JP6171482B2 - Vane type compressor - Google Patents

Description

  The present invention relates to a vane type compressor.

  Patent Document 1 discloses a conventional vane type compressor. The vane type compressor includes a front housing, a cylinder block, a rear side plate, a rear housing, a drive shaft, a rotor, a plurality of vanes, and a back pressure supply mechanism.

  A cylinder chamber is formed in the cylinder block. The front housing is located in front of the cylinder block and closes the front of the cylinder chamber. The rear housing is located behind the cylinder block. The rear housing is formed with a suction chamber and a discharge chamber.

  The rear side plate is sandwiched between the cylinder block and the rear housing, and closes the rear of the cylinder chamber. The drive shaft is rotatably provided on the housing. The rotor is provided so as to be able to rotate synchronously with the drive shaft, and is disposed 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. A back pressure chamber is formed between the bottom surface of each vane and each vane groove.

  Each of these vanes forms a plurality of compression chambers together with the inner surface of the cylinder chamber, the outer surface of the rotor, the rear surface of the front housing, and the front surface of the rear side plate. Each compression chamber communicates with the suction chamber in the suction stroke, and the volume is reduced in the compression stroke. Each compression chamber communicates with the discharge chamber via a discharge valve in the discharge stroke.

  The back pressure supply mechanism includes a valve cover, a valve plate, a back pressure flow path, and a valve device. The valve cover is fixed to the rear end of the rear side plate. An upper flow path communicating with the discharge chamber is formed in the valve cover. The rear side plate is formed with a lower flow path communicating with the back pressure chamber in the compression stroke. The valve plate is rotatably accommodated in the valve cover. The valve plate is formed with a larger diameter than the drive shaft. The valve plate is connected to the rear end of the drive shaft, and can rotate synchronously with the drive shaft. The valve plate is formed with a valve chamber and an intermediate flow path. These valve chambers and the middle channel communicate with the upper channel and the lower channel.

  The back pressure flow path includes an upper flow path, a valve chamber, an intermediate flow path, and a lower flow path. The discharge chamber and each back pressure chamber communicate with each other through this back pressure channel. The valve device is provided in the valve chamber. This valve device has a valve body that changes the communication area between the upper flow path and the valve chamber by increasing the rotational speed of the drive shaft.

  This vane type compressor is used in a vehicle air conditioner. In this vane type compressor, when the rotational speed of the drive shaft increases, the valve element reduces the communication area between the upper flow path and the valve chamber. Thereby, in this vane type compressor, it becomes difficult for lubricating oil to distribute | circulate from a discharge chamber to each back pressure chamber through a back pressure flow path. For this reason, in this vane type compressor, even when the rotational speed of the drive shaft increases, an excessive pressing force toward the inner surface of the cylinder chamber does not act on the vane. For this reason, in this vane type compressor, the inner surfaces of the vane and the cylinder chamber are not easily worn, and the durability is high. Moreover, since this vane type compressor can reduce power loss, the fuel consumption of the vehicle can be improved.

Japanese Utility Model Publication No. 57-1879

  However, in the conventional vane type compressor, a valve plate is essential for the back pressure supply mechanism, and a part of the back pressure flow path and a valve device are provided on the valve plate. For this reason, this vane type compressor causes an increase in the manufacturing cost due to an increase in the number of parts and an increase in size.

  The present invention has been made in view of the above-described conventional situation, and it is an object to be solved to provide a vane type compressor capable of realizing a reduction in manufacturing cost and a reduction in size.

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 drive shaft rotatably provided in the housing; a rotor provided in a synchronous manner with the drive shaft in the cylinder chamber; and a plurality of vane grooves formed; A plurality of vanes that form 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 back pressure chamber is formed between the bottom surface of each vane and each vane groove,
Each back pressure chamber is communicated with the discharge chamber by a back pressure supply mechanism in a compression stroke,
The back pressure supply mechanism is a vane type compressor having a back pressure channel communicating the discharge chamber and each back pressure chamber, and a valve device provided on the back pressure channel,
The back pressure channel has a rotation path formed on the drive shaft,
The valve device is provided in the drive shaft and synchronously rotatably inside the driving shaft, the centrifugal force increases with increase in the rotational speed of the drive shaft, the inside of the drive shaft to move, communication of the rotation path It has the valve body which makes an area small, It is characterized by the above-mentioned.

  In the vane type compressor of the present invention, the back pressure supply mechanism has a back pressure flow path and a valve device. The back pressure flow path has a rotation path. And in this vane type compressor, while a rotating path is formed in a drive shaft, a valve apparatus is provided in a drive shaft. For this reason, in this vane type compressor, even if it provides a rotary path and a valve apparatus, it does not enlarge.

  Therefore, according to the vane type compressor of the present invention, it is possible to reduce the manufacturing cost and reduce the size.

In the vane type compressor of the present invention, it is preferable that the back pressure supply mechanism has an intermittent mechanism in which the rotation path is in communication with or out of communication with the discharge chamber and each back pressure chamber according to the phase in the rotation direction of the drive shaft. better not.

  In this case, in the vane type compressor, the rotation path communicates with the discharge chamber and the back pressure chambers depending on the phase in the rotation direction of the drive shaft or is not communicated with the intermittent mechanism. In other words, in this vane compressor, if the drive shaft is in the first phase in the rotational direction, the rotation path communicates with the discharge chamber and each back pressure chamber, and the discharge chamber communicates with each back pressure chamber. It becomes a state to do. On the other hand, if the drive shaft is in the second phase in the rotational direction, the rotation path is not in communication with the discharge chamber and each back pressure chamber, and the discharge chamber and each back pressure chamber are in non-communication.

  By having such an intermittent mechanism, in this vane type compressor, high-pressure lubricating oil is intermittently supplied to each back pressure chamber during the compression stroke, and each vane is pressed against the inner surface of the cylinder chamber intermittently. It is done. For this reason, in this vane type compressor, each vane is lubricated in each vane groove, chattering is prevented, and leakage of the refrigerant gas from the compression chamber is prevented, so that the operation efficiency is improved. Further, in this vane type compressor, in addition to the back pressure supply according to the rotational speed of the drive shaft, an intermittent mechanism is further provided, so that the pressing force of each vane against the inner surface of the cylinder chamber can be further increased in accordance with the operation situation. It becomes possible to adjust appropriately.

  In this vane type compressor, the rotation of the drive shaft is stopped. In this state, unless the discharge chamber and each back pressure chamber communicate with each other, the reverse flow of the refrigerant gas or the like and the reverse rotation of the drive shaft do not occur. Further, in this vane type compressor, even if the rotation of the drive shaft is stopped in a state where the discharge chamber and each back pressure chamber are in communication, a slight backflow of refrigerant gas or the like and a reverse rotation of the drive shaft will occur. As a result, the phase of the drive shaft is shifted, so that the discharge chamber and each back pressure chamber are immediately disconnected from each other, and further reverse flow of the refrigerant gas or the like and reverse rotation of the drive shaft do not occur. For this reason, this vane type compressor can prevent the reverse flow of the refrigerant gas and the like and the reverse rotation of the drive shaft reliably and early.

In the vane type compressor of the present invention, the rotation path extends in the radial direction of the drive shaft, communicates with the radial hole opening in the peripheral surface of the drive shaft, and extends in the axial direction of the drive shaft. Existing shaft holes. Then, the intermittent mechanism is provided in the diameter hole, not preferable that the valve body is provided in the axial hole.

  In this case, the configuration of the rotation path can be simplified, and the rotation path can be easily formed on the drive shaft. In addition, by providing the intermittent mechanism in the diameter hole, the intermittent mechanism can be suitably connected to the discharge chamber and each back pressure chamber or not communicated. Furthermore, by providing the valve body in the shaft hole, the valve body can reduce the communication area of the shaft hole due to an increase in the rotational speed of the drive shaft.

In the vane type compressor of the present invention, it is possible to employ valve devices having various configurations. In particular, the valve device has a guide hole that is formed in the drive shaft and accommodates the valve body in communication with the rotation path, and an urging means that urges the valve body in the direction of increasing the communication area. it is not preferable.

  In this case, in this valve device, when the rotational speed of the drive shaft is increased, the valve body moves in the guide hole against the urging force of the urging means. Thus, in this vane type compressor, when the rotational speed of the drive shaft increases, the communication area of the rotation path can be reduced. In this vane type compressor, the configuration of the valve device can be simplified and the size can be reduced. For this reason, the manufacturing cost of the vane compressor can be further reduced, and further downsizing can be realized.

The valve device may also have a valve case. Furthermore, the valve case may have a guide hole, a valve body provided in the guide hole, and an urging means provided between the valve case and the valve body. The valve case is not preferable to have been disposed at the rear end portion of the drive shaft.

  In this case, by disposing the valve case at the rear end portion of the drive shaft, the valve device can be provided in the drive shaft so as to be able to rotate synchronously with the drive shaft while eliminating the need for a lid. For this reason, in this vane type compressor, it becomes possible to facilitate manufacture and to further reduce the manufacturing cost. Further, since the guide hole does not open to the peripheral surface of the drive shaft, even when the rear end of the drive shaft is supported, the bearing or the like can favorably support the peripheral surface of the drive shaft. Here, the valve case can be formed of a resin for weight reduction, and can also be formed of a metal such as an aluminum alloy from the viewpoint of ensuring durability.

Further, the valve case can be disposed in a storage chamber formed at the rear end of the drive shaft. By the guide hole faces the inner wall of the storage room, it is not preferable that the movement of the valve body by the biasing means is restricted.

  In this case, the movement of the valve element can be restricted by the inner wall of the storage chamber, and a dedicated member for restricting the movement of the valve element by the urging means becomes unnecessary. For this reason, it becomes possible to reduce the number of parts of a vane type compressor.

  According to the vane type compressor of the present invention, it is possible to realize a reduction in manufacturing cost and a reduction in size.

1 is a cross-sectional view illustrating a vane type compressor of Example 1. FIG. FIG. 2 is a cross-sectional view taken along the arrow II-II in FIG. 1 according to the vane type compressor of the first embodiment. 1 is an enlarged cross-sectional view of a main part of a vane type compressor according to Embodiment 1. FIG. It is an expanded sectional view from the centrifugal separator side which shows the intermittent mechanism etc. concerning the vane type compressor of Example 1. FIG. The figure (A) has shown the state which the upper flow path and the diameter hole connected. FIG. (B) shows a state where the upper flow path and the diameter hole are not in communication. FIG. 3 is an enlarged cross-sectional view showing a valve unit and the like in a state where the rotational speed of the drive shaft is low, according to the vane type compressor of Example 1. FIG. 3 is an enlarged cross-sectional view illustrating a valve unit and the like in a state where the rotational speed of the drive shaft is high, according to the vane compressor of the first embodiment. It is an expanded sectional view from the centrifugal separator side which concerns on the vane type compressor of Example 1, and shows an intermittent mechanism, a valve unit, etc. FIG. (A) shows a state where the upper flow path and the diameter hole communicate with each other in a state where the rotational speed of the rotating shaft is low. FIG. (B) shows a state in which the upper flow path and the diameter hole are not in communication in a state where the rotational speed of the rotating shaft is low. It is an expanded sectional view from the centrifugal separator side which concerns on the vane type compressor of Example 1, and shows an intermittent mechanism, a valve unit, etc. FIG. (A) shows a state where the upper flow path and the diameter hole communicate with each other in a state where the rotational speed of the rotary shaft is high. FIG. (B) shows a state where the upper flow path and the diameter hole are not in communication with each other in a state where the rotational speed of the rotary shaft is high. 3 is an enlarged cross-sectional view of a main part of a vane type compressor of Example 2. FIG. It is an expanded sectional view from the centrifugal separator side which shows the intermittent mechanism etc. concerning the vane type compressor of Example 2. FIG. FIG. 6 is an enlarged cross-sectional view showing a ball valve and the like in a state where the rotational speed of a drive shaft is low, according to the vane type compressor of Example 3. FIG. 6 is an enlarged cross-sectional view showing a ball valve and the like in a state where the rotational speed of a drive shaft is high, according to the vane type compressor of Example 3. FIG. 10 is an enlarged cross-sectional view illustrating a centrifugal valve and the like in a state where the rotational speed of a drive shaft is low, according to the vane compressor of Example 4. FIG. 10 is an enlarged cross-sectional view illustrating a centrifugal valve and the like in a state where the rotational speed of a drive shaft is high, according to the vane compressor of Example 4. FIG. 6 is an enlarged cross-sectional view of a main part of a vane compressor according to a fifth embodiment. FIG. 10 is an enlarged cross-sectional view of a main part of a vane compressor according to a sixth embodiment.

  Embodiments 1 to 6 embodying the present invention will be described below with reference to the drawings. The vane type compressors of Examples 1 to 6 are all mounted on a vehicle and constitute a refrigeration circuit of a vehicle air conditioner.

Example 1
The vane type compressor according to the first embodiment includes a housing 1, a front side plate 3, a rear side plate 5, a drive shaft 7, a rotor 9, and five vanes 11 shown in FIG. The back pressure supply mechanism 13a shown in FIG.

  As shown in FIG. 1, the housing 1 includes a front housing 15, a rear housing 17, and a cylinder block 19.

  The front housing 15 is located in front of the vane type compressor. The front housing 15 has a first accommodating space 15a recessed therein. Further, the front housing 15 is formed with an inlet 15b and a boss 15c. The suction port 15b communicates with the first accommodation space 15a and opens toward the outside of the vane compressor. The boss 15 c protrudes toward the front of the front housing 15. The boss 15c is provided with a shaft hole 15d that communicates with the first accommodation space 15a. A shaft seal device 21 is provided in the first accommodation space 15a.

  The rear housing 17 is located behind the vane compressor, and is joined to the front housing 15 by a plurality of bolts (not shown). The rear housing 17 has a second housing space 17a recessed therein. The rear housing 17 has a discharge port 17b that communicates with the second housing space 17a and opens toward the outside of the vane compressor.

  The cylinder block 19 is stored on the front side of the second storage space 17a, and is fixed in the second storage space 17a. Thus, the cylinder block 19 is located between the front housing 15 and the rear housing 17.

  As shown in FIG. 2, the cylinder block 19 is formed with an elliptical cylinder chamber 19a in a direction perpendicular to the axis. The cylinder block 19 is formed with two suction spaces 19b and a plurality of suction ports 19c. The suction space 19b and the suction port 19c communicate with each other.

  Further, two concave portions 19 d are formed on the outer peripheral surface of the cylinder block 19. These recesses 19 d form two discharge spaces 19 e between the cylinder block 19 and the rear housing 17. The cylinder block 19 has a plurality of discharge ports 19f communicating with the discharge space 19e.

  In each discharge space 19e, a plurality of discharge valves 21 for closing each discharge port 19f and a plurality of retainers 23 for regulating the lift amount of each discharge valve 21 are provided.

  As shown in FIG. 1, the front side plate 3 is fixed in the first accommodation space 15 a and is positioned in front of the cylinder block 19. The front end of the cylinder chamber 19 a is closed by the rear end surface 3 a of the front side plate 3. Thus, by providing the front side plate 3 in the first housing space 15 a, the suction chamber 25 is formed in the first housing space 15 a, that is, in the front housing 15. The suction chamber 25 communicates with the suction port 15b.

  The front side plate 3 is provided with a cylindrical bearing surface 3b and two suction holes 3c. Sliding layers 27a made of tin plating are formed on the bearing surface 3b and the rear end surface 3a of the front side plate 3, respectively.

  Each suction hole 3c communicates with the suction chamber 25 and each suction space 19b. Thus, each suction space 19b communicates with the suction chamber 25. In FIG. 1, only one suction hole 3c is shown.

  The rear side plate 5 is fixed in the second accommodation space 17 a and is located behind the cylinder block 19. The rear end of the cylinder chamber 19 a is closed by the front end surface 5 a of the rear side plate 5. Thus, by providing the rear side plate 5 in the second housing space 17a, the discharge chamber 29 is formed in the second housing space 17a, that is, in the rear housing 17. The discharge chamber 29 communicates with the discharge port 17b.

  Further, as shown in FIG. 3, the rear side plate 5 includes a boss 5b, a cylindrical bearing surface 5c, an upper flow path 5d, two supply holes 5e, a pair of oil drain grooves 5f, and a first discharge. A hole 31a is formed. The boss 5 b is located at the center of the rear end surface 5 g of the rear side plate 5 and protrudes toward the rear of the rear side plate 5. The bearing surface 5 c extends from the boss 5 b toward the front of the rear side plate 5. Sliding layers 27 b and 27 c made of tin plating are also formed on the bearing surface 5 c and the front end surface 5 a of the rear side plate 5.

  The upper flow path 5d extends in the vertical direction of the rear side plate 5 from below the rear side plate 5 toward the bearing surface 5c. The lower end of the upper flow path 5d is open in the discharge chamber 29, and the upper end is open on the bearing surface 5c. That is, the upper flow path 5d extends from the discharge chamber 29 to the bearing surface 5c.

  Each supply hole 5 e extends in the front-rear direction of the rear side plate 5 from the boss 5 b toward the front end side of the rear side plate 5. As shown in FIG. 4, each oil drain groove 5f is formed in a substantially fan shape. Each oil drain groove 5 f is formed on the front end side of the rear side plate 5. In FIG. 4, a valve case 47 and the like which will be described later are not shown for ease of explanation. The same applies to FIG.

  As shown in FIG. 3, the first discharge hole 31a extends from the front end surface 5a of the rear side plate 5 to the rear end surface 5g. The front end of the first discharge hole 31a is open to the discharge space 19e.

  Further, a centrifugal separator 33 is fixed to the rear end of the rear side plate 5. Thereby, the centrifugal separator 33 is located in the discharge chamber 29. The centrifugal separator 33 includes an end frame 35 and a separation cylinder 37.

  The end frame 35 is joined to the rear end surface 5 g of the rear side plate 5. At this time, the boss 5b of the rear side plate 5 is inserted into the recess 35a provided in the end frame 35. Thereby, a supply chamber 39 is formed between the boss 5b and the recess 35a, that is, between the rear side plate 5 and the end frame 35. The supply chamber 39 communicates with each supply hole 5e.

In addition, the end frame 35 is formed with a guide space 35b, an oil separation chamber 35c communicating with the guide space 35b, a communication hole 35d, and a second discharge hole 31b. The guide space 35 b and the oil separation chamber 35 c extend in a cylindrical shape in the vertical direction of the end frame 35. The guide space 35b circulates the refrigerant gas discharged from the compression chamber 43 described later along its wall surface. The communication hole 35 d is located at the lower end of the end frame 35. The communication hole 35d, and the oil separation chamber 35 c and a discharge chamber 29 are communicated. The second discharge hole 31b communicates with the first discharge hole 31a on the front end side, and communicates with the guide space 35b on the rear end side. The discharge space 19e and the guide space 35b communicate with each other through the first and second discharge holes 31a and 31b.

  The separation cylinder 37 is formed coaxially with the guide space 35b and is press-fitted into the guide space 35b. An opening 37 a that opens toward the discharge chamber 29 is formed at the upper end of the separation cylinder 37. The separation cylinder 37 can recirculate the refrigerant gas on its own outer peripheral surface and guide the refrigerant gas from which the lubricating oil has been separated to the inside of the separation cylinder 37.

  As shown in FIG. 1, the drive shaft 7 is inserted into the housing 1 through the shaft hole 15d from the front to the rear of the vane type compressor. The drive shaft 7 is pivotally supported in the housing 1 by a shaft seal device 21 and bearing surfaces 3b and 5c. As a result, the drive shaft 7 can rotate around the axis O.

  As shown in FIG. 3, the rear end of the drive shaft 7 protrudes from the rear side plate 5 while being pivotally supported by the shaft seal device 21 and the bearing surfaces 3 b and 5 c, and is positioned in the supply chamber 39. As shown in FIG. 5, a center hole 7a, a diameter hole 7b, and a storage chamber 7c are formed on the rear end side of the drive shaft 7. The center hole 7a corresponds to the shaft hole of the present invention. The center hole 7a and the diameter hole 7b constitute the rotation path of the present invention. Further, the drive shaft 7 is formed with a first shaft peripheral surface 7d facing the bearing surface 5c and a second shaft peripheral surface 7e facing the bearing surface 3b shown in FIG. The first shaft peripheral surface 7d corresponds to the peripheral surface in the present invention.

  As shown in FIG. 5, the center hole 7 a extends from the rear end surface of the drive shaft 7 toward the front end side of the drive shaft 7 while passing through the axis O of the drive shaft 7. The radial hole 7b communicates with the center hole 7a, extends from the front end side of the center hole 7a to the first shaft peripheral surface 7d in a direction orthogonal to the axial direction of the drive shaft 7, and opens to the first shaft peripheral surface 7d. ing. The diameter hole 7b is formed to have the same diameter as the center hole 7a. The storage chamber 7 c is coaxial with the center hole 7 a and is recessed in a cylindrical shape from the rear end surface of the drive shaft 7 toward the front end side of the drive shaft 7. Thus, the storage chamber 7c communicates with the center hole 7a and the diameter hole 7b. The storage chamber 7c is formed to have a larger diameter than the center hole 7a and the diameter hole 7b.

  The upper flow path 5d and the supply chamber 39 communicate with each other through the center hole 7a, the diameter hole 7b, and the storage chamber 7c. That is, the discharge chamber 29 and each supply hole 5e communicate with each other through the center hole 7a, the diameter hole 7b, and the storage chamber 7c. The intermittent mechanism 100 is formed by the diameter hole 7b, the center hole 7a, the storage chamber 7c, the supply chamber 39, the upper flow path 5d, and the supply holes 5e.

On the other hand, as shown in FIG. 1, the front end of the drive shaft 7 is exposed from the boss 15c to the outside of the vane compressor. Thereby, an electromagnetic clutch or pulley (not shown) can be fixed to the front end of the drive shaft 7. A driving force is transmitted to the electromagnetic clutch and pulley by a vehicle engine or motor.

  The rotor 9 is disposed in the cylinder chamber 19a. A drive shaft 7 is press-fitted into the rotor 9. Thereby, the rotor 9 can rotate synchronously with the drive shaft 7 in the cylinder chamber 19a.

  As shown in FIG. 2, the rotor 9 is formed in a cylindrical shape having a circular cross section. Further, five vane grooves 9 a are recessed in the radial direction on the outer peripheral surface of the rotor 9. The vane grooves 9a are spaced equiangularly around the axis O of the drive shaft 7. A vane 11 is stored in each vane groove 9a. The number and size of the vane grooves 9a and the vanes 11 can be set as appropriate.

  A back pressure chamber 41 is formed between the bottom surface of each vane 11 accommodated in each vane groove 9a and the bottom surface of each vane groove 9a. As shown in FIG. 4, among the back pressure chambers 41, the back pressure chambers 41 in the compression stroke or the like can communicate with the supply holes 5e through the oil drain grooves 5f. Thereby, the back pressure chamber 41 in the compression stroke or the like can communicate with the discharge chamber 29 through the supply holes 5e. Thus, the lubricating oil can be supplied to the back pressure chamber 41 in the compression stroke or the like together with the high-pressure refrigerant gas. Each vane 11 can be moved in and out with respect to each vane groove 9 a due to a pressure change in each back pressure chamber 41.

  Five compression chambers 43 are formed by the cylinder chamber 19 a whose front and rear are closed by the front side plate 3 and the rear side plate 5, the five vanes 11, and the outer peripheral surface of the rotor 7. Of the compression chambers 43, the compression chambers 43 in the suction stroke communicate with the suction port 19c. On the other hand, the compression chamber 43 in the discharge stroke communicates with the discharge port 19f.

As shown in FIG. 3, the back pressure supplying mechanism 13a includes a back pressure passage 200, and the accommodation chamber 7c, a valve casing 47 is constituted by the above intermittent Organization 1 00.

  As shown in FIGS. 5 and 6, a spool valve 49 and a coil spring 51 are built in the valve case 47. The valve case 47 corresponds to the valve device in the present invention. The spool valve 49 corresponds to the valve body in the present invention, and the coil spring 51 corresponds to the urging means in the present invention.

  The valve case 47 is made of resin. The valve case 47 is formed in substantially the same shape as the storage chamber 7c, and is fixed in the storage chamber 7c. The valve case 47 is formed with a connecting path 47a extending in the axial direction, a guide hole 47b extending in the radial direction orthogonal to the connecting path 47a, and a notch 47c. The communication path 47 a includes a first communication path 471 and a second communication path 472. The first communication path 471 communicates with the center hole 7a. The first communication path 471 and the second communication path 472 communicate with each other through the guide hole 47b. The rear end of the second communication path 472 is open to the rear end surface of the drive shaft 7, that is, the supply chamber 39. That is, the valve case 47 is fixed in the storage chamber 7c, so that the first communication path 471 and the second communication path 472 constitute a shaft hole and a part of the rotation path in the present invention.

The guide hole 47b communicates with the communication path 47a. Guide holes 47b in a state where the valve casing 4 7 is fixed in the housing chamber 7c, has an inner wall facing the housing chamber 7c. Thereby, both ends of the guide hole 47b are closed by the inner wall of the storage chamber 7c. A spring seat 47d is formed in the guide hole 47b. The valve case 47 may be formed of an aluminum alloy or the like.

  The spool valve 49 and the coil spring 51 are housed in the guide holes 47b, respectively. The spool valve 49 has a head portion 49a, a shaft portion 49b, a skirt portion 49c, and a seat portion 49d. The head 49a and the shaft portion 49b are integrally formed. The shaft portion 49b passes through the skirt portion 49c and is fixed to the seat portion 49d. As a result, a valve body passage 49e is formed between the head 49a and the skirt 49c. The coil spring 51 is provided between the spring seat 47 d and the seat portion 49 d of the spool valve 49. Due to the biasing force of the coil spring 51, the spool valve 49 is biased in a state where the head portion 49 is close to the axis O of the drive shaft 7. The spool valve 49 can move in the radial direction in the guide hole 47 b by resisting the biasing force of the coil spring 51. That is, in the valve case 47, as shown in FIG. 5, the head 49a of the spool valve 49 is close to the axis O of the drive shaft 7, or as shown in FIG. It is possible to be remote from the axis O of the drive shaft 7.

  Here, in the spool valve 49, when the head portion 49a is in a state closest to the axis O of the drive shaft 7, the skirt portion 49c contacts the spring seat 47d as shown in FIG. In this state, the positions of the first and second communication paths 471 and 472 are aligned with the position of the valve body passage 49e.

  The back pressure flow path 200 is formed by the upper flow path 5d, the diameter hole 7b, the center hole 7a, the storage chamber 7c, the communication path 47a, the valve body passage 49e, the supply chamber 39, the supply holes 5e, and the oil drain grooves 5f. ing.

  In this vane type compressor, the discharge port 17b shown in FIG. 1 is connected to a condenser by piping. The condenser is connected to the expansion valve by piping. Furthermore, the expansion valve is connected to the evaporator by piping. The evaporator is connected to the suction port 15b by a pipe. As described above, the refrigeration circuit of the vehicle air conditioner is configured by connecting the vane type compressor, the condenser, the expansion valve, and the evaporator with each pipe. In addition, illustration is abbreviate | omitted for each piping, a condenser, an expansion valve, and an evaporator.

In the vane compressor configured as described above, when the drive shaft 7 is rotated by an engine or the like, the rotor 9 rotates synchronously with the drive shaft 7. For this reason, a volume change occurs in each compression chamber 43. The low-pressure refrigerant gas that has passed through the evaporator is sucked into the suction chamber 25 from the suction port 15b. The refrigerant gas in the suction chamber 25 is sucked into the compression chamber 43 in the suction stroke through the suction holes 3c, the suction spaces 19b, and the suction ports 19c and compressed. The refrigerant gas compressed to a high pressure in the compression chamber 43 is discharged into each discharge space 19e through the discharge port 19f. The refrigerant gas discharged to the discharge space 19e is first and second discharge holes 31a, through 31b, reaches the guide space 35b between the outer peripheral surface and the end plate 35 of the separating cylinder 3 7. Then, in the separator 33, the lubricating oil is centrifuged from the refrigerant gas. The refrigerant gas from which the lubricating oil has been separated flows into the discharge chamber 29 from the opening 37 a of the separation cylinder 37. On the other hand, the lubricating oil separated from the refrigerant gas is stored below the discharge chamber 29 from the oil separation chamber 35c through the communication hole 35d. The refrigerant gas in the discharge chamber 29 is discharged from the discharge port 17d toward the condenser.

  Further, a part of the refrigerant gas in the discharge chamber 29 is supplied into the respective back pressure chambers 41 together with the lubricating oil through the back pressure channel 200 (hereinafter referred to as the high-pressure refrigerant gas supplied into each back pressure chamber 41 and In the refrigerant gas, the lubricating oil is collectively referred to as the lubricating oil). Specifically, as shown in FIG. 3, the lubricating oil or the like supplied into each back pressure chamber 41 flows from the discharge chamber 29 through the upper flow path 5d, the diameter hole 7b, and the center hole 7a, as shown in FIG. The supply chamber 39 is reached through the first communication path 471, the valve body passage 49e, and the second communication path 472 in the valve case 47 in the storage chamber 7c. Lubricating oil or the like is supplied from the supply chamber 39 into the back pressure chamber 41 in the compression stroke or the like through the supply holes 5e and the drainage grooves 5f shown in FIG.

Furthermore, in this vane type compressor, the back pressure supply mechanism 13 a has the intermittent mechanism 100. Thereby, in this vane type compressor, if the drive shaft 7 rotates and the diameter hole 7b moves to a position communicating with the upper flow path 5d as shown in FIG. 4A, the discharge chamber 29 and the supply chamber 39, communication is with the back pressure chamber 41 and thus, the lubricating oil or the like in the upstream path 5 in d becomes possible flow into the supply chamber 39 through the diameter hole 7b. Thereby, in this vane type compressor, it becomes possible to supply the lubricating oil etc. in the supply chamber 39 to each back pressure chamber 41.

  On the other hand, if the diameter hole 7b is moved by the rotation of the drive shaft 7 and is not in communication with the upper flow path 5d, the upper flow path 5d and the supply chamber 39 are not in communication with each other, as shown in FIG. Lubricating oil or the like in the upper flow path 5d does not flow into the supply chamber 39. For this reason, in this vane type compressor, lubricating oil or the like is not supplied to each back pressure chamber 41.

  In this vane type compressor, the valve case 47 fixed in the storage chamber 7c rotates synchronously with the drive shaft 7. Thereby, in this vane type compressor, a centrifugal force acts on the valve case 47. Therefore, as shown in FIGS. 5 and 6, the spool valve 49 moves in the radial direction in the guide hole 47 b in the valve case 47.

  That is, in this vane type compressor, when the rotational speed of the drive shaft 7 is low, the centrifugal force acting on the valve case 47 is small, and therefore, as shown in FIG. 49 heads 49 a are close to the axis O of the drive shaft 7. Thereby, in the valve case 47, the position of the communication path 47a and the position of the valve body passage 49e approach each other, and the communication area between the first and second communication paths 471 and 472 and the valve body passage 49e increases. For this reason, the lubricating oil or the like that has reached the diameter hole 7 b preferably flows through the communication path 47 a and the valve body passage 49 e and flows into the supply chamber 39. That is, in this vane type compressor, when the rotational speed of the drive shaft 7 is low, the communication area between the first and second communication paths 471 and 472 and the valve body passage 49e is increased, so that the communication area of the rotation path is reduced. growing. Thereby, in this vane type compressor, the flow rate of the lubricating oil or the like flowing into the supply chamber 39 increases, and the flow rate of the lubricating oil or the like supplied into the back pressure chamber 41 increases.

  On the other hand, if the rotational speed of the drive shaft 7 increases, the centrifugal force acting on the valve case 47 gradually increases. Therefore, the head of the spool valve 49 is resisted against the biasing force of the coil spring 53 as shown in FIG. The portion 49a is remote from the axis O of the drive shaft 7. For this reason, the positions of the first and second communication paths 471 and 472 and the valve body passage 49e are distant from each other, and the positions of both are shifted in the radial direction. Thereby, in the valve case 47, the communication area between the first and second communication paths 471 and 472 and the valve body passage 49e is reduced, and the lubricating oil or the like reaching the diameter hole 7b flows through the communication path 49a and the valve body passage 49e. It becomes difficult to do. For this reason, compared with the case where the rotation speed of the drive shaft 7 is low, the communication area between the first and second communication paths 471 and 472 and the valve body passage 49e is reduced, so that the communication area of the rotation path is reduced. Thereby, in this vane type compressor, the flow rate of the lubricating oil or the like flowing into the supply chamber 39 is reduced. Thus, in this vane type compressor, it is possible to reduce the flow rate of the lubricating oil or the like supplied into each back pressure chamber 41 as the rotational speed of the drive shaft 7 increases. Here, since both ends of the guide hole 47 b are closed by the inner wall of the storage chamber 7 c as described above, the head portion 49 a is in the state of being close to the axis O of the drive shaft 7 in the valve case 47. The spool valve 49 does not jump out of the valve case 47 even if it is in a remote state.

  Thus, in this vane type compressor, the movement of the spool valve 49 in the valve case 47 and the action of the intermittent mechanism 100 are combined to rotate the drive shaft 7 as shown in FIG. When the number is low and the diameter hole 7b moves to a position where it communicates with the upper flow path 5d, the flow rate of the lubricating oil or the like flowing into the supply chamber 39 increases. As shown in FIG. 8A, when the rotational speed of the drive shaft 7 is high and the diameter hole 7b moves to a position where it communicates with the upper flow path 5d, lubricating oil or the like is supplied to the supply chamber 39. Inflow is possible, but the flow rate is reduced.

  On the other hand, as shown in FIGS. 7B and 8B, in this vane type compressor, if the drive hole 7 rotates, the diameter hole 7b moves to a position where it is not in communication with the upper flow path 5d. The lubricating oil does not flow into the supply chamber 39 regardless of the rotational speed of the drive shaft 7.

  Thereby, in this vane type compressor, it is possible to suitably adjust the pressure in the back pressure chamber 41 in accordance with the rotational speed of the drive shaft 7. For this reason, in this vane type compressor, even when the rotational speed of the drive shaft 7 increases, an excessive pressing force toward the inner surface of the cylinder chamber 19a does not act on the vane 11. For this reason, in this vane type compressor, the inner surface of each vane 11 and the cylinder chamber 19a is not easily worn, and the durability is high. Moreover, in this vane type compressor, since the power loss can be reduced, it is possible to improve the fuel consumption of the mounted vehicle.

  In the vane compressor, the center hole 7a, the diameter hole 7b, and the storage chamber 7c constituting the intermittent mechanism 100 and the back pressure flow path 200 are formed in the drive shaft 7 in the back pressure supply mechanism 13a. . The valve case 47 is provided in the drive shaft 7 by storing the valve case 47 in the storage chamber 7c. Here, since the valve case 47 is provided in the drive shaft 7, the communication path 47 a and the valve body passage 49 e are also located in the drive shaft 7. Thus, in this vane type compressor, even if the center hole 7a, the diameter hole 7b, the storage chamber 7c, and the valve case 47 are provided, the size is not increased.

  Further, in this vane type compressor, the spool valve 49 and the coil spring 51 are built in the valve case 47 so that they are integrated. Thereby, in this vane type compressor, simplification of the configuration of the valve device is realized. Further, in this vane type compressor, the valve case 47 can be synchronously rotated with respect to the drive shaft 7 only by fixing the valve case 47 in the storage chamber 7c. Here, since the guide hole 47b is formed in the valve case 47, in this vane type compressor, there is no need to penetrate the guide hole 47b in the drive shaft 7, and the guide hole 47d is formed in the first shaft peripheral surface 7d. There is no opening. For this reason, in this vane type compressor, the bearing surface 5c can suitably support the first shaft peripheral surface 7d.

  Further, in this vane type compressor, a sliding layer 27 a is formed on the front side plate 3, and sliding layers 27 b and 27 c are formed on the rear side plate 5. Thereby, in this vane type compressor, the slip resistance at the bearing surface 3b and the second shaft peripheral surface 7e is reduced, and the slip resistance at the bearing surface 5c and the first shaft peripheral surface 7d is reduced. . Thus, in this vane type compressor, in reducing the sliding resistance between the bearing surface 5c and the first shaft peripheral surface 7d and the sliding resistance between the bearing surface 3b and the second shaft peripheral surface 7e, a sliding bearing or a rolling bearing is used. Etc. need not be provided. Thereby, in this vane type compression, the enlargement is suppressed and the number of parts is also reduced.

  Furthermore, in this vane type compression mechanism, the sliding resistance between the rear end surface 3a of the front side plate 3 and the rotor 9 is reduced by the sliding layer 27a, and the front end surface 5a of the rear side plate 5 is reduced by the sliding layer 27c. The sliding resistance between the rotor 9 and the rotor 9 is also reduced.

  Moreover, since each sliding layer 27a-27c is all formed by tin plating, in this vane type compressor, formation of each sliding layer 27a-27c is easy.

  Further, in this vane type compressor, the upper flow path 5 d extends from the discharge chamber 29 to the bearing surface 5 c of the rear side plate 5. For this reason, in this vane type compressor, it is possible to suitably guide the lubricating oil or the like from the discharge chamber 29 to the bearing surface 5c while simplifying the configuration of the upper flow path 5d.

  Moreover, in this vane type compressor, the center hole 7a is a part of the configuration in the rotation path, that is, the configuration in the intermittent mechanism 100 and the back pressure flow path 200. For this reason, in this vane type compressor, when forming the intermittent mechanism 100 and the back pressure flow path 200, it is possible to suppress an increase in the number of parts and an increase in the number of processes during manufacture. Thereby, in this vane type compressor, it is possible to easily form the intermittent mechanism 100 and the back pressure flow path 200.

  Further, by making the storage chamber 7 c coaxial with the center hole 7 a, in this vane type compressor, the storage chamber 7 c can be easily recessed with respect to the drive shaft 7.

  Therefore, according to the vane type compressor of Example 1, it is possible to realize a reduction in manufacturing cost and a reduction in size.

  In particular, in this vane type compressor, the back pressure supply mechanism 13a has the intermittent mechanism 100, so that high-pressure lubricating oil or the like is intermittently supplied to each back pressure chamber 41 during the compression stroke. For this reason, in this vane type compressor, each vane 11 is intermittently pressed against the inner surface of the cylinder chamber 19a. For this reason, in this vane type compressor, each vane 11 is lubricated in each vane groove 9a, chattering is prevented, and leakage of refrigerant gas from the compression chamber 43 is prevented. It has become. Further, in this vane type compressor, in addition to the back pressure supply according to the rotational speed of the drive shaft 7, an intermittent mechanism 100 is further provided, so that each vane 11 can be applied to the inner surface of the cylinder chamber 19a according to the operating condition. It is possible to adjust the pressing force more appropriately.

  In this vane type compressor, the rotation of the drive shaft 7 is stopped. If the discharge chamber 29 and each back pressure chamber 41 are not communicated with each other in this state, the reverse flow of the lubricating oil or the like and the reverse rotation of the drive shaft 7 Does not occur. Further, in this vane type compressor, even if the rotation of the drive shaft 7 is stopped in a state where the discharge chamber 29 and each back pressure chamber 41 communicate with each other, the reverse flow of the lubricating oil or the like and the reverse rotation of the drive shaft 7 As a result, the phase of the drive shaft 7, that is, the phase of the diameter hole 7 b and the upper flow path 5 d is shifted, so that the discharge chamber 29 and each back pressure chamber 41 are immediately disconnected from each other, and more lubrication is required. The backflow of oil or the like and the reverse rotation of the drive shaft 7 do not occur. For this reason, this vane type compressor can prevent the reverse flow of lubricating oil and the like and the reverse rotation of the drive shaft 7 reliably and early.

  In this vane type compressor, the valve case 47 is fixed to the storage chamber 7c, so that the guide hole 47b faces the inner wall of the storage chamber 7c, and both ends of the guide hole 47b are closed by the inner wall of the storage chamber 7c. The For this reason, in this vane type compressor, a dedicated member for regulating the movement of the spool valve 49 by the coil spring 51, that is, the amount of movement of the spool valve 49 in the guide hole 47b is not required.

(Example 2)
The vane type compressor according to the second embodiment includes a back pressure supply mechanism 13b as shown in FIG. 9 instead of the back pressure supply mechanism 13a in the vane type compression mechanism according to the first embodiment. Further, this vane type compressor has a rear side plate 55 instead of the rear side plate 5 in the vane type compression mechanism of the first embodiment.

  Similar to the rear side plate 5, the rear side plate 55 is fixed in the second storage space 17 a of the rear housing 17. The rear side plate 55 is also formed with a boss 55a that protrudes rearward, a cylindrical bearing surface 55b, and a first discharge hole 31a. Sliding layers 27 b and 27 c are formed on the bearing surface 55 b and the front end surface 55 c of the rear side plate 55. Further, the end frame 35 of the centrifugal separator 33 is joined to the rear end surface 55 d of the rear side plate 55. Thereby, a supply chamber 39 is also formed between the rear side plate 55 and the end frame 35.

  The rear side plate 55 includes a first upper flow path 55e, a second upper flow path 55f, a pair of supply grooves 55g and 55h, a pair of supply holes 55i and 55j, and a pair of oil drain grooves 55k. ing.

  The first upper flow path 55 e extends in the vertical direction of the rear side plate 55. The lower end of the first upper flow path 55 e is open in the discharge chamber 29. The second upper flow path 55 e extends in the front-rear direction of the rear side plate 55. The front end of the second upper flow path 55f communicates with the upper end of the first upper flow path 55e. On the other hand, the rear end of the second upper flow path 55 f is open in the supply chamber 39.

  As shown in FIG. 10, the supply grooves 55g and 55h are recessed with respect to the bearing surface 55b. The supply grooves 55g and 55h are arranged to face each other with the drive shaft 7 interposed therebetween. As shown in FIG. 9, the supply holes 55 i and 55 j extend in the front-rear direction of the rear side plate 55 toward the back pressure chamber 41. The rear end of the supply hole 55i is opened in the supply groove 55g. The rear end of the supply hole 55j is opened in the supply groove 55h. Each oil drain groove 55k has the same configuration as each oil drain groove 5f in the vane type compressor of the first embodiment.

  In this vane type compressor, the supply chamber 39 and the supply grooves 55g and 55h communicate with each other through the center hole 7a, the diameter hole 7b, and the valve case 47 in the storage chamber 7c. Thereby, the discharge chamber 29 and each supply hole 55i and 55j are connected. And in this vane type compressor, these 1st, 2nd upper flow paths 55e and 55f, the diameter hole 7b, the center hole 7a, the storage chamber 7c, the valve case 47, the supply chamber 39, each supply groove | channel 55g, 55h, and each supply The intermittent mechanism 101 is formed by the holes 55i and 55j.

  In this vane type compressor, the first and second upper flow paths 55e and 55f, the diameter hole 7b, the center hole 7a, the communication path 47a, the valve body passage 49e, the supply chamber 39, the supply grooves 55g and 55h, and the supply holes A back pressure channel 201 is formed by 55i, 55j and each oil drain groove 55k.

  The back pressure supply mechanism 13 b includes a back pressure channel 201, a storage chamber 7 c, a valve case 47, and an intermittent mechanism path 101. Other configurations of the vane compressor are the same as those of the vane compressor of the first embodiment, and the same components are denoted by the same reference numerals and detailed description thereof is omitted.

  In this vane type compressor, the intermittent mechanism 101 supplies lubricating oil or the like in the discharge chamber 29 into each back pressure chamber 41 as follows. That is, in this vane type compressor, the lubricating oil or the like in the discharge chamber 29 flows through the first and second upper flow paths 55e and 55f and flows into the supply chamber 39. The lubricating oil or the like in the supply chamber 39 reaches the diameter hole 7b through the communication path 47a, the valve body passage 49e, and the center hole 7a. Here, when the drive shaft 7 rotates and the diameter hole 7b moves to a position where it communicates with the supply groove 55g, as shown in FIG. 9, the lubricating oil or the like that has reached the diameter hole 7b is supplied to the supply holes 55i and the respective drains. The oil is supplied to each back pressure chamber 41 through the oil groove 55k. Similarly, if the diameter hole 7b moves to a position where it communicates with the supply groove 55h, the lubricating oil or the like that has reached the diameter hole 7b is supplied to each back pressure chamber 41 via the supply hole 55j and each oil drain groove 55k. .

  On the other hand, as shown in FIG. 10, when the drive shaft 7 is rotated, the diameter hole 7b is moved so that neither the supply groove 55g nor the supply groove 55h is in communication. It will not be done.

  The back pressure supply mechanism 13b in the vane type compressor is the same as that in the vane type compressor of the first embodiment by combining the action of the intermittent mechanism 101 and the movement of the spool valve 49 in the valve case 47 described above. The same effect as the back pressure supply mechanism 13a can be obtained. Other functions of the vane compressor are the same as those of the vane compressor of the first embodiment.

(Example 3)
The vane type compressor of the third embodiment includes a drive shaft 57 and a back pressure supply mechanism 13c as shown in FIG. 11 instead of the drive shaft 7 and the back pressure supply mechanism 13a in the vane type compressor of the first embodiment. ing.

  The drive shaft 57 is formed with a shaft hole 57a, a diameter hole 57b, and a guide hole 57c communicating with each other. The shaft hole 57a, the diameter hole 57b, and the guide hole 57c constitute a rotation path in the present invention. In addition to the first shaft peripheral surface 57d, the drive shaft 57 is formed with a second shaft peripheral surface (not shown). The first shaft peripheral surface 57d corresponds to the peripheral surface in the present invention.

  The rear end of the shaft hole 57 a is open in the rear end surface of the drive shaft 57, that is, in the supply chamber 39, and extends toward the front end side of the drive shaft 57 in parallel with the axis O of the drive shaft 57. The diameter hole 57b extends to the first shaft peripheral surface 57d in a direction orthogonal to the shaft hole 57a, and opens to the first shaft peripheral surface 57d. The guide hole 57c is formed so as to gradually move away from the axis O of the drive shaft 57 from the rear end side to the front end side of the drive shaft 57. Further, the guide hole 57c is formed so as to gradually reduce the diameter from the rear end side to the front end side of the drive shaft 57. The guide hole 57c communicates with the shaft hole 57a at the rear end, and communicates with the radial hole 57b at the front end.

A ball valve 59 and a coil spring 61 are provided in the guide hole 57c. The ball valve 59 can move in the guide hole 57c, and the communication area between the guide hole 57c and the shaft hole 57a can be changed by its own position in the guide hole 57c. The coil spring 61 urges the ball valve 59 toward the rear end side of the guide hole 57c. That is, the coil spring 61 biases the ball valve 59 in a direction that increases the communication area between the guide hole 57c and the shaft hole 57a. These ball valve 59 and coil spring 61 correspond to the valve body and the urging means in the present invention, respectively. The guide hole 57c, the ball valve 59, and the coil spring 61 correspond to the valve device in the present invention.

  Further, a circlip 62 a is fitted to the drive shaft 57. The circlip 62a is located between the shaft hole 57a and the guide hole 57c. The circlip 62a abuts on the ball valve 59 to restrict the ball valve 59 from entering the shaft hole 57a.

  In this vane type compressor, the upper flow path 5d and the supply chamber 39 communicate with each other through the shaft hole 57a, the diameter hole 57b, and the guide hole 57c. That is, the discharge chamber 29 and each supply hole 5e communicate with each other through the shaft hole 57a, the diameter hole 57b, and the guide hole 57c. The shaft hole 57a, the diameter hole 57b, the guide hole 57c, the supply chamber 39, the upper flow path 5d, and the supply holes 5e form an intermittent mechanism 102.

  Further, in this vane type compressor, the back pressure flow path 202 is formed by the upper flow path 5d, the shaft hole 57a, the diameter hole 57b, the guide hole 57c, the supply chamber 39, each supply hole 5e, and each oil drain groove 5f.

  The back pressure supply mechanism 13c includes a back pressure flow path 202, a guide hole 57c, a ball valve 59, a coil spring 61, and an intermittent mechanism 102. Other configurations of the vane compressor are the same as those of the vane compressor of the first embodiment.

  In this vane type compressor, lubricating oil or the like in the upper flow path 5d flows in the supply chamber 39 through the radial hole 57b, the guide hole 57c, and the shaft hole 57a in this order. In this vane type compressor, a centrifugal force acts on the ball valve 59 as the drive shaft 57 rotates. Therefore, as shown in FIGS. 11 and 12, the ball valve 59 moves in the guide hole 57c.

  That is, in this vane type compressor, when the rotational speed of the drive shaft 57 is low, the centrifugal force acting on the ball valve 59 is small, and therefore, as shown in FIG. 59 is close to the axis O of the drive shaft 57. Thereby, the communication area between the shaft hole 57a and the guide hole 57c, that is, the communication area of the rotation path is increased. For this reason, also in this vane type compressor, the flow rate of the lubricating oil or the like supplied into the back pressure chamber 41 increases.

  On the other hand, if the rotational speed of the drive shaft 57 increases, the centrifugal force acting on the ball valve 59 gradually increases, so that the ball valve 59 is driven against the biasing force of the coil spring 61 as shown in FIG. It moves away from the axis O of the shaft 7 and moves to the front end side of the guide hole 57c. Here, since the guide hole 57c has a shape that decreases in diameter toward the front end side as described above, the communication area between the shaft hole 57a and the guide hole 57c as the ball valve 59 moves to the front end side of the guide hole 57c. That is, the communication area of the rotating path is gradually reduced. Thus, also in this vane type compressor, as the rotational speed of the drive shaft 57 increases, the flow rate of the lubricating oil or the like supplied into each back pressure chamber 41 can be reduced.

  Moreover, in this vane type compression mechanism, the intermittent mechanism 102 acts in the same manner as the intermittent mechanism 100 in the first embodiment.

Further, in this vane compressor, a shaft hole 57a and diameter hole 57 b, the rotation path is formed by the guide hole 57c, it is possible to easily form the rotational path relative to the drive shaft 57 ing. Other operations in this vane type compressor are the same as those in the first embodiment.

Example 4
The vane type compressor according to the fourth embodiment includes a drive shaft 63 and a back pressure supply mechanism 13d as shown in FIG. 13 instead of the drive shaft 7 and the back pressure supply mechanism 13a in the vane type compressor according to the first embodiment. ing.

  The drive shaft 63 has a guide hole 63a and a diameter hole 63b. The guide hole 63a functions as a shaft hole, and the rotation path of the present invention is constituted by the guide hole 63a and the diameter hole 63b. In addition to the first shaft peripheral surface 63c, the drive shaft 63 is formed with a second shaft peripheral surface (not shown). The first shaft peripheral surface 63c corresponds to the peripheral surface in the present invention.

  The guide hole 63 a has a rear end that opens in the rear end surface of the drive shaft 63, that is, in the supply chamber 39, and extends toward the front end side of the drive shaft 63 in parallel with the axis O of the drive shaft 63. Further, the guide hole 63a is formed with a larger diameter than the diameter hole 63b. The diameter hole 63b extends to the first shaft peripheral surface 63c in a direction orthogonal to the guide hole 63a, and opens to the first shaft peripheral surface 63c. The diameter hole 63b communicates with the front end side of the guide hole 63a.

  A centrifugal valve 65 and a coil spring 67 are provided in the guide hole 63a. The centrifugal valve 65 and the coil spring 67 correspond to the valve body and the urging means in the present invention, respectively. Further, the guide hole 63a, the centrifugal valve 65, and the coil spring 67 correspond to the valve device in the present invention.

  The centrifugal valve 65 includes first and second cam plates 65a and 65b, a fixed body 65c, and first and second movable bodies 65d and 65e. The first and second cam plates 65a and 65b have a substantially triangular cross section, and inclined surfaces 651 and 652 are formed, respectively. The first and second cam plates 65a and 65b are disposed on the front side of the guide hole 63a. The fixed body 65 c includes a vertical wall 653 extending perpendicularly to the radial direction of the drive shaft 63, and a horizontal wall 654 extending perpendicularly to the vertical wall 653 and extending in the axial direction of the drive shaft 63. Further, a fixed body passage 65f is formed in the fixed body 65c. The fixed body 65c is fixed to the rear end of the guide hole 63a. The first and second movable bodies 65d and 65e are formed in a substantially rectangular shape. The first and second movable bodies 65d and 65e are formed with inclined surfaces 655 and 656 parallel to the inclined surfaces 651 and 652 of the first and second cam plates 65a and 65b, respectively. The first and second movable bodies 65d and 65e are disposed between the first and second cam plates 65a and 65b and the fixed body 65c in the guide hole 63a. In addition, the first movable body 65d and the second movable body 65e are disposed with the horizontal wall 654 interposed therebetween.

  The coil spring 67 is disposed on the front end side of the guide hole 63a and between the wall surface of the guide hole 63a and the first and second cam plates 65a and 65b. The coil spring 67 urges the first and second cam plates 65a and 65b toward the rear end side of the guide hole 63a.

  In this vane type compressor, the upper flow path 5d and the supply chamber 39 communicate with each other through the guide hole 63a, the diameter hole 63b, and the fixed body passage 65f. That is, the discharge chamber 29 and each supply hole 5e communicate with each other through the guide hole 63a, the diameter hole 63b, and the fixed body passage 65f. The intermittent mechanism 103 is formed by the guide hole 63a, the diameter hole 63b, the fixed body passage 65f, the supply chamber 39, the upper flow path 5d, and the supply holes 5e.

  Further, in this vane type compressor, the back pressure flow path 203 is formed by the upper flow path 5d, the guide hole 63a, the diameter hole 63b, the fixed body passage 65f, the supply chamber 39, each supply hole 5e, and each oil drain groove 5f. .

  The back pressure supply mechanism 13d includes a back pressure channel 203, a guide hole 63a, a centrifugal valve 65, a coil spring 67, and an intermittent mechanism 103. Other configurations of the vane compressor are the same as those of the vane compressor of the first embodiment.

  In this vane type compressor, the lubricating oil or the like in the upper flow path 5d flows in the supply chamber 39 through the diameter hole 63b, the guide hole 63a, and the fixed body passage 65f in this order. In this vane type compressor, centrifugal force acts on the centrifugal valve 65 by rotating the drive shaft 63. For this reason, as shown in FIGS. 13 and 14, the centrifugal valve 65 moves in the guide hole 63c.

  That is, in this vane type compressor, when the rotational speed of the drive shaft 63 is low, the centrifugal force acting on the centrifugal valve 65 is small, so that the first and second movable bodies 65d and 65e are provided as shown in FIG. Both are close to the axis O of the drive shaft 63. Accordingly, the first cam plate 65a moves toward the rear end side of the guide hole 63a along the inclined surface 655 of the first movable body 65d by the biasing force of the coil spring 67. Similarly, the second cam plate 65b moves toward the rear end side of the guide hole 63a along the inclined surface 656 of the second movable body 65e. Thus, the communication area between the guide hole 63a and the diameter hole 63b is increased. For this reason, also in this vane type compressor, the flow rate of the lubricating oil or the like supplied into the back pressure chamber 41 increases.

On the other hand, if the rotational speed of the drive shaft 63 increases, the centrifugal force acting on the centrifugal valve 65 gradually increases, so that the first and second movable bodies 65d and 65e are respectively connected to the drive shaft 7 as shown in FIG. Move in a direction away from the axis O. Therefore, the first cam plate 65a moves toward the front end side of the guide hole 63a along the inclined surface 655 of the first movable body 65d while resisting the biasing force of the coil spring 67. Similarly, the second cam plate 65b moves toward the front end side of the guide hole 63a along the inclined surface 656 of the second movable body 65e. Accordingly, the communication area between the guide hole 63a and the diameter hole 63b is gradually reduced. Thus, also in this vane type compressor, it is possible to reduce the flow rate of the lubricating oil or the like supplied into each back pressure chamber 41 as the rotational speed of the drive shaft 63 increases. In this centrifugal valve 65, the guide hole 63a and the diameter hole 63b are not communicated with each other as the rotational speed of the drive shaft 63 increases, that is, the communication area between the guide hole 63a and the diameter hole 63b is made zero. Is possible.

  Moreover, in this vane type compressor, the intermittent mechanism 103 acts in the same manner as the intermittent mechanism 100 in the first embodiment. Other operations in this vane type compressor are the same as those in the first embodiment.

(Example 5)
The vane type compressor of the fifth embodiment includes a drive shaft 69 and a back pressure supply mechanism 13e as shown in FIG. 15, instead of the drive shaft 7 and the back pressure supply mechanism 13a in the vane type compressor of the first embodiment. ing.

  The drive shaft 69 is formed with a shaft hole 69a, a diameter hole 69b, and a guide hole 69c. These shaft hole 69a and diameter hole 69b correspond to the rotation path in the present invention. The drive shaft 69 is formed with a second shaft peripheral surface (not shown) in addition to the first shaft peripheral surface 69d. The first shaft peripheral surface 69d corresponds to the peripheral surface in the present invention.

  The shaft hole 69 a has a rear end that opens in the rear end surface of the drive shaft 69, that is, in the supply chamber 39, and extends parallel to the axis O of the drive shaft 69 toward the front end side of the drive shaft 69. The diameter hole 69b extends to the first shaft peripheral surface 69d in a direction orthogonal to the shaft hole 69a, and opens to the first shaft peripheral surface 69d. The diameter hole 69b communicates with the front end side of the shaft hole 69a. The guide hole 69c extends in a direction orthogonal to the shaft hole 69a of the drive shaft 69, and penetrates the drive shaft 69 in the radial direction while dividing the shaft hole 69a into a front end side and a rear end side. The guide hole 69c communicates with the rear end side of the shaft hole 69a. A spring seat 69d is formed in the guide hole 69c.

  A spool valve 49 and a coil spring 51 in the vane type compressor of the first embodiment are provided in the guide hole 69c. The guide hole 69c, the spool valve 49, and the coil spring 51 correspond to the valve device in the present invention.

  Further, a pair of circlips 62b and 62c are fitted in the guide hole 69c. The circlips 62b and 62c are respectively in contact with the head 49a and the seat 49d of the spool valve 49, thereby restricting the amount of movement of the spool valve 49 in the guide hole 69c.

  In this vane type compressor, the upper flow path 5d and the supply chamber 39 communicate with each other through the shaft hole 69a, the diameter hole 69b, and the valve body passage 49e. That is, the discharge chamber 29 and each supply hole 5e communicate with each other through the shaft hole 69a, the diameter hole 69b, and the valve body passage 49e. An intermittent mechanism 104 is formed by the shaft hole 69a, the diameter hole 69b, the valve body passage 49e, the supply chamber 39, the upper flow path 5d, and the supply holes 5e.

  Further, in this vane type compressor, the back pressure flow path 204 is formed by the upper flow path 5d, the shaft hole 69a, the diameter hole 69b, the valve body passage 49e, the supply chamber 39, each supply hole 5e, and each oil drain groove 5f. .

  The back pressure supply mechanism 13e includes a back pressure flow path 204, a guide hole 69c, a spool valve 49, a coil spring 51, and an intermittent mechanism 104. Other configurations of the vane compressor are the same as those of the vane compressor of the first embodiment.

  In this vane compressor, the lubricating oil or the like in the upper flow path 5d flows into the supply chamber 39 through the diameter hole 69b, the front end side of the shaft hole 69a, the valve body passage 49e, and the rear end side of the shaft hole 69a. To do. In this vane type compressor, when the drive shaft 69 rotates, the spool valve 49 moves in the guide hole 69c as in the vane type compressor of the first embodiment.

  Thereby, in this vane type compressor, when the rotational speed of the drive shaft 57 is low, the front end side of the shaft hole 69a, the valve body passage 49e, and the rear end side of the shaft hole 69a communicate with each other. The communication area between the hole 69a and the valve body passage 49e is increased. For this reason, in this vane type compressor, the communication area of the shaft hole 69a is increased, so that the communication area of the rotation path is increased, and the flow rate of the lubricating oil or the like supplied into the back pressure chamber 41 is increased. On the other hand, when the rotational speed of the drive shaft 69 increases, the communication area between the shaft hole 69a and the valve body passage 49e gradually decreases. Thus, in this vane type compressor, as the rotational speed of the drive shaft 69 increases, the communication area between the shaft hole 69a and the valve body passage 49e decreases, so that the communication area of the rotation path decreases, and each back pressure The flow rate of the lubricating oil or the like supplied into the chamber 41 can be reduced.

  Further, in this vane type compression mechanism, the intermittent mechanism 104 operates in the same manner as the intermittent mechanism 100 in the first embodiment. Other operations in this vane type compressor are the same as those in the first embodiment.

  In this vane type compression mechanism, the configuration can be simplified as compared with the vane type compressor of the first embodiment, and the manufacturing cost can be further reduced.

(Example 6)
The vane type compressor according to the sixth embodiment includes a back pressure supply mechanism 13f as shown in FIG. 16 instead of the back pressure supply mechanism 13a in the vane type compression mechanism according to the first embodiment. Further, this vane type compressor has a rear side plate 71 instead of the rear side plate 5 in the vane type compression mechanism of the first embodiment.

  The rear side plate 71 is also fixed in the second storage space 17 a of the rear housing 17. The rear side plate 71 is also formed with a boss 71a projecting rearward, a cylindrical bearing surface 71b, and the like, as with the rear side plate 5. Further, although not shown, the end frame 35 of the centrifugal separator 33 is joined to the rear end surface 71 g of the rear side plate 71. Thus, a supply chamber 39 is also formed between the rear side plate 71 and the end frame 35.

  Further, the rear side plate 71 is formed with an upper flow path 71c, a supply groove 71d, a pair of supply holes 71e, and a pair of oil drain grooves 71f. The upper flow path 71 c extends in the vertical direction of the rear side plate 71. The upper end of the upper flow path 71c is open in the supply groove 71d. Although not shown, the lower end of the upper flow path 71 c is open in the discharge chamber 29. The supply groove 71d is formed in an annular shape coaxially with the bearing surface 71b along the first shaft peripheral surface 7d of the drive shaft 7. Each supply hole 71 e extends in the front-rear direction of the rear side plate 71 from the boss 71 a toward the front end side of the rear side plate 71. Each oil drain groove 71f has the same configuration as each oil drain groove 5f in the vane compressor of the first embodiment.

  In this vane compressor, the upper flow path 71c, the supply groove 71d, the diameter hole 7b, the center hole 7a, the storage chamber 7c, the communication path 47a, the valve body passage 49e, the supply chamber 39, each supply hole 71e, and each oil drain groove 71f. Thus, a back pressure channel 205 is formed.

  The back pressure supply mechanism 13 f includes a back pressure flow path 205, a storage chamber 7 c, and a valve case 47. Other configurations of the vane compressor are the same as those of the vane compressor of the first embodiment.

  In this vane type compressor, lubricating oil or the like flows through the upper flow path 71c and reaches the supply groove 71d. Here, since the supply groove 71d is formed in an annular shape along the first shaft peripheral surface 7d of the drive shaft 7, the supply hole 71d is supplied regardless of the position of the radial hole 7b as the drive shaft 7 rotates. The groove 71d and the diameter hole 7b communicate with each other. Therefore, the lubricating oil or the like in the supply groove 71d always flows through the diameter hole 7b, the center hole 7a, the communication path 47a, and the valve body passage 49e and flows into the supply chamber 39. Thereby, in this vane type compressor, it is possible to always supply the lubricating oil or the like in the discharge chamber 29 to each back pressure chamber 41.

  That is, in this vane type compressor, it is possible to adjust only the flow rate of the lubricating oil or the like supplied from the discharge chamber 29 to each back pressure chamber 41 according to the rotational speed of the drive shaft 69. Other operations in this vane type compressor are the same as those in the first embodiment.

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

  For example, in the vane type compressor of the first embodiment, the communication path 47a and the valve body passage 49e are not in communication with each other as the rotational speed of the drive shaft 7 increases, that is, the flow between the communication path 47a and the valve body passage 49e. The spool valve 49 or the like may be configured so that the road area becomes zero. The same applies to the vane type compressor of the fifth embodiment. On the other hand, in the vane type compressor of Example 4, even when the first and second movable bodies 65d and 65e are in the most remote state, a certain degree of communication area between the guide hole 65a and the diameter hole 65b is ensured. The centrifugal valve 65 may be configured.

Further, in the vane type compressor of the fourth embodiment, even when the centrifugal force acting on the centrifugal valve 65 is maximized, the communication area between the guide hole 63a and the diameter hole 63b is secured to a certain extent. One or two cam plates 65a and 65b may be configured.

  Furthermore, in the vane type compressor of Examples 1-5, you may comprise without providing the intermittent mechanisms 100-104.

  Further, in the vane type compressor according to the first embodiment, the first and second shaft peripheral surfaces 7d and 7e are subjected to tin plating on the first and second shaft peripheral surfaces 7d and 7e of the drive shaft 7, whereby the sliding layer May be formed. The same applies to the vane type compressors of Examples 3 to 5.

  The present invention is applicable to a vehicle air conditioner or the like.

3 ... Front side plate 5 ... Rear side plate 7 ... Drive shaft 7a ... Center hole (shaft hole)
7b: Diameter hole 7c: Storage chamber 7d: First shaft circumferential surface (circumferential surface)
DESCRIPTION OF SYMBOLS 9 ... Rotor 9a ... Vane groove 11 ... Vane 13a-13e ... Back pressure supply mechanism 15 ... Front housing (housing)
17 ... Rear housing (housing)
19 ... Cylinder block (housing)
19a ... Cylinder chamber 25 ... Suction chamber 29 ... Discharge chamber 41 ... Back pressure chamber 43 ... Compression chamber 45 ... Valve unit 47 ... Valve case 47b ... Guide hole 49 ... Spool valve (valve element)
51 ... Coil spring (biasing means)
55 ... Rear side plate 57 ... Drive shaft 57a ... Shaft hole 57b ... Diameter hole 57c ... Guide hole 57d ... First shaft peripheral surface (circumferential surface)
59 ... Ball valve (valve)
61 ... Coil spring (biasing means)
63 ... Drive shaft 63a ... Guide hole 63b ... Diameter hole 63c ... First shaft circumferential surface (circumferential surface)
65 ... Centrifugal valve (valve)
67 ... Coil spring (biasing means)
69 ... Drive shaft 69a ... Center hole (shaft hole)
69b ... Diameter hole 69c ... Guide hole 69d ... First shaft circumferential surface (circumferential surface)
71 ... Rear side plate 100-104 ... Intermittent mechanism 200-205 ... Back pressure channel

Claims (7)

A housing in which a cylinder chamber, a suction chamber and a discharge chamber are formed, a front side plate for closing the front of the cylinder chamber, a rear side plate for closing the rear of the cylinder chamber, and a drive rotatably provided in the housing A shaft, a rotor provided in a synchronized manner with the drive shaft in the cylinder chamber, and formed with a plurality of vane grooves; A plurality of vanes that form each compression chamber together with the outer surface of the front side plate, the rear surface of the front side plate, and 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,
Each back pressure chamber is communicated with the discharge chamber by a back pressure supply mechanism in a compression stroke,
The back pressure supply mechanism is a vane type compressor having a back pressure channel communicating the discharge chamber and each back pressure chamber, and a valve device provided on the back pressure channel,
The back pressure channel has a rotation path formed on the drive shaft,
The valve device is provided in the drive shaft and synchronously rotatably inside the driving shaft, the centrifugal force increases with increase in the rotational speed of the drive shaft, the inside of the drive shaft to move, communication of the rotation path A vane type compressor having a valve body that reduces an area.   2. The vane type according to claim 1, wherein the back pressure supply mechanism has an intermittent mechanism in which the rotation path is in communication or non-communication with the discharge chamber and each of the back pressure chambers according to the phase in the rotation direction of the drive shaft. Compressor. A housing in which a cylinder chamber, a suction chamber and a discharge chamber are formed, a front side plate for closing the front of the cylinder chamber, a rear side plate for closing the rear of the cylinder chamber, and a drive rotatably provided in the housing A shaft, a rotor provided in a synchronized manner with the drive shaft in the cylinder chamber, and formed with a plurality of vane grooves; A plurality of vanes that form each compression chamber together with the outer surface of the front side plate, the rear surface of the front side plate, and 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,
Each back pressure chamber is communicated with the discharge chamber by a back pressure supply mechanism in a compression stroke,
The back pressure supply mechanism is a vane type compressor having a back pressure channel communicating the discharge chamber and each back pressure chamber, and a valve device provided on the back pressure channel,
The back pressure channel has a rotation path formed on the drive shaft,
The valve device is provided in the drive shaft so as to be able to rotate synchronously with the drive shaft, and has a valve body that reduces the communication area of the rotation path by increasing the rotation speed of the drive shaft,
The back pressure supply mechanism has an intermittent mechanism in which the rotation path is in communication with or out of communication with the discharge chamber and each of the back pressure chambers according to the phase in the rotation direction of the drive shaft. Compressor. The rotation path includes a radial hole that extends in a radial direction of the drive shaft and opens in a peripheral surface of the drive shaft, and a shaft hole that communicates with the radial hole and extends in the axial direction of the drive shaft. Have
The vane compressor according to claim 2 or 3, wherein the intermittent mechanism is provided in the diameter hole, and the valve body is provided in the shaft hole.   The valve device includes a guide hole that is formed in the drive shaft and accommodates the valve body in communication with the rotation path, and a biasing unit that biases the valve body in a direction of increasing the communication area. The vane type compressor according to any one of claims 1 to 4, further comprising: The valve device has a valve case,
The valve case has the guide hole, the valve body provided in the guide hole, and the urging means provided between the valve case and the valve body,
The vane compressor according to claim 5, wherein the valve case is disposed at a rear end portion of the drive shaft. The valve case is disposed in a storage chamber formed at the rear end of the drive shaft,
The vane type compressor according to claim 6, wherein movement of the valve body by the urging means is restricted by the guide hole facing the inner wall of the storage chamber.

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