JP2018025124A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor that has a passage for providing communication between a discharge area and a back pressure chamber and can achieve high compression performance and a low power loss.SOLUTION: A compressor of the present invention comprises a back pressure flow passage 56 forming a back pressure supply passage 100, a throttling member 61, a coil spring 63 working as a biasing member, and a stopper 65. The back pressure flow passage 56 has an enlarged diameter part 561 and a reduced diameter part 562. The throttling member 61 is formed with a spiral groove 611. The throttling member 61 is moved in the back pressure flow passage 56 by a differential pressure across the throttling member 61 while being guided by the reduced diameter part 562. The back pressure supply passage 100 is configured such that the same is more throttled by the spiral groove 611 at the time when the throttling member 61 is separated from the stopper 65 and is moved in the reduced diameter part 562 as compared with the time when the throttling member 61 abuts on the stopper 65.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a compressor.

  Patent Document 1 discloses a conventional compressor. This compressor is a vane type compressor and includes a drive shaft provided in a housing and a rotor provided so as to be able to rotate synchronously with the drive shaft. A plurality of vane grooves are formed in the rotor. A vane is provided in each vane groove so that it can appear and disappear. A cylinder chamber is defined by a side plate in the housing, and a compression chamber is formed in the cylinder chamber by a rotor and a vane. An oil reservoir chamber is provided at the rear end of the drive shaft.

  An oil supply passage is formed in the side plate. The oil supply passage communicates the discharge region and the oil reservoir chamber. Thereby, in this compressor, the back pressure from the discharge region can be supplied to the vane via the oil reservoir. Further, a pin type throttle mechanism is provided in the oil supply passage. A spiral groove is formed on the outer peripheral surface of the pin type diaphragm mechanism.

  In this compressor, a throttle passage is formed between the spiral groove and the inner peripheral surface of the oil supply passage. For this reason, the lubricating oil in the oil reservoir chamber is decompressed by flowing through the throttle passage. Thus, in the oil supply passage, it is possible to supply the vane back pressure while reducing the pressure of the lubricating oil in the oil reservoir chamber. For this reason, in this compressor, it is possible to reduce power loss caused by excessively pressing each vane against the inner peripheral surface of the cylinder chamber by the vane back pressure.

JP-A-57-146096

  However, in the above-described conventional compressor, when the pressure in the discharge region is not sufficiently increased, the pressure for introducing the lubricating oil into the oil supply passage is insufficient, and therefore the back pressure for pushing out each vane is insufficient. There is. For this reason, so-called chattering in which each vane repeatedly appears and disappears without being suitably biased to the inner peripheral surface of the cylinder chamber is likely to occur. For this reason, a refrigerant | coolant tends to leak from a compression chamber, and compression performance falls.

  The problem of such back pressure is also the same in a scroll compressor including a fixed scroll, a movable scroll, and a back pressure chamber. That is, even in such a compressor, if the pressure in the back pressure chamber is insufficient, the movable scroll cannot be suitably pressed against the fixed scroll, and the refrigerant easily leaks from the compression chamber, so that the compression performance is lowered. On the other hand, if the pressure in the back pressure chamber becomes too high, the movable scroll is pressed against the fixed scroll, resulting in a large power loss.

  The present invention has been made in view of the above-described conventional situation, and is a compressor provided with a passage communicating the discharge region and the back pressure chamber, and capable of realizing high compression performance and low power loss. Providing is an issue to be solved.

The compressor of the present invention includes a housing,
A movable member provided in the housing and defining a compression chamber;
A discharge region that is provided in the housing and discharges the refrigerant compressed in the compression chamber;
A back pressure chamber that is provided on the back side of the movable member and applies a back pressure to the movable member;
A compressor comprising a back pressure supply passage communicating the discharge region and the back pressure chamber;
A throttle member movably provided in the back pressure supply path;
A stopper for restricting movement of the diaphragm member;
A biasing member that biases the throttle member toward the stopper;
The back pressure supply path has an enlarged diameter portion that accommodates the stopper, and a reduced diameter portion that is connected to the enlarged diameter portion with a step and is smaller in diameter than the enlarged diameter portion and accommodates the biasing member. And
A spiral groove is formed on one of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member,
The throttle member is guided by the reduced diameter portion by the differential pressure via the throttle member and moves in the back pressure supply path.
The back pressure supply path is configured such that the spiral groove is throttled when the throttle member moves away from the stopper and moves within the reduced diameter portion, compared to when the throttle member abuts against the stopper. It is characterized by.

  In the compressor of the present invention, when the pressure in the discharge region is low and the differential pressure between the discharge region and the back pressure chamber is small, the throttle member comes into contact with the stopper by the biasing force of the biasing member. On the other hand, when the pressure in the discharge region is high and the differential pressure between the discharge region and the back pressure chamber is large, the throttle member moves away from the stopper against the biasing force of the biasing member and moves in the reduced diameter portion. . At this time, the spiral groove forms a flow path between the inner peripheral surface of the reduced diameter portion and the other outer peripheral surface of the throttle member. As a result, the back pressure supply path is throttled when the throttle member moves away from the stopper and moves in the reduced diameter portion, compared to when the throttle member abuts against the stopper.

  Thus, in this compressor, when the pressure in the discharge region is low, the fluid flowing through the back pressure supply path reaches the back pressure chamber without being reduced in pressure. For this reason, in this compressor, the leakage of the refrigerant from the compression chamber is prevented, and the compression performance is improved. On the other hand, when the pressure in the discharge region is high, the fluid flowing through the back pressure supply path reaches the back pressure chamber while being decompressed. For this reason, in this compressor, power loss during operation can be reduced.

  Therefore, in the compressor according to the present invention, high compression performance and low power loss can be realized in the compressor provided with a passage communicating the discharge region and the back pressure chamber.

  The spiral groove can be formed by a crest provided on one of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member, and a trough that is continuous with the crest. And it is preferable that the other of the inner peripheral surface of a diameter-reduced part and the outer peripheral surface of an aperture | diaphragm | squeeze member is formed with the slidable contact surface which contacts a peak part.

  In this case, the squeezing member moves away from the stopper against the urging force of the urging member and moves in the reduced diameter portion, so that the peak portion of the spiral groove and the sliding contact surface come into sliding contact. Thereby, a channel | path will be formed between the trough part of a spiral groove, and a sliding contact surface.

  The spiral groove is preferably formed on the outer peripheral surface of the aperture member. It is also preferable that the spiral groove is formed on the inner peripheral surface of the reduced diameter portion. In these cases, it is possible to easily form the throttle member and the back pressure supply path.

  A guide passage that communicates the discharge region side of the throttle member and the back pressure chamber side may be formed by the throttle member and the inner peripheral surface of the reduced diameter portion or by the throttle member. The back pressure supply path is preferably throttled by the guide path when the throttle member contacts the stopper. In this case, the back pressure supply path is further throttled as compared with the case of the guide path by the throttle member moving away from the stopper and moving in the reduced diameter portion.

  The guide passage is preferably provided in a groove shape on the outer peripheral surface of the throttle member, and is formed by a concave groove communicating with the spiral groove and an inner peripheral surface of the reduced diameter portion. The guide passage is preferably formed flat on the outer peripheral surface of the throttle member, and is formed by a concave groove communicating with the spiral groove and an inner peripheral surface of the reduced diameter portion. Furthermore, it is preferable that the guide passage is formed of a through hole that opens to the outer peripheral surface of the throttle member so as to be able to communicate with the spiral groove and extends into the throttle member. In these cases, the guide passage can be easily formed.

  The cross-sectional area of the guide passage is larger than the cross-sectional area of the passage formed by the spiral groove and the other of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member, and the length of the guide passage is the length of the spiral groove. Shorter than that. In this case, it is possible to reliably squeeze the back pressure supply path when the throttle member moves away from the stopper and moves in the reduced diameter portion, rather than when the throttle member contacts the stopper.

  A compressor according to the present invention includes a side plate that defines a cylinder chamber in a housing, a rotary shaft that is rotatably provided in the housing, a rotary shaft that is rotatably provided in the cylinder chamber, and a plurality of vane grooves. And a formed rotor. Further, the movable member may be a vane provided in each vane groove so as to be able to appear and disappear. Further, the compression chamber may be formed by the front surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the rear surface of the cylinder chamber, the outer peripheral surface of the rotor, and each vane. The back pressure chamber can be provided between the bottom surface of each vane and each vane groove. And it is preferable that the back pressure supply path is formed in the side plate.

  In this case, the compressor of the present invention is embodied in a vane type compressor.

  In addition, the compressor of the present invention is connected to a rotary shaft that is rotatably provided in the housing, a fixed scroll that is fixed in the housing and forms a discharge region between the housing, and the rotary shaft. A movable scroll disposed opposite to the scroll may be provided. The movable member may be a movable scroll. Further, the compression chamber can be formed between the fixed scroll and the movable scroll. The back pressure supply path is preferably formed in a fixed scroll.

  In this case, the compressor of the present invention is embodied as a scroll compressor.

  In the compressor of the present invention, high compression performance and low power loss can be realized in a compressor provided with a passage communicating the discharge region and the back pressure chamber.

FIG. 1 is a cross-sectional view illustrating a compressor according to a first embodiment. FIG. 2 is a cross-sectional view illustrating the compression mechanism according to the compressor of the first embodiment. FIG. 3 is an essential part enlarged cross-sectional view illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is low in the compressor of the first embodiment. FIG. 4 is a cross-sectional view illustrating the throttle member according to the compressor of the first embodiment. FIG. 5 is an essential part enlarged cross-sectional view illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is high in the compressor of the first embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is low, according to the compressor of the second embodiment. FIG. 7 is an enlarged cross-sectional view of a main part illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is low, according to the compressor of the third embodiment. FIG. 8 is an essential part enlarged cross-sectional view illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is low in the compressor of the fourth embodiment. FIG. 9 is a cross-sectional view illustrating a back pressure flow path according to the compressor of the fourth embodiment. FIG. 10 is an essential part enlarged cross-sectional view illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is high, according to the compressor of the fourth embodiment. FIG. 11 is a cross-sectional view illustrating the compressor of the fifth embodiment. FIG. 12 is an enlarged cross-sectional view of a main part illustrating the back pressure flow path and the throttle member when the refrigerant pressure in the discharge region is low, according to the compressor of the fifth embodiment.

  Hereinafter, Embodiments 1 to 5 embodying the present invention will be described with reference to the drawings.

Example 1
As shown in FIG. 1, the electric vane compressor of the first embodiment (hereinafter simply referred to as “compressor”) is an example of a specific aspect of the compressor of the present invention. The compressor includes a front housing 1, a motor mechanism 3, a cylinder block 7, a rear housing 9, an inverter cover 67, and a compression mechanism 13. The front housing 1, the cylinder block 7, and the rear housing 9 are examples of the “housing” of the present invention.

  In the following description, the front housing 1 side on the left side of FIG. 1 is the front side of the compressor, and the rear housing 9 side on the right side of FIG. 1 is the rear side of the compressor. Further, the upper side of the page of FIG. 1 is the upper side of the compressor, and the lower side of the page of FIG. 1 is the lower side of the compressor. In FIG. 2 and subsequent figures, the front-rear direction and the vertical direction are displayed in correspondence with FIG. In addition, the front-back direction and the up-down direction in Example 1 are examples. The mounting posture of the compressor of the present invention is appropriately changed in accordance with the vehicle or the like to be mounted.

  The front housing 1 extends in the axial direction from the front end side to the rear end side, and has a bottomed cylindrical shape in which the front end side is closed by the bottom wall 1a and has an opening 1b on the rear end side. The front housing 1 forms a motor chamber 1c that also serves as a suction chamber. The front housing 1 is formed with a suction port 1d that communicates the outside with the motor chamber 1c. An evaporator 6a of the vehicle air conditioner, an expansion valve 6b, and a condenser 6c are connected to the suction port 1d in this order by a pipe 6. A shaft support portion 1e is projected from the bottom wall 1a. A bearing device 21 is provided on the shaft support 1e.

  The motor mechanism 3 includes a stator 15 and a motor rotor 17. The stator 15 is fixed to the inner peripheral surface of the front housing 1. Moreover, the lead wire 16c and the cluster block 16 are accommodated in the motor chamber 1c.

  The cluster block 16 has connection terminals 16a and 16b. The connection terminal 16a passes through the bottom wall 1a and protrudes into an accommodation space 67a described later. The connection terminal 16b is connected to the stator 15 via the lead wire 16c.

  An inverter cover 67 is fixed to the front end of the front housing 1. The inverter cover 67 forms an accommodation space 67 a between the front surface of the bottom wall 1 a of the front housing 1. An inverter 69 and an insulating sheet 71 are provided in the accommodation space 67a. The inverter 69 is fixed to the front surface of the bottom wall 1a. The inverter 69 is connected to the connection terminal 16a through the cable 69a. Thus, the stator 15 is appropriately supplied with power from the power supply device (not shown) via the inverter 69, the cluster block 16, and the lead wire 16c.

  The motor rotor 17 is disposed in the stator 15. The motor rotor 17 passes through a rotation shaft 19 having a rotation axis O extending in the front-rear direction as an axis. A front end portion of the rotating shaft 19 is pivotally supported by a bearing device 21.

  A rear housing 9 is fixed to the rear end of the front housing 1 by a plurality of bolts (not shown). The rear housing 9 has a bottomed cylindrical shape whose rear end is closed by a bottom wall 9d and has an opening 9e on the front end. The front housing 1 and the rear housing 9 are closed by the front end surface of the rear housing 9 coming into contact with the rear end surface of the front housing 1. The first side plate 4 is fitted on the opening 9 e side of the rear housing 9. An O-ring 23 is provided between the outer peripheral surface of the first side plate 4 and the inner peripheral surface of the rear housing 9. The first side plate 4 is provided with a shaft hole 4a through which the rotary shaft 19 is inserted. The shaft hole 4a is formed with a plating (not shown) for suitably sliding the rotating shaft 19.

  Further, the second side plate 5 is fitted in the center of the rear housing 9. The first side plate 4 and the second side plate 5 are examples of the “side plate” in the present invention.

  An O-ring 24 is provided between the outer peripheral surface of the second side plate 5 and the inner peripheral surface of the rear housing 9. The second side plate 5 has a shaft hole 5c through which the rotary shaft 19 is inserted. The shaft hole 5c is formed with a plating (not shown) that suitably slides the rotating shaft 19. The rear end portion of the rotary shaft 19 is supported by the shaft hole 5c. Thus, the rotating shaft 19 is pivotally supported at both ends by the bearing device 21 and the shaft hole 5c of the second side plate 5 and is rotatable.

  A cylinder block 7 is fixed between the first side plate 4 and the second side plate 5 by bolts 25a to 25d shown in FIG. As shown in FIG. 1, the cylinder block 7 extends in a cylindrical shape in the axial direction. The cylinder block 7 is fixed to the first and second side plates 4 and 5, thereby forming a cylinder chamber 31 together with the first and second side plates 4 and 5. As shown in FIG. 2, the cylinder chamber 31 has a perfect circular cross-sectional shape perpendicular to the axial direction. The axis of the cylinder chamber 31 is eccentric from the rotation axis O. On the front surface on the front end side, the inner peripheral surface, and the rear surface on the rear end side of the cylinder chamber 31, plating (not shown) that suitably slides the rotor 45 and the vanes 47a and 47b is formed. Details of the rotor 45 and the vanes 47a and 47b will be described later.

  As shown in FIG. 1, the first side plate 4 is formed with a suction passage 33a that opens in the axial direction and communicates with the motor chamber 1c. The cylinder block 7 is formed with a suction passage 33b communicating with the suction passage 33a. As shown in FIG. 2, the suction passage 33 b communicates with the cylinder chamber 31 through a suction port 33 c that is recessed from the outer peripheral surface of the cylinder chamber 31.

  The cylinder block 7 is provided with a discharge space 37 that opens to the outer peripheral side. The discharge space 37 communicates with the cylinder chamber 31 by a discharge port 37 a that is recessed from the outer peripheral surface of the cylinder chamber 31. In the discharge space 37, a discharge reed valve 39 that opens and closes the discharge port 37 a and a retainer 41 that regulates the opening degree of the discharge reed valve 39 are fixed to the cylinder block 7 by bolts 43.

  In the cylinder chamber 31, the rotor 45 is rotatably provided by the rotation shaft 19. The rotor 45 is press-fitted or key-connected to the rotary shaft 19. The rotor 45 has two vane grooves 45a and 45b. Flat vanes 47a and 47b are provided in the vane grooves 45a and 45b so as to be able to appear and disappear. Back pressure chambers 49a and 49b are provided between the bottom surfaces of the vanes 47a and 47b and the vane grooves 45a and 45b, respectively.

  The compression mechanism 13 is configured by the first and second side plates 4 and 5, the rotation shaft 19, the rotor 45, and the vanes 47a and 47b. Two compression chambers 50a and 50b are formed by the front surface of the cylinder chamber 31, the inner peripheral surface of the cylinder chamber 31, the rear surface of the cylinder chamber 31, the outer peripheral surface of the rotor 45, and the vanes 47a and 47b.

  As shown in FIG. 1, an annular groove 4 b is recessed around the rotation axis O on the rear surface of the first side plate 4. Further, an annular groove 5 a that faces the annular groove 4 b in the front-rear direction is recessed around the rotation axis O on the front surface of the second side plate 5.

  A discharge chamber 9 a serving as a discharge pressure region is formed between the rear housing 9 and the second side plate 5. The rear housing 9 is formed with a discharge port 9b that communicates the outside with the discharge chamber 9a. A condenser 6 c is connected to the discharge port 9 b by a pipe 6. A block 35 is fixed to the second side plate 5.

  The block 35 is formed with a cylindrical oil separation chamber 35a. A cylindrical tube member 53 is fixed to the oil separation chamber 35a. The upper end of the cylindrical member 53 is opened to the discharge chamber 9a, and the lower end of the oil separation chamber 35a is opened to the discharge chamber 9a by the oil discharge port 35b. An oil separator is constituted by the oil separation chamber 35 a and the cylindrical member 53. A lower portion of the discharge chamber 9a is an oil storage portion 35c that stores the lubricating oil separated in the oil separation chamber 35a. In the second side plate 5 and the block 35, discharge passages 5b and 35e that connect the discharge space 37 to the oil separation chamber 35a are formed.

  An oil supply chamber 55 communicating with the shaft hole 5 c is formed between the second side plate 5 and the block 35. Further, a back pressure channel 56 communicating with the oil storage part 35 is formed in the second side plate 5. Further, the second side plate 5 is formed with a first passage 57 that communicates with the back pressure channel 56 and the oil supply chamber 55, and a second passage 58 that communicates with the oil supply chamber 55 and the annular groove 5 a. The back pressure supply path 100 is constituted by the back pressure flow path 56, the first passage 57, the oil supply chamber 55, the second passage 58, and the annular groove 5a. The formation of the oil supply chamber 55 may be omitted, and the annular groove 5a may be formed in another shape. Further, the back pressure supply path 100 on the downstream side of the oil supply chamber 55 may be provided in the rotary shaft 19.

  The back pressure channel 56 extends linearly upward from the outer peripheral surface of the second side plate 5 so as to approach the rotation axis O. The back pressure channel 56 communicates the discharge chamber 9a with the back pressure chambers 49a and 49b through the first passage 57, the oil supply chamber 55, the second passage 58, and the annular groove 5a that are downstream of the back pressure channel 56.

  The area X in FIG. 1 is enlarged and shown in FIG. As shown in the figure, the back pressure flow path 56 has an inlet 56 a that communicates with the oil storage portion 35 c and an outlet 56 b that communicates with the first passage 57. Further, the back pressure flow channel 56 includes a diameter-enlarged portion 561 having a first inner diameter L1 and a diameter-reduced portion 562 having a second inner diameter L2 smaller than the first inner diameter L1. The enlarged diameter portion 561 is located on the inlet 56a side, and communicates with the inlet 56a at the lower end. The reduced diameter portion 562 is located on the outlet 56b side and communicates with the outlet 56b at the upper end. The reduced diameter portion 562 has an inner peripheral surface 562a and an upper wall 562b continuous with the inner peripheral surface 562a. On the lower end side of the inner peripheral surface 562a, a slidable contact surface 562c slidably contacted with a peak portion 611a described later is formed. The reduced diameter portion 562 is connected to the enlarged diameter portion 561 via a tapered portion 563 located between the upper end side of the enlarged diameter portion 561 and the reduced diameter portion 562. The tapered portion 563 has a shape that gradually decreases in diameter from the enlarged diameter portion 561 side toward the reduced diameter portion 562 side. The back pressure channel 56 has a substantially cylindrical shape due to the enlarged diameter portion 561, the reduced diameter portion 562, and the tapered portion 563. The tapered portion 563 is an example of the “step” in the present invention. The “step” in the present invention may have other shapes.

  A throttle member 61, a coil spring 63, and a stopper 65 are provided in the back pressure channel 56. The coil spring 63 is an example of the “biasing member” in the present invention.

  The throttle member 61 is coaxial with the back pressure channel 56 and extends in the same direction as the back pressure channel 56. The aperture member 61 has a main body portion 61a, a first shaft portion 61b, and a second shaft portion 61c, and has a substantially cylindrical shape. The main body portion 61 a is formed to have substantially the same diameter as the reduced diameter portion 562 of the back pressure channel 56. That is, the main body 61 a has a smaller diameter than the diameter-enlarged portion 561 of the back pressure channel 56. Further, the first shaft portion 61b and the second shaft portion 61c are formed with a smaller diameter than the main body portion 61a. Thereby, the throttle member 61 is guided in the reduced diameter portion 562 by the differential pressure through itself, that is, the differential pressure between the discharge chamber 9a and the back pressure chambers 49a and 49b. Moving. As a result, the throttle member 61 moves away from the stopper 65 against the urging force of the coil spring 63 as shown in FIG. It can be displaced to a separation position that moves in the reduced diameter portion 562 toward the side. Details of the contact position and the separation position will be described later.

  The main body 61a has an outer peripheral surface 610. On the outer peripheral surface 610, a spiral groove 611 is formed on the lower end side of the main body 61a. The spiral groove 611 has a peak part 611a and a valley part 611b continuous with the peak part 611a.

  In addition, on the outer peripheral surface 610, a tapered surface 612 that gradually decreases in diameter upward is formed on the upper end side of the main body 61a. Further, as shown in FIG. 4, concave grooves 613 and 614 are formed between the spiral groove 611 and the tapered surface 612 on the outer peripheral surface 610. The concave grooves 613 and 614 communicate with the valley 611b of the spiral groove 611 at the lower ends, respectively, and linearly extend upward toward the tapered surface 612. The upper ends of the concave grooves 613 and 614 communicate with the tapered surface 612. A guide passage 620 is formed by the recessed grooves 613 and 614 and the inner peripheral surface 562a of the reduced diameter portion 562 including the sliding contact surface 562c. The guide passage 620 communicates the upstream side and the downstream side in the fluid flow direction, which will be described later, in the throttle member 61. Here, the cross-sectional area of the guide passage 620 is larger than the cross-sectional area of the throttle passage S1 (see FIG. 5) described later, and the length of the guide passage 620 is shorter than the length of the spiral groove 611. Note that only the groove 613 may be formed on the outer peripheral surface 610, and a groove may be further formed in addition to the grooves 613 and 614.

  The first shaft portion 61 b is connected to the lower end of the main body portion 61 a, that is, the lower end of the spiral groove 611, and extends downward from the throttle member 61. A first communication passage 615 extending in the radial direction and opening on the outer peripheral surface of the first shaft portion 61b is recessed in the lower end surface of the first shaft portion 61b. The first communication passage 615 communicates with a communication hole 65a described later when the throttle member 61 contacts the stopper 65. In addition, it is good also as a structure which provides a protrusion in the lower end surface of the 1st axial part 61b, and uses the space formed by the stopper 65 and protrusion as the 1st communicating path 615. FIG.

  The second shaft portion 61 c is connected to the upper end of the tapered surface 612 of the main body portion 61 a and extends toward the upper side of the diaphragm member 61. A second communication path 616 that extends in the radial direction and opens to the outer peripheral surface of the second shaft portion 61c is recessed in the upper end surface of the second shaft portion 61c.

  As shown in FIG. 3, the coil spring 63 is disposed in the reduced diameter portion 562. The second shaft portion 61 c of the throttle member 61 is inserted through the coil spring 63. The upper end of the coil spring 63 is in contact with the upper wall 562 b of the reduced diameter portion 562, and the lower end of the coil spring 63 is in contact with the tapered surface 612 of the aperture member 61. Accordingly, the coil spring 63 biases the throttle member 61 toward the inlet 56 a of the back pressure channel 56. In addition, the outer peripheral surface of the second shaft portion 61 c functions as a guide member for the coil spring 63.

  The stopper 65 has a cylindrical shape and is disposed in the enlarged diameter portion 561. The stopper 65 is fixed to the lower end of the enlarged diameter portion 561 by press fitting or screwing. The stopper 65 is provided with a communication hole 65a. The stopper 65 can come into contact with the throttle member 61 biased by the coil spring 63. In addition, you may comprise the stopper of this invention with a circlip, S character spring, etc. FIG.

  The back pressure supply mechanism 14 is configured by the back pressure channel 56, the throttle member 61, the coil spring 63, and the stopper 65.

  In this compressor, when power is supplied to the stator 15 shown in FIG. 1, the motor mechanism 3 operates and the rotating shaft 19 rotates around the rotation axis O. For this reason, the compression mechanism 13 operates and the rotor 45 rotates in the cylinder block 7. Thereby, each compression chamber 50a, 50b repeats expansion and contraction of the volume. For this reason, each compression chamber 50a, 50b performs a suction stroke for sucking low-pressure refrigerant gas from the motor chamber 1c through the suction passages 33a, 33b through the suction port 33c. In addition, after the intake stroke, a compression stroke is performed in which the refrigerant gas is compressed in the compression chambers 50a and 50b. Further, after the compression stroke, a discharge stroke is performed in which high-pressure refrigerant gas in the compression chambers 50a and 50b is discharged from the discharge port 37a to the discharge space 37. The refrigerant gas in the discharge space 37 is discharged into the discharge chamber 9a through the discharge passages 5b and 35e. And a refrigerant | coolant circulates through the piping 6, the condenser 6c, the expansion valve 6b, and the evaporator 6a connected to the discharge port 9b, and the vehicle interior is air-conditioned.

  Further, the lubricating oil is separated from the refrigerant gas discharged into the discharge chamber 9a by centrifugal force in the oil separation chamber 35a. This lubricating oil is stored in the oil storage part 35c. Then, due to the pressure in the discharge chamber 9 a, the lubricating oil stored in the oil storage portion 35 c is supplied from the annular groove 5 a to the back pressure chambers 49 a and 49 b by the back pressure supply mechanism 14. Thereby, in this compressor, it is possible to apply a back pressure to the vanes 47a and 47b. During the operation of the compressor, the lubricating oil is mainly supplied to the back pressure chambers 49a and 49b, but the refrigerant gas in the discharge chamber 9a is also supplied depending on the conditions. For this reason, in this embodiment, the lubricating oil and refrigerant (including refrigerant gas and liquid refrigerant) are collectively referred to as “fluid”.

  Here, in this compressor, when the pressure in the discharge chamber 9a is low immediately after the start of operation and the differential pressure between the discharge chamber 9a and the back pressure chambers 49a and 49b is small, the throttle member 61 Due to the urging force, the contact position shown in FIG. In this contact position, the spiral groove 611 is located in the enlarged diameter portion 561. At this time, in this compressor, the first throttle amount of the back pressure supply path 100 including the back pressure flow path 56 is determined by the cross-sectional area and length of the guide passage 620. For this reason, when the throttle member 61 is in the contact position, the back pressure flow channel 56 causes the fluid to flow toward the back pressure chambers 49a and 49b with the first throttle amount. Specifically, as indicated by the arrows in the figure, the fluid that has flowed into the back pressure flow path 56 from the inflow port 56a flows from the communication hole 65a through the first communication path 615 through the enlarged diameter portion 561, thereby forming a concave groove. 613, 614, that is, the guide passage 620 (see FIG. 4 for the concave groove 614). Then, the fluid reaching the guide passage 620 flows through the reduced diameter portion 562 from the guide passage 620 and flows out from the outlet 56 b to the first passage 57. Thus, the fluid flowing out into the first passage 57 is supplied to the back pressure chambers 49a and 49b shown in FIG. 2 through the oil supply chamber 55, the second passage 58 and the annular groove 5a shown in FIG.

  As described above, the main body 610 of the throttle member 61 is smaller in diameter than the enlarged diameter portion 561, so that when the throttle member 61 is in the contact position, there is no fluid between the enlarged diameter portion 561 and the main body portion 610. Sufficient clearance is ensured for the circulation. Further, a sufficient gap is also ensured between the inner peripheral surface 562 a including the sliding contact surface 562 c constituting the guide passage 20 and the second concave grooves 613 and 614. For this reason, the fluid which circulated between the enlarged diameter part 561 and the main-body part 610 distribute | circulates the guide channel | path 620, without being pressure-reduced so much. That is, at the first throttle amount, the fluid is not depressurized so much in the back pressure channel 56. Thus, in this compressor, when the pressure in the discharge chamber 9a is low, the fluid flowing through the back pressure flow path 56 reaches the back pressure chambers 49a and 49b without much pressure reduction.

  For this reason, in this compressor, even if the pressure in the discharge chamber 9a is low, the pressure in the back pressure chambers 49a and 49b does not decrease excessively, and the back pressure is suitably applied to the vanes 47a and 47b. Can be granted. As a result, the vanes 47a and 47b can be favorably biased toward the inner peripheral surface of the cylinder chamber 31, so that chattering hardly occurs. For this reason, in this compressor, it is difficult for the refrigerant gas to leak from the compression chambers 50a and 50b even immediately after the start of operation, and the compression performance can be improved. In addition, since chattering is less likely to occur, the generation of noise can be prevented.

  On the other hand, if the pressure in the discharge chamber 9a is high and the differential pressure between the discharge chamber 9a and the back pressure chambers 49a and 49b increases, the throttle member 61 resists the biasing force of the coil spring 63 as shown in FIG. Thus, it becomes a separation position that moves away from the stopper 65 and moves in the reduced diameter portion 562 toward the outlet 56b side. For this reason, the main body 610 moves in the reduced diameter portion 562 toward the outlet 56b. The throttle member 61 is restricted from moving toward the outflow port 56b when the upper end surface of the second shaft portion 61c contacts the upper wall 562b.

  Then, the main body 610 moves in the reduced diameter portion 562 toward the outflow port 56b, so that the spiral groove 611 enters the reduced diameter portion 562. For this reason, the peak part 611a of the spiral groove 611 and the sliding contact surface 562c of the reduced diameter part 562 are in sliding contact. Accordingly, the spiral groove 611 forms a spiral throttle passage S1 between the valley portion 611b and the sliding contact surface 562c. Thus, the throttle member 61 is moved to the separated position and the throttle passage S1 is formed. In this compressor, the cross-sectional area and the length (distance of the throttle passage S1) of the throttle passage S1 are used in the compressor. A second aperture amount is determined. As described above, the cross-sectional area of the guide passage 620 is larger than the cross-sectional area of the throttle passage S1, and the length of the guide passage 620 is shorter than the length of the spiral groove 611. As a result, in the back pressure supply path 100, the throttle member 61 is in the separated position compared to the throttle member 61 being in the contact position, and the main body 610 is throttled when moving in the reduced diameter portion 562. Become. That is, as shown by the arrow in the figure, the fluid that has flowed from the inlet 56a through the communication hole 65a into the enlarged diameter portion 561 flows from the enlarged diameter portion 561 to the valley portion 611b, that is, the throttle passage S1. Then, the fluid is depressurized by flowing through the throttle passage S <b> 1 toward the guide passage 620. The decompressed fluid is guided by the guide passage 620 to the reduced diameter portion 562 and eventually to the outflow port 56b. At this time, part of the fluid in the reduced diameter portion 562 flows through the second communication path 616 and reaches the outlet 56b. And the fluid which flowed out into the 1st channel | path 57 from the outflow port 56b is supplied to the back pressure chambers 49a and 49b through the oil supply chamber 55, the 2nd channel | path 58, and the annular groove 5a.

  Thus, in this compressor, when the pressure in the discharge chamber 9a is high, it is possible to supply the fluid to the back pressure chambers 49a and 49b while decompressing the fluid. For this reason, the pressure in the back pressure chambers 49 a and 49 b can be suitably adjusted, and the vanes 47 a and 47 b can be prevented from being excessively pressed against the inner peripheral surface of the cylinder chamber 31. For this reason, in this compressor, even if the pressure in the discharge chamber 9a is high, it is possible to reduce power loss.

  Therefore, in the compressor of the first embodiment, high compression performance and low power loss can be realized in the compressor provided with a passage communicating the discharge chamber 9a and the back pressure chambers 49a and 49b.

  In this compressor, the spiral groove 611 can be easily formed in the throttle member 61 by forming the spiral groove 611 on the outer peripheral surface 610 of the main body 61a. Here, since the spiral groove 611 is formed only on the outer peripheral surface 610 of the main body portion 61 a, a sliding contact surface 562 c may be formed on the inner peripheral surface 562 a of the reduced diameter portion 562, and corresponds to the spiral groove 611. It is not necessary to form a concave groove. For this reason, it is easy to form the back pressure channel 56. Further, since the spiral groove 611 and the sliding contact surface 562c can be formed with high accuracy, the accuracy of the throttle passage S1 can be increased as a result. In addition, since the fluid flows through the throttle passage S1, the back pressure channel 56 is less likely to be clogged with foreign matters.

  The throttle passage S1 formed by the spiral groove 611 has a spiral shape. Therefore, the throttle passage S1 can increase the distance when the fluid flows through itself while suppressing the communication area between the upstream side and the downstream side of the throttle member 61 in the fluid flow direction. For this reason, the throttle passage S1, and thus the spiral groove 611, can be quickly circulated with respect to the refrigerant gas and function as a suitable throttle with respect to the lubricating oil.

  In addition, in this compressor, the guide passage 620 can be easily formed by forming the guide passage 620 by the concave grooves 613 and 614 and the inner peripheral surface 562a of the reduced diameter portion 562 including the sliding contact surface 562c. Is possible.

(Example 2)
As shown in FIG. 6, in the compressor according to the second embodiment, a concave groove 617 is formed in the throttle member 61. The concave groove 617 is formed flat on the outer peripheral surface 610 of the main body portion 61a and extends in the vertical direction. Similar to the concave grooves 613 and 614, the concave groove 617 communicates with the valley 611b of the spiral groove 611 at the lower end and communicates with the tapered surface 612 at the upper end. Thus, in this compressor, a guide passage 621 is formed by the concave groove 617 and the inner peripheral surface 562a of the reduced diameter portion 562 including the sliding contact surface 562c. The cross-sectional area of the guide passage 621 is also larger than the cross-sectional area of the throttle passage S1, and the length of the guide passage 621 is shorter than the length of the spiral groove 611. A plurality of concave grooves 617 may be formed on the outer peripheral surface 610. Other configurations of the compressor are the same as those of the compressor according to the first embodiment, and the same components are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, the fluid that has flowed through the enlarged diameter portion 561 and the trough portion 611b of the spiral groove 611, that is, the throttle passage S1, is guided to the reduced diameter portion 562 and eventually the outlet 56b by the guide passage 621. Here, in this compressor, when the throttle member 61 is in the contact position, the first throttle amount of the back pressure supply path 100 is determined by the cross-sectional area and length of the guide passage 621. Also in this compressor, a sufficient gap is ensured between the inner peripheral surface 562 a including the sliding contact surface 562 c constituting the guide passage 621 and the concave groove 617. For this reason, when the throttle member 61 becomes the contact position and the fluid flows through the guide passage 621, the fluid is not depressurized so much. Thus, this compressor can achieve the same operation as the compressor of the first embodiment.

(Example 3)
As shown in FIG. 7, in the compressor of the third embodiment, the throttle member 61 is formed with a through hole 618 as a guide passage. The through hole 618 is formed inside the throttle member 61 and has a radial path 618a and an axial path 618b. The radial path 618 a extends in the radial direction of the throttle member 61 and opens to the valley portion 611 b of the spiral groove 611. The axial path 618b extends from the main body part 61a to the second axial part 61c in the radial direction of the throttle member 61 while communicating with the radial path 618a. The upper end of the axial path 618 b communicates with the second communication path 616. The cross-sectional area of the through hole 618 is also larger than the cross-sectional area of the throttle passage S1, and the length of the through hole 618 is shorter than the length of the spiral groove 611. Other configurations of the compressor are the same as those of the compressor of the first embodiment.

  In this compressor, the fluid that has flowed through the enlarged diameter portion 561 and the trough portion 611b of the spiral groove 611 flows from the trough portion 611b of the spiral groove 611 through the diameter passage 618a and the axial passage 618b. Then, it is guided from the through hole 618 to the reduced diameter portion 562 and eventually to the outflow port 56b through the second communication passage 616. Here, in this compressor, when the throttle member 61 is in the contact position, the first throttle amount of the back pressure supply path 100 is determined by the cross-sectional area and length of the through hole 618. For this reason, like the compressors of the first and second embodiments, the fluid is not depressurized so much when flowing through the through hole 618. Thus, this compressor can achieve the same operation as the compressor of the first embodiment.

Example 4
As shown in FIGS. 8 to 10, in the compressor of the fourth embodiment, a spiral groove 564 is formed on the inner peripheral surface 562 a of the reduced diameter portion 562 in the back pressure flow channel 56. As shown in FIG. 9, the spiral groove 564 extends spirally while continuing to the tapered portion 563 at the lower end. The spiral groove 564 has a peak part 564a and a valley part 564b continuous with the peak part 564a. In the reduced diameter portion 562, the portion where the spiral groove 564 is formed has a smaller diameter than the first inner diameter L1 of the enlarged diameter portion 561.

  As shown in FIGS. 8 and 10, in this compressor, a sliding contact surface 619 that is in sliding contact with the mountain portion 564 a is formed on the outer peripheral surface 611 of the main body 61 a of the throttle member 61. The lower ends of the concave grooves 613 and 614 are continuous with the sliding contact surface 619. As with the compressor of the first embodiment, a guide passage 620 is formed by the recessed grooves 613 and 614 and the inner peripheral surface 562a of the reduced diameter portion 562. The cross-sectional area of the guide passage 620 is larger than the cross-sectional area of the throttle passage S2 (see FIG. 10) described later, and the length of the guide passage 620 is shorter than the length of the spiral groove 564. Other configurations of the compressor are the same as those of the compressor of the first embodiment.

  As indicated by the arrows in FIG. 8, in this compressor, when the pressure in the discharge chamber 9a is low immediately after the operation starts, the fluid that flows into the back pressure channel 56 from the inlet 56a flows through the enlarged diameter portion 561. Then, it reaches the guide passage 620. Here, like the compressor of the first embodiment, in this compressor, when the pressure in the discharge chamber 9a is low and the throttle member 61 is in the contact position, the back pressure depends on the cross-sectional area and the length of the guide passage 620. A first throttle amount of the supply path 100 is determined. When the aperture member 61 is in the contact position, the sliding contact surface 619 is located in the enlarged diameter portion 561 in the main body portion 61 a of the aperture member 61, and the concave grooves 613 and 614 are in contact with the peak portion 564 a of the spiral groove 564. Face to face. For this reason, in addition to between the enlarged diameter part 561 and the sliding contact surface 619, the clearance gap for a fluid to circulate also between the ditch | groove 613,614 and each peak part 564a is fully ensured. For this reason, even in this compressor, the fluid flowing through the guide passage 620 is not reduced in pressure by the first throttle amount. Thus, the fluid is supplied to the back pressure chambers 49a and 49b as in the compressor of the first embodiment.

  On the other hand, as shown in FIG. 10, the pressure in the discharge chamber 9 a is high, the throttle member 61 is in the separated position, and the sliding surface 619 enters the reduced diameter portion 562. The sliding contact surface 619 is in sliding contact. Thus, the spiral groove 564 forms a spiral throttle passage S2 between the sliding contact surface 619 and the spiral groove 564. Thus, when the throttle member 61 is in the separated position and the throttle passage S2 is formed, in this compressor, the second throttle amount of the back pressure supply passage 100 is determined by the cross-sectional area and length of the throttle passage S2. The cross-sectional area of the guide passage 620 is larger than the cross-sectional area of the throttle passage S2, and the length of the guide passage 620 is shorter than the length of the spiral groove 564. For this reason, as shown by the arrow in the figure, the fluid that has flowed through the enlarged diameter portion 561 is decompressed by flowing through the throttle passage S2. The decompressed fluid is supplied to the back pressure chambers 49a and 49b. Thus, this compressor can achieve the same operation as the compressor of the first embodiment.

  Further, in this compressor, the spiral groove 564 can be easily formed by forming the spiral groove 564 on the inner peripheral surface 562a of the reduced diameter portion 562. Further, in this compressor, unlike the compressor of the first embodiment, since it is not necessary to form the spiral groove 611 in the throttle member 61, it is easier to form the throttle member 61.

(Example 5)
As shown in FIGS. 11 and 12, the present invention can also be applied to the electric scroll compressor as the fifth embodiment. In this compressor, a fixed scroll 120 and a movable scroll 140 are provided in a housing 200. This compressor also includes a back pressure channel 56, a throttle member 61, a coil spring 63, and a stopper 65, as in the compressor of the first embodiment.

  As shown in FIG. 11, a fixed block 160 is provided in front of the fixed scroll 120 and the movable scroll 140 in the housing 200. A flat and annular elastic plate 240 is interposed between the fixed scroll 120 and the fixed block 160. In the fixed block 160, a bearing device 340 and a sealing material 360 are provided. The rotating shaft 300 is inserted through the fixed block 160, the bearing device 340, and the seal material 360. An eccentric pin 300a protrudes from the rear end of the rotating shaft 300. A drive bush 380 is fitted to the eccentric pin 300a.

  The fixed scroll 120 includes a fixed substrate 120b, a fixed peripheral wall 120a, and a fixed spiral wall 120c. Further, the fixed scroll 120 is formed with a through hole 120e extending from the rear end surface to the front end surface. The movable scroll 140 includes a movable substrate 140b and a movable spiral wall 140c. The fixed scroll 120 and the movable scroll 140 are meshed with each other. The movable scroll 140 is urged toward the fixed scroll 120 by the restoring force when the elastic plate 240 is elastically deformed. The movable scroll 140 is connected to the rotary shaft 300 via the bearing device 400 and the drive bush 380.

  Further, between the movable substrate 140b and the fixed block 160, a rotation prevention mechanism including a rotation prevention pin 280a, a rotation prevention hole 420, and a ring 440 is provided. A revolution mechanism 180 is configured by the rotation shaft 300, the eccentric pin 300a, the drive bush 380, and the rotation prevention mechanism.

  A compression chamber 460 is formed between the fixed scroll 120 and the movable scroll 140. A back pressure chamber 480 is formed between the movable scroll 140 and the fixed block 160. That is, the back pressure chamber 480 is located on the back side of the compression chamber 460 in the movable scroll 140 with the movable substrate 140b interposed therebetween.

  A discharge chamber 500 is formed between the fixed scroll 120 and the housing 200. The discharge chamber 500 communicates with the compression chamber 460 through a discharge port 120d provided through the fixed substrate 120b. Further, an oil supply chamber 720 is formed between the fixed scroll 120 and the housing 200 and on the outer peripheral side of the discharge chamber 500.

  In addition, an air supply hole 140d is provided in the vicinity of the center of the movable spiral wall 140c in the movable scroll 140 and the movable substrate 140b. The air supply hole 140d is opened to the compression chamber 460 so that the compression chamber 460 communicates with the inside of the fixed block 160. For this reason, when the compression chamber 460 becomes high pressure, the high-pressure refrigerant gas in the compression chamber 460 is released from the air supply hole 140d to the back pressure chamber 480, and the movable scroll 140 is fixed to the fixed scroll 120 by the pressure of the back pressure chamber 480. It is designed to be pressed.

  An oil separation chamber 580 is formed on the rear side in the housing 200. A cylindrical member 600 is fixed above the oil separation chamber 580. The oil separation chamber 580 and the cylindrical member 600 constitute an oil separator. A filter 760 is provided at the lower end of the oil separation chamber 580. The discharge chamber 500 and the oil separation chamber 580 communicate with each other through the discharge passage 220a. A discharge region is formed by the discharge chamber 500 and the oil separation chamber 580.

  On the other hand, the front side in the housing 200 is a motor chamber 640 that also serves as a suction chamber. A motor mechanism 700 is provided in the motor chamber 640.

  The area Y in FIG. 11 is enlarged and shown in FIG. As shown in the figure, in this compressor, the back pressure flow path 56 is formed in the fixed scroll 120. As in the compressor of the first embodiment, the throttle member 61 and the coil spring 63 are provided in the back pressure channel 56.

  The fixed scroll 120 is formed with a communication passage 740 that communicates with the back pressure flow channel 56 and the oil supply chamber 720. Although not shown, the fixed scroll 120 is formed with a plurality of oil return holes that allow the oil supply chamber 720 and the compression chamber 460 to communicate with each other. Furthermore, as shown in FIG. 11, the elastic plate 240 is formed with a notch 240a. Although not shown in detail, the notch 240 a communicates with the back pressure chamber 480. Thus, the oil supply chamber 720 communicates with the back pressure chamber 480 through the through hole 120e and the notch 240a.

  As shown in FIG. 12, in the back pressure flow path 56, the inflow port 56 a communicates with the oil separation chamber 580 and the outflow port 56 b communicates with the communication passage 740. Thereby, in this compressor, the back pressure flow path 56 is connected to the discharge chamber 500, the oil separation chamber 580, which is a discharge region, and the back pressure chamber 400 through the communication passage 740, the oil supply chamber 720, the through hole 120e, and the notch 240a. Is communicated. And in this compressor, the back pressure supply path 101 is comprised by the back pressure flow path 56, the communication channel | path 740, the oil supply chamber 720, the recessed part 120e, and the notch 240a. Further, the back pressure supply mechanism 800 is configured by the back pressure channel 56, the throttle member 61, the coil spring 63, and the stopper 65.

  In this compressor, when the rotating shaft 300 is rotated by the motor mechanism 700, the fixed scroll 120 and the movable scroll 140 are engaged with each other to form the compression chamber 460. Then, the compression chamber 460 moves to the center side while reducing the volume by the revolution mechanism 180. As a result, the compression chamber 460 sucks and compresses the refrigerant gas in the motor chamber 640 and discharges it into the discharge chamber 500.

  Also in this compressor, the refrigerant gas discharged into the discharge chamber 500 is guided to the oil separation chamber 580 to separate the lubricating oil. Then, the lubricating oil flows into the back pressure channel 56 from the inflow port 56a. Thus, in this compressor, the lubricating oil is supplied to the back pressure chamber 480 by the back pressure supply mechanism 800, and the back pressure can be applied to the movable scroll 140.

  Here, as in the compressor of the first embodiment, in this compressor, when the pressure in the discharge chamber 500 and the oil separation chamber 580 is low immediately after the start of operation and the throttle member 61 is in the contact position, the back pressure supply path 101 is the first aperture amount. For this reason, the fluid is not depressurized so much in the back pressure channel 56. Then, the fluid reaches the back pressure chamber 480 from the back pressure channel 56 through the communication passage 740, the oil supply chamber 720, the through hole 120e, and the notch 240a. Thus, even in this compressor, even when the pressure in the discharge chamber 500 and the oil separation chamber 580 is low, the pressure in the back pressure chamber 480 does not decrease excessively, and the back pressure is suitably applied to the movable scroll 140. Can be granted. Thereby, the movable scroll 140 is suitably biased toward the fixed scroll 120 by the pressure of the back pressure chamber 480 and the restoring force of the elastic plate 240.

  Further, when the pressure in the discharge chamber 500 and the oil separation chamber 580 is high and the throttle member 61 moves away from the stopper 65 and moves to the outlet 56b side in the reduced diameter portion 562, the back pressure supply path 101 is the second aperture amount. For this reason, the fluid is decompressed in the back pressure flow path 56 as in the compressor of the first embodiment. For this reason, the pressure in the back pressure chamber 480 can be suitably adjusted by supplying the decompressed fluid to the back pressure chamber 480. Thereby, in this compressor, it is possible to prevent the movable scroll 140 from being excessively biased toward the fixed scroll 120 side.

  Thus, like the compressor of the first embodiment, this compressor makes it difficult for the refrigerant gas to leak from the compression chamber 460 even immediately after the start of operation, so that the compression performance can be improved and the discharge chambers 500 and 580 can be improved. It is possible to reduce power loss when the internal pressure is high. Other functions of this compressor are the same as those of the compressor of the first embodiment.

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

  For example, you may comprise a compressor by combining suitably each structure of the compressor of Examples 1-5.

  In the compressor of the first embodiment, the first throttle amount is determined by the guide passage 620. However, the present invention is not limited to this. For example, the first throttle amount may be determined by making the flow rate of the communication hole 65a in the stopper 65 or the flow rate of the first communication path 615 of the first shaft portion 61b smaller than that of the guide path 620. The same applies to the compressors of Examples 2 to 5.

  Furthermore, in the compressors of the first to fifth embodiments, the second shaft portion 61c of the throttle member 61 is inserted into the lower end of the coil spring 63. However, the present invention is not limited to this, and the coil spring 63 is disposed inside the second shaft portion 61c. It is good also as a structure in which the lower end of is accommodated.

  In the compressors of the first to fourth embodiments, it is sufficient that the shaft hole 4a formed in the first side plate 4 is kept airtight with the rotating shaft 19 as much as possible. In addition to plating, a sliding bearing or a rolling bearing can be employed between the rotary shaft 19 and the shaft holes 4a and 5c.

  The present invention can be used for a vehicle air conditioner or the like.

1, 7, 9, 200 ... housing (1 ... front housing, 7 ... cylinder block, 9 ... rear housing)
4 ... 1st side plate (side plate)
5 ... Second side plate (side plate)
9a, 500 ... discharge chamber (discharge region)
19, 300 ... Rotating shaft 35a ... Oil separation chamber 45 ... Rotor 47a, 47b ... Vane (movable member)
49a, 49b, 400 ... back pressure chambers 50a, 50b, 480 ... compression chamber 56 ... back pressure channel 61 ... throttle member 61a ... main body 63 ... coil spring (biasing member)
65: Stopper 100, 101 ... Back pressure supply path 120 ... Fixed scroll 140 ... Movable scroll (movable member)
561 ... Diameter-enlarged portion 562 ... Reduced-diameter portion 563 ... Tapered portion (step)
562a ... Inner peripheral surface 564a, 611a ... Mountain portion 564b, 611b ... Valley portion 564, 611 ... Spiral groove 562c, 619 ... Sliding contact surface 580 ... Oil separation chamber (discharge region)
610: outer peripheral surface 613, 614, 617 ... concave groove 618 ... through hole (guide passage)
620, 621 ... guide passage

Claims (11)

A housing;
A movable member provided in the housing and defining a compression chamber;
A discharge region that is provided in the housing and discharges the refrigerant compressed in the compression chamber;
A back pressure chamber that is provided on the back side of the movable member and applies a back pressure to the movable member;
A compressor comprising a back pressure supply passage communicating the discharge region and the back pressure chamber;
A throttle member movably provided in the back pressure supply path;
A stopper for restricting movement of the diaphragm member;
A biasing member that biases the throttle member toward the stopper;
The back pressure supply path has an enlarged diameter portion that accommodates the stopper, and a reduced diameter portion that is connected to the enlarged diameter portion with a step and is smaller in diameter than the enlarged diameter portion and accommodates the biasing member. And
A spiral groove is formed on one of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member,
The throttle member is guided by the reduced diameter portion by the differential pressure via the throttle member and moves in the back pressure supply path.
The back pressure supply path is configured such that the spiral groove is throttled when the throttle member moves away from the stopper and moves within the reduced diameter portion, compared to when the throttle member abuts against the stopper. The compressor characterized by having. The spiral groove is formed by a crest provided on one of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member, and a trough continuous with the crest.
2. The compressor according to claim 1, wherein a sliding contact surface that is in sliding contact with the peak portion is formed on the other of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member.   The compressor according to claim 2, wherein the spiral groove is formed on the outer peripheral surface of the throttle member.   The compressor according to claim 2, wherein the spiral groove is formed on the inner peripheral surface of the reduced diameter portion. A guide passage that connects the discharge region side of the throttle member and the back pressure chamber side is formed by the throttle member and the inner peripheral surface of the reduced diameter portion, or by the throttle member,
The compressor according to any one of claims 1 to 4, wherein the back pressure supply path is throttled by the guide path when the throttle member abuts on the stopper.   6. The guide passage according to claim 5, wherein the guide passage is formed in a groove shape on the outer peripheral surface of the throttle member, and is formed by a concave groove communicating with the spiral groove and the inner peripheral surface of the reduced diameter portion. Compressor.   The compressor according to claim 5, wherein the guide passage is formed flat on the outer peripheral surface of the throttle member, and is formed by a concave groove communicating with the spiral groove and the inner peripheral surface of the reduced diameter portion. .   The compressor according to claim 5, wherein the guide passage includes a through hole that opens to the outer peripheral surface of the throttle member so as to be able to communicate with the spiral groove and extends into the throttle member.   The cross-sectional area of the guide passage is larger than the cross-sectional area of the passage formed by the spiral groove and the other of the inner peripheral surface of the reduced diameter portion and the outer peripheral surface of the throttle member, and the guide passage The compressor according to any one of claims 5 to 8, wherein a length is shorter than a length of the spiral groove. A side plate that defines a cylinder chamber in the housing;
A rotating shaft rotatably provided in the housing;
A rotor provided rotatably with the rotating shaft in the cylinder chamber, and having a plurality of vane grooves formed;
The movable member is a vane provided in each vane groove so as to be able to appear and disappear,
The compression chamber is formed by the front surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the rear surface of the cylinder chamber, the outer peripheral surface of the rotor, and the vanes.
The back pressure chamber is provided between the bottom surface of each vane and each vane groove,
The compressor according to any one of claims 1 to 9, wherein the back pressure supply path is formed in the side plate. A rotating shaft rotatably provided in the housing;
A fixed scroll fixed in the housing and forming the discharge region with the housing;
A movable scroll connected to the rotating shaft and disposed opposite to the fixed scroll;
The movable member is the movable scroll;
The compression chamber is formed between the fixed scroll and the movable scroll,
The compressor according to any one of claims 1 to 9, wherein the back pressure supply path is formed in the fixed scroll.

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