JP2005163579A - Rotating fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure the sealing performance of a sealing member even if a fixed side valve plate of a rotary valve of a rotating fluid machine is put in oscillating motion. <P>SOLUTION: A pressure chamber 84 into which high-temperature and high-pressure stream is introduced, is opened to a mating surface 83 of the valve body part 72 of the rotary valve 71 with a fixed side valve plate 73. A leakage of steam to the mating surface 83 is prevented by the V-packing 88 enclosed in the pressure chamber 84, and the fixed side valve plate 73 and a movable side valve plate 74 are brought into close contact at a sliding surface 77 by the pressure applied to the pressure chamber 84. A seal lip S1 of the V-packing 88 and a seat surface 73a of the fixed side valve plate 73 on which the seal lip S1 abuts are formed in spherical surface shape. Consequently, even if the fixed side valve plate 73 supported to float is put in oscillating motion following the movable side valve plate 74 rotated together with a rotor, the seal lip S1 is positively brought into close contact with the seat surface 73a to secure the sealing performance of an abutting part. <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

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 not supplied 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 against the sliding surface with a spring, and when the combustion gas is supplied, the pressing member is pressed with the pressure of the combustion gas via the free piston to be in close contact with the sliding surface. This is known from the following patent document 1.
Japanese Utility Model Publication No. 61-155610

  By the way, in a rotary valve for an expander that controls supply / discharge of a working medium by contacting a fixed valve plate supported by a valve body and a movable valve plate supported by a rotor on a sliding surface, the valve body A pressure chamber that opens to the mating surface with the fixed side valve plate is formed on the surface, and the pressure of the working medium is applied to the back surface of a flexible sealing member such as a V-packing housed in the pressure chamber. It is conceivable to secure the sealing performance of the sliding surface by pressing the side valve plate against the movable side valve plate.

  However, it is inevitable that the movable side valve plate provided on the rotor will swing slightly, and if the fixed side valve plate that contacts the movable side valve plate via the sliding surface swings, Adhesion between the seating surface of the side valve plate and the lip of the sealing member of the pressure chamber may be impaired, and steam may leak from that portion and the expander may not exhibit sufficient performance.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to ensure the sealing performance of a sealing member even when a fixed valve plate of a rotary valve of a rotary fluid machine swings.

  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. The movable valve plate is brought into contact with the sliding surface perpendicular to the axis, and a pressure chamber into which a high-pressure working medium is introduced is opened on the mating surface with the fixed valve plate of the valve body, and the pressure chamber is stored in this pressure chamber. The sealing member prevents the working medium from leaking from the pressure chamber to the mating surface, and the pressure of the working medium acting on the pressure chamber is used to fix the fixed side bar. A rotary fluid machine for tightly contacting a valve plate and a movable valve plate on a sliding surface, wherein a lip of a sealing member and a seating surface of a fixed valve plate with which the sealing member abuts have a spherical shape centered on the axis A rotating fluid machine characterized by the above is proposed.

  According to the second aspect of the present invention, in addition to the configuration of the first aspect, the lip of the sealing member has a convex shape, and the seating surface of the stationary valve plate has a concave shape. A machine is proposed.

  The axial piston cylinder group A of the embodiment corresponds to the operating portion of the present invention, the first seal lip S1 of the embodiment corresponds to the seal lip of the present invention, and the V packing 88 of the embodiment corresponds to the seal of the present invention. Corresponds to the member.

  According to the configuration of the first aspect, the pressure chamber into which the high-pressure working medium is introduced is opened on the mating surface of the valve body of the rotary valve with the fixed valve plate, and the pressure member is accommodated in the pressure chamber. When preventing the working medium from leaking from the chamber to the mating surface, the fixed valve plate and the movable valve plate are brought into close contact with the sliding surface by the pressure of the working medium acting on the pressure chamber. Since the seating surface of the fixed valve plate with which the lip abuts has a spherical shape, even if the fixed valve plate that is floatingly supported swings following the movable valve plate that rotates with the rotor, the fixed valve It is possible to ensure the sealing performance of the abutting portion by reliably bringing the lip of the sealing member into close contact with the seat surface of the plate.

  According to the configuration of the second aspect, since the lip having the convex shape of the seal member is brought into contact with the seat surface having the concave shape of the fixed side valve plate, the swinging movement of the fixed side valve plate supported by floating is prevented. The followability of the seal member is further improved, and the sealability is further improved.

  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 seating surface 73a at the center of the mating surface 83 of the fixed side valve plate 73 is recessed in a spherical shape having a center on the axis L, and the first seal lip S1 of the V packing 88 that abuts on the seating surface 73a has the axis L It protrudes in a spherical shape with a center on the top. The curvature radii and centers of the seating surface 73a and the first seal lip S1 are the same, and therefore the first seal lip S1 is in close contact with the seating surface 73a without any gaps, and the sealing performance is secured. Can be swung.

  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.

  As is apparent from FIG. 6, a circular second steam passage P2 for supplying high-temperature and high-pressure steam and a circular arc-shaped fifth for discharging low-temperature and low-pressure steam on the sliding surface 77 of the fixed-side valve plate 73 of the rotary valve 71. The steam passage P5 is open, and the moment when one of the five third steam passages P3... Of the movable side valve plate 74 communicates with the circular second steam passage P2 is the intake stroke, and the third steam passage P3. Is the expansion stroke from when communication with the second steam passage P2 is interrupted until communication with the arcuate fifth steam passage P5, and the third steam passage P3 communicates with the arcuate fifth steam passage P5. The exhaust stroke is performed during the period.

  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, it is inevitable that the output shaft 32 of the rotor 22 is inclined with respect to the axis L due to a slight misalignment of the combined angular bearings 23 and 23 and the radial bearing 24. For this reason, the movable side valve plate supported by the rotor 22 is unavoidable. When the head 74 swings, the fixed valve plate 73 that is floatingly supported by the valve body 72 and contacts the movable valve plate 74 via the sliding surface 77 also swings. At this time, the V packing 88 housed in the pressure chamber 84 formed in the valve body 72 has a relatively large degree of freedom for movement in the direction of the axis L, but is inclined with respect to the axis L. The first seal lip S1 of the V-packing 88 is separated from the seat surface 73a of the fixed side valve plate 73 and the sealing performance may be lost. .

  However, according to the present embodiment, the seat surface 73a of the fixed side valve plate 73 and the first seal lip S1 of the V packing 88 that contacts the fixed side valve plate 73 are in contact via a common spherical surface. The plate 73 can be swung while the seat surface 73a and the first seal lip S1 are in close contact with each other, the sealing performance of that portion is ensured to prevent leakage of high-temperature and high-pressure steam, and the output of the expander E A decrease can be prevented. In particular, the seating surface 73 of the fixed-side valve plate 73 has a concave curved surface, and the first seal lip S1 of the V-packing 88 has a convex curved surface, so that the followability of the V-packing 88 to the swinging motion of the fixed-side valve plate 73 is improved. It can be further increased to suppress the leakage of high-temperature and high-pressure steam more effectively.

  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 seat surface 73a of the fixed valve plate 73 is recessed to project the first seal lip S1 of the seal member 88. However, the relationship is reversed to project the seat surface 73a. The seal lip S1 may be recessed.

  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. 5-5 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 72 Valve body 73 Fixed valve plate 73a Seat surface 74 Movable valve plate 77 Sliding surface 83 Matching surface 84 Pressure chamber 88 V packing (seal member)
A Axial piston cylinder group (working part)
L axis S1 first seal lip (seal lip)

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 brought into contact with the sliding surface (77) perpendicular to the axis (L), and a high-pressure working medium is introduced into the mating surface (83) of the valve main body (72) with the fixed valve plate (73). The pressure chamber (84) is opened, and the seal member (88) accommodated in the pressure chamber (84) prevents the working medium from leaking from the pressure chamber (84) to the mating surface (83), and the pressure is reduced. A rotary fluid machine that causes the stationary valve plate (73) and the movable valve plate (74) to closely contact each other on the sliding surface (77) with the pressure of the working medium acting on the chamber (84),
The lip (S1) of the seal member (88) and the seating surface (73a) of the fixed side valve plate (73) with which the lip (S1) abuts have a spherical shape centered on the axis (L). Rotating fluid machine characterized by. The rotary fluid machine according to claim 1, wherein the lip (S1) of the sealing member (88) has a convex shape, and the seating surface (73a) of the stationary valve plate (73) has a concave shape.

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