JP6115228B2 - Vane type compressor - Google Patents

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 front side plate, a rear side plate, a rotating shaft, a rotor, and a plurality of vanes.

  A cylinder chamber, a suction chamber, and a discharge chamber are formed in the housing. The front of the cylinder chamber is closed by a front side plate. The rear of the cylinder chamber is closed by a rear side plate. A rotation shaft is rotatably provided in the housing.

  A rotor is provided in the cylinder chamber so as to be able to rotate synchronously with the rotation shaft. In the rotor, a plurality of vane grooves are formed in the radial direction, and vanes are provided in the respective vane grooves so as to be able to appear and disappear. A compression chamber is formed by the inner surface of the cylinder chamber, the outer surface of the rotor, the rear surface of the front side plate, the front surface of the rear side plate, and the vanes. A back pressure chamber is formed between the bottom surface of each vane and each vane groove.

  In this vane type compressor, a sliding bearing is not employed between the rotating shaft and the rear side plate. For this reason, the rear side plate is formed with a cylindrical bearing surface that supports the rotating shaft. The shaft circumferential surface of the rotating shaft is supported by the bearing surface.

  Further, each back pressure chamber is communicated with the discharge chamber by a back pressure supply mechanism in the compression stroke. The back pressure supply mechanism includes a supply chamber, an upper flow path, a rotation path, and a lower flow path. The supply chamber is formed on the rear end side of the rotating shaft. The upper flow path is formed in the rear side plate and extends to the discharge chamber or the supply chamber. The rotating path is formed in the rotating shaft and has a rotating opening that communicates with the supply chamber and opens on the circumferential surface of the shaft. The lower flow path is formed in the rear side plate. The lower flow path includes a first lower flow path that is partially recessed in the circumferential direction on the bearing surface, and a second lower flow path that connects the first lower flow path and each back pressure chamber in the compression stroke. If the rotation opening and the first lower flow path face each other according to the rotation of the rotation shaft, the upper flow path and the second lower flow path communicate with each other through the supply chamber. Further, if the rotation opening and the first lower flow path are not opposed to each other according to the rotation of the rotation shaft, the upper flow path and the second lower flow path are not communicated with each other through the supply chamber.

  In this vane type compressor, since the sliding bearings generally adopted are abolished, the number of parts can be reduced correspondingly, and the manufacturing cost can be reduced.

  Further, in this vane type compressor, the rotation path makes the discharge chamber communicate with the back pressure chamber during the compression stroke or makes it non-communication depending on the phase in the rotation direction of the rotation shaft. For this reason, high-pressure lubricating oil is intermittently supplied to each back pressure chamber during the compression stroke. For this reason, each vane is intermittently 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.

  If the rotation of the rotating shaft is stopped and the discharge chamber and each back pressure chamber are not communicated with each other in this state, the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotating shaft do not occur. Even if the rotation of the rotary shaft is stopped in a state where the discharge chamber and each back pressure chamber communicate with each other, if the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotary shaft occur, the phase of the rotary shaft shifts accordingly. Therefore, the discharge chamber and each back pressure chamber are immediately disconnected, and no further reverse flow of the refrigerant gas or the like and the reverse rotation of the rotating shaft do not occur. For this reason, this vane type compressor can prevent the reverse flow of refrigerant gas or the like and the reverse rotation of the rotating shaft reliably and early.

  Moreover, in this vane type compressor, the rotating path is formed in the rotating shaft. For this reason, it is not necessary to secure a space in the vane compressor for providing a conventional on-off valve or check valve, and the vane compressor does not increase in size. In addition, since the rotating path can be easily formed on the rotating shaft, it is possible to save time and labor when developing many different models for vehicles and the like.

FIGS. 11-14 of JP2012-127335A

  However, in the conventional vane type compressor, the first lower flow path, which is a part of the lower flow path of the back pressure supply mechanism, is partially recessed in the circumferential direction with respect to the cylindrical bearing surface. For this reason, it is difficult to process, and it is difficult to further reduce the manufacturing cost.

  In this vane type compressor, when the first lower flow path is partially recessed in the circumferential direction, the first lower flow path is easily opened at a large angle around the axis of the rotation shaft, and the rotation path is the first lower flow path. It is hard to become disconnected. For this reason, there exists a possibility of producing reverse flow of refrigerant gas etc. and reverse rotation of a rotating shaft.

  The present invention has been made in view of the above-described conventional situation, and is a vane type compression that can more reliably reduce the backflow of refrigerant gas and the like and the reverse rotation of the rotating shaft while further reducing the manufacturing cost. Providing a machine is an issue to be solved.

The vane compressor of the present invention includes a housing in which a cylinder chamber, a suction chamber, and a discharge chamber are formed, a front side plate that closes the front of the cylinder chamber, a rear side plate that closes the rear of the cylinder chamber, A rotary shaft body rotatably provided in the housing, a rotor provided in a synchronous manner with the rotary shaft body in the cylinder chamber, and formed with a plurality of vane grooves, and capable of appearing and retracting in each vane groove. Provided with an inner surface of the cylinder chamber, an outer surface of the rotor, a rear surface of the front side plate, and a vane that forms each compression chamber together with the front surface of the rear side plate,
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
The rear side plate is formed with a cylindrical bearing surface,
The shaft peripheral surface of the rotating shaft body is supported by the bearing surface,
Each of the back pressure chambers is a vane compressor that communicates with the discharge chamber by a back pressure supply mechanism in a compression stroke,
The back pressure supply mechanism is formed in the rear side plate and extends from the discharge chamber and has an upstream flow path having an upstream opening that opens to the bearing surface;
A supply chamber formed on the rear end side of the rotary shaft body;
A rotary path formed in the rotary shaft body, having a rotary opening that opens on the circumferential surface of the shaft and communicating with the supply chamber;
The rear side plate is formed of a lower flow path that communicates the supply chamber and the back pressure chambers of the compression stroke,
The upstream opening and the rotary opening communicate the upper flow path and the supply chamber according to the rotation of the rotary shaft body ,
It said supply chamber and said downstream path, regardless of the rotation of the rotary shaft body, you characterized that you have communicated.

  In the vane type compressor of the present invention, in the back pressure supply mechanism, if the upstream opening of the upper flow path and the rotary opening of the rotary path face each other due to the phase in the rotation direction of the rotary shaft, the upper flow path is supplied via the rotary path. The chamber communicates with each other, and the discharge chamber communicates with each back pressure chamber. For this reason, high-pressure refrigerant gas or the like in the discharge chamber passes through the rotation path and the supply chamber, and is supplied to each back pressure chamber via the lower flow path. Further, if the upstream opening and the rotation opening are not opposed to each other due to the rotation direction phase of the rotation shaft, the upper flow path and the supply chamber are not communicated with each other via the rotation path, and the discharge chamber and each back pressure chamber are not connected. It becomes communication. For this reason, high-pressure refrigerant gas or the like in the discharge chamber does not reach the rotation path from the upper flow path, and is not supplied to each back pressure chamber. For this reason, high-pressure lubricating oil is intermittently supplied to each back pressure chamber during the compression stroke. For this reason, each vane is intermittently pressed against the inner surface of the cylinder chamber. For this reason, each vane is lubricated in the vane groove, chattering is prevented, and leakage of refrigerant gas or the like from the compression chamber is prevented, thereby improving efficiency.

  Further, in this vane type compressor, when the rotation of the rotating shaft is stopped and the rotating path and the upper flow path are not communicated in this state, the reverse flow of the refrigerant gas or the like and the rotating shaft are not reversed. Even if the rotation of the rotary shaft is stopped in a state where the rotary path and the upper flow path are in communication, if the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotary shaft occur, the phase of the rotary axis shifts thereby, Immediately, the rotation path and the upper flow path are disconnected, and no further reverse flow of the refrigerant gas or the like and no reversal of the rotation shaft occur. For this reason, this vane type compressor can reliably prevent the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotating shaft.

  Further, in this vane type compressor, the refrigerant gas or the like in the discharge chamber passes through the upper flow path, passes through the rotation path, and then flows through the supply chamber to the lower flow path. This path does not require a concave groove like the conventional first lower flow path on the bearing surface. For this reason, a partial concave cutting process in the circumferential direction is not required for the bearing surface of the rear side plate. For this reason, processing is easy, and the manufacturing cost can be further reduced.

  In addition, this vane compressor does not require a concave groove like the conventional first lower flow path that easily opens at a large angle around the axis of the rotation shaft. For this reason, the rotation path tends to be surely connected or disconnected with the upper flow path. For this reason, it is hard to produce reverse flow of refrigerant gas etc. and reverse rotation of a rotating shaft.

  Further, in this vane type compressor, the rotation path is in communication or non-communication with the upper flow path depending on the phase of the rotation shaft. For this reason, the high-pressure lubricating oil in the discharge chamber reliably reaches the bearing surface and the shaft circumferential surface from the upper flow path. For this reason, even if it eliminates a sliding bearing, a rotating shaft can be rotated suitably.

  Therefore, according to this vane type compressor, it is possible to more reliably reduce the backflow of the refrigerant gas and the like and the reverse rotation of the rotating shaft while further reducing the manufacturing cost.

At least one of the bearing surfaces and the shaft periphery, it is not preferable that sliding layer to reduce the sliding resistance between the bearing surface and the shaft periphery is formed. In this case, the rotating shaft can be suitably rotated. If high-pressure lubricating oil is supplied to the sliding layer, the rotating shaft can be rotated more suitably. As the sliding layer, it is possible to employ a fluorine resin such as tin plating or PTFE.

  The sliding layer may be formed on the bearing surface, may be formed on the shaft circumferential surface, or may be formed on the bearing surface and the shaft circumferential surface. A sliding layer can be easily formed on the shaft peripheral surface.

Sliding layer, it is not preferable tin plating formed on the bearing surface. Tin plating is provided on the inner surfaces of the front side plate and the rear side plate, respectively. This is for reducing the sliding resistance against the rotor provided between the front side plate and the rear side plate by tin plating. If the tin plating is formed on the bearing surface, the tin plating on the bearing surface can be formed at the same time when the tin plating is formed on the inner surface side of the rear side plate. No process is required. For this reason, in this case, the manufacturing cost can be surely reduced.

Rotating path, a shaft hole extending in the axial direction, passed through the axial hole and communicates, Ru obtained consists of a diameter hole extending radially to the axis circumference. The shaft hole may be a center hole formed in the rotating shaft . If the center hole is a shaft hole, there is no need to form a special shaft hole, and the manufacturing cost can be reduced.

Rotating passage is recessed into the shaft circumference, Ru can consist axial grooves extending axially. The high-pressure lubricating oil is supplied to the shaft groove when the rotation path communicates with the upper flow path by the phase of the rotation shaft. The opening area facing the bearing surface in the axial groove extending in the axial direction is larger than the opening area of the diameter hole not extending in the axial direction. For this reason, when a rotating shaft rotates, a high pressure lubricating oil is more easily supplied between a bearing surface and a shaft peripheral surface, and a rotating shaft can be rotated more suitably. Further, since the shaft groove is provided on the shaft peripheral surface in the axial direction, the cutting process becomes easier and the manufacturing cost can be further reduced.

  According to the vane type compressor of the present invention, it is possible to more reliably reduce the backflow of refrigerant gas and the like and the reverse rotation of the rotating shaft while further reducing the manufacturing cost.

1 is a cross-sectional view of a vane type compressor of Example 1. FIG. It is a vane type compressor of Example 1, and is a II-II arrow sectional view of Drawing 1. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. It is a back view of the partial cross section in the state which concerns on the vane type compressor of Example 1, and removed the centrifugal separator. FIG. 3 is an enlarged cross-sectional view of a main part of the vane compressor according to the first embodiment. Fig. (A) shows a state where the upper flow path and the rotation path are in communication, and Fig. (B) shows a state where the upper flow path and the rotation path are not in communication. 3 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 2. FIG. FIG. 6 is an enlarged cross-sectional view of a main part of a vane compressor according to a second embodiment. Fig. (A) shows a state where the upper flow path and the rotation path are in communication, and Fig. (B) shows a state where the upper flow path and the rotation path are not in communication. FIG. 6 is an enlarged cross-sectional view of a main part of a vane type compressor according to a third embodiment. Fig. (A) shows a state where the upper flow path and the rotation path are in communication, and Fig. (B) shows a state where the upper flow path and the rotation path are not in communication. 6 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 4. FIG. FIG. 6 is an enlarged cross-sectional view of a main part of a vane compressor according to a fourth embodiment. Fig. (A) shows a state where the upper flow path and the rotation path are in communication, and Fig. (B) shows a state where the upper flow path and the rotation path are not in communication.

  Embodiments 1 to 4 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIGS. 1 and 2, the vane compressor according to the first embodiment is fixed in a state in which a cylinder block 3 is accommodated in a front housing 1 and a rear housing 2 that are coupled to each other. The cylinder block 3 is formed with an elliptical cylinder chamber 3a in a direction perpendicular to the axis. The front housing 1, the rear housing 2, and the cylinder block 3 correspond to the housing.

  A front side plate 4 and a rear side plate 5 are fixed in the front housing 1 and the rear housing 2, and the front and rear of the cylinder chamber 3a are closed by the front side plate 4 and the rear side plate 5, respectively. ing.

  Shaft holes 4a and 5a are formed in the front side plate 4 and the rear side plate 5, respectively. Cylindrical bearing surfaces 4b and 5b are formed on the inner surfaces of the shaft holes 4a and 5a, respectively. A sliding layer 4c is formed on the rear surface of the front side plate 4 and the shaft hole 4a. When the sliding layer 4c is formed on the rear surface side of the front side plate 4, it is also formed on the bearing surface 4b at the same time. A sliding layer 5c is formed on the front surface of the rear side plate 5 and the shaft hole 5a. When the sliding layer 5c is formed on the front side of the rear side plate 5, it is also formed on the bearing surface 5b at the same time. As the sliding layers 4c and 5c, tin plating is adopted. A rotary shaft 9 is rotatably held in the shaft holes 4a and 5a via a shaft seal device 7. The rotating shaft 9 is a rotating shaft body.

  The tip of the rotating shaft 9 protrudes through the shaft hole 1a of the front housing 1, and an electromagnetic clutch or pulley (not shown) is fixed to the tip. A driving force is transmitted to the electromagnetic clutch or pulley by the engine or motor of the vehicle. A cylindrical shaft peripheral surface 9c facing the bearing surface 5b is formed on the rear side plate 5 side of the rotary shaft 9.

  A rotor 10 having a circular cross section is fixed to the rotary shaft 9 so as to be disposed in the cylinder chamber 3a. As shown in FIG. 2, five vane grooves 10 a are formed in the radial direction on the outer peripheral surface of the rotor 10, and the vanes 11 are accommodated in the respective vane grooves 10 a so as to be able to appear and retract. A back pressure chamber 40 is formed between the bottom surface of each vane 11 and each vane groove 10a. Two compression chambers 12 are formed by two adjacent vanes 11 and 11, the outer peripheral surface of the rotor 10, the inner peripheral surface of the cylinder block 3, the inner surface of the front side plate 4 and the inner surface of the rear side plate 5.

  As shown in FIG. 1, a suction chamber 13 is formed between the front housing 1 and the front side plate 4. In the front housing 1, an inlet 1b for connecting the suction chamber 13 to the outside is opened upward. The front side plate 4 is provided with two suction holes 4 d communicating with the suction chamber 13, and each suction hole 4 d communicates with each suction space 3 b of the cylinder block 3. As shown in FIG. 2, each suction space 3b communicates with the compression chamber 12 in the suction stroke by a suction port 3c.

  In addition, two discharge spaces 3 d are formed between the cylinder block 3 and the rear housing 2. The compression chamber 12 in the discharge stroke communicates with each discharge space 3d through a discharge port 3e. In each discharge space 3d, a discharge valve 14 for closing the discharge port 3e and a retainer 15 for regulating the lift amount of the discharge valve 14 are provided.

  As shown in FIGS. 3 and 4, a bulging portion 5 n bulging to the rear side with a certain thickness is formed at the center of the outer surface of the rear side plate 5. The bulging portion 5n extends downward with the same thickness as the step portion 5f and the boss portion 5e bulging rearward around the rotating shaft 9, the step portion 5f having a smaller thickness than the boss portion 5e, and the step portion 5f. It consists of a hanging part 5g. Two discharge grooves 5h and 5i are formed in the stepped portion 5f so as to extend from the vicinity of the upper center toward the lower outer side. Discharge holes 5j and 5k communicating with the respective discharge spaces 3d are formed through the lower ends of the discharge grooves 5h and 5i.

  As shown in FIG. 1, a discharge chamber 16 is formed between the rear side plate 5 and the rear housing 2. In the discharge chamber 16, the centrifugal separator 50 is fixed by being sandwiched between the rear side plate 5 and the rear housing 2. As shown in FIG. 3, the centrifugal separator 50 includes an end frame 17 and a cylindrical portion 18 that is fixed in the end frame 17 and extends vertically.

  The end frame 17 is formed with an oil separation chamber 17a extending vertically in a cylindrical shape. A cylindrical portion 18 is press-fitted into the upper end of the oil separation chamber 17a. For this reason, a part of the oil separation chamber 17 a serves as a guide surface 17 b for circulating the refrigerant gas around the outer peripheral surface of the cylindrical portion 18. The discharge grooves 5h and 5i shown in FIG. 4 communicate with the pair of separation ports 17c on the left and right sides shown in FIG. 3, and both separation ports 17c communicate with the cylindrical portion 18 and the guide surface 17b.

  In addition, a communication port 17 e is formed at the lower end of the end frame 17 to communicate the bottom surface of the oil separation chamber 17 a with the discharge chamber 16. Further, the end frame 17 is provided with a recess 17f for housing the boss portion 5e of the rear side plate 5 together with the rotary shaft 9.

  On the inner surface (front surface) of the rear side plate 5, as shown in FIGS. 2, 4, 5 (A) and (B), a pair of oil drain grooves 5q having a fan shape is recessed. Each oil drain groove 5q communicates with the back pressure chamber 40 in the suction stroke or the like by the rotation of the rotor 10. As shown in FIGS. 1 and 3, the rear side plate 5 is provided with a valve chamber 5d communicating with the discharge chamber 16 and each oil drain groove 5q. The valve chamber 5d has a ball-like shape. The valve body 20 is accommodated. The valve body 20 is urged toward the discharge chamber 16 by a spring 19 housed in the valve chamber 5d. The valve body 20 prevents chattering when the vane compressor is started.

  As shown in FIG. 3, an upper flow path 5 m extending from the lower end to the bearing surface 5 b is provided through the hanging part 5 g of the rear side plate 5. The upstream opening 5x of the upper flow path 5m is open to the bearing surface 5b.

  As shown in FIGS. 3, 5A and 5B, the rotary shaft 9 has one shaft hole 9a extending in the axial direction from the rear end, and communicates with the shaft hole 9a, and the front end of the shaft hole 9a. To the shaft peripheral surface 9c is formed with one radial hole 9b extending in the radial direction. The shaft hole 9 a is a center hole formed in the rotating shaft 9. The shaft hole 9a and the diameter hole 9b are rotation paths extending from the shaft peripheral surface 9c to the supply chamber 17f. The rotation opening 9x of the diameter hole 9b is opened in the shaft peripheral surface 9c.

  Two lower flow paths 5p extending from the rear end of the boss portion 5e to the front end on the rotor 10 side are formed in the boss portion 5e provided on the rear side plate 5. Both lower flow paths 5p communicate with the supply chamber 17f and the back pressure chamber 40 in the compression stroke by the rotation of the rotor 10.

  1 and 3, the rear housing 2 is formed with an outlet 2a for connecting the upper end of the discharge chamber 16 to the outside. The outflow port 2 a is located above the cylindrical portion 18. Although not shown, the outlet 2a 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 1b by piping. ing. A condenser, an expansion valve, and an evaporator constitute an external refrigeration circuit. The refrigeration circuit including the compressor constitutes a vehicle air conditioner.

  In the vane type compressor configured as described above, when the rotary shaft 9 is driven by an engine or the like, the rotor 10 rotates synchronously with the rotary shaft 9 and the compression chamber 12 changes in volume. For this reason, the refrigerant gas having passed through the evaporator is sucked into the suction chamber 13 from the inlet 1b. The refrigerant gas in the suction chamber 13 is sucked into the compression chamber 12 through the suction hole 4d, the suction space 3b, and the suction port 3c. Further, the refrigerant gas compressed in the compression chamber 12 passes through the discharge port 3e and the discharge space 3d and is discharged into the discharge holes 5j and 5k as shown in FIG. Therefore, the refrigerant gas is discharged from the separation port 17c of the centrifugal separator 50 toward the guide surface 17b through the discharge grooves 5h and 5i as shown in FIG. For this reason, the refrigerant gas circulates around the guide surface 17b, and the lubricating oil is centrifuged from the refrigerant gas. The separated lubricating oil is stored in the discharge chamber 16 from the oil separation chamber 17a through the communication port 17e.

  Further, as shown in FIG. 5A, if the upstream opening 5x of the upper flow path 5m and the rotation opening 9x of the rotation path face each other due to the phase of the rotation shaft 9, the upper flow path 5m and the supply chamber are interposed via the rotation path. 17f communicates, and the discharge chamber 16 communicates with each back pressure chamber 40. For this reason, the high-pressure lubricating oil in the discharge chamber 16 passes through the upper flow path 5m, the diameter hole 9b, the shaft hole 9a, and the supply chamber 17f, and is supplied to each back pressure chamber 40 via both the lower flow paths 5p. In particular, in this vane type compressor, when the upper flow path 5m and the diameter hole 9b communicate with each other, both the lower flow paths 5p communicate with the single supply chamber 17f and the back pressure chamber 40, so that they exist in the discharge chamber 16. The high-pressure lubricating oil is easily supplied to each back pressure chamber 40 evenly.

  As shown in FIG. 5B, if the upstream opening 5x and the rotation opening 9x are not opposed to each other due to the phase of the rotation shaft 9, the upper flow path 5m, the supply chamber 17f, and the like are connected via the shaft hole 9b and the diameter hole 9a. Is not connected, and the discharge chamber 16 and each back pressure chamber 40 are not connected. For this reason, although the high-pressure lubricating oil in the discharge chamber 16 is supplied up to the upper flow path 5 m, it does not reach the diameter hole 9 b and the shaft hole 9 a and is not supplied to each back pressure chamber 40.

  For this reason, high-pressure lubricating oil is intermittently supplied to each back pressure chamber 40 during the compression stroke. For this reason, each vane 11 is pressed against the inner surface of the cylinder chamber 3a. Therefore, each vane 11 is lubricated in the vane groove 10a, chattering is prevented, and leakage of the refrigerant gas from the compression chamber 12 is prevented, thereby improving efficiency.

  In addition, by supplying the lubricating oil intermittently and reliably to the back pressure chamber 40, the back pressure supply amount can be adjusted to adjust the back pressure of each vane 11. For this reason, it is also possible to reduce the pressing force of each vane 11 and to reduce the power during operation.

  If the diameter hole 9b is not in communication with the upper flow path 5m in a state where the rotation of the rotating shaft 9 is stopped, the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotating shaft 9 do not occur. As shown in FIG. 5A, even if the rotation of the rotary shaft 9 is stopped in a state where the diameter hole 9b communicates with the upper flow path 5m, the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotary shaft 9 occur slightly. Then, as shown in FIG. 5 (B), the phase of the rotary shaft 9 is thereby shifted, so that the diameter hole 9b immediately becomes out of communication with the upper flow path 5m. No reversal. For this reason, this vane type compressor can reliably prevent the reverse flow of the refrigerant gas or the like and the reverse rotation of the rotary shaft 9.

  Here, in this vane type compressor, the refrigerant gas or the like in the discharge chamber 16 passes through the upper flow path 5m, passes through the radial hole 9b and the shaft hole 9a, and then flows into the lower flow path 5p through the supply chamber 17f. In this path, a concave groove like the conventional first lower flow path is not required on the bearing surface 5b. For this reason, a partial concave cutting process in the circumferential direction is not required for the bearing surface 5 b of the rear side plate 5. For this reason, processing is easy, and further reduction in manufacturing cost can be realized.

  Further, in this vane type compressor, there is no need for a concave groove like the conventional first lower flow path that easily opens at a large angle around the axis of the rotary shaft 9. For this reason, the diameter hole 9b tends to be surely connected or disconnected with the upper flow path 5m. For this reason, it is hard to produce reverse flow of refrigerant gas etc. and reverse rotation of the rotating shaft 9.

  As shown in FIGS. 3, 5 </ b> A and 5 </ b> B, the diameter hole 9 b communicates with or does not communicate with the upper flow path 5 m depending on the phase of the rotating shaft 9. If the diameter hole 9b communicates with the upstream hole 5m, the lubricating oil supplied to the supply chamber 17f is supplied between the bearing surface 5b and the shaft peripheral surface 9c and lubricates between them. If the diameter hole 9b is not in communication with the upstream hole 5m due to the phase of the rotating shaft 9, the high-pressure lubricating oil in the discharge chamber 16 does not reach the diameter hole 9b and the shaft hole 9a, and the bearing is driven by the rotation of the rotating shaft 9. It is supplied between the surface 5b and the shaft peripheral surface 9c. For this reason, even if it eliminates a sliding bearing, the rotating shaft 9 can be rotated suitably.

  Therefore, according to this vane type compressor, it is possible to more reliably reduce the backflow of the refrigerant gas and the like and the reverse rotation of the rotary shaft 9 while further reducing the manufacturing cost.

  Further, in this vane type compressor, the sliding resistance between the rotor 10 provided between the front side plate 4 and the rear side plate 5 is reduced by using tin plating for the sliding layers 4c and 5c. . If the tin plating is formed on the bearing surface 5b, the tin plating on the bearing surface 5b can be simultaneously formed when the tin plating is formed on the inner surface side of the rear side plate 5. For this reason, since a special process is not required for forming the sliding layers 4c and 5c, the manufacturing cost is reliably reduced.

  Furthermore, in this vane type compressor, since the center hole formed in the rotating shaft 9 is the shaft hole 9a, it is not necessary to form a special shaft hole, and this also reduces the manufacturing cost. Realized.

(Example 2)
As shown in FIGS. 6, 7 </ b> A and 7 </ b> B, the vane compressor according to the second embodiment uses two shaft grooves 9 d that are recessed in the shaft peripheral surface 9 d of the rotation shaft 9 as a rotation path. Adopted. Both shaft grooves 9d are formed at point-symmetrical positions around the axis of the rotating shaft 9, and each extend in the axial direction. The rotational openings 9y of both shaft grooves 9d are open in the shaft peripheral surface 9c. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, when the rotating shaft 9 rotates, the upper flow path 5m and one shaft groove 9d are in communication or non-communication. For this reason, high-pressure refrigerant gas or the like is intermittently supplied to each back pressure chamber 40. In the first embodiment, as shown in FIGS. 5A and 5B, when the rotating shaft 9 rotates 360 °, the upper flow path 5m and the diameter hole 9b communicate with each other. As shown in FIGS. 7A and 7B, when the rotating shaft 9 rotates 180 °, the upper flow path 5m and the one shaft groove 9d communicate with each other. For this reason, compared with Example 1, the upper flow path 5m and the shaft groove 9d are easier to communicate with each other. For this reason, high-pressure refrigerant gas or the like is easily supplied from the back pressure chamber 40.

  Further, as shown in FIG. 6, the high-pressure lubricating oil is supplied to one shaft groove 9d if one shaft groove 9d communicates with the upper flow path 5m by the phase of the rotary shaft 9. The opening area facing the bearing surface 5b in both axial grooves 9d extending in the axial direction is larger than the opening area of the diameter hole 9b not extending in the axial direction in the first embodiment. For this reason, when the rotating shaft 9 rotates, high-pressure lubricating oil is more easily supplied between the bearing surface 5b and the shaft peripheral surface 9c, and the rotating shaft 9 can be rotated more suitably.

  Moreover, in this vane type compressor, since both the shaft grooves 9d are provided in the axial circumferential surface 9c in the axial direction, the cutting process becomes easier and the manufacturing cost is further reduced. Other functions and effects are the same as those of the first embodiment.

(Example 3)
As shown in FIGS. 8A and 8B, the vane compressor of Example 3 employs a sliding layer 5s made of a fluororesin such as PTFE, and this sliding layer 5s is used as a bearing for the rear side plate 5. It is formed on the shaft peripheral surface 9c of the rotating shaft 9 facing the surface 5b. The same applies to the sliding layer facing the bearing surface 4b of the front side plate 4.

  The rotating shaft 9 has one shaft hole 9a extending in the axial direction from the rear end, and two diameter holes communicating with the shaft hole 9a and extending in the radial direction from the front end of the shaft hole 9a to the shaft peripheral surface 9c. 9e is formed. Both diameter holes 9 e are open at point-symmetric positions around the axis of the rotating shaft 9. The shaft hole 9a and both diameter holes 9e are rotation paths extending from the shaft peripheral surface 9c to the supply chamber 17f. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, a fluororesin such as PTFE having a smaller friction coefficient than tin plating is used. For this reason, the slip resistance with the rotor 10 provided between the front side plate 4 and the rear side plate 5 can be further reduced. Other functions and effects are the same as those of the second embodiment.

Example 4
The vane type compressor of Example 4 does not employ the sliding layers 4c, 5c, and 5s as in Examples 1 to 3, as shown in FIGS. 9, 10A, and 10B. The bearing surfaces 4b and 5b and the shaft peripheral surface 9c are in contact with each other. Other configurations are the same as those of the first embodiment.

  In this vane type compressor, since the sliding layers 4c, 5c, and 5s are not employed, the manufacturing cost can be further reduced. Other functions and effects are the same as those of the first and second embodiments.

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

  For example, the rotating shaft body may be composed of a plurality of parts. For example, the rotating shaft body is not limited to the rotating shaft, and may include a component for a rotating path that rotates in synchronization with the rotating shaft.

  The present invention is applicable to a vehicle air conditioner.

1. Front housing (housing)
2 ... Rear housing (housing)
3 ... Cylinder block (housing)
3a ... Cylinder chamber 4 ... Front side plate 4c, 5c, 5s ... Sliding layer 5 ... Rear side plate 5b ... Bearing surface 5x ... Upstream opening 5m ... Upper flow path 5p ... Lower flow path 9 ... Rotating shaft (Rotating shaft body)
9a, 9b, 9d, 17f, 5m, 5p ... back pressure supply mechanism 9x, 9y ... rotating opening 9a ... shaft hole (rotating path)
9b ... Diameter hole (rotating path)
9c ... Shaft peripheral surface 9d ... Shaft groove (rotating path)
DESCRIPTION OF SYMBOLS 10 ... Rotor 10a ... Vane groove 11 ... Vane 12 ... Compression chamber 13 ... Suction chamber 14 ... Discharge valve 16 ... Discharge chamber 17f ... Supply chamber 40 ... Back pressure chamber

Claims (6)

A housing in which a cylinder chamber, a suction chamber, and a discharge chamber are formed, a front side plate that closes the front of the cylinder chamber, a rear side plate that closes the rear of the cylinder chamber, and a rotation that is rotatably provided in the housing A shaft body, a rotor provided in synchronization with the rotating shaft body in the cylinder chamber, and a rotor formed with a plurality of vane grooves; A vane that forms each compression chamber together with an outer surface of the rotor, a rear surface of the front side plate, and a front surface of the rear side plate;
A back pressure chamber is formed between the bottom surface of each vane and each vane groove,
The rear side plate is formed with a cylindrical bearing surface,
The shaft peripheral surface of the rotating shaft body is supported by the bearing surface,
Each of the back pressure chambers is a vane compressor that communicates with the discharge chamber by a back pressure supply mechanism in a compression stroke,
The back pressure supply mechanism is formed in the rear side plate and extends from the discharge chamber and has an upstream flow path having an upstream opening that opens to the bearing surface;
A supply chamber formed on the rear end side of the rotary shaft body;
A rotary path formed in the rotary shaft body, having a rotary opening that opens on the circumferential surface of the shaft and communicating with the supply chamber;
The rear side plate is formed of a lower flow path that communicates the supply chamber and the back pressure chambers of the compression stroke,
The upstream opening and the rotary opening communicate the upper flow path and the supply chamber according to the rotation of the rotary shaft body ,
It said supply chamber and said downstream path, regardless of the rotation of the rotary shaft body, vane compressor characterized that you have communicated.   The vane type compressor according to claim 1, wherein a sliding layer is formed on at least one of the bearing surface and the shaft peripheral surface to reduce a sliding resistance force between the bearing surface and the shaft peripheral surface.   The vane type compressor according to claim 2, wherein the sliding layer is made of tin plating formed on the bearing surface.   4. The vane compressor according to claim 1, wherein the rotation path includes an axial hole extending in an axial direction, and a radial hole communicating with the axial hole and extending in a radial direction to the circumferential surface of the shaft. 5. .   The vane compressor according to claim 4, wherein the shaft hole is a center hole formed in the rotating shaft body.   The vane compressor according to any one of claims 1 to 3, wherein the rotation path includes a shaft groove that is recessed in the shaft peripheral surface and extends in the axial direction.

Images