicates with a suction port 53 of an oil pump 49 via an oil pipe 52 and an oil passage 95b of a pump body 95, and a discharge port 54 of the oil pump 49 communicates with an oil passage 95c of the pump body 95. The output shaft 32 communicates with the annular groove 32b.
[0041]
The piston 42 slidably fitted to the cylinder sleeve 41 includes an end portion 61, an intermediate portion 62, and a top portion 63. The end portion 61 is a member having a spherical portion 61a that comes into contact with the dimple 31a of the swash plate 31, and is joined to the tip of the intermediate portion 62 by welding. The intermediate portion 62 is a cylindrical member having a large-capacity hollow space 62a, and has a small-diameter portion 62b whose diameter is slightly reduced at an outer peripheral portion near the top portion 63, and penetrates therethrough in the radial direction. Are formed as described above, and a plurality of spiral oil grooves 62d are formed in the outer peripheral portion in front of the small diameter portion 62b. The top portion 63 facing the expansion chamber 43 is formed integrally with the intermediate portion 62, and a heat insulating space 65 is provided between a partition wall 63a formed on the inner surface thereof and a lid member 64 fitted and welded to its rear end surface. (See FIG. 9) is formed. Two compression rings 66, 66 and one oil ring 67 are mounted on the outer periphery of the top portion 63, and an oil ring groove 63b in which the oil ring 67 fits is inserted through a plurality of oil holes 63c. It communicates with the hollow space 62a of the intermediate part 62.
[0042]
The end portion 61 and the intermediate portion 62 of the piston 42 are made of high carbon steel, and the top portion 63 is made of stainless steel. The end portion 61 is induction hardened and the intermediate portion 62 is hardened. As a result, a high surface pressure resistance of the end portion 61 abutting against the swash plate 31 with a large surface pressure, a wear resistance of the intermediate portion 62 slidably contacting the cylinder sleeve 41 under severe lubrication conditions, and a high temperature and high pressure The heat resistance and corrosion resistance of the top portion 63 exposed to water are satisfied.
[0043]
An annular groove 41b (see FIGS. 6 and 9) is formed on the outer periphery of the intermediate portion of the cylinder sleeve 41, and a plurality of oil holes 41c are formed in the annular groove 41b. Regardless of the mounting position of the cylinder sleeve 41 in the rotation direction, an oil hole 32c formed in the output shaft 32 and an oil hole 34b formed in the center sleeve support flange 34 of the rotor 22 (see FIGS. 4 and 6). Communicates with the annular groove 41b. Spaces 68 formed between the sleeve support flanges 33 and 35 on the front and rear sides of the rotor 22 and the heat insulating cover 40 are formed via oil holes 40a formed in the heat insulating cover 40 (see FIGS. 4 and 7). It communicates with the internal space of the casing 11.
[0044]
An annular lid member 69 is welded to the front side or the expansion chamber 43 side of the rotor head 38 which is connected to the rear surface of the sleeve support flange 33 on the front side of the rotor 22 with bolts 37. An annular heat insulating space 70 (see FIG. 9) is defined. The rotor head 38 is positioned in the rotation direction with respect to the rear sleeve support flange 35 by the knock pin 55.
[0045]
The five cylinder sleeves 41 and the five pistons 42 constitute an axial piston cylinder group 56 of the present invention.
[0046]
Next, the structure of the rotary valve 71 for supplying and discharging steam to and from the five expansion chambers 43 of the rotor 22 will be described with reference to FIG. 5 and FIGS.
[0047]
As shown in FIG. 5, the rotary valve 71 arranged along the axis L of the rotor 22 includes a valve body 72 integrally formed at the center of the rear cover 18 and a fixed valve plate 73 made of carbon. And a movable valve plate 74 made of carbon, Teflon, metal or the like. The movable-side valve plate 74 is fixed to the rear surface of the rotor 22 with bolts 76 screwed to the oil passage closing member 45 (see FIG. 4) in a state of being positioned in the rotational direction by a knock pin 75 (see FIG. 10). The bolt 76 also has a function of fixing the rotor head 38 to the output shaft 32.
[0048]
An annular holder 79 fitted to the outer periphery of the valve body 72 via a seal member 78 is fixed by a plurality of bolts 80. The inside of the holder 79 is prevented from rotating by two knock pins 81, 81. The fixed side valve plate 73 is supported via a seal member 82. The backup ring 90 disposed on the rear side of the seal member 82 has a role of protecting the heat-sensitive seal member 82 from the heat of high-temperature and high-pressure steam. The backup ring 91 disposed on the front side of the seal member 82 is It has a role of preventing the seal member 82 from falling off from the front end of the holder 79 due to the pressure of the steam. Either one or both of these backup rings 90 and 91 may be provided according to the temperature and pressure of the high-temperature and high-pressure steam.
[0049]
A flange 79a protruding radially inward from the front end of the holder 79 faces the front surface of the fixed-side valve plate 73 via a gap β (see FIG. 10). It is movable in the direction of the axis L. Since the knock pins 81 are coated with a self-lubricating material such as Teflon, the fixed valve plate 73 can move smoothly in the direction of the axis L. Further, since the knock pins 81 are provided substantially at the center of the fixed-side valve plate 73, the rotating torque applied thereto is reduced, so that the size can be reduced, and the fixed-side valve plate 73 can easily follow the swinging motion. it can. In addition, since the seal member 82 has a radial allowance, the fixed side valve plate 73 can be substantially floatingly supported in the radial direction and the axis L direction while exhibiting the damping characteristic.
[0050]
As is clear from FIG. 5 and FIG. 10, an annular pressure chamber 84 surrounding the axis L is opened at a mating surface 83 where the valve body 72 contacts the fixed-side valve plate 73. A steam supply pipe 85 connected to the valve body 72 at a position eccentric from the axis L communicates with the pressure chamber 84 via a first steam passage P1 penetrating the inside of the valve body 72. Inside the pressure chamber 84, a coil spring 86, a packing retainer 87, and a V-packing 88 are sequentially arranged in the direction of the axis L.
[0051]
Therefore, the high-temperature and high-pressure steam introduced into the pressure chamber 84 is also introduced into the mating surface 83 and is sealed by the seal member 82 on the outer periphery, so that the mating surface 83 on the back surface of the fixed-side valve plate 73 also has a sliding surface 77. This is a region that exerts a pressing action on.
[0052]
As is clear from FIG. 15, the coil spring 86 is formed of a tapered coil spring whose winding diameter decreases toward the fixed-side valve plate 73. The metal packing retainer 87 includes a conical surface 87a with which the coil spring 86 abuts, a conical surface 87b for supporting the V-packing 88 on the opposite side of the conical surface 87a, and an inner peripheral surface 84a of the pressure chamber 84 (see FIG. 10). ) Is provided with a circular opening 87c guided with a slight gap. The V packing 88 made of synthetic resin includes a conical surface 88 a supported by a conical surface 87 b of the packing retainer 87, a flat surface 88 b abutting on a mating surface 83 with the fixed side valve plate 73, and an inner peripheral surface of the pressure chamber 84. And a circular opening 88c guided by 84a.
[0053]
The coil spring 86 applies a preload that presses the V-packing 88 against the mating surface 83 with the fixed-side valve plate 73 before the pressure of the high-temperature and high-pressure steam rises, and also vibrates the fixed-side valve plate 73 with the seal member 82 and the pressure chamber. It has a function of attenuating in cooperation with the pressure of the high-temperature and high-pressure steam in 84. The packing retainer 87 has a function of holding the V-packing 88 in a correct position in the pressure chamber 84 and blocking heat of high-temperature and high-pressure steam to increase the durability of the V-packing 88.
[0054]
Further, the coil spring 86 has a structure in which a spring seat is eliminated in order to increase the number of turns of the spring in a small space of the pressure chamber 84, and is interposed between the V packing 88 without directly contacting the V packing 88. The use of the packing retainer 87 as a spring seat eliminates the need to provide a special spring seat for the V-packing 88, and reduces the dimension of the pressure chamber 84 in the direction of the axis L while ensuring the maximum length of the coil spring 86. The size can be reduced. Further, the conical surfaces 87a and 87b of the packing retainer 87 cooperate with the tapered coil spring 86 and the V-packing 88 to exhibit a function of increasing the followability of the fixed valve plate 73 to the swinging motion.
[0055]
The first steam passage P1 formed in the valve body 72 communicates with the sliding surface 77 via the second steam passage P2 formed in the fixed valve plate 73. The sliding surface 77 is provided with an arc-shaped fifth steam passage P5 and a circular sixth steam passage P6 which are in communication with each other, and the sixth steam passage P6 is formed on the seventh line formed on the axis L. It communicates with the mating surface 83 via the steam passage P7. An eighth steam passage P8 formed in the valve body 72 so as to be located on the axis L has one end communicating with the seventh steam passage P7 at the mating surface 83 and a steam discharge pipe at the rear end face of the valve body 72. Communicates with 89. Since the volume of the low-temperature and low-pressure steam after expansion is larger than that of the high-temperature and high-pressure steam before expansion, the diameter of the steam discharge pipe 89 is larger than the diameter of the steam supply pipe 85.
[0056]
As shown in FIGS. 10 and 12, an arc-shaped pressure groove 77 a communicating with the second steam passage P <b> 2 is formed in the sliding surface 77 of the fixed-side valve plate 73. , Two pressure holes 77b, 77b communicating with the pressure chamber 84 are opened.
[0057]
Five third steam passages P3... Arranged at equal intervals so as to surround the axis L pass through the movable side valve plate 74, and five fourth steam passages P3 formed in the rotor 22 so as to surround the axis L. Both ends of the steam passages P4 communicate with the third steam passages P3 and the expansion chambers 43, respectively. The portion of the second steam passage P2 that opens to the sliding surface 77 is circular, whereas the portion of the fifth steam passage P5 that opens to the sliding surface 77 is formed in an arc shape centered on the axis L.
[0058]
Next, the operation of the expander E of the present embodiment having the above configuration will be described.
[0059]
The high-temperature and high-pressure steam generated by heating water in the evaporator is supplied from the steam supply pipe 85 to the first steam passage P1 of the valve body 72, the pressure chamber 84, the mating surface 83, and the second It reaches the sliding surface 77 with the movable side valve plate 74 via the steam passage P2. The second steam passage P2 opening to the sliding surface 77 instantaneously communicates with a corresponding third steam passage P3 formed in the movable valve plate 74 that rotates integrally with the rotor 22 during a predetermined intake period, and the high temperature and high pressure The steam is supplied from the third steam passage P3 to the expansion chamber 43 in the cylinder sleeve 41 via the fourth steam passage P4 formed in the rotor 22.
[0060]
Even after the communication between the second steam passage P2 and the third steam passage P3 is cut off with the rotation of the rotor 22, the high-temperature and high-pressure steam expands in the expansion chamber 43, so that the piston 42 fitted to the cylinder sleeve 41 is moved. It is pushed forward from the top dead center toward the bottom dead center, and the end part 61 at the front end presses the dimple 31 a of the swash plate 31. As a result, a rotational torque is applied to the rotor 22 by the reaction force received by the piston 42 from the swash plate 31. Then, each time the rotor 22 rotates one fifth, the high-temperature and high-pressure steam is supplied into the adjacent new expansion chamber 43, and the rotor 22 is continuously driven to rotate.
[0061]
While the piston 42 that has reached the bottom dead center with the rotation of the rotor 22 is pressed by the swash plate 31 and retreats toward the top dead center, the low-temperature and low-pressure steam pushed out of the expansion chamber 43 is A fourth steam passage P4, a third steam passage P3 of the movable valve plate 74, a sliding surface 77, a fifth steam passage P5, a sixth steam passage P6, and a seventh steam passage P7 of the fixed valve plate 73; The gas is supplied to the condenser via the mating surface 83, the eighth steam passage P <b> 8 of the valve body 72, and the steam discharge pipe 89.
[0062]
The oil pump 49 provided on the output shaft 32 is operated with the rotation of the rotor 22, and the oil sucked from the oil pan 21 through the oil pipe 52, the oil passage 95 b of the pump body 95, and the suction port 53 is discharged from the discharge port 54. The oil is discharged, the oil passage 95c of the pump body 95, the oil passage 32a of the output shaft 32, the annular groove 32b of the output shaft 32, the oil hole 32c of the output shaft 32, the annular groove 41b of the cylinder sleeve 41 and the oil hole of the cylinder sleeve 41. Are supplied to the space between the small-diameter portion 62b formed in the intermediate portion 62 of the piston 42 and the cylinder sleeve 41 via the cylinder sleeve 41. A part of the oil held in the small diameter portion 62b flows into a spiral oil groove 62d formed in the intermediate portion 62 of the piston 42 to lubricate the sliding surface with the cylinder sleeve 41, The other part lubricates the sliding surfaces of the compression sleeves 66, 66 and the oil ring 67 provided on the top part 63 of the piston 42 and the cylinder sleeve 41.
[0063]
It is inevitable that the water in which a part of the supplied high-temperature and high-pressure steam condenses enters the sliding surfaces of the cylinder sleeve 41 and the piston 42 from the expansion chamber 43 and mixes with the oil. Although the conditions become severe, the necessary amount of oil is supplied directly from the oil pump 49 through the inside of the output shaft 32 to the sliding surfaces of the cylinder sleeve 41 and the piston 42, thereby maintaining a sufficient oil film and improving the lubrication performance. As a result, the size of the oil pump 49 can be reduced.
[0064]
The oil scraped off from the sliding surfaces of the cylinder sleeve 41 and the piston 42 by the oil ring 67 flows into the hollow space 62a inside the piston 42 from the oil holes 63c formed at the bottom of the oil ring groove 63b. The hollow space 62a communicates with the inside of the cylinder sleeve 41 through a plurality of oil holes 62c penetrating the intermediate portion 62 of the piston 42, and the inside of the cylinder sleeve 41 communicates through a plurality of oil holes 41c. It communicates with an annular groove 41b on the outer periphery of the cylinder sleeve 41. The periphery of the annular groove 41b is covered by a sleeve support flange 34 at the center of the rotor 22. Since the oil hole 34b is formed in the sleeve support flange 34, the oil in the hollow space 62a of the piston 42 is subjected to centrifugal force. , And is discharged to the space 68 in the heat insulating cover 40 through the oil hole 34b of the sleeve support flange 34, and then returned to the oil pan 21 through the oil hole 40a of the heat insulating cover 40. At this time, since the oil hole 34b is located at a position deviated toward the axis L from the radially outer end of the sleeve support flange 34, the oil radially outside of the oil hole 34b is centrifugally applied to the piston 42. It is held in the hollow space 62a.
[0065]
As described above, the oil held in the hollow space 62a inside the piston 42 and the oil held in the small diameter portion 62b on the outer periphery of the piston 42 combine with the small diameter portion 62b during the expansion stroke in which the volume of the expansion chamber 43 increases. From the small diameter portion 62b to the end portion 61 during the compression stroke in which the volume of the expansion chamber 43 is reduced, so that the entire axial direction of the piston 42 can be reliably lubricated. . In addition, since the oil flows inside the hollow space 62a of the piston 42, the heat of the top portion 63 exposed to the high-temperature and high-pressure steam is transmitted to the low-temperature end portion 61 to prevent the temperature of the piston 42 from locally increasing. can do.
[0066]
When the high-temperature and high-pressure steam is supplied from the fourth steam passage P4 to the expansion chamber 43, an adiabatic space 65 is formed between the top part 63 and the intermediate part 62 of the piston 42 facing the expansion chamber 43. Since the heat insulating space 70 is also formed in the rotor head 38 facing the chamber 43, it is possible to minimize the heat escape from the expansion chamber 43 to the piston 42 and the rotor head 38 and contribute to the improvement of the performance of the expander E. it can. Further, since the hollow space 62a having a large volume is formed inside the piston 42, not only the weight of the piston 42 can be reduced, but also the heat mass of the piston 42 is reduced, so that the heat can escape from the expansion chamber 43 more effectively. Can be reduced.
[0067]
Since the expansion chamber 43 is sealed by interposing the metal gasket 36 between the rear sleeve support flange 35 and the rotor head 38, the expansion chamber 43 is sealed with a thick annular sealing member. As a result, the dead volume around the seal can be reduced, whereby a large volume ratio (expansion ratio) of the expander E can be ensured, the thermal efficiency can be increased, and the output can be improved. Further, since the cylinder sleeve 41 is formed separately from the rotor 22, the material of the cylinder sleeve 41 can be selected in consideration of heat conductivity, heat resistance, strength, abrasion resistance and the like without being limited by the material of the rotor 22. It is economical because only the worn or damaged cylinder sleeve 41 can be replaced.
[0068]
Further, since the outer peripheral surface of the cylinder sleeve 41 is exposed from two notches 57 and 58 formed in the outer peripheral surface of the rotor 22 in the circumferential direction, not only can the weight of the rotor 22 be reduced, but also the heat mass of the rotor 22 can be reduced. As a result, the cutouts 57 and 58 function as a heat insulating space, whereby heat escape from the cylinder sleeve 41 can be suppressed. Further, since the outer peripheral portion of the rotor 22 is covered with the heat insulating cover 40, heat escape from the cylinder sleeve 41 can be more effectively suppressed.
[0069]
Since the rotary valve 71 supplies and discharges steam to the axial piston cylinder group 56 via the flat sliding surface 77 between the fixed valve plate 73 and the movable valve plate 74, it is possible to effectively prevent steam leakage. Can be. This is because the flat sliding surface 77 can be easily processed with high precision, so that the clearance can be easily managed as compared with the cylindrical sliding surface.
[0070]
By the way, the rotor 22 is inevitably tilted to some extent due to the play of the combined angular bearings 23f, 23r and the radial bearing 24 which support the rotor 22, especially due to the thermal expansion at the time of high temperature. The sliding surface 77 of the movable-side valve plate 74 is not always strictly perpendicular to the axis L. Therefore, the fixed-side valve plate 73 that contacts the movable-side valve plate 74 via the sliding surface 77 performs a slight swinging movement with the rotation of the rotor 22, and the adhesion of the sliding surface 77 is impaired. There is a possibility that it will be.
[0071]
However, as is apparent from FIG. 10, when high-temperature and high-pressure steam is supplied from the first steam passage P1 of the valve body 72 to the pressure chamber 84, the pressure in the pressure chamber 84 increases to the area A2 where the pressure acts on the mating surface 83. A pressing load of a corresponding magnitude is applied to the fixed-side valve plate 73. Since the fixed-side valve plate 73 is movable in the direction of the axis L within the range of the gap β with respect to the valve body 72, the pressing load urges the fixed-side valve plate 73 toward the movable-side valve plate 74. Thus, the adhesion of the sliding surface 77 is ensured. The area A2 where the pressure of the pressure chamber 84 acts on the mating surface 83 is included up to the outer end of the mating surface 83 sealed by the seal member 82.
[0072]
At this time, the first seal lip S1 on the outer periphery of the V-packing 88 is bent forward in the direction of the axis L by the pressure of the high-temperature and high-pressure steam supplied to the pressure chamber 84, so that the first seal lip S1 is brought into contact with the mating surface 83 of the fixed-side valve plate 73. Is effectively sealed. Even if the valve body 72 thermally expands in the direction of the axis L1 due to the heat of the high-temperature and high-pressure steam, the V packing 88 moves in the direction of the axis L, and the first seal lip S1 is elastically deformed by the pressure of the high-temperature and high-pressure steam. By doing so, the sealing property can be maintained. As a result, it is possible to reliably prevent the high-temperature and high-pressure steam in the pressure chamber 84 from leaking to the low-pressure seventh and eighth steam passages P7 and P8 via the mating surface 73, thereby contributing to an increase in the output of the expander E. In particular, since the first seal lip S1 formed on the outer peripheral portion of the V-packing 88 has a long circumferential length, the first seal lip S1 has a large pressure receiving area and can be effectively bent. High sealing performance can be exhibited by firmly adhering to the mating surface 83.
[0073]
The second seal lip S2 on the inner peripheral surface of the V-packing 88 is in contact with the inner peripheral surface 84a of the pressure chamber 84. Inside the second seal lip S2, an eighth steam passage P8 through which a low-temperature and low-pressure working medium passes is formed. Therefore, the thermal expansion of the inner peripheral surface 84a is relatively small, so that the sealing property of the second seal lip S2 of the V-packing 88 does not pose any particular problem.
[0074]
Further, since the coil spring 86 is tapered toward the packing retainer 87, the packing retainer 87 and the V-packing 88 have a damping characteristic around the axis L and allow the swinging motion, and the close contact of the sliding surface 77 is achieved. Can be enhanced. Moreover, when the coil spring 86 expands and contracts following the vibration of the fixed side valve plate 73, the vibration of the fixed side valve plate 73 is reduced by the resistance of the high temperature and high pressure steam in the pressure chamber 84 in which the coil spring 86 is stored. It is possible to effectively attenuate in cooperation with the attenuation characteristic of 82.
[0075]
Further, the diameter of the eighth exhaust passage P8 formed on the axis L in the valve body 72 cannot be reduced because the low-temperature and low-pressure steam after expansion passes therethrough, and therefore, the eighth exhaust passage P8 is formed so as to surround the eighth exhaust passage P8. The area A2 where the applied pressure of the pressure chamber 84 acts on the mating surface 83 naturally increases. As a result, the pressing load generated by the pressure chamber 84 also increases, and the surface pressure of the sliding surface 77 may become excessive. However, the high pressure in the second steam passage P2 through which the high-temperature and high-pressure steam passes is introduced into the pressure groove 77a opened in the sliding surface 77 of the fixed valve plate 73, and the pressure opened in the sliding surface 77 of the fixed valve plate 73. By guiding the high pressure of the pressure chamber 84 to the holes 77b, 77b, the pressing load on the sliding surface 77 is controlled, the surface pressure of the sliding surface 77 is prevented from excessively increasing, and the frictional force is reduced and abnormal wear is reduced. Prevention can be achieved.
[0076]
When the pressure of the high-temperature and high-pressure steam supplied to the pressure chamber 84 increases, the high-temperature and high-pressure steam easily leaks from the sliding surfaces 77 of the fixed-side valve plate 73 and the movable-side valve plate 74. Since the pressing load generated by the chamber 84 is increased and the surface pressure of the sliding surface 77 is increased, it is possible to exhibit a sealing property corresponding to the pressure of the high-temperature and high-pressure steam. In particular, in FIG. 10, the surface pressure of the sliding surface 77 can be arbitrarily set by appropriately setting the ratio A2 / A1 of the area A2 in which the pressure of the pressure chamber 84 acts on the mating surface 83 with respect to the area A1 of the sliding surface 77. Can be adjusted. Specifically, increasing the ratio A2 / A1 increases the surface pressure of the sliding surface 77, and decreasing the ratio A2 / A1 decreases the surface pressure of the sliding surface 77.
[0077]
In other words, the optimal pressing load is a pressing load that maximizes the output of the expander E and has high thermal efficiency in consideration of a slight leak at the sliding surface 77 and is supplied to the expansion chambers 43. When the pressure of the high-temperature and high-pressure steam and the pressing load are the same, the balance ratio A2 / A1 ≒ 1. Since the pressure of the high-temperature and high-pressure steam supplied to the expansion chambers 43 decreases immediately after the supply by the expansion action, the pressure of the pressure chamber 84 is set to be lower than the pressure of the high-temperature and high-pressure just before being supplied to the expansion chambers 43. The pressing load on the sliding surface 77 may be set in consideration of the pressure.
[0078]
In the embodiment mainly shown in FIG. 10, the detent dowel pins 81 are provided substantially at the center of the back surface of the fixed valve plate 73, and the fixed valve plate 73 is moved in the direction of the axis L by the gap β. Since the fixed side valve plate 73 can be freely moved in the radial direction by the crushing allowance of the seal member 82, a large swing range of the fixed side valve plate 73 can be secured, especially when the steam pressure is low. Suitable for.
[0079]
Furthermore, since the rotary valve 71 can be attached to and detached from the casing body 12 simply by removing the rear cover 18 from the casing body 12, maintenance workability such as repair, cleaning, and replacement is greatly improved. Although the rotary valve 71 through which the high-temperature and high-pressure steam passes becomes hot, the swash plate 31 and the output shaft 32 which require lubrication with oil are arranged on the opposite side of the rotary valve 71 with the rotor 22 interposed therebetween. The lubrication performance of the swash plate 31 and the output shaft 32 can be prevented from lowering due to the oil being heated by the heat of the rotary valve 71. The oil also has a function of cooling the rotary valve 71 to prevent overheating.
[0080]
By the way, when assembling the expander E, the size of the dead volume between the bottom of the cylinder sleeve 41 (that is, the lid member 69 supported by the rotor head 38) and the top of the piston 42, that is, the piston 42 is at the top dead center. It is necessary to adjust the volume of the working chamber 43 at that time. When the shim 97 interposed between the flange 32d of the output shaft 32 and the inner races of the combined angular bearings 23f and 23r is thinned, the output shaft 32 moves forward (to the right in FIG. 1), so that the rotor head 38 also moves forward. Although moving, the piston 42 is restricted by the swash plate 31 and cannot move forward, so that the dead volume is reduced. Conversely, when the shim 97 is thickened, the dead volume increases because the rotor head 38 moves rearward (to the left in FIG. 1) together with the output shaft 32. As a result, it is possible to arbitrarily adjust the dead volume only by replacing the shim 97, and the time required for adjusting the dead volume can be eliminated, thereby greatly reducing the time.
[0081]
Further, a single shim 97 having a predetermined thickness is interposed between the flange 32d of the output shaft 32 and the angular bearings 23f and 23r, and an angular bearing 30 for supporting the swash plate 31 and an angular bearing for supporting the rotor 22. The dead volume can be adjusted by simply tightening the front cover 15 incorporating the 23f, 23r and the rotor 22 incorporating the pistons 42 with one nut 98, so that the thickness of the conventional front and rear two shims can be adjusted. The adjustment work can be performed easily as compared with the case where each is adjusted. Moreover, when adjusting the dead volume, the rotor 22 incorporating the pistons 42 may be left attached to the casing main body 12. Therefore, the work of checking the dead volume after the adjustment is performed by directly watching the contact state between the pistons 42 and the swash plate 31. Will be able to do it.
[0082]
As described above, when the position of the output shaft 32 is adjusted to the front and rear with respect to the combined angular bearings 23f and 23r by changing the thickness of the shim 97, the position of the rotor head 38 at the rear end of the rotor 22 is also adjusted to the front and rear. However, since the rotor head 38 is slidable in the direction of the axis L with respect to the inner race of the radial bearing 24 provided between the rotor head 38 and the casing main body 12, the adjustment of the position of the output shaft 32 is hindered. I can't.
[0083]
Thus, when the piston 42 is urged in the direction of being pushed out of the cylinder sleeve 41 by the pressure of the high-temperature and high-pressure steam supplied to the expansion chamber 43, the pressing force of the piston 42 is reduced by the swash plate 31, the angular bearing 30, and the swash plate. The outer race of the combined angular bearings 23f, 23r is pressed forward (to the right in FIG. 1) via the holder 28 and the front cover 15, and the pressing force of the cylinder sleeve 41, which is opposite to the pressing force of the piston 42, is applied to the rotor. The inner race of the combined angular bearings 23f, 23r is pressed rearward (to the left in FIG. 1) via the head 38 and the output shaft 32. That is, the load generated by the high-temperature and high-pressure steam supplied to the expansion chamber 43 is canceled inside the combined angular bearings 23f and 23r, and is not transmitted to the casing body 12.
[0084]
The rotor 22 including the output shaft 32, the three sleeve support flanges 33, 34, 35, the rotor head 38, and the heat insulating cover 40 is made of an iron-based material having a relatively small thermal expansion. The casing 11 supporting the rotor 22 via the angular bearings 23f, 23r and the radial bearing 24 is made of an aluminum-based material having a relatively large thermal expansion. This causes a difference in the amount of thermal expansion particularly in the direction along the axis L.
[0085]
The casing 11 having a larger thermal expansion than the rotor 22 expands more than the rotor 22 at a high temperature and relatively increases in the dimension in the direction of the axis L. Is relatively reduced. At this time, since the casing 11 and the rotor 22 are positioned in the direction of the axis L via the combined angular bearings 23f and 23r, the difference in the amount of thermal expansion between the two is determined by the sliding of the rotor head 38 against the inner race of the radial bearing 24. And prevents the combined angular bearings 23f, 23r, the radial bearing 24 and the rotor 22 from being subjected to an excessive load in the direction of the axis L. As a result, not only the durability of the combined angular bearings 23f, 23r and the radial bearing 24 is improved, but also the support of the rotor 22 can be stabilized to enable smooth rotation. And the dead volume between the top of the piston 42 and the top of the piston 42 can be prevented.
[0086]
This is because if the both ends of the rotor 22 are restrained by the casing 11 so as not to move in the axial direction, the casing 11 tends to contract with respect to the rotor 22 in the direction of the axis L at low temperatures. The piston 42 whose head is in contact with the swash plate 31 supported by the swash plate holder 28 is pressed rearward, and the rotor head 38 supported by the casing 11 via the radial bearing 24 is pressed forward. This is because the piston 42 is pushed into the cylinder sleeve 41 and the dead volume is reduced. Conversely, when the temperature is high, the casing 11 tends to extend in the direction of the axis L with respect to the rotor 22, so that the piston 42 is pulled out from the inside of the cylinder sleeve 41 and the dead volume increases. An increase in the initial volume of the high-temperature and high-pressure steam in the operating state, that is, a decrease in the thermal efficiency due to a decrease in the volume ratio (expansion ratio) of the expander E occurs.
[0087]
On the other hand, in this embodiment, since the rotor 22 is supported by the casing 11 in a floating state in the direction of the axis L, the gap between the bearings of the combined angular bearings 23f and 23r and the radial bearing 24 is increased, and the preload is reduced. The fall is prevented, and the fluctuation of the dead volume due to the temperature change is prevented. Thereby, it is possible to prevent a change in the volume ratio (expansion ratio) of the expander E and secure stable performance.
[0088]
In particular, in the expander E that uses high-temperature and high-pressure steam as a working medium, the above-described effect is effectively exhibited because the temperature difference between high temperature and low temperature is large. In the vicinity of the rotary valve 71 to which the high-temperature and high-pressure steam is supplied, the temperature difference between the high temperature and the low temperature becomes large, but the rotor head 38 is moved along the axis L with respect to the radial bearing 24 disposed near the rotary valve 71. Since it is slidable in the direction, the difference in the amount of thermal expansion between the casing 11 and the rotor 22 can be absorbed without any trouble.
[0089]
16 to 19 show a second embodiment of the present invention. FIG. 16 is an enlarged sectional view around a rotary valve, FIG. 17 is a view taken along line 17-17 of FIG. 16, and FIG. FIG. 19 is a perspective view of the coil spring, the packing retainer, and the V-packing taken along line -18.
[0090]
In the first embodiment, the steam discharge pipe 89 is arranged on the axis L of the rotor 22, and the steam supply pipe 85 is arranged so as to be deviated radially outward. In the second embodiment, the positional relationship is changed. A steam supply pipe 85 is arranged on the axis L of the rotor 22, and a steam discharge pipe 89 is arranged so as to be deviated radially outward.
[0091]
Further, the valve body 72 of the first embodiment is formed integrally with the rear cover 18, but the valve body 72 of the second embodiment is detachably attached to the rear cover 18. That is, a circular flange 72a integrally formed on the rear portion of the valve body 72 comes into contact with the rear surface of the rear cover 18 via the seal member 101, and is fixed with a plurality of bolts 102. At this time, the support portion 72b having a circular cross section formed integrally with the front portion of the valve body portion 72 fits into the support hole 18a of the rear cover 18. An annular holder 79 is fixed to a support surface 18b connected to the support hole 18a of the rear cover 18 with a plurality of bolts 80. The holder 79 follows the swing of the fixed-side valve plate 73 mainly. The fixed-side valve plate 73 held via the seal member 82 functioning as an elastic body is prevented from rotating by the Teflon-coated knock pins 81, 81. The fixed side valve plate 73 is positioned in the rotation direction by the knock pins 81, 81, and is floatingly supported so as to be slightly movable in the radial direction and the axis L direction.
[0092]
A pressure chamber 84 having a circular cross section is opened on a mating surface 83 where the valve body 72 contacts the fixed-side valve plate 73. A steam supply pipe 85 penetrating through the valve body 72 through the seal member 103 extends to the mating surface 83 through the center of the pressure chamber 84, and inside the pressure chamber 84, a coil spring is formed around the outer periphery of the steam supply pipe 85. 86, a packing retainer 87 and a V-packing 88 are sequentially arranged.
[0093]
A slight gap is set between the tip of the steam supply pipe 85 and the mating surface 83 of the fixed side valve plate 73, and even if the steam supply pipe 85 thermally expands in the direction of the axis L, the tip of the steam supply pipe 85 is 83 so as not to interfere. One through hole 85 a formed in the steam supply pipe 85 communicates with the rear part of the pressure chamber 84. The number of the through holes 85 a may be plural depending on the strength of the steam supply pipe 85 and the necessary steam supply to the pressure chamber 84.
[0094]
The metal packing retainer 87 has a cylindrical portion 87d loosely fitted to the outer periphery of the steam supply pipe 85, a conical surface 87e with which a non-tapered coil spring 86 abuts, and V on the opposite side of the conical surface 87e. And a conical surface 87f for supporting the packing 88. The V-packing 88 made of synthetic resin has a through-hole 88d loosely fitted to the outer periphery of the steam supply pipe 85, a conical surface 88e supported by a conical surface 87f of the packing retainer 87, and a mating surface 83 of the fixed-side valve plate 73. And a flat surface 88f that abuts the flat surface 88f.
[0095]
The first steam passage P1 formed inside the steam supply pipe 85 communicates with the sliding surface 77 via the second steam passage P2 formed in the fixed valve plate 73. A pressure groove 73a formed in the fixed valve plate 73 and opening to the mating surface 83 communicates with a second steam passage P2 formed in the fixed valve plate 73 through a communication hole 77b.
[0096]
A steam discharge chamber 104 is formed between the casing body 12 and the rear cover 18. The steam discharge chamber 104 communicates with a steam discharge pipe 89 and a seventh steam passage formed inside the valve body 72. It communicates with the sliding surface 77 via P7 and fifth and sixth steam passages P5 and P6 formed in the fixed-side valve plate 73. Note that the fifth steam passage P5 is formed in an arc shape and opens to the sliding surface 77, and the sixth and seventh steam passages P6 and P7 communicating with the fifth steam passage P5 are each divided into two and joined together. Open at 83.
[0097]
According to the second embodiment, the high-temperature and high-pressure steam supplied from the through hole 85a of the steam supply pipe 85 to the pressure chamber 84 elastically deforms the first seal lip S1 of the V packing 88 forward in the direction of the axis L. The sealing performance is exerted by pressing against the mating surface 83 of the fixed side valve plate 73 and elastically deforming the second seal lip S2 of the V-packing 88 radially inward and pressing against the outer peripheral surface of the steam supply pipe 85. Although the steam supply pipe 85 through which the high-temperature and high-pressure steam flows undergoes large thermal expansion, the peripheral length of the sealing surface with the second seal lip S2 becomes shorter due to its relatively small diameter. Can reduce the frictional force generated between the two.
[0098]
In the second embodiment, since the pressure chamber 84 is formed so as to surround the periphery of the steam supply pipe 85 having a smaller diameter than the steam discharge pipe 89, the area A2 in which the pressure of the pressure chamber 84 acts on the mating surface 83 is reduced. It is easy to make it small, and the ratio A2 / A1 can be set small so that the pressing load for pressing the fixed side valve plate 73 can be made small, and the generation of excessive surface pressure on the sliding surface 77 is suppressed. effective. If excessive surface pressure still occurs on the sliding surface 77, the pressure on the sliding surface 77 is released from the communication hole 73b penetrating the fixed side valve plate 73 to the pressure groove 73a opened on the mating surface 83. Further, the surface pressure of the sliding surface 77 can be reduced to reduce the sliding resistance.
[0099]
In the second embodiment, the locking pins 81, 81 for preventing rotation are arranged radially outside the fixed valve plate 73 in comparison with the first embodiment. Since the amount of movement is small and the amount of movement in the direction of the axis L is large, as a result, the swing range of the fixed-side valve plate 73 is reduced, so that the followability to high-frequency vibrations mainly in a high steam pressure state is improved. Are better. Further, the second embodiment is suitable especially when the temperature of the steam is high because the mating surface 83 is not directly exposed to the introduced steam unlike the first embodiment.
[0100]
Other functions and effects of the second embodiment are the same as those of the above-described first embodiment.
[0101]
20 and 21 show a third embodiment of the present invention. FIG. 20 is an enlarged sectional view around a rotary valve according to the third embodiment, and FIG. 21 is a perspective view of a coil spring, a packing retainer and a V-packing. is there.
[0102]
The third embodiment differs from the above-described second embodiment only in the structure inside the pressure chamber 84, and therefore the description will focus on the differences. In the second embodiment shown in FIG. 16, the first seal lip S1 of the V packing 88 seals the gap between the V-packing 88 and the mating surface 83 of the fixed valve plate 73, and the second seal lip S2 is connected to the steam supply pipe 85. In the third embodiment, the first seal lip S1 of the V-packing 88 seals the gap with the mating surface 83 of the fixed-side valve plate 73, and the second seal is formed. Seal lip S2 seals between the inner peripheral surface 84a of the pressure chamber 84.
[0103]
That is, the packing retainer 87 urged by the non-tapered coil spring 86 having the same diameter has a flat surface 87g with which the coil spring 86 comes into contact, a conical surface 87h formed on the opposite side of the flat surface 87g, and steam supply. A through hole 87i that fits loosely on the outer periphery of the pipe 85 is provided. The V-packing 88 held by the packing retainer 87 has a conical surface 88g supported by the conical surface 87h of the packing retainer 87 and a conical surface 88h formed on the opposite side of the conical surface 88g. A first seal lip S1 for sealing between the mating surface 83 of the plate 73 and a second seal lip S2 for sealing between the inner peripheral surface 84a of the pressure chamber 84 are formed.
[0104]
The main purpose of this V-packing 88 is to seal between the inner peripheral surface 84a of the pressure chamber 84 and the second seal lip S2 having the thin end of the conical surface 88h by the vapor pressure of the pressure chamber 84. It is configured to be deformed radially outward and adhere to the inner peripheral surface 84a. Accordingly, the second seal lip S2 can follow the enlargement of the inner diameter of the inner peripheral surface 84a of the pressure chamber 84 due to the thermal expansion of the valve body 72, and can secure the sealing property.
[0105]
Other functions and effects of the third embodiment are the same as those of the above-described second embodiment.
[0106]
The embodiments of the present invention have been described above. However, various design changes can be made in the present invention without departing from the gist thereof.
[0107]
For example, the expander E of the embodiment includes the axial piston cylinder group 56 as an operation unit, but the structure of the operation unit is not limited thereto.
[0108]
Also, the cross-sectional shape of the V-packing 88 is not limited to the embodiment and can be changed as appropriate. Generally, when the vapor pressure acting on the V-packing 88 is high, a sealing effect due to the bending of the seal lip can be expected. Therefore, it is desirable to make the seal lip as thin as possible to facilitate bending. Conversely, when the vapor pressure acting on the V-packing 88 is low, the sealing effect due to the bending of the seal lip cannot be expected. Therefore, it is desirable to increase the thickness of the seal lip and obtain the sealing effect by the elasticity of the seal lip itself.
[0109]
The V-packing 88 is not limited to the synthetic resin of the embodiment, and may be made of metal or ceramic. In this case, in order to easily bend the seal lips S1 and S2, it is desirable to form annular grooves g1 and g2 near the seal lips S1 and S2 as shown in FIG.
[0110]
The rotary fluid machine of the present invention is not limited to the expander E, but can be applied to a compressor, a hydraulic pump, a hydraulic motor, and the like.
[0111]
【The invention's effect】
As described above, according to the first aspect of the invention, the fixed-side valve plate is non-rotatably floatingly supported on the valve body fixed to the casing, and the valve body is opened at the mating surface with the fixed-side valve plate. A high-pressure working medium is supplied to the pressure chamber formed so that the mating surface is sealed with a sealing member to receive the pressure of the high-pressure working medium, so that the fixed-side valve plate can be moved by the pressure of the working medium in the pressure chamber. A pressing load is generated that presses against the sliding surface with the side valve plate, and the sliding surface is brought into close contact to prevent leakage of the working medium. In addition, the floating valve supports the fixed-side valve plate to follow the runout of the sliding surface, so that the followability of the pressing load to the sliding surface is enhanced, and the sealing performance of the sliding surface can be ensured.
[0112]
In particular, when leakage from the sliding surface is likely to occur due to high pressure of the working medium, the pressing load generated by the pressure chamber increases accordingly, so that even if the pressure of the working medium fluctuates, the sliding surface While preventing the leakage of the working medium by always generating the optimum surface pressure, it is possible to prevent the surface pressure from excessively increasing and minimize the frictional resistance of the sliding surface.
[0113]
Moreover, since the seal between the fixed side valve plate floatingly supported by the valve body and the pressure chamber is sealed by a sealing member to prevent leakage of the working medium, the pressing load generated by the pressure chamber can be stabilized, and Since the fixed-side valve plate can move in the axial direction and the radial direction, it can follow the inclination of the sliding surface by oscillating while securing the sealing performance.
[0114]
According to the second aspect of the present invention, since the seal member has the seal lip which is elastically deformed by the softening due to the pressure and heat of the working medium, the seal lip is formed in accordance with an increase in the pressure of the working medium and an increase in the temperature. The seal lip can be deformed to further enhance the sealability, and can move in the axial direction with low friction from the shape of the seal lip.
[0115]
According to the third aspect of the present invention, the seal member is urged toward the mating surface with the fixed-side valve plate by the elastic urging means, so that the seal member is not pressed when the pressure of the working medium does not rise. To ensure the sealing property, and also to attenuate the vibration of the fixed side valve plate due to the runout of the sliding surface by the elastic force of the elastic urging means together with the damping characteristic of the seal member, Adhesion of the sliding surface can be ensured.
[0116]
According to the fourth aspect of the present invention, since the resilient urging means is constituted by the tapered coil spring tapering toward the seal member, the spring is generated by the movable side valve plate due to the alignment of the tapered coil spring. The fixed-side valve plate swings around the axis to follow the swinging of the fixed-side valve plate due to the swing of the sliding surface, and the sliding is performed in accordance with the damping characteristics of the elastic urging means. The adhesion of the moving surface can be more effectively ensured.
[0117]
According to the invention described in claim 5, since the annular pressure chamber is formed so as to surround the periphery of the passage of the low-temperature side working medium provided at the center of the valve body, the seal member housed in the pressure chamber. Temperature rise can be suppressed and the sealing property can be maintained. In addition, the fixed-side valve plate and the movable-side valve plate can be effectively cooled with the low-temperature side working medium, so that the smoothness and wear resistance of the sliding surface can be maintained.
[0118]
According to the invention described in claim 6, since the annular pressure chamber is formed so as to surround the high pressure side working medium passage provided at the center of the valve body, the pressing load generated in the pressure chamber is formed. Can uniformly act on the sliding surface. Thus, even if the pressure chamber is downsized and the pressing load is set to be small, it is possible to secure the adhesion of the sliding surface and prevent uneven wear, and to appropriately minimize the pressing load on the sliding surface. Therefore, the frictional resistance generated on the sliding surface can be reduced, and the loss torque of the rotary fluid machine can be reduced.
[0119]
According to the invention described in claim 7, the first seal lip of the seal member seals between the mating surface of the fixed-side valve plate and the second seal lip contacts the inner peripheral surface of the pressure chamber. In particular, the second sealing lip can prevent the pressure fluctuation of the working medium and the axial and radial displacement of the fixed valve plate from the lip structure. Thus, the sealing property can be improved by closely adhering to the inner peripheral surface of the pressure chamber with good followability.
[0120]
According to the invention described in claim 8, the first seal lip of the seal member seals between the mating surface of the fixed side valve plate and the second seal lip from the lip structure into the pressure chamber. Following the radial thermal expansion of the inserted working medium pipe due to the high-temperature working medium, the space between the working medium pipe and the outer peripheral surface of the working medium pipe can be sealed to maintain the tightness of the pressure chamber. The seal lip of No. 2 seals the outer peripheral surface of the working medium pipe having a smaller diameter than the inner peripheral surface of the pressure chamber. , And the stationary valve plate can follow the axial and radial swinging movement of the sliding surface around the seal member.
[0121]
According to the ninth aspect, the surface pressure of the sliding surface is set by the ratio of the area of the pressure chamber acting on the mating surface to the area of the sliding surface. It is possible to obtain an optimum surface pressure that can reduce the frictional resistance of the sliding surface while ensuring the performance.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of an expander.
FIG. 2 is a sectional view taken along line 2-2 of FIG.
FIG. 3 is a view taken along line 3-3 in FIG. 1;
FIG. 4 is an enlarged view of four parts of FIG. 1;
FIG. 5 is an enlarged view of part 5 of FIG.
FIG. 6 is an exploded perspective view of a rotor.
FIG. 7 is a sectional view taken along line 7-7 of FIG. 4;
8 is a sectional view taken along line 8-8 in FIG. 4;
FIG. 9 is an enlarged view of a part 9 in FIG.
FIG. 10 is an enlarged view of part 10 in FIG.
FIG. 11 is a view taken along line 11-11 of FIG. 10;
FIG. 12 is a view taken along line 12-12 of FIG. 10;
FIG. 13 is a sectional view taken along line 13-13 of FIG. 5;
FIG. 14 is a sectional view taken along line 14-14 of FIG. 5;
FIG. 15 is a perspective view of a coil spring, a packing retainer, and a V-packing.
FIG. 16 is an enlarged sectional view around a rotary valve according to a second embodiment of the present invention.
FIG. 17 is a view taken along line 17-17 of FIG. 16;
FIG. 18 is a view taken along line 18-18 in FIG. 16;
FIG. 19 is a perspective view of a coil spring, a packing retainer, and a V-packing.
FIG. 20 is an enlarged sectional view around a rotary valve according to a third embodiment of the present invention.
FIG. 21 is a perspective view of a coil spring, a packing retainer, and a V-packing.
FIG. 22 is a view showing another embodiment of the V packing.
[Explanation of symbols]
11 Casing
22 rotor
56 axial piston cylinder group (actuator)
71 Rotary valve
72 Valve body
73 Fixed side valve plate
74 Movable valve plate
77 Sliding surface
83 mating surface
84 pressure chamber
84a inner peripheral surface
85 Steam supply pipe (working medium pipe)
86 coil spring (elastic biasing means)
88 V packing (seal member)
A1 Area of sliding surface
A2 Area where pressure of pressure chamber acts on mating surface
L axis
P1 First steam supply passage (supply passage)
P2 Second steam supply passage (supply passage)
P5 Fifth steam supply passage (discharge passage)
P6 6th steam supply passage (discharge passage)
P7 Seventh steam supply passage (discharge passage)
P8 8th steam supply passage (discharge passage)
S1 First seal lip (seal lip)
S2 Second seal lip (seal lip)

Claims (9)

A casing (11);
A rotor (22) rotatably supported by the casing (11);
An operating part (56) provided on the rotor (22);
A rotary valve (71) provided between the casing (11) and the rotor (22) to switch a supply path (P1, P2) and a discharge path (P5 to P8) of the working medium to the working part (56);
The rotary valve (71) includes a movable valve plate (74) provided on a rotor (22) and a fixed valve plate non-rotatably floatingly supported by a valve body (72) fixed to a casing (11). (73) is brought into contact with a sliding surface (77) orthogonal to the axis (L) in a rotary fluid machine,
The valve body (72) is actuated from the high pressure side passage among the supply passages (P1, P2) and the discharge passages (P5 to P8) of the working medium on the mating surface (83) of the valve body (72) with the fixed side valve plate (73). The pressure chamber (84) for introducing the medium is opened, and the leakage of the working medium from the pressure chamber (84) to the mating surface (83) is sealed by the sealing member (88) housed in the pressure chamber (84). A rotary fluid machine, wherein the fixed-side valve plate (73) is pressed toward the sliding surface (77) by the pressure of the working medium acting on the pressure chamber (84). The rotary fluid machine according to claim 1, wherein the seal member (88) has a seal lip (S1, S2) that can be elastically deformed by softening due to pressure and heat of the working medium. The rotary fluid machine according to claim 1 or 2, further comprising a resilient urging means (86) for urging the seal member (88) toward the mating surface (83). The rotary fluid machine according to claim 3, wherein the resilient biasing means (86) is a tapered coil spring tapering toward the seal member (88). A low-temperature passage among the supply passages (P1, P2) and the discharge passages (P5 to P8) for the working medium is provided at the center of the valve body (72), and is annular so as to surround the low-temperature passage. The rotary fluid machine according to any one of claims 1 to 4, wherein a pressure chamber (84) is formed. A high pressure side passage among the supply passages (P1, P2) and the discharge passages (P5 to P8) for the working medium is provided at the center of the valve body (72), and is annular so as to surround the high pressure side passage. The rotary fluid machine according to any one of claims 1 to 4, wherein a pressure chamber (84) is formed. The seal member (88) includes a first seal lip (S1) for sealing between the mating surface (83) of the fixed-side valve plate (73) and an inner peripheral surface (84a) of the pressure chamber (84). The rotary fluid machine according to any one of claims 1 to 4, further comprising a second seal lip (S2) for sealing a gap between the rotary fluid machines. The seal member (88) includes a first seal lip (S1) for sealing between the fixed surface and the mating surface (83) of the valve plate (73), and a working medium pipe inserted into the pressure chamber (84). 85. The rotary fluid machine according to any one of claims 1 to 4, further comprising a second seal lip (S2) for sealing between the outer peripheral surface and the outer peripheral surface of the rotary seal. The surface pressure of the sliding surface (77) is determined by the ratio (A2 / A1) of the area (A2) where the pressure of the pressure chamber (84) acts on the mating surface (83) to the area (A1) of the sliding surface (77). The rotary fluid machine according to any one of claims 1 to 4, wherein

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