JP2015034518A - Vane-type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane-type compressor capable of surely reducing back-flow of a refrigerant gas and the like, and reverse rotation of a driving shaft.SOLUTION: In a vane-type compressor, back pressure supply means is composed of an upstream path communicated with a discharge chamber, a downstream path communicated with each of back pressure chambers 15b, and an intermittent mechanism disposed between the upstream path and the downstream path. The downstream pash is formed on a second section wall, and has a discharge hole 4e capable of discharging a lubricant passing through the intermittent mechanism, toward a cylinder chamber, and first and second fine grooves 16a-16e recessed on a back face at second section wall side of a rotor 15, extended from each of the back pressure chambers 15b toward a shaft center O, and communicatable with the discharge hole 4e according to a phase in the rotating direction of a driving shaft 8.

Description

  The present invention relates to a vane type compressor.

  Patent Document 1 discloses a conventional vane type compressor. This vane type compressor includes a housing, a drive shaft, a rotor, and a plurality of vanes.

  The housing includes a front housing, a rear housing, a cylinder block, a front side plate, and a rear side plate. The front housing and the rear housing are joined. A cylinder chamber is formed in the cylinder block. The cylinder chamber is defined by the rear surface of the front side plate and is defined by the front surface of the rear side plate. The cylinder block, the front side plate, and the rear side plate are accommodated in the front housing and the rear housing. The front housing and the front side plate form a suction chamber, and the rear housing and the rear side plate form a discharge chamber.

  The drive shaft is provided in the housing so as to be rotatable around the axis. The rotor is provided so as to be able to rotate synchronously with the drive shaft in the cylinder chamber. A plurality of vane grooves are formed in the rotor. Each vane is provided in each vane groove so as to be able to appear and disappear. Each vane forms each compression chamber together with the inner surface of the cylinder chamber, the outer surface of the rotor, the rear surface of the front side plate, and the front surface of the rear side plate. A space between each vane groove and the bottom surface of each vane is a back pressure chamber defined by the rear surface of the front side plate and the front surface of the rear side plate.

  Between the discharge chamber and each back pressure chamber, a back pressure supply means capable of supplying high-pressure lubricating oil in the discharge chamber to each back pressure chamber is provided. The back pressure supply means has an intermittent mechanism that connects or disconnects the discharge chamber and each back pressure chamber according to the phase in the rotational direction of the drive shaft.

  In this vane type compressor, the back pressure supply means supplies the high pressure lubricating oil in the discharge chamber to each back pressure chamber, so that each vane is preferably pressed against the inner surface of the cylinder chamber. Therefore, each vane is lubricated in the vane groove, chattering is prevented, and leakage of the refrigerant gas from the compression chamber is prevented, thereby improving efficiency.

  Further, in this vane type compressor, the intermittent mechanism can make the discharge chamber and each back pressure chamber non-communication after the drive shaft stops, so that the reverse flow of the refrigerant gas and the like after the drive shaft stops and the reverse of the drive shaft Can be prevented. Specifically, if the phase of the drive shaft is not in communication when the drive shaft is stopped, the discharge chamber and each back pressure chamber are not in communication. Even if the phase of the drive shaft communicates when the drive shaft is stopped, if there is a slight backflow of refrigerant gas and reverse rotation of the drive shaft, the phase of the drive shaft will be shifted thereby, so The pressure chamber is not in communication.

JP 2012-127335 A

  However, in the above conventional vane type compressor, depending on the setting of the flow path of the back pressure supply means and the flow path of the intermittent mechanism, there is a risk that reverse flow of the refrigerant gas or the like after the drive shaft stops and reverse rotation of the drive shaft will occur. There is.

  The present invention has been made in view of the above-described conventional situation, and it is a problem to be solved to provide a vane-type compressor that can more reliably reduce the backflow of refrigerant gas and the like and the reverse of the drive shaft. Yes.

The vane compressor of the present invention includes a housing in which a suction chamber, a discharge chamber, and a cylinder chamber are formed,
A drive shaft rotatably provided in the housing;
A rotor provided in a synchronous manner with the drive shaft in the cylinder chamber and having a plurality of vane grooves;
Each vane groove is provided so as to be able to appear and disappear, and includes a vane that forms each compression chamber,
The housing has a first partition wall and a second partition wall, and the cylinder chamber is disposed between a first surface that is a rear surface of the first partition wall and a second surface that is a front surface of the second partition wall. Formed, the second partition wall partitions the cylinder chamber and the discharge chamber,
The compression chamber is formed by an inner surface of the cylinder chamber, an outer surface of the rotor, the first surface, the second surface, and the vanes.
A space between each of the vane grooves and each of the vanes is a back pressure chamber defined by the first surface and the second surface.
Between the discharge chamber and each back pressure chamber, in the vane type compressor provided with back pressure supply means capable of supplying lubricating oil in the discharge chamber to each back pressure chamber,
The back pressure supply means includes an upper flow path communicating with the discharge chamber, a lower flow path communicating or not communicating with the back pressure chambers by the rotor according to a phase in a rotation direction of the drive shaft, and the upper flow path. And an intermittent mechanism that connects or disconnects the upper channel and the lower channel according to the phase in the rotational direction of the drive shaft,
When the intermittent mechanism communicates the upper flow path and the lower flow path, the rotor does not communicate the lower flow path with any of the back pressure chambers, and the rotor causes the lower flow path to any of the back pressure chambers. When communicating with the chamber, the intermittent mechanism makes the upper flow path and the lower flow path non-communication (Claim 1).

  In the conventional vane type compressor, no contrivance is applied to the rear side plate that partitions the cylinder chamber and the discharge chamber, and neither to the rotor. For this reason, when the intermittent mechanism communicates the upper flow path and the lower flow path, the rotor may communicate the lower flow path with any one of the back pressure chambers.

  On the other hand, in the vane type compressor of the present invention, when the intermittent mechanism communicates the upper flow path and the lower flow path, the rotor does not communicate the lower flow path with any back pressure chamber. Further, when the rotor communicates the lower flow path with any one of the back pressure chambers, the intermittent mechanism makes the upper flow path and the lower flow path not communicated.

  Therefore, according to this vane type compressor, at least one place is not connected between the discharge chamber and the back pressure chamber, and the reverse flow of the refrigerant gas and the like and the reverse rotation of the drive shaft can be more reliably reduced.

  The lower flow path is formed in the second partition wall, and is provided with a discharge hole through which the lubricating oil having passed through the intermittent mechanism can be discharged toward the cylinder chamber, and recessed on the rear surface of the rotor on the second partition wall side. It may have a narrow groove extending toward the shaft center and capable of communicating with the discharge hole by a phase in the rotational direction of the drive shaft.

  In this case, due to the rotation of the rotor, the discharge hole of the lower flow path communicates with each back pressure chamber through the narrow groove. Since the narrow groove extends from each back pressure chamber toward the axial center, the angular range in which the discharge hole communicates with each back pressure chamber becomes smaller as compared with the conventional case as the rotor rotates. For this reason, in this vane type compressor, it is easy to set an angle at which the intermittent mechanism or the rotor makes the discharge chamber and each back pressure chamber not communicated.

  Each narrow groove can extend in the same direction from the respective back pressure chambers toward the axial center. However, each narrow groove has a first narrow groove extending in a first direction from each back pressure chamber toward the axis, and a second extending in a second direction different from the first direction from each back pressure chamber toward the axis. It is preferable to have a narrow groove (claim 3). As described above, by adopting the narrow grooves extending in different directions, the timing at which the discharge holes communicate with the narrow grooves can be arbitrarily changed. For this reason, it is possible to make it difficult for reverse flow of refrigerant gas and the like and reverse rotation of the drive shaft to occur.

  Various types of back pressure supply means and intermittent mechanism can be employed.

  For example, a shaft support hole that pivotally supports the rear end portion of the drive shaft and a supply chamber that is positioned behind the shaft support hole and is partitioned from the shaft support hole by the rear end portion are formed in the second partition wall. obtain. The upper flow path may be formed of an introduction path that is formed in the second partition wall and extends from the discharge chamber to the supply chamber, a supply chamber, and an axial path that is formed in the rear end portion and communicates with the supply chamber. The lower flow path may include a receiving path that is formed in the second partition wall and opens in the shaft support hole, and a discharge hole that communicates with the receiving path. The intermittent mechanism is preferably provided between the axial path and the receiving path.

  In this case, the lubricating oil present in the discharge chamber reaches the introduction path, the supply chamber, and the axial path. If the axial path and the receiving path communicate with each other according to the phase of the drive shaft, the lubricating oil in the axial path is guided to the discharge hole through the receiving path. Further, if the axial path and the receiving path are not in communication due to the phase of the drive shaft, the lubricating oil in the axial path is not supplied to the receiving path and the discharge hole.

  The second partition wall is formed with a shaft support hole that supports the rear end portion of the drive shaft and a supply chamber that is positioned behind the shaft support hole and is partitioned from the shaft support hole by the rear end portion. obtain. The upper flow path may be formed of an introduction path formed in the second partition wall and extending from the discharge chamber to open to the shaft support hole. The lower flow path may be formed of an axial path that is formed at the rear end portion and communicates with the supply chamber, and a discharge hole that is formed in the second partition wall and communicates with the supply chamber. It is preferable that the intermittent mechanism is provided between the introduction path and the axial path.

  In this case, the lubricating oil present in the discharge chamber reaches the introduction path. If the introduction path and the axis path communicate with each other according to the phase of the drive shaft, the lubricating oil in the introduction path is guided to the supply chamber via the axis path, and further to the discharge hole. Further, if the introduction path and the axis path are not in communication due to the phase of the drive shaft, the lubricating oil in the introduction path is not supplied to the axis path, the supply chamber, and the discharge hole.

  The axial path may have a plurality of intermittent openings on the peripheral surface of the drive shaft. The intermittent port is preferably in a point-symmetrical position with respect to the axis of the drive shaft. In this case, every time the drive shaft rotates 180 °, the intermittent mechanism makes the upper flow path and the lower flow path communicated or non-communication, so that the vane compressor of the present invention can be easily realized.

  According to the vane type compressor of the present invention, it is possible to more reliably reduce the backflow of refrigerant gas or the like and the reverse rotation of the drive shaft.

1 is a cross-sectional view of a vane type compressor of Example 1. FIG. FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1 according to the vane type compressor of the first embodiment. 1. It is a BB arrow sectional drawing of FIG. 1 regarding the vane type compressor of Example 1. FIG. 1 is an end view of a rotor according to a vane type compressor of Example 1. FIG. 1 is an enlarged view of a main part of an end surface of a rotor according to a vane type compressor of Example 1. FIG. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. FIG. (A) shows a state in which the through hole and the diameter hole are not in communication in the back pressure supply means, and FIG. (B) shows a state in which the through hole and the diameter hole are in communication in the back pressure supply means. It shows the state. 2 is a timing chart of the vane type compressor according to the first embodiment. It is a principal part enlarged view of the end surface of a rotor in connection with the vane type compressor of a comparative example. It is a timing chart of the vane type compressor of a comparative example. 3 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 2. FIG. 3 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 2. FIG. FIG. (A) shows a state in which the introduction path and the axial path are not in communication with each other in the back pressure supply means, and FIG. (B) shows that the introduction path and the axial path in the back pressure supply means are in communication. It shows the state.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIG. 1, the vane compressor according to the first embodiment includes a front housing 1, a rear side plate 3, and a shell 5. The front housing 1 corresponds to a first housing, and the rear side plate 3 corresponds to a second housing. Further, the front housing 1, the rear side plate 3, and the shell 5 correspond to the housing.

  The front housing 1 has a cylindrical cylinder forming portion 7a and a first partition wall 2 provided integrally with the cylinder forming portion 7a at the front end of the cylinder forming portion 7a. A cylinder chamber 7 is recessed in the cylinder forming portion 7a from the rear to the front. As shown in FIGS. 2 and 3, the cylinder chamber 7 has a columnar shape whose section perpendicular to the axis O of the drive shaft 8 is an elliptical shape. As shown in FIG. 1, a boss 1a protruding forward is formed in the first partition wall 2, and a shaft support hole 2b through which the front portion of the drive shaft 8 is inserted is formed in the boss 1a. The rear surface of the first partition wall 2 is a first surface 2 a orthogonal to the axis O.

  An annular suction chamber 9 is recessed in the outer peripheral surface of the cylinder forming portion 7a. As shown in FIG. 2, the suction chamber 9 communicates with the cylinder chamber 7 through two suction ports 9c.

  As shown in FIG. 1, the rear side plate 3 has a second partition wall 4 that contacts the rear end of the cylinder forming portion 7 a of the front housing 1. A shaft support hole 4b in which the rear end portion 8a of the drive shaft 8 is accommodated is recessed in the second partition wall 4 from the front to the rear. The front surface of the second partition wall 4 is a second surface 4 a orthogonal to the axis O. A supply chamber 2c defined by a rear end 8a is formed behind the shaft support hole 4b.

  The shell 5 accommodates the cylinder forming portion 7 a of the front housing 1 and the rear side plate 3. A mounting foot 5 a is formed on the shell 5. The mounting foot 5a is attached to an engine or the like (not shown) of the vehicle. A discharge chamber 10 is formed between the shell 5 and the rear side plate 3. The discharge chamber 10 is partitioned from the cylinder chamber 7 by the second partition wall 4.

  The shell 5 is formed with an inlet 9a that opens the suction chamber 9 to the outside and an outlet 10a that opens the discharge chamber 10 to the outside. O-rings 13 a and 13 b are mounted on the outer peripheral surface of the cylinder forming portion 7 a before and after the suction chamber 9. The O-ring 13 a seals between the shell 5 and the front housing 1 in front of the suction chamber 9. The O-ring 13 b seals between the shell 5 and the front housing 1 behind the suction chamber 9. An O-ring 13 c is attached to the outer peripheral surface of the second partition wall 4. The O-ring 13b seals between the second partition wall 4 and the shell 5. A drive shaft 8 is rotatably provided in the shaft support hole 2b of the front housing 1 through a shaft seal device 11 and a slide bearing 12a. A communication passage 9 b is formed in the first partition wall 2 to allow the suction chamber 9 and the shaft seal device 11 to communicate with each other.

  As shown in FIGS. 2 and 3, a rotor 15 is press-fitted into the drive shaft 8. The rotor 15 has a columnar shape with a circular cross section orthogonal to the axis O and is rotatable in the cylinder chamber 7. On the outer peripheral surface of the rotor 15, five vane grooves 15 a are recessed while being slightly inclined toward the axis O. The vane groove 15 a is formed at a position closer to the drive shaft 8 than the rectangular portion 15 c so as to be connected to the rectangular portion 15 c and a rectangular portion 15 c having a rectangular cross section having two parallel surfaces extending so as to face the vane 17. And a circular hole 15d having a circular cross section. A vane 17 is accommodated in each vane groove 15a so as to be able to appear and retract. A back pressure chamber 15b is formed between the bottom surface of each vane 17 and each vane groove 15a. Five compression chambers 19 are formed by the two adjacent vanes 17, the outer peripheral surface of the rotor 15, the inner peripheral surface of the cylinder chamber 7, the first surface 2 a, and the second surface 4 a. The compression chamber 19 and the suction chamber 9 in the suction stroke communicate with each other through a suction port 9c.

  As shown in FIG. 3, two discharge spaces 10 a are formed between the cylinder forming portion 7 a of the front housing 1 and the shell 5. The compression chamber 19 in the discharge stroke and each discharge space 10a communicate with each other through a discharge port 10b. In each discharge space 10a, a discharge valve 10c that closes the discharge port 10b and a retainer 10d that regulates the lift amount of the discharge valve 10c are provided.

  As shown in FIGS. 1 and 6, a bulging portion 3 a that bulges toward the discharge chamber 10 with a certain thickness is formed at the center of the rear side plate 3. An oil separation chamber 21 is formed in the bulging portion 3a so as to extend vertically in a cylindrical shape. A separation cylinder 21 c formed in a two-stage cylindrical shape is press-fitted into the upper end of the oil separation chamber 21. The upper end of the separation cylinder 21c communicates with the discharge chamber 10 and faces the outflow port 10a. The oil separation chamber 21 is formed with a cylindrical guide surface 21a that faces the lower portion of the separation cylinder 21c. The discharge space 10a and the oil separation chamber 21 communicate with each other through a discharge hole 10f. The refrigerant gas discharged from the discharge hole 10f goes around the guide surface 21a. The oil separation chamber 21 communicates with the discharge chamber 10 through a communication hole 21b at the lower end. The separator 20 is constituted by the oil separation chamber 21, the discharge hole 10f, the separation cylinder 21c, the guide surface 21a, and the communication hole 21b.

  The second partition wall 4 is formed with a first introduction path 23a and a second introduction path 23b. The first introduction path 23 a extends upward from the lower end of the second partition wall 4 and communicates with the discharge chamber 10. The second introduction path 23b extends from the upper end of the first introduction path 23a to the supply chamber 2c. The rear end of the second introduction path 23b is sealed. The first introduction path 23a and the second introduction path 23b correspond to the introduction path.

  The rear end portion 8a of the drive shaft 8 communicates with one shaft hole 8b extending along the axis O from the rear end to the front, and the shaft hole 8b. From the front portion of the shaft hole 8b to the rear end portion 8a. Two radial holes 8c extending in the radial direction to the shaft peripheral surface are formed. As shown in FIG. 7, the both-diameter holes 8 c are opened by the intermittent openings 8 x at point-symmetric positions around the axis O of the drive shaft 8. The shaft hole 8b and the diameter hole 8c correspond to an axial path. The introduction path, the supply chamber 2c, the shaft hole 8b, and the diameter hole 8c correspond to the upper flow path.

  As shown in FIGS. 6 and 7, a sliding bearing 12 b is press-fitted into the shaft support hole 4 b of the second partition wall 4. Two through holes 25a are provided in the sliding bearing 12b in the radial direction. Both through holes 25 a are also symmetric with respect to the axis O of the drive shaft 8. An annular path 4d is formed in the shaft support hole 4b along the outer peripheral surface of the sliding bearing 12b. The annular path 4d has an annular shape that is coaxial with the drive shaft 8. The through hole 25a and the annular path 4d are receiving paths. As shown in FIGS. 7A and 7B, the rotation of the drive shaft 8 causes the diameter hole 8c and the through hole 25a to communicate or not communicate with each other. The diameter hole 8c and the through hole 25a constitute an intermittent mechanism.

  As shown in FIG. 6, the second partition wall 4 is formed with two discharge holes 4 e extending in the axial direction from the annular path 4 d to the second surface 4 a of the second partition wall 4. Both the discharge holes 4 e are also symmetric with respect to the axis O of the drive shaft 8. Further, as shown in FIG. 7, two oil drain grooves 4 c having an arc shape around the axis O are recessed in the second surface 4 a of the second partition wall 4. Both oil drain grooves 4 c are also symmetrical with respect to the axis O of the drive shaft 8. As shown in FIG. 4, each oil drain groove 4 c communicates with the back pressure chamber 15 b in the suction stroke or the like by the rotation of the rotor 15.

  On the rear surface of the rotor 15 on the second partition wall 4 side, first and second narrow grooves 16a to 16e that are respectively communicated with the back pressure chamber 15b and extend toward the axis O are recessed.

  Each first narrow groove 16a to 16d extends in the same direction as the direction in which each vane groove 15a extends. On the other hand, the second narrow groove 16e extends in a direction different from the direction in which each vane groove 15a extends. As shown in FIG. 5, each of the first and second narrow grooves 16 a to 16 e has an angular width W <b> 1 around the axis O at a position of a radius r <b> 1 from the axis O. The angular width W1 is narrower than the angular width W2 around the axis O in the round hole 15d of the back pressure chamber 15b at the radius r2 from the axis O. The radius r1 is smaller than the radius r2. That is, the first and second narrow grooves 16a to 16e extend from each back pressure chamber 15b toward the axis O with an angle width narrower than the angle width around the axis O of each back pressure chamber 15b.

  Both the discharge holes 4 e are open from the axis O to the position of the radius r 1 on the second surface 4 a of the second partition wall 4. Therefore, each back pressure chamber 15 b communicates with the annular path 4 d through the discharge hole 4 e and the first and second narrow grooves 16 a to 16 e by the rotation of the rotor 15. The rotation angle of the discharge hole 4e with the first and second narrow grooves 16a to 16e by the rotation of the rotor 15 is θ1. Both the through holes 25a, the annular path 4d, the discharge hole 4e, and the first and second narrow grooves 16a to 16e correspond to the lower flow path. The upper flow path, the lower flow path, and the intermittent mechanism correspond to back pressure supply means.

  Although not shown, the outlet 10e is connected to the condenser by piping, the condenser is connected to the expansion valve by piping, the expansion valve is connected to the evaporator by piping, and the evaporator is connected to the inlet 9a by piping. ing. A condenser, an expansion valve, and an evaporator constitute an external refrigeration circuit. The refrigeration circuit including the vane type compressor of Example 1 constitutes a vehicle air conditioner.

  In the vane type compressor of the first embodiment, when the drive shaft 8 is driven by an engine or the like, the rotor 15 rotates in synchronization with the drive shaft 8 and each compression chamber 19 undergoes a volume change. For this reason, the refrigerant gas that has passed through the evaporator is sucked into the suction chamber 9 from the inlet 9a, and is sucked into the compression chambers 19 through the suction port 9c. Then, the refrigerant gas compressed in each compression chamber 19 is discharged into the discharge space 10a through the discharge port 10b, and is discharged toward the guide surface 21a of the separator 20 from the discharge hole 10f. For this reason, lubricating oil is centrifuged from refrigerant gas. The separated lubricating oil is stored in the discharge chamber 10 from the oil separation chamber 21 through the communication hole 21b. The refrigerant gas from which the lubricating oil has been separated is discharged from the outlet 10a toward the condenser.

  During this time, as shown in FIG. 7 (A), if both the diameter holes 8c and both the through holes 25a are not in communication due to the phase of the drive shaft 8, the discharge chamber 10 and both the discharge holes 4e are not in communication. . For this reason, the high-pressure lubricating oil in the discharge chamber 10 is supplied to the first introduction path 23a, the second introduction path 23b, the supply chamber 2c, the shaft hole 8b, and the both diameter holes 8c, but both the through holes 25a, It does not reach the annular path 4d and the two discharge holes 4e, and is not supplied to each back pressure chamber 15b.

  On the other hand, as shown in FIG. 7 (B), if both the diameter holes 8c and both the through holes 25a communicate with each other by the phase of the drive shaft 8, the discharge chamber 10 and both the discharge holes 4e communicate with each other. Therefore, the high-pressure lubricating oil in the discharge chamber 10 is discharged from the first introduction path 23a, the second introduction path 23b, the supply chamber 2c, the shaft hole 8b, the both diameter holes 8c, the both through holes 25a, the annular path 4d, and both. It is supplied to the hole 4e and supplied to each back pressure chamber 15b.

  In the vane type compressor according to the first embodiment, as illustrated in FIG. 5, the first and second narrow grooves 16 a to 16 e are provided on the rear surface of the rotor 15. The back pressure chambers 15b communicate with each other through the two narrow grooves 16a to 16e. Therefore, the first and second narrow grooves 16a to 16e communicate with the discharge holes 4e in the angle range θ1.

  FIG. 8 shows an angle range θ1 in which each of the first and second narrow grooves 16a to 16e communicates with each discharge hole 4e, and an angle range R in which both the diameter holes 8c communicate with both the communication holes 25a. The angle range θ1 is set so as not to overlap with the angle range R. That is, when the both diameter holes 8c are in a position communicating with both the through holes 25a, the first and second narrow grooves 16a to 16e are in positions not communicating with the respective discharge holes 4e. On the other hand, when each of the first and second narrow grooves 16a to 16e is in a position where it communicates with each of the discharge holes 4e, both the diameter holes 8c are in a position where they are not in communication with both the communication holes 25a. That is, at any rotation angle of the drive shaft 8, at least one of the plurality of communication locations existing in the back pressure supply means is not in communication.

  In addition, even if any of each of the first and second narrow grooves 16a to 16e is in a position not communicating with each discharge hole 4e, each discharge hole 4e is quickly driven by the rotation of the drive shaft 8. The lubricating oil communicated with any one of the two narrow grooves 16a to 16e and temporarily held in the discharge hole 4e is discharged into any one of the first and second narrow grooves 16a to 16e. For this reason, the back pressure of the back pressure chamber 15b does not become insufficient.

  Further, when any one of the first and second narrow grooves 16a to 16e is in a position not communicating with each discharge hole 4e, and both the diameter holes 8c are located in positions not communicating with both the communication holes 25a, that is, In FIG. 8, even when the angle range is neither R nor θ, the lubricating oil is temporarily held in the discharge holes 4 e, but each discharge hole 4 e quickly follows by the rotation of the drive shaft 8. Lubricating oil communicated with any of the first and second narrow grooves 16a to 16e and temporarily held in the discharge hole 4e is discharged into any of the first and second narrow grooves 16a to 16e. For this reason, the back pressure of the back pressure chamber 15b is not insufficient in this case.

  In particular, in the present embodiment, the second narrow groove 16e extends in a direction different from the direction in which the first narrow grooves 16a to 16d extend. Compared with the case where the narrow grooves 16a to 16e all extend in the same direction with respect to the plurality of vane grooves 15a arranged at equal intervals, and the angular range θ1 of the narrow grooves 16a to 16e is equal, the second narrow grooves. The angle range θ1 of 16e is shifted to the leading side. Therefore, the angle range θ1 of the second narrow groove 16e overlaps with the angle range θ1 of the first narrow groove 16b that is a narrow groove that is not adjacent to the second narrow groove 16e, and the second narrow groove 16e and the first narrow groove There is an angular range in which 16b communicates with the discharge holes 4e simultaneously. In addition, the angle range between the angle range θ1 of the second narrow groove 16e and the angle range θ1 of the following first narrow groove 16c is large, and both the diameter holes 8c are both through holes in this angle range. An angle range R communicating with 25a is set. For this reason, it is desirable to change the direction of each narrow groove.

  With such a configuration, when the drive shaft 8 is stopped, if the phase of the drive shaft 8 is not in communication, that is, if both the diameter holes 8c are not in communication with both the communication holes 25a, the discharge chamber 10 and The back pressure chambers 15b are not in communication with each other, and the backflow of the refrigerant gas and the reverse rotation of the drive shaft 8 can be prevented. Even if the phase of the drive shaft 8 communicates when the drive shaft 8 is stopped, that is, both the diameter holes 8c are in a position where the both communication holes 25a communicate with each other, the first and second narrow grooves 16a to 16e and the respective discharge holes Since 4e is in a position where it does not communicate, reverse flow of the refrigerant gas and reverse rotation of the drive shaft 8 can be prevented.

  That is, during operation of the compressor, the back pressure can be sufficiently supplied even if there is a non-communication portion in the back pressure supply means, and a small amount of refrigerant gas generated when the drive shaft 8 is stopped The reverse flow of the refrigerant gas and the reverse rotation of the drive shaft 8 can be reliably prevented without depending on the phase shift of the drive shaft 8 due to the reverse flow and the reverse rotation of the drive shaft 8.

  Thus, in the vane type compressor of the first embodiment, both the diameter holes 8c communicate with the both through holes 25a in the angle range R. For this reason, in the vane type compressor of the first embodiment, each vane 17 is preferably pressed against the inner surface of the cylinder chamber 7, so that each vane 7 is lubricated in the vane groove 15a and chattering is prevented, and the compression chamber Leakage of refrigerant gas from 19 is prevented and efficiency is improved.

  In order to compare with the vane type compressor of Example 1, the vane type compressor of the comparative example will be examined. In the vane type compressor of the comparative example, as shown in FIG. 9, the first and second narrow grooves 16 a to 16 e are not recessed on the rear surface of the rotor 15 on the second partition wall 4 side. Further, both the discharge holes 4 e are open from the axis O to the position of the radius r 2 on the second surface 4 a of the second partition wall 4. The angle range in which the discharge hole 4e communicates with each back pressure chamber 15b by the rotation of the rotor 15 is θ2. The angle range θ2 is larger than the angle range θ1. Other configurations are the same as those of the vane type compressor of the first embodiment.

  In the vane type compressor of the comparative example, each discharge hole 4e communicates directly with each back pressure chamber 15b by the rotation of the rotor 15. In this case, since the angular range θ2 in which each discharge hole 4e and each back pressure chamber 15b communicate with each other according to the rotation of the rotor 15 is large, the discharge hole 4e communicates with each back pressure chamber 15b as shown in FIG. It is difficult to set the angle range R between each angle range θ2.

  That is, in the vane type compressor of Comparative Example 1, it is difficult to set an angle at which the intermittent mechanism or the rotor 15 makes the discharge chamber 10 and each of the back pressure chambers 15b communicate with each other. For this reason, in order to shorten the communication time between each discharge hole 4e and each back pressure chamber 15b, it is conceivable to narrow the angle range θ2. That is, it is conceivable to reduce the round hole 15d of the back pressure chamber 15b. However, the round hole portion 15d is formed so as to penetrate the cylinder 15 in the axial direction, and it requires manufacturing costs and man-hours to drill a small diameter through hole. In the first embodiment, only the first and second narrow grooves 16a to 16e are recessed on the rear surface of the rotor 15, and processing is easy.

  As shown in FIG. 8, in order to set the angle range θ1 so as not to overlap the angle range R, the extending direction of the specific narrow groove is changed, and the timing at which the specific narrow groove communicates in the angle range θ1 is preceded. It may be shifted to the side or the following side. In the vane type compressor of the first embodiment, since the extending direction of the second narrow groove 16e is different from that of the first narrow grooves 16a to 16d, the discharge hole 4e communicates with the first and second narrow grooves 16a to 16e. The timing can be changed arbitrarily.

  Therefore, according to the vane type compressor of the first embodiment, at least one place is not communicated between the discharge chamber 10 and the back pressure chamber 15b, and the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft 8 are more reliably performed. It can be reduced.

(Example 2)
In the vane type compressor of the second embodiment, as shown in FIG. 11, a supply chamber 2d is formed behind the shaft support hole 4b. The supply chamber 2d is partitioned from the shaft support hole 4b by the rear end portion 8a of the drive shaft 8, and is larger in the radial direction than the shaft support hole 4b.

  Further, a first introduction path 23 c is formed in the second partition wall 4. The first introduction path 23c extends upward from the lower end of the second partition wall 4 and opens in the shaft support hole 4b. A sliding layer 26 is formed on the inner peripheral surface of the shaft support hole 4b. As the sliding layer 26, tin plating is adopted. The sliding layer 26 is provided with a second introduction path 23d that communicates with the first introduction path 23c. The first introduction path 23c and the second introduction path 23d correspond to the introduction path and the upper flow path. Instead of the sliding bearing 12a provided in the shaft support hole 2b of the front housing 1, a sliding layer (not shown) is also formed.

  Furthermore, two discharge holes 4 f extending in the axial direction from the supply chamber 2 d to the second surface 4 a of the second partition wall 4 are formed in the second partition wall 4. Both the discharge holes 4f are also symmetric with respect to the axis O of the drive shaft 8, as shown in FIGS. 12 (A) and 12 (B). Both diameter holes 8c, shaft hole 8b, supply chamber 2d, and both discharge holes 4f correspond to the lower flow path. By the rotation of the drive shaft 8, the second introduction path 23d and the diameter hole 8c are in communication or non-communication. The second introduction path 23d and the diameter hole 8c constitute an intermittent mechanism. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, as shown in FIG. 12A, if the second introduction path 23d and both the diameter holes 8c are not in communication due to the phase of the drive shaft 8, the discharge chamber 10 and the both discharge holes 4f Is not connected. For this reason, although the high-pressure lubricating oil in the discharge chamber 10 is supplied to the first introduction path 23c and the second introduction path 23d, the both-diameter hole 8c, the shaft hole 8b, the supply chamber 2d, and both the discharge holes 4f It does not reach and is not supplied to each back pressure chamber 15b.

  Further, as shown in FIG. 12B, if the second introduction path 23d and both the diameter holes 8c communicate with each other by the phase of the drive shaft 8, the discharge chamber 10 and both the discharge holes 4f communicate with each other. For this reason, the high-pressure lubricating oil in the discharge chamber 10 is supplied to the first introduction path 23c, the second introduction path 23d, the both-diameter holes 8c, the shaft hole 8b, the supply chamber 2d, and the both discharge holes 4f. It is supplied to the chamber 15b. Other functions and effects are the same as those of the first embodiment.

  In the above, the present invention has been described with reference to the first and second embodiments. However, the present invention is not limited to the first and second embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, it is possible to form a narrow groove or the like on the second partition wall.

  The shaft path is not limited to the shaft hole 8b and the diameter hole 8c, but may be a shaft groove that is recessed in the axial direction on the outer peripheral surface of the rear end portion 8a of the drive shaft 8.

  Further, the receiving path is not limited to the through hole 25a and the annular groove 4d, but may be a concave portion that is partially recessed on the inner peripheral surface of the shaft support hole 4b.

  Further, the sliding layer 26 may be formed on the inner peripheral surface of the shaft support hole 4 b or may be formed on the shaft peripheral surface of the drive shaft 8.

  The present invention is applicable to a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 2 ... 1st partition wall 4 ... 2nd partition wall 2a ... 1st surface 4a ... 2nd surface 7 ... Cylinder chamber 9 ... Suction chamber 10 ... Discharge chamber 1, 3, 5 ... Housing (1 ... 1st housing, front housing 3 ... second housing, rear side plate, 5 ... shell)
O ... shaft center 8 ... drive shaft 15a ... vane groove 15 ... rotor 19 ... compression chamber 17 ... vane 15b ... back pressure chamber 23a, 23b, 2c, 8b, 8c, 25a, 4d, 4e, 16a-16e ... back pressure supply Means (23a, 23b, 2c, 8b, 8c ... upper flow path, 4d, 4e, 16a-16e, 25a ... lower flow path, 8c, 25a ... intermittent mechanism)
16a to 16e ... narrow groove (16a to 16d ... first narrow groove, 16e ... second narrow groove)
8a ... rear end 4b ... shaft support hole 2c, 2d ... supply chamber 23a, 23b, 23c, 23d ... introduction path (23a, 23c ... first introduction path, 23b, 23d ... second introduction path)
8b, 8c ... axial path (8b ... axial hole, 8c ... radial hole)
25a, 4d ... receiving path (25a ... through hole, 4d ... circular path)
4e, 4f ... discharge hole 8x ... intermittent port

Claims (6)

A housing in which a suction chamber, a discharge chamber and a cylinder chamber are formed;
A drive shaft rotatably provided in the housing;
A rotor provided in a synchronous manner with the drive shaft in the cylinder chamber and having a plurality of vane grooves;
Each vane groove is provided so as to be able to appear and disappear, and includes a vane that forms each compression chamber,
The housing has a first partition wall and a second partition wall, and the cylinder chamber is disposed between a first surface that is a rear surface of the first partition wall and a second surface that is a front surface of the second partition wall. Formed, the second partition wall partitions the cylinder chamber and the discharge chamber,
The compression chamber is formed by an inner surface of the cylinder chamber, an outer surface of the rotor, the first surface, the second surface, and the vanes.
A space between each of the vane grooves and each of the vanes is a back pressure chamber defined by the first surface and the second surface.
Between the discharge chamber and each back pressure chamber, in the vane type compressor provided with back pressure supply means capable of supplying lubricating oil in the discharge chamber to each back pressure chamber,
The back pressure supply means includes an upper flow path communicating with the discharge chamber, a lower flow path communicating or not communicating with the back pressure chambers by the rotor according to a phase in a rotation direction of the drive shaft, and the upper flow path. And an intermittent mechanism that connects or disconnects the upper channel and the lower channel according to the phase in the rotational direction of the drive shaft,
When the intermittent mechanism communicates the upper flow path and the lower flow path, the rotor does not communicate the lower flow path with any of the back pressure chambers, and the rotor causes the lower flow path to any of the back pressure chambers. The vane type compressor, wherein the intermittent mechanism makes the upper flow path and the lower flow path non-communication when communicating with the chamber.   The lower flow path is formed in the second partition wall, and is provided with a discharge hole through which the lubricating oil having passed through the intermittent mechanism can be discharged into the cylinder chamber, and recessed on the rear surface of the rotor on the second partition wall side. The vane type compressor according to claim 1, further comprising a narrow groove extending from each of the back pressure chambers toward the shaft center and capable of communicating with the discharge hole according to a phase in a rotation direction of the drive shaft.   Each narrow groove includes a first narrow groove extending in a first direction from each back pressure chamber toward the axis, and a second direction different from the first direction from each back pressure chamber toward the axis. The vane type compressor according to claim 2, further comprising: a second narrow groove extending at a distance. The second partition wall includes a shaft support hole that pivotally supports a rear end portion of the drive shaft, and a supply chamber that is positioned behind the shaft support hole and is partitioned from the shaft support hole by the rear end portion. Formed,
The upper flow path is formed in the second partition wall and extends from the discharge chamber to the supply chamber, the supply chamber, and an axial path formed in the rear end portion and communicating with the supply chamber. Become
The lower flow path is formed in the second partition wall, and includes a receiving path that opens in the shaft support hole, and the discharge hole that communicates with the receiving path.
The vane compressor according to any one of claims 1 to 3, wherein the intermittent mechanism is provided between the axial path and the receiving path. The second partition wall includes a shaft support hole that pivotally supports a rear end portion of the drive shaft, and a supply chamber that is positioned behind the shaft support hole and is partitioned from the shaft support hole by the rear end portion. Formed,
The upper flow path is formed on the second partition wall and includes an introduction path that extends from the discharge chamber and opens into the shaft support hole,
The lower flow path is formed in the rear end portion, and includes an axial path communicating with the supply chamber, and formed in the second partition wall, and the discharge hole communicating with the supply chamber.
4. The vane compressor according to claim 1, wherein the intermittent mechanism is provided between the introduction path and the axial path. 5. The axial path has a plurality of intermittent openings on the peripheral surface of the drive shaft,
The vane type compressor according to claim 4 or 5, wherein the intermittent port is in a point-symmetrical position with respect to the axis of the drive shaft.

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