JP2005163581A - Rotating fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a leakage of an operating medium and the occurrence of abnormal wear at a sliding surface by suppressing fluctuation of bearing pressure of the sliding surface of a rotary valve of a rotating fluid machine. <P>SOLUTION: A high-pressure operating medium lead-in hole 73b for introducing high-temperature and high-pressure steam to the sliding surface 77 when a single first high-pressure operating medium passage P2 opened to the sliding surface 77 from a fixed side valve plate 73 and a plurality of second high-pressure operating medium passages P3 opened to the sliding surface 77 from a movable side valve plate 74, sequentially communicate following the rotation of a rotor, is opened to the fixed side valve plate 73. The high-temperature and high-pressure steam from the first high-pressure operating medium passage P2 and the high-temperature and high-pressure steam from the high-pressure operating medium lead-in hole 73b are thereby introduced uniformly to the whole area of the sliding surface 77. The fluctuation of bearing pressure of the sliding surface 77 is suppressed to stabilize the behavior of the fixed side valve plate 73 to thereby prevent the leakage of the high-temperature and high-pressure steam and the occurrence of abnormal wear. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a casing, a rotor rotatably supported by the casing, an operating part provided in the rotor, and a rotary valve provided between the casing and the rotor for controlling supply / discharge of the working medium to the operating part. The present invention relates to a rotary fluid machine including

  Such a rotating fluid machine is known from Japanese Patent Application Laid-Open No. 2004-228561. The rotary valve of this rotary fluid machine has a sliding surface in contact with a fixed valve plate supported on the casing side and a movable valve plate supported on the rotor side. The steam supply passage and the steam discharge passage are opened, and a plurality of steam passages communicating with the plurality of expansion chambers of the rotor are opened at equal intervals in the circumferential direction on the sliding surface of the movable valve plate.

Therefore, the high-temperature and high-pressure steam supplied from the steam supply passage of the fixed valve plate to the predetermined steam passage of the movable valve plate expands in the expansion chamber to drive the piston, and the low-temperature and low-pressure steam that has finished the expansion work is movable side The steam is discharged from the predetermined steam passage of the valve plate to the steam supply / discharge passage of the fixed valve plate, and this action is sequentially performed on each expansion chamber, so that the rotor is rotationally driven.
JP 2002-256805 A

  By the way, in the rotary valve, a single high-pressure steam passage that opens on the sliding surface of the fixed-side valve plate is sequentially communicated with a plurality of high-pressure steam passages that open on the sliding surface of the movable-side valve plate. Therefore, as the rotor rotates, the high-pressure steam passage on the fixed side valve plate side and the high-pressure steam passage on the movable side valve plate side repeat communication and interruption alternately, and the reaction force on the sliding surface decreases during communication. As the reaction force of the sliding surface increases during shut-off, the degree of adhesion of the sliding surface changes periodically in the vicinity of the high-pressure steam passage on the fixed side valve plate side, which is the high-temperature high-pressure steam from the sliding surface. There is a problem that causes leakage and abnormal wear of the sliding surface.

  The present invention has been made in view of the above-described circumstances, and suppresses fluctuations in the surface pressure of the sliding surface of the rotary valve of the rotary fluid machine, and prevents leakage of working medium and abnormal wear on the sliding surface. With the goal.

  To achieve the above object, according to the first aspect of the present invention, a casing, a rotor rotatably supported by the casing, an operating portion provided in the rotor, and a casing and the rotor are provided. A rotary valve that controls the supply and discharge of the working medium to and from the working unit. The rotary valve has a sliding surface that includes a fixed valve plate supported on the casing side and a movable valve plate supported on the rotor side on the sliding surface. A single first high-pressure working medium passage that is brought into contact and opens from the fixed-side valve plate to the sliding surface, and a plurality of second high-pressure working medium passages that open from the movable-side valve plate to the sliding surface include a rotor. In a rotating fluid machine that sequentially communicates with the rotation of the high-pressure working medium, the high-pressure working medium introduction hole for introducing the high-pressure working medium into the sliding surface is opened in the fixed valve plate. Rotating fluid machine is proposed characterized.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the first high-pressure working medium passage and the high-pressure working medium introduction hole are arranged so as to be equiangular in the circumferential direction. A featured rotating fluid machine is proposed.

  According to the third aspect of the present invention, in addition to the configuration of the first or second aspect, the high pressure working medium introduced from the high pressure working medium introduction hole to the sliding surface is the first high pressure working medium passage. A high pressure working medium supplied to the second high pressure working medium passage in the expansion stroke, or a high pressure working medium discharged from the second high pressure working medium passage in the compression stroke to the first high pressure working medium passage. A rotating fluid machine is proposed.

  The axial piston cylinder group A of the embodiment corresponds to the operating portion of the present invention, the second steam passage P2 of the embodiment corresponds to the first high pressure working medium passage of the present invention, and the third steam passage P3 of the embodiment. Corresponds to the second high-pressure working medium passage of the present invention.

  According to the configuration of the first aspect, in the rotary valve in which the fixed valve plate supported on the casing side and the movable valve plate supported on the rotor side are brought into contact with each other on the sliding surface, the rotary valve slides from the fixed valve plate. When a single first high-pressure working medium passage that opens to the surface and a plurality of second high-pressure working medium passages that open from the movable valve plate to the sliding surface are sequentially communicated with the rotation of the rotor, sliding By opening the high pressure working medium introduction hole for introducing the high pressure working medium into the fixed side valve plate, the high pressure working medium from the first high pressure working medium passage and the high pressure working medium from the high pressure working medium introduction hole are slid. It can be introduced uniformly over the entire moving surface, and the fluctuation of the surface pressure of the sliding surface can be suppressed to stabilize the behavior of the stationary side valve plate, and the leakage of the working medium and the occurrence of abnormal wear can be prevented. In particular, even if the sealing degree of the sliding surface is increased in order to prevent leakage of the working medium, it is possible to improve the wear resistance by preventing the sliding surface from becoming solid lubricated by the introduced working medium.

  According to the configuration of the second aspect, since the first high pressure working medium passage and the high pressure working medium introduction hole are arranged at equal angles in the circumferential direction, the high pressure working medium introduced from the first high pressure working medium passage. And the high-pressure working medium introduced from the high-pressure working medium introduction hole can be more evenly supplied to the entire sliding surface, and the behavior of the fixed-side valve plate can be further stabilized.

  According to the configuration of the third aspect, when the rotary fluid machine is an expander, the high-pressure working medium supplied from the first high-pressure working medium passage to the second high-pressure working medium passage in the expansion stroke is used as the sliding surface. When the rotary fluid machine is a compressor, the high-pressure working medium discharged from the second high-pressure working medium passage in the compression stroke to the first high-pressure working medium passage is introduced into the sliding surface. be able to.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

  1 to 9 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an expander, FIG. 2 is an enlarged view of two parts of FIG. 1, FIG. 3 is an exploded perspective view of a rotor, and FIG. 4 is an enlarged view taken along the line 5-5 in FIG. 4, FIG. 6 is a view taken along the line 6-6 in FIG. 4, FIG. 7 is a view taken along the line 7-7 in FIG. 8 is a perspective view taken along line 8-8 in FIG. 4, and FIG. 9 is a perspective view of the coil spring, packing retainer, and V packing.

  As shown in FIGS. 1 to 3, the expander E of the present embodiment is used in, for example, a Rankine cycle device, and converts thermal energy and pressure energy of high-temperature and high-pressure steam as a working medium into mechanical energy and outputs it. To do. The casing 11 of the expander E includes a casing main body 12, a front cover 15 coupled to the front opening of the casing main body 12 with a plurality of bolts 14 through a seal member 13, and a rear opening of the casing main body 12. A rear cover 18 coupled with a plurality of bolts 17 through a sealing member 16, and an oil pan 21 coupled with a plurality of bolts 20 with a lower surface opening of the casing body 12 through a sealing member 19. Consists of.

  The rotor 22 arranged to be rotatable around the axis L extending in the front-rear direction in the center of the casing 11 is supported by combination angular bearings 23, 23 provided on the front cover 15 at the front part thereof, and the rear part thereof as the casing body 12. Is supported by a radial bearing 24 provided on the surface. 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 inclination angle is fixed.

  The rotor 22 includes an output shaft 32 supported on the front cover 15 by combined angular bearings 23, 23, three sleeve support flanges 33, 34, 35 integrally formed on the rear portion of the output shaft 32, and a rear side Are connected to the sleeve support flange 35 by a plurality of bolts 37 through a metal gasket 36 and supported by the casing body 12 by the radial bearing 24, and three sleeve support flanges 33, 34, 35. And a heat insulating cover 40 coupled to the front sleeve support flange 33 by a plurality of bolts 39.

  The three sleeve support flanges 33, 34, 35 are each formed with five sleeve support holes 33a, 34a, ..., 35a ... around the axis L at intervals of 72 °, and these sleeve support holes 33a, ..., Five cylinder sleeves 41 are fitted to the rear 34a, 35a,. A flange 41 a is formed at the rear end of each cylinder sleeve 41, and the flange 41 a is fitted to the metal gasket 36 in a state where the flange 41 a is fitted in a step portion 35 b formed in the sleeve support hole 35 a of the sleeve support flange 35 on the rear side. Abutting and positioning in the axial direction. A piston 42 is slidably fitted inside each cylinder sleeve 41, and the front end of the piston 42 abuts a dimple 31 a formed on the swash plate 31, and the rear end of the piston 42 and the rotor head 38 are in contact with each other. A steam expansion chamber 43 is defined between them.

  Next, the structure of the rotary valve 71 that supplies and discharges steam to and from the five expansion chambers 43 of the rotor 22 will be described with reference to FIGS.

  As shown in FIG. 4, the rotary valve 71 arranged along the axis L of the rotor 22 includes a valve main body 72, a carbon fixed side valve plate 73, carbon, and Teflon (registered trademark), And a movable valve plate 74 made of metal or the like. The movable side valve plate 74 is fixed to the rear surface of the rotor 22 with a bolt 76 that is screwed into the oil passage closing member 45 (see FIG. 2) while being positioned in the rotational direction by a knock pin 75. The bolt 76 also has a function of fixing the rotor head 38 to the output shaft 32.

  The valve body 72 is fixed by a plurality of bolts 92... A circular flange 72 a formed integrally at the rear thereof abuts the rear surface of the rear cover 18 via a seal member 91. At this time, the support section 72 b having a circular cross section formed integrally with the front portion of the valve main body 72 is fitted into the support hole 18 a 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, and a fixed side valve plate 73 held inside the holder 79 via a seal member 82. Is prevented by Teflon-coated knock pins 81, 81. The fixed side valve plate 73 is positioned in the rotational direction by the knock pins 81, 81, but is supported floating so as to be slightly movable in the radial direction and the axis L direction.

  A pressure chamber 84 having a circular cross section opens on a mating surface 83 where the valve main body 72 abuts on the fixed valve plate 73. A steam supply pipe 85 that penetrates the valve main body 72 through the seal member 93 extends to the mating surface 83 through the center of the pressure chamber 84, and a coil spring is provided on the outer periphery of the steam supply pipe 85 inside the pressure chamber 84. 86, a packing retainer 87, and a V packing 88 are sequentially arranged.

  A slight gap is set between the tip of the steam supply pipe 85 and the mating surface 83 of the fixed valve plate 73. Even if the steam supply pipe 85 is thermally expanded in the direction of the axis L, the tip of the steam supply pipe 85 is the mating surface. 83 is not interfered with. One through hole 85 a formed in the steam supply pipe 85 communicates with the rear portion of the pressure chamber 84. The high-temperature and high-pressure steam supplied to the pressure chamber 84 urges the fixed side valve plate 73 toward the movable side valve plate 74 and exerts a function of improving the sealing performance by bringing the sliding surfaces 77 into close contact with each other. The number of the through holes 85a may be plural according to the strength of the steam supply pipe 85 and the required steam supply amount to the pressure chamber 84.

  As apparent from FIGS. 4 and 9, the packing retainer 87 biased by the coil spring 86 having an equal diameter which is not tapered is formed on the flat surface 87a with which the coil spring 86 abuts and on the opposite side of the flat surface 87a. And a through-hole 87c that fits loosely on the outer periphery of the steam supply pipe 85. The V-packing 88 held by the packing retainer 87 includes a first seal lip S1 that seals between the conical surface 88a supported by the conical surface 87b of the packing retainer 87 and the mating surface 83 of the fixed valve plate 73. And a second seal lip S2 that seals between the pressure chamber 84 and the inner peripheral surface 84a of the pressure chamber 84.

  The V-packing 88 is mainly intended for sealing with the inner peripheral surface 84a of the pressure chamber 84. The second seal lip S2 is deformed radially outward by the vapor pressure of the pressure chamber 84 to thereby change the inner periphery. It is made to adhere to the surface 84a. Therefore, the second seal lip S2 can follow the expansion of the inner diameter of the inner peripheral surface 84a of the pressure chamber 84 due to the thermal expansion of the valve main body 72, and can ensure the sealing performance.

  The coil spring 86 provides a preload that presses the V packing 88 against the mating surface 83 with the fixed valve plate 73 before the pressure of the high-temperature and high-pressure steam rises, and also vibrates the fixed valve plate 73 with the seal member 82 and the pressure chamber. It has the function to attenuate by cooperation with the pressure of the high-temperature high-pressure steam in 84. The packing retainer 87 has a function of holding the V packing 88 in a correct posture in the pressure chamber 84 and increasing the durability of the V packing 88 by blocking the heat of the high-temperature and high-pressure steam.

  In addition, the coil spring 86 has a structure in which the spring seat is eliminated in order to increase the number of spring windings in the small space of the pressure chamber 84, and is interposed between the V packing 88 without directly contacting the V packing 88. By using the packing retainer 87 as a spring seat, it is not necessary to provide a special spring seat on the V-packing 88, and the dimension of the pressure chamber 84 in the axis L direction can be increased while ensuring the maximum length of the coil spring 86. It can be downsized.

  As is clear from FIGS. 4 to 8, the steam supply pipe 85 is disposed on the axis L of the rotor 22, and the steam discharge pipe 89 is disposed biased radially outward. The first steam passage P <b> 1 formed inside the steam supply pipe 85 communicates with the sliding surface 77 via the second steam passage P <b> 2 formed in the fixed side valve plate 73. 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 fourths 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 where the second steam passage P2 opens to the sliding surface 77 is circular, whereas the portion where the fifth steam passage P5 opens to the sliding surface 77 is formed in an arc shape with the axis L as the center.

  Further, the sliding surface 77 of the fixed side valve plate 73 is provided with an arcuate fifth steam passage P5 and two arcuate sixth steam passages P6 and P6 that are in communication with each other. The passages P6 and P6 communicate with two seventh steam passages P7 and P7 formed in the valve body 72 at the mating surface 83. A steam discharge chamber 94 is formed between the casing body 12 and the rear cover 18, and this steam discharge chamber 94 communicates with the steam discharge pipe 89 and two seventh steam passages formed in the valve body 72. It communicates with P7 and P7.

  On the sliding surface 77, a circular second steam passage P2 for supplying high-temperature and high-pressure steam and an arc-shaped fifth steam passage P5 for discharging low-temperature and low-pressure steam are opened, and five movable valve plates 74 are provided. The moment when one of the third steam passages P3... Communicates with the circular second steam passage P2 is the intake stroke, and after the third steam passage P3 is disconnected from the second steam passage P2, the arc-shaped second steam passage P3. The expansion stroke occurs until the fifth steam passage P5 communicates, and the exhaust stroke occurs when the third steam passage P3 communicates with the arcuate fifth steam passage P5.

  As apparent from FIGS. 4, 6, and 7, two high-pressure working medium introduction passages 73 a and 73 a are opened on the mating surface 83 of the fixed valve plate 73 of the rotary valve 71, and these high-pressure working mediums Two high-pressure working medium introduction holes 73 b and 73 b extending from the bottoms of the introduction passages 73 a and 73 a are opened in the sliding surface 77 between the movable side valve plate 74. The high-pressure working medium introduction passages 73a and 73a communicate with the steam supply pipe 85 through a gap between the packing retainer 87 and the fixed side valve plate 73. Therefore, high-temperature and high-pressure steam from the steam supply pipe 85 is high-pressure from the gap. It is supplied to the sliding surface 77 through the working medium introduction passages 73a and 73a and the high pressure working medium introduction holes 73b and 73b.

  As best shown in FIG. 6, two high-pressure working medium introduction holes 73 b and 73 b that open to the sliding surface 77 of the fixed-side valve plate 73, and a second steam passage P <b> 2 that opens to the sliding surface 77. Are arranged at equal angles in the circumferential direction around the axis L, that is, at intervals of 120 °. Further, the radial positions of the two high-pressure working medium introduction holes 73b and 73b opened in the sliding surface 77 are closer to the axis L than the radial inner ends of the second steam passage P2 and the fifth steam passage P5. ing. Therefore, even if the movable valve plate 74 rotates with respect to the fixed valve plate 73, two high-pressure working media are provided in the five third steam passages P3 that open to the sliding surface 77 of the movable valve plate 74. The introduction holes 73b and 73b do not communicate with each other.

  Next, the operation of the expander E of the present embodiment having the above configuration will be described.

  The high-temperature and high-pressure steam generated by heating water in the evaporator passes through the first steam passage P1 in the steam supply pipe 85, the mating surface 83, and the second steam passage P2 of the fixed-side valve plate 73. A sliding surface 77 with 74 is reached. The second steam passage P2 opened in the sliding surface 77 is instantaneously communicated with the five third steam passages P3 formed in the movable valve plate 74 that rotates integrally with the rotor 22 at a predetermined timing. The high-pressure steam is supplied from the third steam passage P3 to the expansion chamber 43 in the cylinder sleeve 41 through the fourth steam passage P4 formed in the rotor 22.

  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 its 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 a reaction force that the piston 42 receives from the swash plate 31. Each time the rotor 22 rotates by one fifth, high-temperature and high-pressure steam is supplied into adjacent new expansion chambers 43 and the rotor 22 is continuously rotated.

  The low-temperature and low-pressure steam pushed out of the expansion chamber 43 while the piston 42 reaching 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 4 steam passage P4, the third steam passage P3 of the movable side valve plate 74, the sliding surface 77, the fifth steam passage P5 and the sixth steam passages P6, P6 of the fixed side valve plate 73, and the mating surface 83 The steam is supplied to the condenser through the seventh steam passages P7 and P7 of the valve main body 72, the steam discharge chamber 94, and the steam discharge pipe 89.

  Since the rotary valve 71 supplies and discharges steam to and from the axial piston cylinder group A through a flat sliding surface 77 between the fixed side valve plate 73 and the movable side valve plate 74, it is possible to effectively prevent steam leakage. Can do. This is because the flat sliding surface 77 is easy to process with high accuracy, and thus the clearance can be managed more easily than the cylindrical sliding surface. In addition, when the pressure of the high-temperature and high-pressure steam supplied to the expander E 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, but as the pressure increases. Since the pressure load generated by the pressure chamber 84 is increased and the surface pressure of the sliding surface 77 is increased, the sealing performance corresponding to the pressure of the high-temperature high-pressure steam can be exhibited.

  By the way, the high temperature and high pressure steam supplied from the second steam passage P2 of the fixed side valve plate 73 to the sliding surface 77 between the fixed side valve plate 73 and the movable side valve plate 74 has the second steam passage P2 of 5 of the movable side valve plate 74. .. Is supplied to the expansion chamber 43 at the moment when it communicates with any one of the third steam passages P3... And is not blocked by the sliding surface 77 when it does not communicate with any third steam passage P3. As described above, the second steam passage P2 and the third steam passage P3 are repeatedly communicated and cut off with the rotation of the movable valve plate 74, and the steam pressure in the vicinity of the second steam passage P2 decreases during the communication. The surface pressure of the sliding surface 77 increases, and when shut off, the vapor pressure near the second steam passage P2 increases and the surface pressure of the sliding surface 77 decreases.

  Accordingly, the degree of adhesion between the fixed valve plate 73 and the movable valve plate 74 periodically changes in the vicinity of the second steam passage P2, which causes leakage of high-temperature and high-pressure steam from the sliding surface 77 or sliding. This may cause abnormal wear of the surface 77.

  However, according to the present embodiment, the second steam passage P2 and the two high-pressure working medium introduction holes 73b and 73b are opened at equal angles in the circumferential direction on the sliding surface 77 of the fixed-side valve plate 73. The high-temperature and high-pressure steam is uniformly supplied to the entire sliding surface 77 from the second steam passage P2 and the two high-pressure working medium introduction holes 73b and 73b, and the behavior of the fixed-side valve plate 73 supported by floating is stabilized. Leakage of high temperature and high pressure steam and abnormal wear of the sliding surface 77 can be suppressed. In particular, since steam is used as the working medium, the water in which the steam is liquefied intervenes on the sliding surface 77, so that the lubrication performance, cooling performance, sealing performance, etc. of the sliding surface 77 are greatly improved. This can contribute to improving the durability of the valve 71. In particular, even if the sealing degree of the sliding surface 77 is increased so as to prevent leakage of high-temperature and high-pressure steam, the sliding surface 77 can be prevented from becoming solid lubrication and wear resistance can be improved.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the expander E according to the embodiment includes the axial piston cylinder group A as the operation unit, but the structure of the operation unit is not limited thereto.

  The rotary fluid machine of the present invention is not limited to the expander E, and can be applied to a compressor. When the rotary fluid machine is the expander E, the high-pressure working medium introduced into the sliding surface 77 from the high-pressure working medium introduction holes 73b, 73b is the third steam passage P3 in the expansion stroke from the second steam passage P2. When the rotary fluid machine is a compressor, the high-pressure working medium introduced into the sliding surface 77 from the high-pressure working medium introduction holes 73b and 73b is the third steam in the compression stroke. It is a high-pressure working medium discharged from the passage P3... To the second steam passage P2.

  In the embodiment, the fixed-side valve plate 73 includes two high-pressure working medium introduction holes 73b and 73b, but the number is arbitrary.

  In the embodiment, the high-pressure working medium introduction holes 73b and 73b are opened further radially inward than the radially inner ends of the second steam passage P2 and the fifth steam passage P5. You may open to the radial direction outer side further than the radial direction outer end of the steam path P5.

Vertical section of expander 2 enlarged view of FIG. Exploded perspective view of rotor 4 enlarged view of FIG. 5-5 arrow view of FIG. 6-6 arrow view of FIG. 7-7 arrow view of FIG. 8-8 arrow view of FIG. Perspective view of coil spring, packing retainer and V packing

Explanation of symbols

11 Casing 22 Rotor 71 Rotary valve 73 Fixed side valve plate 73b High pressure working medium introduction hole 74 Movable side valve plate 77 Sliding surface A Axial piston cylinder group (actuating part)
P2 Second steam passage (first high-pressure working medium passage)
P3 Third steam passage (second high-pressure working medium passage)

Claims (3)

A casing (11);
A rotor (22) rotatably supported by the casing (11);
An actuator (A) provided in the rotor (22);
A rotary valve (71) provided between the casing (11) and the rotor (22) for controlling the supply / discharge of the working medium to the working part (A),
The rotary valve (71) contacts the fixed valve plate (73) supported on the casing (11) side and the movable valve plate (74) supported on the rotor (22) side on the sliding surface (77). A single first high-pressure working medium passage (P2) opened from the fixed valve plate (73) to the sliding surface (77), and from the movable valve plate (74) to the sliding surface (77). In the rotating fluid machine in which the plurality of second high-pressure working medium passages (P3) that are opened communicate sequentially with the rotation of the rotor (22),
A rotary fluid machine, wherein a high-pressure working medium introduction hole (73b) for introducing a high-pressure working medium into a sliding surface (77) is opened in a fixed side valve plate (73).   The rotary fluid machine according to claim 1, wherein the first high-pressure working medium passage (P2) and the high-pressure working medium introduction hole (73b) are arranged so as to be equiangular in the circumferential direction. The high-pressure working medium introduced into the sliding surface (77) from the high-pressure working medium introduction hole (73b) is supplied from the first high-pressure working medium passage (P2) to the second high-pressure working medium passage (P3) in the expansion stroke. The high-pressure working medium that is discharged from the second high-pressure working medium passage (P3) in the compression stroke to the first high-pressure working medium passage (P2). The rotary fluid machine according to 2.

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