JP5938054B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor that compresses refrigerant by forming a compression chamber in a cylinder chamber by a vane that rotates together with a rotor in the cylinder chamber.

  Various vane rotary compressors have been proposed (see Patent Document 1). 5 and 6 show a first conventional example of such a compressor. In FIG. 5, the compressor 100 includes a housing 101. The housing 101 includes an electric motor 102 and a housing member 101a that houses a compression mechanism 103 that is driven by the electric motor 102, and a front housing member 101b that is disposed on an opening side surface of the housing member 101a. The compression mechanism unit 103 includes a cylinder block 105 in which a cylinder chamber 104 is provided, and a front side block 106 and a rear side block 107 that are respectively disposed on both side surfaces of the cylinder block 105. The electric motor 102 is energized with a drive current from the motor control unit 109.

  As shown in FIG. 6, the rotor 110 is rotatably accommodated in the cylinder chamber 104. The rotor 110 is disposed so as to be rotatable around a position shifted with respect to the center of the cylinder chamber 104. A rotation shaft 111 is passed through the center of the rotor 110, and the rotor 110 and the rotation shaft 111 are fixed to each other. The rotating shaft 111 is rotatably supported by the front side block 106 and the rear side block 107. The front side of the rotating shaft 111 protrudes from the front side block 106 and is connected to the electric motor 102.

  The rotor 110 is provided with a plurality of vane grooves 112 that open to the outer peripheral surface thereof. The vane grooves 112 are arranged at equally spaced positions on the outer peripheral surface of the rotor 110. A vane 113 is disposed in each vane groove 112 so as to be movable in the protruding and retracting directions of the cylinder chamber 104. Each vane 113 is configured to be biased in the protruding direction by back pressure. The cylinder chamber 104 is partitioned by two vanes 113 to form a compression chamber 114. The front side block 106 and the rear side block 107 are formed with a suction port 120 that opens into the cylinder chamber 104. The cylinder block 105 is formed with two discharge ports 115 for discharging the refrigerant compressed to a predetermined discharge pressure in the compression chamber 114. Each discharge port 115 is opened and closed by an on-off valve 116.

  As shown in FIG. 5, a discharge chamber 117 that discharges the refrigerant compressed in the compression chamber 114 is provided on the rear end side of the rear side block 107. An oil reservoir 118 is provided at the bottom of the discharge chamber 117 to store oil separated from the refrigerant.

  A discharge pressure supply groove 121 and an intermediate pressure supply groove 122 communicating with the back pressure side of the rotor 110 are formed on the surfaces of the front side block 106 and the rear side block 107 on the cylinder chamber 104 side. The discharge pressure supply groove 121 communicates mainly with the back pressure side of the vane 113 in the discharge process, and the intermediate pressure supply groove 122 is formed to communicate with the back pressure side of the vane 113 in the suction process and the compression process.

  The discharge pressure supply groove 121 communicates with the oil reservoir 18 via the back pressure supply passage 119. As a result, discharge pressure oil is supplied from the discharge pressure supply groove 121 to the back pressure side of the vane 113. The intermediate pressure supply groove 122 communicates with the back pressure supply passage 119 through a bearing gap of the rotating shaft 111. As a result, intermediate pressure oil lower than the discharge pressure and higher than the suction pressure is supplied from the intermediate pressure supply groove 122 to the back pressure side of the vane 113.

  In the above configuration, the vane 113 is urged in the protruding direction by the oil of the intermediate pressure supplied through the intermediate pressure supply groove 122 in the suction process and the compression process of the compression mechanism unit 103. In the discharge process, the vane 113 is urged in the protruding direction by the oil having the discharge pressure supplied through the discharge pressure supply groove 121. As a result, the cylinder chamber 104 is partitioned by the two adjacent vanes 113 and the compression chamber 114 is formed.

  Further, as a second conventional example of such a compressor, the back pressure of the vane is discharged by closing the back pressure supply passage and confining the back pressure chamber of the vane in the compression and discharge process of the compression mechanism. It is also conceivable to use the above high pressure. As a result, the vane is urged in the protruding direction by high pressure oil equal to or higher than the discharge pressure, so that chattering of the vane can be prevented.

JP 2013-194549 A

  However, in the first conventional example, the force that pushes the vane 113 into the vane groove 112 in the compression process gradually increases, especially under the low compression ratio condition (the difference between the suction pressure and the discharge pressure in the compression chamber 114 is small under a low heat load). In the case where the pressure is small, the pressure in the compression chamber 114 greatly exceeds the discharge pressure, so that the back pressure of the vane 113 is insufficient and chattering of the vane 113 may occur.

  In the second conventional example, there is a section where it is not necessary to confine the back pressure chamber of the vane in the compression and discharge process of the compression mechanism, but the back pressure of the vane is also included in this unnecessary section. Since the chamber is confined, the vane is pressed against the inner peripheral surface of the cylinder block with a large back pressure. As a result, the sliding resistance of the vane becomes excessively large, resulting in an increase in power.

  Therefore, the present invention has been made to solve the above-described problems, and can prevent the occurrence of chattering of the vane under the low compression ratio condition, and increase the power due to the excessive back pressure generated in the vane. It aims at providing the compressor which can be prevented.

In the present invention, a cylinder chamber is provided in a cylinder block and a pair of side blocks, a rotor is rotatably provided in the cylinder chamber, and the rotor is provided with a plurality of vane grooves that are open on an outer peripheral surface thereof. The vanes are arranged in the vane grooves so as to be movable in the protruding and retracting directions, the rotor is provided with a back pressure chamber on the bottom surface side of the vane grooves, and the side blocks are rotated by the rotor. Depending on the position, a discharge pressure supply groove that communicates with the back pressure chamber to supply discharge pressure is provided, and the side block communicates with the back pressure chamber according to the rotational position of the rotor, and between the discharge pressure and the suction pressure. An intermediate pressure supply groove for supplying an intermediate pressure, which is a pressure, is provided in the cylinder chamber, a compression chamber is formed by being partitioned by two adjacent vanes, and a suction step for sucking refrigerant by rotation of the rotor; Refrigerant A compressor that sequentially performs a compression step of compressing and a discharge step of discharging refrigerant, wherein at least a part of the suction step in a rear compression chamber formed on the rear side of the vane in the rotation direction of the rotor includes: An intermediate pressure supply section that supplies an intermediate pressure between the discharge pressure and the suction pressure to the back pressure chamber of the vane from the intermediate pressure supply groove, and is formed on the rear side of the vane in the rotational direction of the rotor. At least the latter half of the compression step in the chamber is a back pressure chamber confinement section that blocks the back pressure chamber from the intermediate pressure supply groove and the discharge pressure supply groove to confine the back pressure chamber, and in the rotational direction of the rotor at least a portion step of the discharge process in the side compression chamber after being formed on the rear side of the vane, the discharge pressure of the discharge pressure supply groove from the back pressure chamber to supply discharge pressure supply interval, said in the discharging step The refrigerant is discharged through a discharge port provided in the cylinder block, and discharge pressure is applied to the back pressure chamber of the vane located in front of the rear compression chamber in the rotation direction of the rotor. When the supply is started, the compression is characterized in that the arcuate tip of the vane positioned on the front side of the rear compression chamber in the rotation direction of the rotor is applied to the discharge port. Machine.

  The intermediate pressure supply process may be the entire process of the suction process, and the discharge pressure supply process may be the entire process of the discharge process. The back pressure chamber confinement section may be the entire compression process. When the back pressure chamber confinement section is the latter half of the compression step, the start timing of the back pressure chamber confinement section is set to a timing before the pressure of the back pressure chamber of the rear side becomes equal to or higher than the discharge pressure. Anyway.

  According to the present invention, in the compression process, the pressure in the compression chamber gradually increases, and accordingly, the force for pushing the vane into the vane groove gradually increases. In particular, under the low compression ratio condition, the pressure in the compression chamber is a pressure that greatly exceeds the discharge pressure. Here, at least in the latter half of the compression process, the process proceeds to the back pressure chamber confinement section, and in the back pressure chamber confinement section, the back pressure becomes equal to or higher than the discharge pressure due to the volume reduction of the back pressure chamber by pushing the vane into the vane groove. Further, chattering can be prevented from occurring under low compression ratio conditions. When the compression process is shifted to the discharge process, the pressure in the compression chamber becomes the discharge pressure. In the discharge process, however, the discharge pressure is supplied to the back pressure chamber because of the discharge pressure supply section, and the vane is excessive. The back pressure is not supplied and the power is not increased. As described above, chattering under low compression ratio conditions can be prevented, and an increase in power due to excessive back pressure occurring in the vane can be prevented. That is, the vane back pressure can be optimized.

1 is a cross-sectional view of a compressor according to an embodiment of the present invention. It is a figure which shows one Embodiment of this invention, and is a figure explaining the area which provides each back pressure to the sectional view which follows the AA line of FIG. 1, and the back pressure chamber of a vane. It is a figure which shows one Embodiment of this invention, and is sectional drawing which follows the AA line of FIG. 1, and each process of a front side compression chamber and a rear side compression chamber. FIG. 4 is a characteristic diagram of pressures in a front compression chamber and a rear compression chamber under a low compression ratio condition according to an embodiment of the present invention. It is sectional drawing of a compressor which shows one prior art example. It is sectional drawing which shows one prior art example and follows the BB line of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  1 to 4 show an embodiment of the present invention. In the sectional views of FIGS. 2 and 3, hunting is omitted for the sake of clarity.

  As shown in FIG. 1, the compressor 1 has a housing 2. The housing 2 includes a bottomed cylindrical housing member 21 and a front housing member 22 disposed on the opening side surface of the housing member 21. The housing member 21 accommodates the electric motor 3 and the compression mechanism unit 4 driven by the electric motor 3.

  The housing member 21 is formed with a suction chamber 5 on one side and a discharge chamber 6 on the other side with the compression mechanism portion 4 as a boundary. An oil reservoir 8 is provided at the bottom of the discharge chamber 6 to store oil separated from the refrigerant.

  The compression mechanism unit 4 includes a cylinder block 41 in which a cylinder chamber 40 is provided, and a front side block (side block) 42 and a rear side block (side block) 43 that are respectively disposed on both side surfaces of the cylinder block 41. A cylinder chamber 40 is formed inside. On each surface of the front side block 42 and the rear side block 43 on the cylinder chamber 40 side, a discharge pressure supply groove 44 and an intermediate pressure supply groove 45 communicating with the back pressure chamber 13 described later are formed. Between the discharge pressure supply groove 44 and the intermediate pressure supply groove 45, a confinement portion 46 that blocks the back pressure supply passage 7 and the back pressure chamber 13 to confine the back pressure chamber 13 is provided.

  A drive current is supplied to the electric motor 3 from the motor control unit 32. The motor control unit 32 is mounted on the front housing member 22.

  As shown in FIGS. 2 and 3, the rotor 10 is rotatably accommodated in the cylinder chamber 40. The rotor 10 is disposed so as to be rotatable around a position shifted with respect to the center of the cylinder chamber 40. A rotating shaft 9 is penetrated through the center of the rotor 10, and the rotor 10 and the rotating shaft 9 are fixed to each other. The rotary shaft 9 is rotatably supported by the front side block 42 and the rear side block 43. The front side of the rotating shaft 9 protrudes from the front side block 42 and is connected to the electric motor 3.

  The rotor 10 is provided with three vane grooves 11 opening on the outer peripheral surface thereof. Each vane groove 11 is disposed at three positions on the outer peripheral surface of the rotor 10 at equally spaced positions. A vane 12 is disposed in each vane groove 11 so as to be movable in the protruding and retracting directions. A back pressure chamber 13 is opened on the bottom surface side of each vane groove 11, and oil supplied from the back pressure chamber 13 acts as a back pressure for each vane 12. Accordingly, each vane 12 is configured to be biased in the protruding direction. This detailed configuration is described below.

  Each vane 12 moves while contacting the inner wall of the cylinder chamber 40 by the biasing force in the protruding direction as described above when the rotary shaft 9 rotates. At this time, a plurality of compression chambers 14 are formed by two adjacent vanes 12.

  Each vane 12 is formed in a plate shape and extends in the axial direction of the rotor 10. The tip of each vane 12 is formed in an arc shape in cross section, and comes into line contact with the inner peripheral surface of the cylinder block 41. The pressure in the compression chamber 14 (hereinafter referred to as the front compression chamber) located on the front side in the rotation direction of the vane 12 is located on the front side of the vane 12 in the rotation direction of the vane 12 from the contact point. Work. A compression chamber 14 (hereinafter referred to as a rear compression chamber) located on the rear side of the vane 12 in the rotation direction of the vane 12 at the rear side of the vane 12 in the rotation direction of the vane 12 from the contact portion. ) Pressure works. Then, the pressure of the front compression chamber 14 and the pressure of the rear compression chamber 14 acts on the tip of the vane 12 according to the ratio of each area, so that the vane 12 is pushed back into the vane groove 11. To be energized.

  The front side block 42 and the rear side block 43 are provided with a suction port 47 that opens the cylinder chamber 40. The suction port 47 communicates with the suction chamber 5 via a refrigerant supply passage 47a (partially shown in FIGS. 2 and 3). The cylinder block 41 is provided with a discharge port 48 that opens into the cylinder chamber 40. The discharge ports 48 are provided at two places. Each discharge port 48 is opened and closed by an open / close valve 49. The two discharge ports 48 communicate with the discharge chamber 6 through a refrigerant discharge passage (not shown).

  On the inner periphery of the cylinder block 41, a substantially elliptical contour shape including a proximity portion A1 where the outer peripheral surface of the rotor 10 is close and a remote portion A2 where the outer peripheral surface of the rotor 10 is farthest away is formed. When the proximity portion A1 is set to 0 degrees as the rotation reference position of the rotor 10, the remote portion A2 is located, for example, 90 degrees downstream as the rotation angle from the proximity portion A1. The contour shape of the inner periphery of the cylinder block 41 is set so that the distance between the inner peripheral surface of the cylinder block 41 and the outer peripheral surface of the rotor 10 gradually increases along the rotational direction from the proximity portion A1 to the remote portion A2. Has been. Thus, each compression chamber 14 expands its volume in accordance with the rotation of the rotor 10, sucks the refrigerant, compresses the volume by compressing the sucked refrigerant, and discharges the compressed refrigerant. The discharging process is repeated. Thereby, the refrigerant is compressed once per rotation of the rotor 10.

  A discharge pressure supply groove 44 and an intermediate pressure supply groove 45 communicating with the back pressure chamber 13 according to the rotational position of the rotor 10 are formed on the surfaces of the front side block 42 and the rear side block 43 on the cylinder chamber 40 side, respectively. The discharge pressure supply groove 44 is arranged to communicate with the back pressure chamber 13 of the vane 12 in the discharge process. The intermediate pressure supply groove 45 is arranged to communicate with the back pressure chamber 13 of the vane 12 in the suction process.

  The back pressure supply passage 7 is formed by oil passages 71, 72, 73 formed in the rear side block 43, an oil passage 74 formed in the cylinder block 41, and an oil passage 75 formed in the front side block 42.

  The discharge pressure supply groove 44 communicates with the oil reservoir 18 via the back pressure supply passage 7. As a result, the oil at the discharge pressure P <b> 2 is supplied from the discharge pressure supply groove 44 to the back pressure chamber 13 of the vane 12. The intermediate pressure supply groove 45 communicates with the back pressure supply passage 7 through a gap between the bearings 91 and 92 of the rotary shaft 9. As a result, intermediate pressure oil lower than the discharge pressure P2 and higher than the suction pressure P1 is supplied from the intermediate pressure supply groove 45 to the back pressure chamber 13 of the vane 12.

  Next, sections R1, R2, and R3 for applying each back pressure to the back pressure chamber 13 of the vane 12 will be described with reference to FIG.

  The suction process is set as an intermediate pressure supply section R1 for supplying an intermediate pressure between the discharge pressure P2 and the suction pressure P1 shown in FIG. The compression step is set as a back pressure chamber confinement section R2 that blocks the back pressure supply passage 7 and the back pressure chamber 13 to confine the back pressure chamber 13. The discharge process is set as a discharge pressure supply section R3 for supplying the discharge pressure P2 to the back pressure chamber 13 from the back pressure supply passage 7. This detailed configuration will be described in detail below.

  In the intermediate pressure supply section R <b> 1, the back pressure chamber 13 communicates with the intermediate pressure supply groove 45, and intermediate pressure oil between the discharge pressure P <b> 2 and the suction pressure P <b> 1 is supplied to the back pressure chamber 13.

  In the back pressure chamber confinement section R2, the back pressure chamber 13 faces a confinement portion 46 interposed between the intermediate pressure supply groove 45 and the discharge pressure supply groove 44, and the back pressure supply passage 7 is blocked.

  In the discharge pressure supply section R3, the back pressure chamber 13 communicates with the discharge pressure supply groove 44, and oil at the discharge pressure P2 is supplied to the back pressure chamber 13.

  Next, the operation of the compressor 1 will be described. When the electric motor 3 rotates during operation of the compressor 1, the compression mechanism unit 4 rotates together with the rotation of the rotating shaft 9, and the rotor 10 rotates the cylinder chamber 40. As a result, the front and rear compression chambers 14 sequentially perform suction, compression, and discharge as described below. Hereinafter, each description of suction, compression, and discharge will be made with reference to the rotation angle of the vane 12 (rotation angle shown in FIGS. 2 and 3) with respect to the front compression chamber 14 and the rear compression chamber 14. FIG. 4 shows a pressure characteristic diagram under a low compression condition. The pressure in the front compression chamber 14 of the vane 12 changes as indicated by the broken line L1 in FIG. 4, and the pressure in the rear compression chamber 14 of the vane 12 is It changes as shown by the solid line L2 in FIG.

  First, the process of the front side compression chamber 14 of the vane 12 will be described. The rotation of the vane 12 from 0 degree to the rotation angle D1 is a suction process, and the refrigerant is sucked into the front compression chamber 14 through the suction port 47. Next, the rotation angle D1 to the rotation angle D2 of the vane 12 is at least a compression stroke because the front compression chamber 14 does not open to the discharge port 48. The vane 12 passes through the position of the inlet 47 and the front compression chamber 14 is confined. Next, when D2 is passed, it is a discharge process, and the refrigerant is discharged into the discharge chamber 6 through the discharge port 48. In the low compression ratio stroke, the pressure in the compression chamber 14 is surely greater than the discharge pressure P2, so that the discharge process is surely performed after D2.

  Next, the process of the rear side compression chamber 14 of the vane 12 will be described. Until the vane 12 reaches the rotational angle D3, the refrigerant is sucked through the suction port 47 as a suction process. Next, since the rear side compression chamber 14 does not open to the discharge port 48 from the rotation angle D3 to the rotation angle D4 of the vane 12, it is at least a compression stroke, and the rear side compression chamber 14 is confined. Next, when D4 is passed, it is a discharge process, and the refrigerant is discharged into the discharge chamber 6 through the discharge port 48. In the low compression ratio stroke, the pressure in the compression chamber 14 is surely greater than the discharge pressure P2, and therefore the discharge process is surely performed after D4.

  In each compression step, the force that pushes the vane 12 into the vane groove 11 gradually increases, and under the low compression ratio condition, the pressure in the rear compression chamber 14 becomes a high pressure P3 that exceeds the discharge pressure P2. As a result, the discharge pressure P2 in the front compression chamber 14 and the high pressure P3 in the rear compression chamber 14 are applied to the front and rear portions of the vane 12 in the rotation direction of the vane 12 from the contact point. Works according to the ratio of each area to try to push the vane 12 back into the vane groove 11.

  However, since this compression process is set as the back pressure chamber confinement section R2, the back pressure supply passage 7 and the back pressure chamber 13 are shut off to confine the back pressure chamber 13 to the vane groove 11 of the vane 12. The back pressure becomes higher than the discharge pressure P2 by reducing the volume of the back pressure chamber 13 by pushing. Accordingly, the vane 12 is urged by the back pressure (high pressure equal to or higher than the discharge pressure P2) and the rotational centrifugal force and is pressed against the inner peripheral surface of the cylinder block 41, so that chattering of the vane 12 can be prevented. .

  Next, when the vane 12 rotates to the rotation angle D4, the pressure in the rear compression chamber 14 reaches the discharge pressure P2, and the vane 12 reaches the position of the discharge port 48 on the upstream side, the rear compression is performed as a discharge process. The refrigerant in the chamber 14 is discharged into the discharge chamber 6 through the discharge port 48. Thereby, the pressure of the rear side compression chamber 14 falls to the discharge pressure P2. Since this discharge process is set as the discharge pressure supply section R3, the discharge pressure P2 is supplied from the back pressure supply passage 7 to the back pressure chamber 13 of the vane 12. Thereby, since the vane 12 is pressed against the inner peripheral surface of the cylinder block 41 by the back pressure (discharge pressure P2) and the rotational centrifugal force, the occurrence of chattering of the vane 12 can be prevented.

  As described above, in the compression process, the pressure in the compression chamber 14 gradually increases, and the force for pushing the vane 12 into the vane groove 11 gradually increases accordingly. In particular, under the low compression ratio condition, as shown in the characteristic diagram of FIG. 4, the pressure in the compression chamber 14 becomes a high pressure P3 that greatly exceeds the discharge pressure P2. Here, in the compression process, the process proceeds to the back pressure chamber confinement section R2, and in the back pressure chamber confinement section R2, the back pressure becomes equal to or higher than the discharge pressure P2 due to the volume reduction of the back pressure chamber 13 due to the vane 12 being pushed into the vane groove 11. Therefore, the occurrence of chattering of the vane 12 under the low compression ratio condition can be prevented. When the compression process is shifted to the discharge process, the pressure in the compression chamber 14 becomes the discharge pressure P2. In the discharge process, the discharge pressure P2 is supplied to the back pressure chamber 13 as the discharge pressure supply section R3. Therefore, an excessive back pressure is not supplied to the vane 12 and the power is not increased. As described above, chattering of the vane 12 under the low compression ratio condition can be prevented, and increase in power due to excessive back pressure occurring in the vane 12 can be prevented. That is, the back pressure of the vane 12 can be optimized.

  As described above, when the rear compression chamber 14 is compressed, the pressure in the rear compression chamber 14 becomes a high pressure P3 exceeding the discharge pressure P2, and the pressure in the front compression chamber 14 is the discharge pressure P2. On the other hand, when the front side compression chamber 14 is compressed, the pressure in the front side compression chamber 14 exceeds the discharge pressure P2, but the pressure in the rear side compression chamber 14 is the suction pressure P1 smaller than the discharge pressure P2. For this reason, when the rear side compression chamber 14 is compressed, the urging force that pushes the vane 12 into the vane groove 11 is larger than when the front side compression chamber 14 is compressed. Prone to problems. Therefore, it is particularly necessary to apply a large back pressure to the vane 12 by using the compression process of the rear compression chamber 14 as the back pressure chamber confinement section R2 as described above.

  In the present embodiment, the intermediate pressure supply process R1 is the entire suction process, and the discharge pressure supply process R3 is the entire discharge process. Accordingly, it is possible to reliably prevent chattering of the vane 12 in the suction process and the discharge process. The intermediate pressure supply process R1 and the suction process do not need to completely match, and the discharge pressure supply process R3 and the discharge process do not need to match completely. At least a part of the suction process may be the intermediate pressure supply section R1, and at least a part of the discharge process may be the discharge pressure supply section R3. Further, even when the end of the suction process and the end of the intermediate pressure supply section R1 are deviated, the start of the discharge process and the start of the discharge pressure supply section R3 may be deviated. That is, the back pressure acting on the vane 12 varies depending on the shape of the compression chamber 14, the tip shape of the vane 12, and the like, so the intermediate pressure supply section R1, the discharge pressure supply section R3, and the back pressure chamber confinement section R2 described below. Is appropriately determined in consideration of the back pressure acting on the vane 12.

  In the present embodiment, since the back pressure chamber confinement section R2 is the entire compression process, the occurrence of chattering of the vanes 12 can be reliably prevented under the low compression ratio condition.

  In the present embodiment, the back pressure chamber confinement section R2 is the entire compression process, but may be the latter half of the compression process. Thereby, also in a compression process, the power increase by the excessive back pressure generate | occur | producing in the vane 12 can be prevented as much as possible. The start timing of the back pressure chamber confinement section R2 is preferably before the pressure in the rear back pressure chamber 14 becomes equal to or higher than the discharge pressure P2 in the characteristic line of FIG. This is because when the pressure in the rear back pressure chamber 14 exceeds the discharge pressure P2 (pressure in the front back pressure chamber 14), the urging force that pushes the vane 12 into the vane groove 11 is surely higher than the discharge pressure P2.

DESCRIPTION OF SYMBOLS 1 Compressor 7 Back pressure supply channel 9 Rotating shaft 10 Rotor 11 Vane groove 12 Vane 13 Back pressure chamber 14 Compression chamber 40 Cylinder chamber 41 Cylinder block 42 Front side block 43 Rear side block 44 Discharge pressure supply groove 45 Intermediate pressure Supply groove P1 Suction pressure P2 Discharge pressure R1 Intermediate pressure supply section R2 Back pressure chamber confinement section R3 Discharge pressure supply section

Claims (4)

A cylinder chamber (40) is provided in the cylinder block (41) and the pair of side blocks (42), (43), a rotor (10) is rotatably provided in the cylinder chamber (40), and the rotor (10 ) Is provided with a plurality of vane grooves (11) opened on the outer peripheral surface thereof, and vanes (12) are disposed in the respective vane grooves (11) so as to be movable in the protruding and retracting directions, The rotor (10) is provided with a back pressure chamber (13) on the bottom surface side of the vane groove (11), and the side blocks (42) and (43) have the back pressure chambers depending on the rotational position of the rotor (10). A discharge pressure supply groove (44) for supplying a discharge pressure (P2) in communication with the pressure chamber (13) is provided, and the side blocks (42) and (43) are provided with the rotation position of the rotor (10) according to the rotation position of the rotor (10). Discharge pressure (P2) communicating with the back pressure chamber (13) An intermediate pressure supply groove (45) for supplying an intermediate pressure that is a pressure between the suction pressures (P1) is provided, and the cylinder chamber (40) is compressed by being divided into two adjacent vanes (12). A compressor (1) in which a chamber (14) is formed and sequentially performs a suction step of sucking refrigerant by rotation of the rotor (10), a compression step of compressing refrigerant, and a discharge step of discharging refrigerant;
At least a part of the suction process in the rear compression chamber formed on the rear side of the vane (12) in the rotational direction of the rotor (10) is between the discharge pressure (P2) and the suction pressure (P1). An intermediate pressure supply section (R1) for supplying intermediate pressure from the intermediate pressure supply groove (45) to the back pressure chamber (13) of the vane (12),
At least the second half of the compression step in the rear compression chamber formed on the rear side of the vane (12) in the rotational direction of the rotor (10) includes the intermediate pressure supply groove (45) and the discharge pressure supply groove ( 44) from which the back pressure chamber (13) is shut off and the back pressure chamber (13) is confined .
At least a part of the discharge process in the rear compression chamber formed on the rear side of the vane (12) in the rotational direction of the rotor (10) is to discharge the discharge pressure (P2) to the discharge pressure supply groove (44). A discharge pressure supply section (R3) to be supplied to the back pressure chamber (13).
In the discharge step, the refrigerant is discharged through a discharge port (48) provided in the cylinder block (41).
When the supply of the discharge pressure (P2) to the back pressure chamber (13) of the vane (12) located on the front side of the rear compression chamber in the rotational direction of the rotor (10) is started, the rotor A compression characterized in that the arcuate tip of the vane (12) located in front of the rear compression chamber in the rotational direction (10) is configured to be on the discharge port (48). Machine (1). A compressor (1) according to claim 1, comprising:
The intermediate pressure supply process (R1) is the entire process of the suction process,
The compressor (1), wherein the discharge pressure supply step (R3) is the entire discharge step. A compressor (1) according to claim 1 or claim 2,
The compressor (1), wherein the back pressure chamber confinement section (R2) is the entire compression process. A compressor (1) according to claim 1, comprising:
When the back pressure chamber confinement section (R2) is the latter half of the compression step, the start timing of the back pressure chamber confinement section (R2) is such that the pressure in the back pressure chamber (14) on the rear side is equal to or higher than the discharge pressure. A compressor (1) characterized in that it is set at a timing just before.

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