JP2006125305A - Variable displacement gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement gas compressor in which reduction in compression efficiency is prevented, and energy loss is inhibited, thus to ensure a smooth operation. <P>SOLUTION: The variable displacement gas compressor comprises a compression mechanism main body 12, leak paths, and valve mechanisms. The compressor main body 12 is provided with a compression chamber 16a, the volume of which is increased/decreased by slide movement of sliding bodies 22. The leak path communicates with the compression chamber 16a via an opening 33a made on the wall surface of the compression chamber 16a on which the sliding bodies 22 perform slide movements to allow a compressed gas to leak from the compression chamber 16a in the compression operation of the compressor main body 12. Each of the valve mechanisms opens/closes the opening 33a so as to change the volume of discharge of the compressed gas. In the valve mechanism, a valve element is provided for opening/closing the opening 33a in the outside of the compression chamber 16a, and a filler member is provided on the tip end opposing to the opening 33a of the valve element. The filler member is made of a material wearing out by sliding of the sliding body 22. The filler member fills up the recess formed of the opening and the tip end of the valve element at the position where the opening 33a of the valve element is closed. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a gas compressor used for compressing a refrigerant gas of a cooling device, for example, and more particularly to a variable capacity gas compressor capable of changing a discharge capacity of a compressed refrigerant gas.

  The main body of the gas compression mechanism has a compression chamber whose volume is increased / decreased by the sliding movement of the sliding body that rotates with the rotation of the rotating shaft that is driven to rotate, and the gas is supplied to the compression chamber as the volume of the compression chamber increases. , And the compressed gas is discharged as the volume decreases. In the capacity variable type gas compressor, a leak passage communicating with the compression chamber is provided through an opening opened on a wall surface of the compression chamber on which the sliding body slides, and the leak passage to the compression chamber is provided. A valve mechanism for opening and closing the opening is provided. If the opening is opened during the compression stroke of the compression mechanism main body, the compressed gas is allowed to leak from the compression chamber through the leak passage. (For example, refer to Patent Document 1).

  FIG. 5 shows a leak passage 2 provided in the vane rotary type gas compressor 1 and a valve mechanism 3 provided in the leak passage for opening and closing the opening 2a of the leak passage 2 as this conventional example. Yes. A cylinder chamber 5 in which a sliding body 4 made of a vane slides is divided into a plurality of compression chambers 5 a and 5 b by the vane 4, and the volume of each compression chamber 5 a and 5 b increases and decreases as the vane 4 slides. When the sliding direction of the vane 4 is indicated by an arrow labeled A1, the volume of the compression chamber 5a located on the sliding direction A1 side decreases with the sliding of the vane 4, but this volume decreases. When the opening 2a, which is one end of the leak passage 2, is closed during the compression stroke, the leakage of compressed gas from the compression chamber 5a through the leak passage 2 is prevented. Keep normal operation in quantity. On the other hand, if the opening 2a is opened, the leakage of compressed gas is allowed from the opening 2a until the sliding position of the vane 4 passes through the opening 2a, thereby reducing the discharge capacity of the gas compressor 1. Accordingly, by controlling the operation of the valve body 3a of the valve mechanism 3 between the closed position of the opening 2a shown in FIG. 5 and the open position of the opening, the normal discharge capacity at the normal discharge capacity in which the opening 2a is closed. A switching operation can be performed between the operation and the small capacity operation in which the opening 2a is opened.

By the way, the valve body 3a is formed of a hard material such as a metal material in order to enable its smooth and reliable opening and closing operation. When the valve body 3a formed of such a hard material protrudes from the opening 2a from the wall surface of the cylinder chamber 5, that is, the wall surface 6 of the compression chamber, at the closed position of the opening 2a, the valve body that has entered the cylinder chamber 5 Interference occurs between the tip of 3a and the vane 4 which is a sliding body that slides on the wall surface 6, and the smooth operation of the gas compressor 1 is hindered. Therefore, considering the manufacturing error of the valve body 3a, the tip of the valve body 3a is formed to be held at a distance d from the wall surface 6 so as not to enter the cylinder chamber 5 at the closed position. Has been.
JP 2001-280281 A (Page 2-5, FIG. 5)

  Therefore, in the normal operation in which the valve body 3a is held in the closed position, a recess having a depth corresponding to the interval d is formed in the opening 2a portion of the wall surface 6 by the opening and the tip of the valve body 3a in the closed position. A place 7 is formed. When the diameter φ of the recess 7 exceeds the thickness t of the vane 4, as indicated by an imaginary line, when the vane 4 passes through the portion of the recess 7, as shown by an arrow A 2 in FIG. 7, the compressed gas leaks from the compression chamber 5 a of the compression stroke divided by the vanes 4 toward the compression chamber 5 b of the suction stroke adjacent to the compression chamber. The leakage of the compressed gas that passes through the recess 7 causes a reduction in compression efficiency during normal operation.

  In order to prevent the flow of compressed gas indicated by the arrow A2, the diameter φ of the recess 7 is made smaller than the plate thickness t of the vane 4, or the plate thickness t of the vane 4 is made larger than the diameter φ of the recess 7. It is possible to do. However, in the former, the movement resistance of the vane 4 is increased by an increase in pressure loss due to the resistance of the gas flow flowing through the leak passage 2 during the small capacity operation, and the latter is similarly caused by an increase in the sliding resistance of the vane 4. Since the movement resistance is increased, the smooth operation of the gas compressor 1 is impaired in any case, resulting in energy loss.

  Therefore, an object of the present invention is to prevent a reduction in compression efficiency and energy loss during normal operation of a variable capacity gas compressor, and to ensure smooth operation thereof.

  In the present invention, basically, a filling member made of a material that can be worn by a sliding body such as a vane is provided at the tip of a valve body that opens and closes the opening of the leak passage, and the filling member opens at a position where the opening of the valve body is closed. And a recess formed between the tip of the valve body and the valve body tip.

  That is, the present invention has a compression chamber whose volume is increased or decreased by the sliding motion of the sliding body that rotates with the rotation of the rotating shaft that is driven to rotate, and gas is supplied to the compression chamber as the volume of the compression chamber increases. A compression mechanism main body that compresses and discharges the gas that has been sucked in as its volume decreases, and the sliding body slides to permit leakage of the compressed gas from the compression chamber during the compression stroke of the compression mechanism main body. A variable capacity gas compressor comprising a leak passage communicating with the compression chamber through an opening opened on a wall surface of the moving compression chamber, and a valve mechanism for opening and closing the opening for switching the discharge capacity of the compressed gas. The valve mechanism has a valve body that is movable in a direction approaching the opening and in a direction away from the opening to open and close the opening outside the compression chamber, and a tip that faces the opening of the valve body There is wear due to sliding of the sliding body Wherein the filling member for filling a recess formed by said distal end of said valve body and opening in the closed position of the opening of the valve body consists capacity material is provided.

  In the variable capacity type gas compressor according to the present invention, the filling member provided at the tip of the valve body is made of a material that can be worn by sliding of the sliding body. Even if the member is formed to protrude from the wall surface of the compression chamber into the compression chamber, for example, the excess portion protruding into the compression chamber of the filling member due to sliding of the sliding body in the acclimation operation or the trial operation or the like will be applied to the wall surface of the compression chamber. Wear almost identical shape. For this reason, even if the filling member is formed so as to protrude from the wall surface of the compression chamber in anticipation of manufacturing errors, it is provided at the tip of the valve body at the closed position of the valve body by a habituation operation or a trial operation as necessary. Since the front end surface of the filled member can be made to coincide with the wall surface of the compression chamber, in the subsequent normal operation, that is, in the normal discharge capacity operation, the valve body and the sliding body interfere with each other at the closed position of the valve body. The recess associated with the opening can be surely filled by the filling member without incurring the above. This reliably prevents leakage of compressed gas between adjacent compression chambers related to the recess during normal operation without increasing the vane plate thickness or reducing the opening diameter of the leak passage. It is possible to prevent a decrease in compression efficiency and energy loss during normal operation due to the leakage of the compressed gas, and to ensure a smooth operation.

  The compressor according to the present invention includes a cylinder that defines a cylinder chamber for the compression chamber, and a rotor that is rotatably disposed in the cylinder chamber, and the vane is moved along with the rotation of the rotor. A gas compressor having a vane rotary type gas compression mechanism in which the vane is held by a rotor to slide on a wall surface of a cylinder chamber, and the cylinder chamber is partitioned in the circumferential direction by the vane to form the compression chamber. Can be applied. In this vane rotary type gas compressor, the sliding body of the compression mechanism main body is a vane that is disposed in the cylinder chamber and slides on the wall surface of the cylinder chamber.

  A tip portion that fits into the opening can be formed at a closed position at an end portion of the valve body facing the opening, and the filling member can be fixed to the tip portion.

  The filling member can be formed of a resin material, or can be formed of a rubber material having elasticity.

  According to the present invention, even if the filling member protrudes from the opening of the leak passage into the compression chamber from the wall of the compression chamber, the excess portion is subjected to wear by the sliding body such as the vane in the acclimation operation, the trial operation, etc. The recess of the opening of the leak passage at the closed position of the valve body can be reliably filled by the filling member without causing various problems due to the valve body protruding into the compression chamber from the opening of the leak passage. Therefore, since the opening of the leak passage can be properly opened and closed, it is possible to prevent leakage of compressed gas between adjacent compression chambers related to the recess of the opening as in the conventional case during normal operation. Further, it is possible to prevent a reduction in compression efficiency and energy loss during normal operation due to this leakage, and to ensure a smooth operation.

  The present invention will be described in detail below with reference to illustrated embodiments.

  The gas compressor according to the present invention is used in, for example, an air conditioner mounted on an automobile, and although not shown, together with conventionally well-known condensers, expansion valves, evaporators, and the like that are components of the air conditioner The refrigerant circulation path for the cooling cycle is configured.

  As shown in FIG. 1, the gas compressor 10 according to the present invention includes a cylindrical housing 11 as a whole and a compression mechanism main body 12 accommodated in the housing. In the illustrated example, the housing 11 includes a housing body 11a that is open at one end and a front housing member 11b that closes the open end of the housing body. The front housing member 11b is formed with a suction port 13 connected to the evaporator, and the housing body 11a is formed with a discharge port 14 connected to the condenser.

  The compression mechanism main body 12 is a well-known concentric vane rotary type compression mechanism. The vane rotary type compression mechanism main body 12 includes a cylinder 15. In the illustrated example, the cylinder 15 includes a cylinder member 15a that is open at both ends, and a front side block 15b and a rear side block 15c that are a pair of end wall members that hermetically close the open ends of the cylinder member. Yes. The cylinder 15 defines a cylinder chamber 16 having an elliptical cross-sectional shape as shown in FIG.

  In the cylinder chamber 16, a columnar rotor 17 having a rotating shaft 17a is accommodated. As shown in FIG. 1, the rotation shaft 17a of the rotor 17 is arranged with its center axis aligned with that of the cylinder chamber 16, and is formed by sliding bearing surfaces 18a and 18b formed on the front side block 15b and the rear side block 15c. It is supported so that it can rotate.

  The rotating shaft 17a extends through the front side block 15b to the outside of the front side block. The rotational force of the engine of the vehicle can be transmitted to the rotary shaft 17a through a conventionally well-known electromagnetic clutch 19 provided at the extended end thereof. The rotor 17 is driven and rotated in one direction integrally with the shaft 17a. The rotary shaft 17 a is provided with an annular seal mechanism 20 similar to the conventional one for preventing leakage of lubricating oil to the electromagnetic clutch 19.

  A plurality of vane grooves 21 are formed in the rotor 17 as shown in FIG. Each vane groove 21 extends in the axial direction of the rotor 17 and opens to the outer peripheral surface of the rotor. In each vane groove 21, for example, a metal vane 22 is accommodated so as to be slidable and projectable in the circumferential direction of the rotor 17. Each vane 22 slides on the wall surface of the cylinder chamber 16 as the rotor 17 rotates by receiving the pressure of the lubricating oil supplied to the back pressure chamber 21 a formed at the bottom of each vane groove 21.

  The cylinder chamber 16 is partitioned in the circumferential direction of the rotor 17 by the vanes 22 held by the rotor 17, and is thereby divided into the compression chambers 16a. In the illustrated example, five compression chambers 16a are formed by five vanes. As is well known in the art, each compression chamber 16a repeatedly increases and decreases in volume in the suction stroke and the compression stroke accompanying the rotation of the rotor 17.

  In the vicinity of both short diameter portions of the cylinder chamber 16, a pair of suction ports 23 for sucking the refrigerant into the compression chambers 16 a are opened. A pair of discharge ports 24 for discharging the refrigerant compressed in the compression chambers 16a from the compression chambers are opened in the vicinity of both short diameter portions of the cylinder chamber 16. When viewed from the short diameter of the cylinder chamber 16, the respective suction ports 23 are arranged in the radial direction of the cylinder chamber 16 at positions displaced toward the rotation direction of the rotor 17 (clockwise in FIG. 2). Each discharge port 24 is arranged in alignment with the radial direction of the cylinder chamber 16 at a position deviated toward the direction opposite to the rotation direction (counterclockwise in FIG. 2). Each discharge port 24 is provided with a conventionally well-known check valve 25a for preventing the reverse flow of the refrigerant discharged from the compression chamber 16a and a valve support 25b for preventing excessive deformation of the check valve.

  As shown in FIG. 1, each discharge port 24 communicates with an oil separator 26 provided in the rear side block 15c via a check valve 25a. The suction port 23 communicates with a suction chamber 27 formed between the front housing member 11b and the front side block 15b.

  In the gas compressor 10 according to the present invention, when the rotational force of the engine is transmitted to the rotary shaft 17a via the electromagnetic clutch 19, the rotor 17 rotates integrally with the rotary shaft. When the rotor 17 rotates, each vane 22 held by the rotor 17 slides in the cylinder chamber 16 as the rotor 17 rotates. A suction force acts on the compression chamber 16a whose volume is increased by sliding of the vane 22. Accordingly, the refrigerant from the evaporator connected to the suction port 13 of the housing 11 is sucked into the compression chamber 16 a in the suction stroke where the suction force acts through the suction port 13, the suction chamber 27 and the suction port 23.

  When the rotation of the rotor 17 continues and the compression chamber 16a in the suction stroke shifts to a compression stroke in which the volume is reduced, the refrigerant in the compression chamber 16a is compressed. When the refrigerant pressure in the compression chamber 16a during the compression stroke exceeds a predetermined value, the compressed refrigerant is discharged from the compression chamber 16a toward the oil separator 26 through the check port 25a from the discharge port 24, as shown in FIG. The oil is guided to an oil separator 26 in a high-pressure chamber 28 formed between the rear side block 15c of the compression mechanism and the housing body 11a on the back side of the compression mechanism body 12 in the housing 11, and the oil separation It is discharged into the high-pressure chamber 28 through the container. The refrigerant from which the pulsating component has been removed in the high pressure chamber 28 is pumped to the condenser via the discharge port 14 formed in the housing 11.

  The lubricating oil separated from the refrigerant by the oil separator 26 is supplied from an oil reservoir 29 formed at the bottom of the high-pressure chamber 28 by the discharge pressure of the high-pressure chamber 28 to the same oil supply path 30 as in the past (for simplifying the drawing). Part of which is shown in the drawings) through the well-known oil reservoirs formed on the sliding bearing surfaces 18a, 18b and on the inner surfaces of the front side block 15b and the rear side block 15c. Are supplied to the recesses 31a and 31b. The lubricating oil supplied to the oil reservoir recesses 31 a and 31 b is supplied to the back pressure chamber 21 a as the back pressure of the vane 22.

  The gas compressor 10 according to the present invention is provided with a capacity changing means 32 as shown in FIG. 1 in order to change the discharge amount from the discharge port 14 without causing the rotation speed of the rotor 17 to change. It has been.

  As shown in an enlarged view in FIG. 3, the capacity changing means 32 includes a pair of leak passages 33 (one of which is shown in FIG. 3) formed in the front side block 15b, and each leak passage. And a valve mechanism 34 for interrupting communication.

  One end of each leak passage 33 communicates with the cylinder chamber 16 via a circular opening 33 a that opens to the cylinder chamber 16, and the other end of each leak passage 33 communicates with the suction chamber 27. As shown in FIG. 2, the opening 33a of each leak passage 33 opens to the cylinder wall of the compression chamber 16a in the compression region so as to open to the compression chamber 16a in the compression stroke. The diameter of the opening 33a is substantially equal to the thickness of the vane 22 in the illustrated example.

  Referring to FIG. 3 again, the front side block 15 b is formed with a recess 36 for accommodating the valve body 35 of the valve mechanism 34 in association with the leak passage 33. The opening of the recess 36 is opened to the suction chamber 27, and the opening 33 a is formed in the bottom of the recess that is the closed end of the recess 36. The recess 36 is fitted with a valve case 37 that is open at one end and that closes its opening, with its internal space 38 opened into the recess 36. In the internal space 38 of the valve case 37, the rod-shaped valve body 35 is accommodated so as to be movable toward and away from the opening 33a. The internal space 38 is used for the valve body 35. Functions as a pressure chamber.

  One end of the valve body 35 facing the open port 33a protrudes from the valve case 37, and the end of the valve body 35 facing the open port 33a is fitted into the open port 33a as shown in an enlarged view in FIG. A matable tip 35a is formed. The distal end portion 35a of the valve body 35 accommodated in the internal space 38 of the valve case 37 outside the compression chamber 16a is the protruding position of the valve body 35 shown in FIGS. The open port 33a is closed by fitting into the open port 33a formed in the above. In this closed position, as shown in FIG. 4, the distal end portion 35a does not protrude into the compression chamber 16a from the opening 33a, and there is an interval s between the cylinder wall surface 15d and the distal end surface of the distal end portion 35a. Is retained. A disc-like elastic filling member 39 having a thickness dimension s substantially equal to the interval s and an outer diameter substantially equal to the diameter of the opening 33a is fixed to the end face of the tip 35a of the valve body 35. ing. When the filling member 39 protrudes from the opening 33a, when the vane 22 slides on the protruding surface, the excess protruding due to the sliding of the vane 22 is easily worn or It is made of a rubber material that can be scraped off.

  Therefore, when the valve body 35 to which the filling member 39 is fixed is assembled to the compression mechanism main body 12, even if the filling member 39 slightly protrudes into the compression chamber 16a in the closed position, the acclimation operation or the trial operation of the gas compressor 10 is performed. The excess of the filling member 39 can be removed by sliding the vane 2 at. Thereby, after the break-in operation or the trial operation, the front end surface of the cylinder wall surface 15d and the front end portion 35a of the valve body 35 in the open port 33a without projecting the filling member 39 into the compression chamber 16a at the closed position of the open port 33a. It is possible to reliably fill the voids, that is, the recesses S, with the filling member 39.

  The valve body 35 receives the pressure of the lubricating oil introduced into the pressure chamber 38 that is the internal space of the valve case 37 at the other end as an acting force toward the closed position. In the example shown in FIG. 3, the pressurized lubricating oil in the oil reservoir 29 (see FIG. 1) communicates with the oil guide passage 40 (see FIG. 1) formed in the cylinder member 15a and the oil guide passage. It is guided into the pressure chamber 38 through a connecting passage 41 formed in the front side block 15 b and an inlet passage 42 formed in the peripheral wall of the valve case 37. By introducing the pressurized lubricating oil into the pressure chamber 38, the valve body 35 receives an acting force toward the closed position of the opening 33a. A flow rate adjusting valve 43 is provided between the oil guide passage 40 and the connection passage 41 to give a predetermined resistance value to the pressure liquid flow from the oil reservoir 29 toward the pressure chamber 38 of the valve mechanism 34. ing. As is well known in the art, the flow rate adjusting valve 43 includes a valve body 43b having an orifice 43a and a coil 43c that applies a spring force to reduce the flow rate to the valve body. When the pressure drops below the pressure in the oil reservoir 29 by exceeding a predetermined value, the resistance value acting on the pressure fluid flow from the oil guide passage 40 toward the connection passage 41 is increased.

  The valve body 35 in the closed position of the opening 33a is securely held in the closed position of the opening 33a as long as the acting force received at the other end exceeds the acting force received from the compression chamber 16a to the tip 35a. When the acting force acting on the other end becomes smaller than the acting force on the distal end portion 35a due to the reduction of the pressure in the pressure chamber 38, the valve body 35 operates toward the open position.

  In order to open the valve body 35, a pressure release path 44 for short-circuiting the connection path to the suction chamber 27 is connected to the connection path 41, and the pressure release path 44 is connected to the pressure release path. For example, an electromagnetic valve device 45 for intermittently connecting is provided.

  When the electromagnetic valve device 45 is held at the closed position where the communication of the pressure release path 44 is blocked, the pressurized lubricating oil in the oil reservoir 29 is introduced into the pressure chamber 38 via the flow rate adjusting valve 43 as described above. As a result, the valve body 35 is held in the closed position of the opening 33a. In the closed state of the opening 33a, the filling member 39 provided at the distal end portion 35a of the valve body 35 defines the recess S between the cylinder wall surface 15d of the opening 33a and the distal end surface of the distal end portion 35a of the valve body 35. Since filling is performed, leakage of the compressed gas through the recess S due to the opening 33a between the adjacent compression chambers 16a as shown by the arrow A2 in FIG. 5 is reliably prevented. Therefore, the compression mechanism main body 12 operates at the maximum discharge amount without incurring loss due to leakage.

  On the other hand, when the electromagnetic valve device 45 is held at an open position allowing the pressure discharge path 44 to communicate, the pressurized lubricating oil in the pressure chamber 38 is guided to the suction chamber 27 through the pressure discharge path 44, thereby The pressure in 38 is released. When the acting force acting on the other end of the valve body 35 becomes smaller than the acting force on the tip portion 35a due to the pressure release in the pressure chamber 38, the valve body 35 operates toward the open position, and the opening port 33a is opened. The flow rate adjusting valve 43 prevents excessive pressurized lubricating oil from flowing from the oil reservoir 29 toward the suction chamber 27 when the pressure in the pressure chamber 38 is released.

  When the valve body 35 is moved to the opening position of the opening 33 a by the opening operation of the electromagnetic valve device 45, a part of the compressed gas passes through the leak passage 33 through the leakage passage 33 in the compression stroke accompanying the sliding of the vane 22. When the vane 22 slides on the peripheral wall of the cylinder chamber 16, the substantial compression stroke is started by passing through the position of the opening 33a, so that the discharge amount by the compression mechanism main body 12 is reduced. .

  Therefore, the pressure release of the pressure chamber 38 can be controlled by controlling the operation of the electromagnetic valve device 45, and the opening / closing operation of the valve body 35 can be controlled via the operation of the electromagnetic valve device 45.

  In the gas compressor 10 according to the present invention, as described above, the filling member 39 provided at the tip 35a of the valve body 35 is made of a material that can be worn by sliding of the vane 22 that is a sliding body. Thus, even if the filling member 39 provided at the tip of the valve body 35 is formed to protrude from the cylinder wall surface 15d of the compression chamber 16a into the compression chamber 16a, for example, the sliding of the vane 22 in the acclimation operation or the trial operation is performed. As a result, the excess portion of the filling member 39 protruding into the compression chamber 16a is easily worn into a shape substantially coinciding with the cylinder wall surface 15d of the compression chamber 16a. For this reason, even if the filling member 39 is formed so as to slightly protrude into the compression chamber 16a in consideration of manufacturing errors in advance, the valve body 35 that closes the opening 33a by the acclimation operation or the trial operation as necessary. Since the front end surface of the filling member 39 provided at the front end of the valve body in the closed position can coincide with the cylinder wall surface 15d of the compression chamber 16a, the valve body 35 is closed at the closed position in normal operation thereafter. The recess S related to the opening 33 a can be reliably filled by the filling member 39 without causing interference between the body and the vane 22.

  Accordingly, it is possible to reliably prevent leakage of compressed gas related to the recess S during normal operation without increasing the plate thickness of the vane 22 or decreasing the diameter of the opening 33a of the leak passage 33. It is possible to prevent a decrease in compression efficiency and energy loss during normal operation due to the leakage of the compressed gas, and to ensure a smooth operation.

  The filling member 39 can be formed of a resin material having no elasticity that can be worn. However, when the filling member 39 is made of an elastic material, the opening 33a can be more reliably sealed by the sealing effect due to the elasticity of the filling member 39.

  In the above description, the present invention has been described with respect to an example of a concentric vane rotary type variable displacement gas compressor provided with a cylinder chamber having an elliptical cross-sectional shape. The present invention can be applied to an eccentric vane rotary type variable capacity gas compressor or a scroll type variable capacity gas compressor provided with a cylinder chamber.

  In this scroll-type variable capacity gas compressor, the filling member is made of a resin material that can be worn by a movable scroll that is a sliding body that slides with respect to the fixed scroll portion, or a rubber material that has wearable elasticity.

It is a longitudinal section showing a capacity variable type gas compressor concerning the present invention. It is sectional drawing obtained along line II-II shown in FIG. It is sectional drawing which expands and shows the on-off valve mechanism of the capacity | capacitance variable type gas compressor shown in FIG. It is sectional drawing which expands and shows a part of valve body of the on-off valve mechanism shown in FIG. It is sectional drawing which expands and shows the conventional on-off valve mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Gas compressor 12 Compression mechanism main body 16a Compression chamber 22 (Sliding body) Vane 33 Leak passage 33a (Leak passage opening) Opening port 34 Valve mechanism 35 Valve body 35a (Lead end of valve body) Tip 39 Filling member S Recess

Claims (5)

  It has a compression chamber whose volume is increased or decreased by the sliding movement of the driven rotating body. Gas is sucked into the compression chamber as the volume of the compression chamber increases, and the sucked gas is compressed as the volume decreases. And a compression mechanism main body to be discharged, and an opening opened to a wall surface of the compression chamber on which the sliding body slides to allow leakage of compressed gas from the compression chamber during a compression stroke of the compression mechanism main body. A variable capacity gas compressor comprising a leak passage communicating with a compression chamber and a valve mechanism for opening and closing the opening for switching the discharge capacity of the compressed gas, wherein the valve mechanism is located outside the compression chamber. A material that has a valve body movable in a direction approaching the opening and a direction away from the opening to open and close the opening, and a material that can be worn by sliding of the sliding body at a tip of the valve body facing the opening A closed position of the opening of the valve body Variable displacement gas compressor, wherein a filling member for filling a recess formed by said tip end of the opening the valve body is provided.   The compression mechanism main body includes a cylinder that defines a cylinder chamber for the compression chamber, and a rotor that is rotatably disposed in the cylinder chamber, and a vane moves along the wall surface of the cylinder chamber as the rotor rotates. A vane rotary type gas compression mechanism in which the vane is held by a rotor so as to slide, and the cylinder chamber is partitioned in the circumferential direction by the vane to form the compression chamber, and the sliding of the compression mechanism main body The variable capacity gas compressor according to claim 1, wherein the moving body is the vane which is disposed in the cylinder chamber and slides on a wall surface of the cylinder chamber.   The said valve body has a front-end | tip part fitted to the said opening in the closed position of this opening in the edge part which faces the said opening, The said filling member is being fixed to this front-end | tip part. Variable capacity gas compressor.   The variable capacity gas compressor according to claim 3, wherein the filling member is made of a resin material.   4. The variable capacity gas compressor according to claim 3, wherein the filling member is made of a rubber material having elasticity.

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