JP2019011682A - Vane compressor - Google Patents

Abstract

To effectively prevent, in a vane compressor in which the front-side end of a drive shaft protrudes to the outside of a housing and the rear-side end is received in the housing, occurrence of chattering by surely urging vanes to the inner peripheral surface of a cylinder at the initial stage of starting or the like.SOLUTION: A high pressure introduction passage 50 is provided, which has one end connected to a discharge fluid receiving chamber 32 and the other end facing the front-side end face of a rotor 3 and communicates with the bottom of a vane groove in a stroke in which the tip of a vane 4 is within a range from the middle of a discharge port 16 to a radial seal part. The high pressure introduction passage 50 is formed of a cylinder-side passage 51 that is formed in a cylinder 12 communicating with the discharge fluid receiving chamber 32, and a side block-side passage 52 that is formed in a front-side side block 21 facing the front-side end face of the rotor 3. The cylinder-side passage 51 and the side block-side passage 52 are put in communication with each other via a through hole 59a of a positioning pin 59 for positioning the cylinder 12 and the front-side side block 21.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a vane type compressor, and more particularly to a vane type compressor having a structure useful for reducing noise (chattering noise) associated with vane vibration that occurs during startup.

  In general, a vane compressor has a cylinder in which both ends are closed and a cam surface is formed on an inner peripheral surface, a rotor that is rotatably supported in the cylinder, and an outer surface of the rotor that is directed inward. The vane groove formed in the vane groove and removably accommodated in the vane groove. The vane is formed by centrifugal force due to rotation of the rotor and back pressure acting from the back pressure chamber provided at the bottom of the vane groove. It is structured to be in contact with and supported on the inner peripheral surface of the cylinder.

  In such a compressor, since the high / low pressure difference is small in the initial stage of the start-up, the state in which the vane leaves the inner peripheral surface of the cylinder and landes on the inner peripheral surface of the cylinder again to generate a collision noise (chattering noise) continues for a long time. Cheap.

  This phenomenon is particularly likely to occur between the vicinity of the vane tip passing through the middle of the discharge port and the passage of the portion where the rotor and the inner peripheral surface of the cylinder are in sliding contact (radial seal portion). As shown in FIG. 7, when the tip of the vane 4 reaches the discharge port 16 (in the drawing, the rotation direction of the vane is indicated by a white arrow), the back side of the vane 4 (the rotation direction of the vane). A high pressure compressed in the compression chamber on the rear side wraps around the discharge port 16 and acts on the entire front end portion of the vane 4, and a back pressure (vane back pressure) acting on the bottom portion of the vane 4 is activated at the time of activation. This is because the pressure applied to the tip portion of the vane 4 when the vane 4 passes through the discharge port cannot be supported because it is not sufficiently high. This phenomenon is more likely to occur when a counterbore 16a extending in the circumferential direction is formed at the opening end of the discharge port 16 with the inner peripheral surface of the cylinder.

Therefore, in order to eliminate such inconvenience, the present applicant, on the end face of the rear side block on the compression chamber side, in the stroke where the tip of the vane is in the range from the middle of the discharge port to the radial seal part, A recess that communicates with the bottom of the vane groove is provided, and the recess communicates with a discharge fluid storage chamber that stores fluid discharged from the discharge port via a communication passage (hereinafter referred to as a high pressure introduction passage). When it is in the range from the middle of the discharge port where chattering is likely to occur to the radial seal, the discharge fluid is guided from the rear side of the rotor to the bottom of the vane groove (back pressure chamber) to ensure the vane's inner peripheral surface The structure which urges | biases is proposed previously (refer patent document 1).

JP 2014-190263 A

  However, the end on the front side of the drive shaft on which the rotor is fixed is required to be directly connected to the drive source, or a power transmission member (pulley, electromagnetic clutch, etc.) for transmitting the power of the drive source is required, It passes through the front side block and protrudes outside the housing.

  In such a configuration, atmospheric pressure acts on the front end protruding from the front side block of the drive shaft to the outside, whereas, on the rear end of the drive shaft, The relatively high pressure inside the compressor acts via the clearance between the rotor and the rear side block, bearings, etc., so the drive shaft moves to the front side due to the pressure difference acting on both the front and rear sides in the axial direction. It will be energized. For this reason, the clearance between the front end of the rotor and the front side block is relatively small, and the clearance between the rear end of the rotor and the rear side block is relatively large.

Therefore, the discharge fluid guided from the discharge fluid storage chamber to the end surface on the compression chamber side of the rear side block via the high pressure introduction passage is connected via the clearance between the rear end of the rotor 3 and the rear side block 13. There is a concern that leakage tends to occur, and the discharge fluid cannot be effectively introduced into the bottom (back pressure chamber) of the vane groove in the stroke where the tip of the vane is in the range from the middle of the discharge port to the radial seal portion.
Further, when the discharge fluid supplied from the discharge fluid storage chamber is likely to leak through the clearance between the rear end of the rotor and the rear side block, the oil film formed between the two is removed, and the oil seal is removed. There is also a concern that the effect is reduced and the compression efficiency is lowered.

  The present invention has been made in view of such circumstances, and in a compressor in which a front side end portion of a drive shaft protrudes to the outside of a housing and a rear side end portion is accommodated in the housing, the initial stage of startup, etc. The main object of the present invention is to provide a vane type compressor that reliably biases the vane toward the inner peripheral surface of the cylinder to prevent chattering of the vane.

  In order to achieve the above object, a vane type compressor according to the present invention includes a housing, a cylinder having a cam surface formed on an inner peripheral surface, constituting a part of the housing, and both axial ends of the cylinder. A pair of front and rear side blocks that are closed and constitute a part of the housing, a drive shaft that is rotatably supported by the pair of side blocks, and a cylinder that is fixedly mounted on the drive shaft. A rotor that is rotatably accommodated, a radial seal portion in which a part of an outer peripheral surface of the rotor and a part of an inner peripheral surface of the cylinder are in sliding contact, a plurality of vane grooves formed in the rotor, and the vane grooves Slidably inserted into the space closed by the plurality of vanes whose tip ends protrude from and retract from the vane groove and slide on the cam surface, and the cylinder and the pair of side blocks. A compression chamber defined by the compressor and the vane, a suction port for sucking fluid into the compression chamber, a discharge port for discharging the fluid compressed in the compression chamber, and a fluid discharged from the discharge port. A vane-type compressor including a discharge fluid storage chamber, wherein one end of the vane compressor is connected to the discharge fluid storage chamber, the other end faces an end surface on a front side of the rotor, and a tip of the vane is connected to the discharge port. In a stroke in the range from the middle to the radial seal portion, a high pressure introduction passage communicating with the bottom of the vane groove is provided.

  Therefore, in the stroke in which the tip of the vane is in the range from the middle of the discharge port to the radial seal portion, the discharge fluid storage chamber and the bottom of the vane groove communicate with each other via the high pressure introduction passage on the front side of the rotor. Will do. The clearance between the front end face of the rotor and the front side block is reduced by the biasing force to the front side due to the pressure difference acting on both ends of the drive shaft, so the discharge supplied from the discharge fluid storage chamber The fluid is less likely to leak through the clearance between the front end face of the rotor and the front side block, and is effectively introduced into the bottom of the vane groove.

For this reason, sufficient back pressure can be secured in an area where chattering of the vane is likely to occur, so that the pressure applied to the tip of the vane after the tip of the vane reaches the discharge port can be supported. It is possible to maintain the state in contact with the cam surface.
In addition, since there is almost no possibility that the discharged fluid leaks through the clearance between the front end face of the rotor and the front side block, the seal between the front end face of the rotor and the front side block is made of oil. There is no risk of impairing the effect, and a good sealing state can be maintained.

  In the case where the vane back pressure is supplied in the same manner as before in the stroke where the tip of the vane is in the range from the radial seal portion to the front of the discharge port, in addition to the above-described configuration, the discharge from the discharge port is performed. An oil reservoir chamber for storing oil at a pressure corresponding to the pressure of the fluid, and at least one side block of the compression chamber side end surface, and the tip of the vane extends from the radial seal portion to the front of the discharge port. In the stroke within the range, an oil introduction groove communicating with the bottom of the vane groove, and an oil introduction passage communicating the oil introduction groove and the oil reservoir chamber may be further provided.

  The high pressure introduction passage includes a cylinder side passage formed in the cylinder communicating with the discharge fluid storage chamber, and a side block side passage formed in the front side block facing a front side end surface of the rotor. The cylinder side passage and the side block side passage may be communicated with each other through a through hole provided in a positioning pin for positioning the cylinder and the front side block. .

  In such a configuration, it is not necessary to separately provide the high pressure introduction passage and the positioning pin mounting portion in the cylinder or the front side block, and the degree of freedom in layout can be increased.

The positioning pin is preferably a spring pin in consideration of ease of processing and assembly.
The housing includes a first housing member integrally formed with the cylinder and a rear side block for closing the rear side of the cylinder, a front side block for closing the front side of the cylinder, and A second housing member integrally formed with a cylindrical portion covering the outer periphery of the first housing member may be combined.

  As described above, according to the present invention, one end is connected to the discharge fluid storage chamber that stores the fluid discharged from the discharge port, the other end faces the end surface on the front side of the rotor, and the tip of the vane discharges. In the stroke from the middle of the port to the radial seal portion, a high pressure introduction passage communicating with the bottom of the vane groove is provided, so that sufficient back pressure can be secured in an area where chattering is likely to occur. Even in the initial stage of startup, the vane can be reliably urged to the inner peripheral surface of the cylinder to prevent chattering of the vane.

  Further, when providing the high pressure introduction passage, a cylinder side passage formed in the cylinder communicating with the discharge fluid storage chamber and a side block side passage formed in the front side block facing the front end face of the rotor And the front side block through a through hole provided in the positioning pin, the high pressure introduction passage and the location of the positioning pin are installed separately on the cylinder and the front side block. Therefore, it is possible to increase the degree of freedom of layout.

FIG. 1 is a side sectional view showing a vane type compressor according to the present invention. 2A is a cross-sectional view taken along line AA of the vane type compressor shown in FIG. 1, and FIG. 2B is a view taken along line BB of the vane end compressor shown in FIG. FIG. FIG. 3 is a perspective view showing the first housing member and the second housing member. FIG. 4 is a side sectional view of the compressor shown in FIG. 1 cut so that a high-pressure introduction passage can be seen. FIG. 5 is an enlarged cross-sectional view showing a portion in which a high-pressure introduction passage is formed in a butt portion between the cylinder and the front side block. 6A and 6B are diagrams showing positioning pins, in which FIG. 6A is a perspective view showing an example in which the positioning pin is configured by a spring pin, and FIG. 6B is a perspective view showing an example in which the positioning pin is configured by a cylindrical pin. FIG. FIG. 7 is an explanatory diagram for explaining the force acting on the tip of the vane when the tip of the vane passes through the discharge port.

  Hereinafter, the vane type compressor of the present invention will be described with reference to the drawings.

  1 and 2 show a vane type compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane compressor 1 includes a drive shaft 2, a rotor 3 that is fixed to the drive shaft 2 and rotates as the drive shaft 2 rotates, a vane 4 attached to the rotor 3, and the drive shaft 2. A housing 5 that supports the rotor 3 and the vanes 4 while supporting the rotor 3 and the vanes 4 is provided. In FIG. 1, the left side is the front side and the right side is the rear side.

The housing 5 is configured by combining two members of the first housing member 10 and the second housing member 20.
The first housing member 10 accommodates the rotor 3 and has a cylinder 12 with a cam surface 11 formed on the inner peripheral surface thereof, and a rear side formed integrally so as to close the axial rear side of the cylinder 12. The side block 13 is comprised. The inner peripheral surface (cam surface 11) of the cylinder 12 is formed in a perfect circle in cross section, and the axial length is substantially equal to the axial length of the rotor 3 described later.

  The second housing member 20 is in contact with the front end surface of the cylinder 12 and closes the front side, and the front side block 21 is formed integrally with the front side block 21, and the axial direction of the drive shaft 2 is formed. And a cylindrical portion 22 formed so as to surround the outer peripheral surface of the first housing member (the cylinder 12 and the rear side block 13).

The first housing member 10 and the second housing member 20 are fastened in the axial direction via fasteners (not shown) such as bolts, and the rear side block 13 and the second side block 13 of the first housing member 10. A sealing member 7 such as an O-ring is interposed between the cylindrical portion 22 of the housing member 20 and hermetically sealed.

  The second housing member 20 is integrally formed with a boss portion 23 extending from the front side block 21 to the front side. A pulley 25 that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23, and rotational power is transmitted from the pulley 25 to the drive shaft 2 via an electromagnetic clutch 26.

  The drive shaft 2 is rotatably supported by the rear side block 13 and the front side block 21 via bearings 14 and 24. The front end portion of the drive shaft 2 passes through the front side block 21 of the second housing member 20 and protrudes into the boss portion 23, and the boss portion 23 is provided by a seal member 27 provided between the boss portion 23. The space between the two is hermetically sealed.

  The rotor 3 is formed into a perfect circle in cross section, and the drive shaft 2 is inserted into an insertion hole 3a provided in the shaft center O, and the rotor 3 is fixed to the drive shaft 2 in a state where the shaft centers coincide with each other. ing. Further, the axial center O ′ of the cylinder 12 and the axial center O of the rotor 3 (drive shaft 2) are such that the outer peripheral surface of the rotor 3 and the inner peripheral surface (cam surface 11) of the cylinder 12 are in one place in the circumferential direction. The radial seal portions 40 are arranged so as to be in contact with each other (they are provided by being shifted by a half of the difference between the inner diameter of the cylinder 12 and the outer diameter of the rotor 3). In the space closed by the cylinder 12, the rear side block 13 and the front side block 21, a compression space 30 is provided between the inner peripheral surface (cam surface 11) of the cylinder 12 and the outer peripheral surface of the rotor 3. It is defined.

  A plurality of vane grooves 8 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 8. The vane groove 8 is opened not only on the outer peripheral surface of the rotor 3 but also on the end surface facing the rear side block 13 and the front side block 21, and the back pressure chamber 8 a defined by the vane 4 at the bottom. Is formed. A plurality of the vane grooves 8 are formed at equal intervals in the circumferential direction. In this example, the vane grooves 8 are formed so as to be substantially parallel to each other at two positions different in phase by 180 degrees. The plane is parallel to the vane 4 and the plane including the axis of the drive shaft 2 is separated by a predetermined distance (offset state).

  The vane 4 is formed such that the width along the axial direction of the drive shaft 2 is equal to the axial length of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 8 is the length of the vane groove 8. It is formed approximately equal to the length in the same direction. The vane 4 is protruded from the vane groove 8 by oil or refrigerant gas, which will be described later, supplied to the back pressure chamber 8 a of the vane groove 8, and a tip portion thereof can come into contact with the inner peripheral surface (cam surface 11) of the cylinder 12. It has become.

  Therefore, the compression space 30 is partitioned into a plurality of compression chambers 31 by the vanes 4 slidably inserted into the vane grooves 8, and the volume of each compression chamber 31 changes as the rotor 3 rotates. ing.

  The second housing member 20 is formed with a suction port (not shown) for sucking working fluid (refrigerant gas) from the outside and a discharge port (not shown) for discharging the working fluid to the outside. The cylinder 12 of the first housing member 10 communicates with the suction port from the vicinity of the front side in the rotational direction of the rotor 3 of the radial seal portion 40 (the arrow direction indicated in the rotor in the drawing), and the compression chamber 31. A suction port 15 is formed for supplying fluid.

Further, the cylinder 12 is provided with a discharge port 16 for discharging the fluid compressed in the compression chamber 31 in the vicinity of the rear side in the rotational direction of the rotor 3 of the radial seal portion 40. A discharge fluid storage chamber 32 is formed between the cylindrical portion 22 and the compressed fluid discharged through the cylinder.
The discharge port 16 has a counterbore 16a that is recessed in a curved shape along the circumferential direction at the opening end with the inner peripheral surface (cam surface 11) of the cylinder 12, and the compressed gas is countersunk 16a. It is discharged through. The discharge port 16 is closed by a discharge valve 33 provided in the discharge fluid storage chamber 32 so as to be opened and closed.
In FIG. 2, reference numeral 35 denotes a screw hole for screwing the fastener.

  The discharge fluid storage chamber 32 extends in the circumferential direction between the cylinder 12 and the cylindrical portion 22, and the discharge fluid discharged therein is an oil separator 34 (see the later-described figure) provided in the rear side block 13. 4), and after the oil is separated by the oil separator 34, the oil is sent out from the discharge port. The high-pressure oil separated by the oil separator 34 is an oil sump formed between the lower portion of the rear side block 13 of the first housing member 10 and the lower portion of the cylindrical portion 22 of the second housing member 20. It is stored in the chamber 18.

Further, as shown in FIG. 3, the opening peripheral edge of the bearing hole 13 a into which the drive shaft 2 is inserted via the bearing 14 is recessed on the surface facing the end surface of the rotor 3 of the rear side block 13. An oil introduction groove 41 extending in the circumferential direction is formed. Further, the oil introduction that extends in the circumferential direction with the opening peripheral edge of the bearing hole 21 a into which the drive shaft 2 is inserted via the bearing 24 is also recessed on the surface of the front side block 21 that faces the end surface of the rotor 3. A groove 42 is formed.

These oil introduction grooves 41 and 42 are located at the bottom (back) of the vane groove 8 within a range in which the tip of the vane 4 moves from the position of the radial seal 40 to the front of the discharge port 16 (before the counterbore 16a). It is formed so as to communicate with the pressure chamber 8a).
The rear oil introduction groove 41 is connected to the oil chamber 18 via an oil introduction passage 19 having a throttle portion.

  Therefore, when the discharge pressure increases, the high-pressure oil stored in the oil chamber 18 is supplied to the rear-side oil introduction groove 41 formed in the rear-side side block 13 via the oil introduction passage 19, and this rear side From the oil introduction groove 41 to a sliding portion such as the bearing 14 and the space 43 formed between the rear end portion of the drive shaft 2 and the rear side block 13 and to the back pressure chamber 8 a of the rotor 3. It is supposed to be. The vane 4 is pressed against the inner peripheral surface (cam surface 11) of the cylinder 12 by the oil fed into the back pressure chamber 8a.

  The oil sent to the back pressure chamber 8a is supplied to the front oil introduction groove 42 in a process in which the back pressure chamber 8a communicates with the front oil introduction groove 42, and the front oil introduction groove 42 is supplied. It is sent to sliding parts, such as bearing 24, via.

In addition, as shown in FIG. 4, the housing 5 is provided with a high-pressure introduction passage 50 having one end communicating with the discharge fluid storage chamber 32 and the other end facing the front end surface of the rotor 3.
In this example, the high-pressure introduction passage 50 includes a cylinder-side passage 51 formed in the cylinder 12 communicating with the discharge fluid storage chamber 32 and a side block formed in the front-side side block 21 facing the front-side end surface of the rotor 3. The side passage 52 is connected to the side passage 52.

  As shown also in FIG. 5, the cylinder side passage 51 is formed from a radial passage hole 53 formed in the radial direction from the discharge fluid storage chamber 32 of the cylinder 12 and an end face facing the front side block 21 of the cylinder 12. An axial passage hole 54 is formed in the axial direction and communicates with the radial passage hole 53.

The side block side passage 52 includes a first axial passage hole 55 formed in the axial direction from a surface facing the cylinder 12 of the front side block 21, and the front side of the rotor 3 of the front side block 21. A boss portion is formed so that the second axial passage hole 56 drilled in the axial direction from the surface facing the end surface and the first axial passage hole 55 and the second axial passage hole 56 communicate with each other. 23 and an inclined passage hole 57 that is formed obliquely from the peripheral surface.
The inclined passage hole 57 is airtightly closed by a sealing member 58 at a portion opened on the peripheral surface of the boss portion 23.

The cylinder side passage 51 and the side block side passage 52 are communicated with each other through a through hole 59a provided in a positioning pin 59 for positioning the cylinder 12 and the front side block 21.
The positioning pin 59 is formed by a spring pin (split pin), is press-fitted into the axial passage hole 54 of the cylinder side passage 51, is formed in the front side block 21, and is loosely inserted into the first axial passage hole 55. It is fitted. In this example, the region where the positioning pin 59 of the axial passage hole 54 is press-fitted is formed to have a somewhat larger diameter so that the high pressure introduction passage 50 is not restricted by the location where the positioning pin 59 is provided. Thus, the inner diameter of the positioning pin 59 is substantially equal to the inner diameter of the other part of the high-pressure introduction passage 50.

  The second axial passage hole 56 can communicate with a back pressure chamber 8 a provided at the bottom of the vane groove 8. In particular, in this example, the tip of the vane 4 is located in the discharge port 16. It is formed so as to communicate with the bottom portion (back pressure chamber 8a) of the vane groove 8 in the stroke in the range from the first to the radial seal portion 40.

  Accordingly, when the bottom portion (back pressure chamber 8a) of the vane groove 8 communicates with the oil introduction groove 41, oil corresponding to the discharge pressure supplied from the oil reservoir chamber 18 is sent to the back pressure chamber 8a via the oil introduction passage 19. It is. When the bottom portion (back pressure chamber 8 a) of the vane groove 8 communicates with the second axial passage hole 56 of the high pressure introduction passage 50, the discharge fluid supplied from the discharge fluid storage chamber 32 via the high pressure introduction passage 50 is discharged. It is sent directly to the back pressure chamber 8a.

  In the above configuration, when the compressor 1 is started and the rotor 3 starts to rotate, the discharge gas compressed in the compression chamber 31 is discharged to the discharge fluid storage chamber 32 through the discharge port 16. The discharge pressure is not sufficiently high, and the oil sent to the oil introduction groove 41 from the oil reservoir chamber 18 through the oil introduction passage 19 due to the discharge pressure is immediately applied to the vane 4 due to its viscous resistance. Insufficient back pressure can be supplied. However, the bottom portion (back pressure chamber 8a) of the vane groove 8 extends from the middle of the discharge port 16 (counterbore 16a) where the tip of the vane 4 is easily separated from the inner peripheral surface (cam surface 11) of the cylinder 12. 50, the discharge gas is directly introduced into the bottom (back pressure chamber 8a) of the vane groove 8. In this way, by supplying the discharge gas directly to the back pressure chamber 8a via the high-pressure introduction passage 50 immediately after the compressor 1 is started, the vane 4 can be used even when the tip of the vane 4 passes through the discharge port 16. Eliminates the collision noise (chattering noise) that is generated when the vane 4 is pressed against the inner peripheral surface (cam surface 11) of the cylinder 12 and landed again away from the inner peripheral surface (cam surface 11) of the cylinder 12. Is possible.

  In particular, the clearance between the front end face of the rotor 3 and the front side block 21 is reduced by the biasing force to the front side due to the pressure difference acting on both ends of the drive shaft 2, and therefore the discharge fluid storage chamber The discharged fluid supplied from 32 hardly leaks from between the front side end face of the rotor 3 and the front side block 21 and is effectively introduced into the bottom of the vane groove 8 (back pressure chamber 8a). The For this reason, the occurrence of chattering can be more effectively suppressed as compared with the case where the high-pressure introduction passage 50 is provided on the rear side.

  Further, since there is almost no risk of the discharge fluid leaking through the clearance between the front side end face of the rotor 3 and the front side block 21, even if the discharge fluid is supplied via the high-pressure introduction passage 50, this time There is no risk of impairing the sealing effect of the oil. On the contrary, since the discharge fluid is supplied from the discharge fluid storage chamber 32 to the front end surface of the rotor 3 without going through the oil separator, the oil in the discharge fluid can be supplied, and the good sealing effect by the oil Can be maintained.

  In the configuration described above, the high pressure introduction passage 50 is provided on the front side, and therefore, the high pressure introduction passage 50 needs to be formed across the cylinder 12 and the front side block 21. For this reason, originally, a location where the high pressure introduction passage 50 is formed at the abutting portion between the cylinder 12 and the front side block 21, and a location where the positioning pin 59 for positioning the cylinder 12 and the front side block 21 is mounted. It is necessary to ensure that. However, in the above-described configuration, since the positioning pin 59 has a cylindrical shape and is a part of the high-pressure introduction passage 50, the positioning pin 59 is moved to the position where the first axial passage hole 55 is formed, or the existing positioning is performed. What is necessary is just to form the 1st axial direction channel | path in the attachment location of a pin, and it becomes possible to enlarge the freedom degree of the layout of the high voltage | pressure introduction channel | path 50. FIG.

In the above configuration, the compressor in the case where there are two vanes 4 has been described. However, a similar configuration can be adopted in a three or more vane type compressor.
In the above-described configuration, the spring pin is provided as the positioning pin 59. However, as shown in FIG. 5B, a cylindrical pin may be used.

DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Drive shaft 3 Rotor 4 Vane 5 Housing 8 Vane groove 8a Back pressure chamber
DESCRIPTION OF SYMBOLS 10 1st housing member 11 Cam surface 12 Cylinder 13 Rear side block 15 Suction port 16 Discharge port 17 Discharge chamber 18 Oil chamber 19 Oil communication path 20 Second housing member 21 Front side block 31 Compression chamber 32 Discharge fluid accommodation Chamber 50 High-pressure introduction passage 51 Cylinder side passage 52 Side block side passage 59 Positioning pin

Claims (5)

A housing;
A cylinder having a cam surface formed on an inner peripheral surface and constituting a part of the housing;
A pair of side blocks on the front side and rear side that close both ends in the axial direction of the cylinder and constitute a part of the housing;
A drive shaft rotatably supported by the pair of side blocks; a rotor fixed to the drive shaft and rotatably accommodated in the cylinder;
A radial seal portion in which a part of the outer peripheral surface of the rotor and a part of the inner peripheral surface of the cylinder are in sliding contact;
A plurality of vane grooves formed in the rotor, and a plurality of vanes which are slidably inserted into the vane grooves, and whose tip ends slide out of the vane grooves and slide on the cam surface;
A compression chamber defined by the rotor and the vane in a space closed by the cylinder and the pair of side blocks;
A suction port for sucking fluid into the compression chamber; a discharge port for discharging the fluid compressed in the compression chamber;
A discharge fluid storage chamber for storing the fluid discharged from the discharge port;
In a vane compressor equipped with
In the stroke in which one end is connected to the discharge fluid storage chamber, the other end faces the end surface on the front side of the rotor, and the tip of the vane is in the range from the middle of the discharge port to the radial seal portion. A vane type compressor having a high-pressure introduction passage communicating with a bottom of a groove. An oil reservoir chamber for storing oil having a pressure corresponding to the pressure of the fluid discharged from the discharge port;
An oil introduction groove communicating with the bottom of the vane groove in a stroke in which the tip of the vane is in a range from the radial seal portion to the front of the discharge port on the end surface of the compression chamber side of at least one side block; ,
An oil introduction passage communicating the oil reservoir chamber and the oil introduction groove;
The vane type compressor according to claim 1, further comprising: The high pressure introduction passage includes a cylinder side passage formed in the cylinder communicating with the discharge fluid storage chamber, and a side block side passage formed in the front side block facing the front end surface of the rotor. Formed by connecting,
3. The cylinder side passage and the side block side passage communicate with each other via a through hole provided in a positioning pin for positioning the cylinder and the front side block. The vane type compressor described in 1.   4. The vane type compressor according to claim 3, wherein the positioning pin is a spring pin.   The housing includes a first housing member integrally formed with the cylinder and the rear side block for closing the rear side of the cylinder, the front side block for closing the front side of the cylinder, and 5. The vane type according to claim 1, wherein the second housing member is integrally formed with a cylindrical portion that covers an outer periphery of the first housing member. Compressor.

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