JP2005163580A - Rotating fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure adhesion of sliding surfaces of a fixed valve plate and a movable valve plate of a rotary valve even when a rotor of a rotary fluid machine swings.
A rotary valve 71 for controlling supply and discharge of high-temperature and high-pressure steam to an expansion chamber of an expander includes a fixed-side valve plate 73 floatingly supported on the casing side and a movable-side valve plate 73 floatingly supported on the rotor side. Are brought into contact with each other on the sliding surface 77, so that the swinging motion of the rotor is effectively absorbed by the swinging of both valve plates 73 and 74, and the adhesion of the sliding surface 77 is ensured to ensure high temperature and high pressure steam. Leakage can be minimized. Further, since the steam passage P3r on the movable side valve plate 74 side and the steam passage P3f on the rotor side are hermetically communicated via the C seal 51, the steam passages P3r, Leakage of high-temperature and high-pressure steam from the P3f communicating portion can be prevented.
[Selection] Figure 5

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, it is inevitable that the rotor is swung out of the axis due to slight displacement of the bearing that supports the rotor on the casing or backlash, and the fixed valve plate provided on the casing side of the rotary valve and the rotor side are provided. There is a possibility that the adhesiveness of the sliding surface with the movable side valve plate will be impaired, and steam will leak from that portion and the rotating fluid machine will not be able to exhibit sufficient performance.

  Therefore, it is conceivable that the fixed valve plate is floatingly supported on the casing to follow the swinging motion of the movable valve plate to ensure the adhesion of the sliding surface. However, the fixed valve plate is floatingly supported. It was difficult to sufficiently prevent leakage of steam by itself.

  The present invention has been made in view of the above-described circumstances, so that even if the rotor of a rotary fluid machine swings, the adhesion of the sliding surfaces of the fixed valve plate and the movable valve plate of the rotary valve can be ensured. The purpose is to.

  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 part. The rotary valve is supported on the rotor side by a fixed side valve plate that is floatingly supported by a valve main body part that is fixed to the casing side so as not to rotate. A rotary fluid machine in which a movable valve plate is brought into contact with a sliding surface orthogonal to the axis, and the movable valve plate is floatingly supported on the rotor, and the working medium passage provided on the movable valve plate side and the rotor side The rotary fluid machine is characterized in that the working medium passage provided in the airtight communication is communicated through the seal member. It is.

  According to a second aspect of the present invention, in addition to the structure of the first aspect, the seal member is a seal disposed so as to surround the working medium passage and opened radially inward. A rotating fluid machine is proposed.

  The axial piston cylinder group A of the embodiment corresponds to the operating portion of the present invention, and the rear third steam passage P3r and the front third steam passage P3f of the embodiment correspond to the working medium passage of the present invention. The C seal 51 corresponds to the seal member of the present invention.

  According to the configuration of the first aspect, the rotary valve for controlling the supply / discharge of the working medium to / from the working part of the rotary fluid machine includes the fixed side valve plate floatingly supported on the casing side and the movable side floatingly supported on the rotor side. Since the valve plate is in contact with the sliding surface, the swinging motion when the rotor rotates is effectively absorbed by the swinging of both the fixed side valve plate and the movable side valve plate. Adhesion can be secured and leakage of the working medium can be minimized. In addition, since the working medium passage on the movable side valve plate side and the working medium passage on the rotor side are communicated in an airtight manner via the seal member, the movable side valve plate is allowed to swing while allowing the movable side valve plate to swing. It is possible to prevent leakage of the working medium.

  According to the configuration of the second aspect, the seal member that connects the working medium passage on the movable valve plate side and the working medium passage on the rotor side in an airtight manner is disposed so as to surround the working medium passage and inward in the radial direction. Since the seal is an open seal, the seal can be expanded by the pressure of the working medium to enhance the sealing performance, and the elastic support of the seal does not hinder the floating support of the movable valve plate. In addition, since the heat transfer area of the C seal is small, heat escape from the movable side valve plate to the rotor is suppressed, the temperature of the movable side valve plate is quickly raised by the heat of the working medium, and the steady state is reached. The leakage of the working medium during the transition period can be minimized.

  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 12 show an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of an expander, FIG. 2 is an enlarged view of part 2 of FIG. 1, FIG. 3 is an exploded perspective view of a rotor, and FIG. 4 is an enlarged view of 5 part of FIG. 4, FIG. 6 is a view taken along line 6-6 of FIG. 5, FIG. 7 is a view taken along line 7-7 of FIG. 4 is a view taken along line 8-8 in FIG. 4, FIG. 9 is a view taken along line 9-9 in FIG. 4, FIG. 10 is a view taken along line 10-10 in FIG. 5, and FIG. FIGS. 12A and 12B are perspective views of a coil spring, a packing retainer, and a 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 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 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 11, 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. The conical surface 87b and the through-hole 87c loosely fitted on the outer periphery of the steam supply pipe 85 are provided. 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 apparent from FIGS. 5, 6, 10 and 11, the base plate 46 is positioned on the rear surface of the rotor head 38 in the rotational direction by the knock pin 75, and is screwed onto the oil passage closing member 45 (see FIG. 2). The bolts 76 are fixed together. The bolt 76 also has a function of fixing the rotor head 38 to the output shaft 32, and the rotor head 38 and the base plate 46 constitute a part of the rotor 22. An annular holder 47 is fixed to the rear surface of the base plate 46 with a plurality of bolts 48. The movable side valve plate 74 is floatingly supported between the base plate 46 and the holder 47 so as to be slightly movable in the radial direction and the axis L direction. The Three semicircular cutouts 47a formed on the inner periphery of the holder 47, three semicircular cutouts 74a formed on the outer periphery of the movable valve plate 74, and three pins formed on the base plate 46 When the three knock pins 49 are fitted into the holes 46a, the movable side valve plate 74 is prevented from rotating with respect to the rotor 22.

  As apparent from FIGS. 4 to 11, 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 rear third steam passages P3r ... and five front third steam passages P3f ... arranged at equal intervals so as to surround the axis L pass through the movable side valve plate 74 and the base plate 46. Both ends of the five fourth steam passages P4 formed in the rotor 22 so as to surround L communicate with the front third steam passages P3f and the expansion chamber 43, respectively.

  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 rear third steam passages P3r communicates with the circular second steam passage P2 is an intake stroke, and the rear third steam passages P3r. The expansion stroke is performed until the fifth steam passage P5 communicates, and the exhaust stroke is performed while the rear third steam passage P3r... Communicates with the arcuate fifth steam passage P5.

  The base plate 46 is formed with five seal member housing grooves 46b... That open to the mating surface 50 with the movable side valve plate 74 and surround the five front third steam passages P3f. The metal C seals 51 having a C-shaped cross section and formed in an annular shape are attached to the seal member receiving grooves 46b. The C seals 51 are mounted so that the open portions of the cross section are radially inward, and when high-temperature and high-pressure steam is supplied to the front third steam passage P3f and the rear third steam passage P3r, The C-shaped cross-section is expanded by the pressure, so that the movable side valve plate 74 can be floatingly supported with respect to the base plate 46, and the communicating portion of the front third steam passage P3f... And the rear third steam passage P3r. Seal hermetically.

  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 at a predetermined timing with five rear third steam passages P3r formed in the movable valve plate 74 rotating integrally with the rotor 22. The high-temperature high-pressure steam is supplied from the rear third steam passage P3r to the expansion chamber 43 in the cylinder sleeve 41 through the mating surface 50, the front third steam passage P3f formed in the base plate 46, and the fourth steam passage P4 formed in the rotor 22. Is done.

  The piston 42 fitted to the cylinder sleeve 41 is expanded by the high-temperature and high-pressure steam expanding in the expansion chamber 43 even after the communication between the second steam passage P2 and the rear third steam passage P3r is cut off as the rotor 22 rotates. Is pushed forward from the top dead center toward the bottom dead center, and its front end presses the dimple 31a 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 front third steam passage P3f of the base plate 46, the mating surface 50, the rear third steam passage P3r of the movable valve plate 74, the sliding surface 77, and the first of the fixed valve plate 73. Supplied to the condenser through the five steam passages P5 and the sixth steam passages P6 and P6, the mating surface 83, the seventh steam passages P7 and P7 of the valve main body 72, the steam discharge chamber 94, and the steam discharge pipe 89 Is done.

  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.

  Now, in the combined angular bearings 23 and 23 and the radial bearing 24 that rotatably support the rotor 22 on the casing 11, a slight radial gap is formed to absorb thermal expansion due to a temperature difference between cold and hot. The rotor 22 is inevitably slightly inclined with respect to the axis L due to the gap. Therefore, the rotor 22 swings with rotation, and the adhesion of the sliding surfaces 77 of the fixed side valve plate 73 and the movable side valve plate 74 is impaired, and the leakage of high temperature and high pressure steam may occur. There is. In particular, when the expansion machine E starts up, or when the vibration is intense, such as during the transition from cold to hot, when the rotational speed changes rapidly, or when the pressure of the high-temperature and high-pressure steam changes rapidly, etc. As a result, the swing of the rotor 22 becomes significant, and the amount of high-temperature and high-pressure steam leakage from the rotary valve 71 increases.

  However, in this embodiment, the fixed side valve plate 73 is floatingly supported by the valve body 72, and the movable side valve plate 74 is floatingly supported by the base plate 46, so that the rotor 22 swings. Also, the coherence of the fixed valve plate 73 and the movable valve plate 74 maintains the adhesion of the sliding surface 77, and effectively suppresses the leakage of high-temperature and high-pressure steam from the sliding surface 77, thereby outputting the expander E. A decrease can be prevented. Further, a C seal 51 that seals the communication part of the rear third steam passage P3r of the movable valve plate 74 and the front third steam passage P3f of the base plate 46 is provided on the mating surface 50 of the movable valve plate 74 and the base plate 46. Since the C seals 51 are elastically deformed, the movable valve plate 74 can be allowed to tilt.

  Further, since the movable side valve plate 74 is formed to be extremely thin and has a small heat mass, the temperature is effectively increased by the high-temperature and high-pressure steam passing through the rear third steam passage P3r. Moreover, since the movable side valve plate 74 is in contact with the base plate 46 via the C seals 51 having a small heat transfer area, the movable side valve plate 74 is movable while minimizing escape from the heat from the movable side valve plate 74 side to the base plate 46 side. The temperature rise of the side valve plate 74 can be promoted. Thereby, the temperature of the movable side valve plate 74 at the time of transition from cold to hot can be raised to a steady state at an early stage, and the sealing performance of the sliding surface 77 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.

  In the embodiment, the movable side valve plate 74 is supported on the rotor head 38 via the independent base plate 46, but the base plate 46 may be integrally formed of the same member as the rotor head 38.

  The rotary fluid machine of the present invention is not limited to the expander E, and can be applied to a compressor.

Vertical section of expander 2 enlarged view of FIG. Exploded perspective view of rotor 4 enlarged view of FIG. 5 enlarged view of FIG. 6-6 arrow view of FIG. 7-7 arrow view of FIG. 8-8 arrow view of FIG. 9-9 arrow view of FIG. 10-10 arrow view of FIG. 11-11 line view of FIG. Perspective view of coil spring, packing retainer and V packing

Explanation of symbols

11 Casing 22 Rotor 51 Seal member (C seal)
71 Rotary Valve 72 Valve Body 73 Fixed Valve Plate 74 Movable Valve Plate 77 Sliding Surface A Axial Piston Cylinder Group (Operating Section)
L axis P3f front third steam passage (working medium passage)
P3r Rear third steam passage (working medium passage)

Claims (2)

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) includes a fixed valve plate (73) that is floatingly supported by a valve main body (72) that is fixed to the casing (11), and a movable valve plate that is supported by the rotor (22). (74) is a rotating fluid machine in which a sliding surface (77) perpendicular to the axis (L) is contacted,
The movable valve plate (74) is floatingly supported on the rotor (22), and the working medium passage (P3r) provided on the movable valve plate (74) side and the working medium passage (P3f) provided on the rotor (22) side are provided. And a rotary fluid machine characterized in that they are communicated in an airtight manner through a seal member (51). The rotary fluid machine according to claim 1, wherein the seal member (51) is a seal disposed so as to surround the working medium passage (P3r, P3f) and opened radially inward.

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