JP2018141430A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly adjust a back pressure acting on a vane and to secure lubricity in a vane type compressor.SOLUTION: An oil passing groove 13a extended in a circumferential direction of a rotating shaft 16 is formed on an end face 13s opposed to a rotor 18 of a partition wall 13p, in opposition to the rotor 18. The oil passing groove 13a is formed in a manner that it can be simultaneously opposed to a plurality of back pressure chambers 41, and has a state of being opposed to each back pressure chamber 41 and a state of not being opposed thereto by rotation of the rotating shaft 16. An end face 18f opposed to the partition wall, of the rotor 18 is provided with an oil guide groove 18d extended from a fixing portion 18s to the rotating shaft 16 to an outer peripheral region direction, on at least one space between the back pressure chambers 41. The oil guide groove 18d is disposed to have a state of being opposed to the oil passing groove 13a and a state of not opposed thereto by the rotation of the rotor 16.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vane type compressor.

  JP-A-2014-194177 (Patent Document 1) is a prior document disclosing the configuration of a vane compressor. In the vane type compressor described in Patent Document 1, a rotor is rotatably accommodated in an internal space formed by closing both ends of a cylinder block with side plates, and a vane groove formed on the outer peripheral surface of the rotor Vane is housed in. In the vane type compressor described in Patent Document 1, a back pressure chamber is formed by the bottom surface of the vane and the bottom surface of the vane groove, and lubricating oil is supplied to the back pressure chamber.

JP 2014-194177 A

  Lubricating oil in the back pressure chamber flows out from the gap between the end face of the rotor and the side plate, passes between the rotating shaft and the shaft hole that accommodates the rotating shaft, and lubricates the bearing and the shaft seal device.

  The rotor is pressed in the axial direction by a differential pressure between the front side and the rear side of the rotor. When this differential pressure is large, the rotor is pressed against the side plate, and the gap between the rotor and the side plate is small. It becomes difficult for lubricating oil to pass through. When the lubricating oil passing through the gap between the rotor and the side plate is insufficient, the lubricating oil is not sufficiently supplied to the sliding portion between the rotating shaft and the shaft hole, and acts on the vane in the intake stroke. Since the back pressure does not decrease sufficiently, the power consumption of the vane compressor increases.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a vane type compressor capable of appropriately adjusting the back pressure acting on the vane and ensuring lubricity.

  The vane type compressor based on this invention is provided with a housing, a rotating shaft, a rotor, and a vane. The housing constitutes a cylinder chamber and has a partition wall that partitions the cylinder chamber. The rotating shaft is supported by the partition wall and is rotatably provided in the cylinder chamber. The rotor is fixed to the rotating shaft. A plurality of vane grooves are formed on the outer periphery of the rotor. The vane is attached to each of the plurality of vane grooves so as to appear and retract. A plurality of compression chambers are defined in the cylinder chamber by a rotor and a vane. A back pressure chamber is defined in the rotor by the bottom of the vane groove and the vane. An oil passage groove extending in the circumferential direction of the rotation shaft is formed on the partition wall so as to face the rotor on the end face facing the rotor. The oil passage groove can be opposed to a plurality of back pressure chambers at the same time, and is provided so as to have a state of facing the back pressure chambers and a state of not facing the back pressure chambers by rotation of the rotation shaft. In the rotor, an oil guide groove extending in the direction of the outer peripheral region from a fixed portion to the rotating shaft is formed in at least one of the back pressure chambers on the end surface facing the partition wall. The oil guide groove is provided so as to have a state facing the oil passage groove and a state not facing the oil passage groove by rotation of the rotor.

  In one embodiment of the present invention, the oil guide groove has a groove shape inclined toward the front in the rotational direction of the rotor so as to draw the lubricating oil toward the center of the rotation shaft.

  In one form of this invention, the communication space is provided between the partition wall and the rotating shaft. The oil guiding groove always faces the communication space.

  In one embodiment of the present invention, a plurality of oil guiding grooves are provided. The oil passage groove always faces at least one of the plurality of oil guide grooves.

  In one form of the present invention, the oil guiding groove is formed one by one between all the back pressure chambers adjacent to each other in the circumferential direction of the rotating shaft.

  In one embodiment of the present invention, a plurality of oil passage grooves are formed and extend in an arc shape.

  According to the present invention, in the vane type compressor, it is possible to properly adjust the back pressure acting on the vane and ensure lubricity.

It is sectional drawing which shows the structure of the vane type compressor which concerns on one Embodiment of this invention. It is sectional drawing which looked at the vane type compressor of FIG. 1 from the II-II line arrow direction. It is sectional drawing which looked at the vane type compressor of FIG. 1 from the III-III line arrow direction. It is a top view which shows the structure of the rotor with which the vane type compressor which concerns on one Embodiment of this invention is provided.

  Hereinafter, a vane type compressor according to an embodiment of the present invention will be described with reference to the drawings. In the following description, the same or corresponding parts in the drawings are denoted by the same reference numerals, and the description thereof will not be repeated.

  FIG. 1 is a cross-sectional view showing a configuration of a vane type compressor according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the vane type compressor of FIG. 1 viewed from the direction of arrows II-II. 3 is a cross-sectional view of the vane type compressor of FIG. 1 viewed from the direction of arrows III-III. A vane type compressor according to an embodiment of the present invention is mounted on a vehicle and used for an air conditioner of the vehicle.

  In the following description, the left direction in the drawing of the vane type compressor 10 shown in FIG. 1 is referred to as the front, and the right direction in the drawing of the vane type compressor 10 shown in FIG. In the following description, the axial direction, the radial direction, and the circumferential direction indicate the axial direction, the radial direction, and the circumferential direction of the rotating shaft 16 and the rotor 18 that are rotating bodies.

  As shown in FIGS. 1 to 3, a housing 11 of a vane compressor 10 according to an embodiment of the present invention includes a bottomed cylindrical rear housing 12 and a front housing coupled to a front end surface of the rear housing 12. 13. The material of the rear housing 12 and the front housing 13 is, for example, metal.

  The front housing 13 has a cylindrical cylinder portion 14 and a bottom wall portion 13p that closes the internal space of the cylinder portion 14. The cylindrical cylinder portion 14 extends from the bottom wall portion 13p. The inner peripheral surface 14c of the cylinder part 14 is formed in an elliptical shape. The cylinder portion 14 has an open end that is open to the side opposite to the bottom wall portion 13p side. The bottom wall portion 13p and the cylinder portion 14 are integrally formed. The front housing 13 is formed in a bottomed cylindrical shape. The bottom wall portion 13p constitutes a first partition wall.

  A shaft hole 13h through which the rotary shaft 16 is inserted is provided in the bottom wall portion 13p. A bearing surface is formed on the bottom wall portion 13p by the shaft hole 13h. A sliding layer 13 c made of tin plating is formed on at least one of the bearing surface of the shaft hole 13 h and the outer peripheral surface of the rotating shaft 16. A front side sliding portion is constituted by the bearing surface of the shaft hole 13 h and the outer peripheral surface of the rotating shaft 16.

  The cylinder portion 14 is accommodated in the rear housing 12. The rear housing 12 has a peripheral wall 12a. A rear side plate 15 is disposed to face the open end of the cylinder portion 14. The rear side plate 15 is fixed to the open end of the cylinder portion 14 using bolts (not shown). The rear side plate 15 constitutes a second partition wall.

  The rear side plate 15 is provided with a shaft hole 15h through which the rotation shaft 16 is inserted. A bearing surface is formed on the rear side plate 15 by the shaft hole 15h. A sliding layer 15 c made of tin plating is formed on at least one of the bearing surface of the shaft hole 15 h and the outer peripheral surface of the rotating shaft 16. The bearing surface of the shaft hole 15 h and the outer peripheral surface of the rotary shaft 16 constitute a rear side sliding portion.

  The front housing 13 and the rear side plate 15 support the rotating shaft 16 in a rotatable manner. The rotating shaft 16 passes through the cylinder portion 14. A lip seal type shaft seal device 17 a is provided in the accommodation space 13 t between the rotary shaft 16 and the front housing 13. The shaft seal device 17 a prevents the refrigerant gas from leaking along the peripheral surface of the rotating shaft 16.

  The bottom wall portion 13p has one end face 13s that partitions the cylinder chamber 14d. The end face 13s faces rearward. The rear side plate 15 has the other end surface 15s that partitions the cylinder chamber 14d. The end face 15s faces the front. One end face 13s and the other end face 15s are provided in parallel with a space therebetween and face each other.

  A cylinder chamber 14d is defined by the cylindrical cylinder portion 14, the bottom wall portion 13p, and the rear side plate 15. In the cylinder chamber 14d, a rotor 18 having a cylindrical shape is attached to the rotary shaft 16 so as to be integrally rotatable.

  FIG. 4 is a plan view showing a configuration of a rotor included in the vane type compressor according to the embodiment of the present invention. In FIG. 4, the rotor 18 is viewed from the front side in the axial direction of the rotating shaft 16.

  As shown in FIGS. 1 and 4, the rotor 18 is fixed to the rotating shaft 16. The front end surface 18f of the rotor 18 faces the end surface 13s of the bottom wall portion 13p. The rear end surface 18r of the rotor 18 faces the end surface 15s of the rear side plate 15. A portion of the front end surface 18f of the rotor 18 that is fixed to the rotating shaft 16 is defined as a fixed portion 18s. The rotating shaft 16 is reduced in diameter from the outer peripheral surface of the portion sliding with the bearing surface of the shaft hole 13 h toward the fixing portion 18 s, and the outer peripheral surface of the reduced diameter portion of the rotating shaft 16 is fixed to the rotor 18. The communication space 13r is defined by the portion 18s, the front end face 18f of the rotor 18, and the shaft hole 13h.

  As shown in FIGS. 2 to 4, a plurality of vane grooves 18 a are formed on the outer peripheral surface 18 c of the rotor 18 so as to extend radially. On the radially inner side of each of the plurality of vane grooves 18a, a bottom portion 18ab having an expanded groove width is formed. The bottom portion 18ab of the vane groove 18a is formed in a substantially circular shape when viewed in the axial direction.

  One vane 19 is mounted in each of the plurality of vane grooves 18a so as to be able to appear and retract. Lubricating oil in a discharge area 35 described later is supplied to each of the plurality of vane grooves 18a.

  As the rotary shaft 16 rotates, the rotor 18 rotates and some of the plurality of vanes 19 are pushed out of the vane groove 18a. When the tip surface of the vane 19 comes into contact with the inner peripheral surface 14c of the cylinder portion 14, the outer peripheral surface 18c of the rotor 18, the inner peripheral surface 14c of the cylinder portion 14, the pair of adjacent vanes 19, and the end surface of the bottom wall portion 13p. A compression chamber 21 is defined between 13 s and the end surface 15 s of the rear side plate 15.

  The outer peripheral surface 18 c of the rotor 18 forms a wall surface on the inner peripheral side of the compression chamber 21. The inner peripheral surface 14 c of the cylinder portion 14 forms a wall surface on the outer peripheral side of the compression chamber 21. The end surface 13 s of the bottom wall portion 13 p forms a wall surface on the front side of the compression chamber 21. An end surface 15 s of the rear side plate 15 forms a wall surface on the rear side of the compression chamber 21. In the present embodiment, as shown in FIGS. 2 and 3, a plurality of compression chambers 21 are partitioned.

  The compression chamber 21 is formed in the cylinder chamber 14d. Regarding the rotation direction R of the rotor 18, the stroke in which the compression chamber 21 expands the volume is the suction stroke, and the stroke in which the compression chamber 21 decreases the volume is the compression stroke.

  As shown in FIGS. 1 and 2, the rear housing 12 is formed with a suction port 22 penetrating the peripheral wall 12a. A joint portion 24 is connected to the outer peripheral portion of the suction port 22. A suction pipe 25 is connected to the joint portion 24. The refrigerant gas flows into the suction port 22 via the suction pipe 25. The suction port 22 forms a refrigerant passage through which the refrigerant passes. A check valve (not shown) that prevents the refrigerant from flowing backward is provided in the suction port 22.

  A concave portion 14 a is formed on the outer peripheral surface of the cylinder portion 14 over the entire circumference in the circumferential direction of the cylinder portion 14. The suction space 20 is defined by the recess 14 a and the inner peripheral surface of the rear housing 12. The suction space 20 communicates with the suction port 22. The cylinder portion 14 cooperates with the inner peripheral surface of the rear housing 12, and defines a suction space 20 in the rear housing 12. The suction space 20 is formed between the cylinder portion 14 and the rear housing 12 in the radial direction of the rotary shaft 16.

  As shown in FIG. 2, the suction space 20 is formed in an annular shape between the cylinder portion 14 and the rear housing 12, and extends in the circumferential direction. The suction space 20 and the accommodation space 13t are communicated with each other through the communication path 13b.

  In the axial direction of the rotating shaft 16, the suction space 20 and the suction port 22 are disposed at positions overlapping the compression chamber 21. The cylinder portion 14 is formed with a pair of suction holes 23 that communicate with the suction space 20. During the suction stroke, the compression chamber 21 and the suction space 20 communicate with each other through the suction hole 23. The suction hole 23 penetrates the cylinder portion 14 in the radial direction. The suction hole 23 opens to the inner peripheral surface 14 c of the cylinder portion 14 and opens to the suction space 20.

  The suction hole 23, the suction space 20, and the suction port 22 are formed on the radially outer side with respect to the compression chamber 21. The inside of each of the suction hole 23, the suction space 20, the suction port 22, and the accommodation space 13t is a suction pressure atmosphere region. The bottom wall portion 13p defines a suction pressure atmosphere region.

  As shown in FIGS. 1 and 3, a pair of recesses 14 b are formed in the outer peripheral surface of the cylinder portion 14. The pair of recesses 14b are located on opposite sides of the rotating shaft 16. Each concave portion 14b includes an extended surface 141b extending from the outer peripheral surface of the cylinder portion 14 toward the rotation shaft 16, and an attachment surface 142b that intersects the extended surface 141b and extends toward the outer peripheral surface of the cylinder portion 14. Is formed.

  A pair of discharge chambers 30 is defined by the extended surface 141 b, the mounting surface 142 b, and the inner peripheral surface of the rear housing 12. The discharge chamber 30 is located between the cylinder portion 14 and the rear housing 12 in the radial direction. The cylinder portion 14 is formed with a discharge port 31 that opens to the attachment surface 142 b and communicates the compression chamber 21 and the discharge chamber 30. The discharge port 31 is opened and closed by a discharge valve 32 attached to the attachment surface 142b. The refrigerant gas compressed in the compression chamber 21 pushes out the discharge valve 32 and is discharged into the discharge chamber 30 via the discharge port 31.

  The discharge chamber 30 is located behind the suction space 20. The suction space 20 and the discharge chamber 30 are formed at different positions in the axial direction. The suction space 20 is located closer to the bottom wall portion 13p than the discharge chamber 30 is. The discharge chamber 30 is located closer to the rear side plate 15 than the suction space 20.

  As shown in FIGS. 2 and 3, a back pressure chamber 41 is formed between the bottom surface of each vane 19 accommodated in each vane groove 18 a and the bottom surface of each vane groove 18 a. A plurality of back pressure chambers 41 are defined by one end surface 13s of the bottom wall portion 13p, the other end surface 15s of the rear side plate 15, the bottom portions 18ab of each of the plurality of vane grooves 18a, and the plurality of vanes 19.

  The strength of the force with which the vane 19 is pressed against the inner peripheral surface 14c of the cylinder part 14 is mainly the pushing force by which the vane 19 is pushed to the outer peripheral side by the back pressure of the back pressure chamber 41 and the centrifugal force acting on the vane 19. This is the difference between the pushing back force that pushes the vane 19 back toward the center of the rotating shaft 16 by the pressure of the refrigerant gas in the compression chamber 21, and due to the balance between the pushing force and the pushing back force, the vane 19 is against the vane groove 18a. Infest.

  Each of the plurality of back pressure chambers 41 is provided so as to be able to communicate with a back pressure supply hole 15 e described later formed in the rear side plate 15. Each of the plurality of back pressure chambers 41 repeats a state of facing the back pressure supply hole 15e and a state of not facing the back pressure supply hole 15e as the rotating shaft 16 rotates. Lubricating oil is supplied to each of the plurality of back pressure chambers 41 from the back pressure supply hole 15e when facing the back pressure supply hole 15e.

  The back pressure chamber 41 in a state facing the back pressure supply hole 15 e is located at a position corresponding to the discharge stroke of the vane compressor 10. In the discharge stroke, it is necessary to reliably partition the compression chamber 21 while maintaining a high back pressure in the back pressure chamber 41.

  As shown in FIGS. 1 and 2, a plurality of oil passage grooves 13 a that are separated from each other in the circumferential direction are formed on the end surface 13 s of the bottom wall portion 13 p so as to face the rotor 18. Each of the plurality of oil passage grooves 13a extends in the circumferential direction so as to connect the back pressure chambers 41 adjacent to each other in the circumferential direction. That is, the oil passage groove 13a can simultaneously face the plurality of back pressure chambers 41, and the plurality of adjacent back pressure chambers 41 are formed so as to communicate with each other through the oil passage groove 13a.

  In the present embodiment, as shown in FIG. 2, each of the two oil passage grooves 13 a extends in an arc shape around the axis O that forms the rotation center of the rotating shaft 16 and the rotor 18. The number of oil passage grooves 13a is not limited to two and may be three or more. Alternatively, one C-shaped oil passage groove 13a that is not continuous may be formed.

  A flat portion 13ac is located between the two oil passage grooves 13a on the end surface 13s of the bottom wall portion 13p. Each of the plurality of back pressure chambers 41 repeats the state facing the oil passage groove 13a and the state not facing the oil passage groove 13a by the rotation of the rotating shaft 16. The back pressure chamber 41 facing the flat portion 13ac is at a position corresponding to the discharge stroke of the vane compressor 10.

  The oil passage groove 13a allows the lubricating oil to go back and forth between the plurality of back pressure chambers 41 facing each other. Specifically, in the compression stroke, the vane 19 receives stress from the inner peripheral surface 14c of the cylinder portion 14 and moves inward in the radial direction. Pressure acts on the lubricating oil in the back pressure chamber 41 from the bottom surface of the vane 19 that moves into the vane groove 18a. At this time, the lubricating oil flows out from the back pressure chamber 41 and flows into the back pressure chamber 41 having a relatively low pressure through the oil passage groove 13a. In this way, the pressure in the back pressure chamber 41 can be adjusted by the oil passage groove 13a.

  As shown in FIGS. 1, 2, and 4, at the front end face 18 f of the rotor 18, at least one of the back pressure chambers 41 that are adjacent to each other in the circumferential direction of the rotary shaft 16 is disposed on the rotary shaft 16. An oil guide groove 18d extending radially from the fixed portion 18s to which the is fixed to the outer peripheral region is formed. The radial means that it extends from the axial center side of the rotating shaft 16 in the outer peripheral direction of the rotating shaft 16 and extends strictly radially or radially from the axis of the rotating shaft 16. It does not mean only. The shape of the oil guide groove 18d is a rectangular shape in the present embodiment, but is not limited to a rectangular shape, and may be an arc shape or the like.

  In the present embodiment, one oil guiding groove 18 d is formed between all back pressure chambers 41 adjacent to each other in the circumferential direction of the rotating shaft 16. The oil guide groove 18 d extends while being inclined with respect to the radial direction of the rotor 18 so that the lubricating oil is drawn from the rotor 18 toward the center of the rotary shaft 16 by the rotation of the rotary shaft 16. The distance from the outer periphery of the rotating shaft 16 decreases from the front side to the rear side in the rotation direction R. The oil guide groove 18 d is provided so as to always face the communication space 13 r formed around the rotation shaft 16. The lubricating oil is guided to the sliding portion between the bottom wall portion 13p and the rotating shaft 16 through the oil guide groove 18d and the communication space 13r.

  A part of the oil guide groove 18d repeats the state facing the oil passage groove 13a and the state not facing the oil passage groove 13a as the rotating shaft 16 rotates. The oil passage groove 13a always faces at least one of the plurality of oil guide grooves 18d. The lubricating oil that has flowed into the oil guide groove 18 d from the oil passage groove 13 a moves in the oil guide groove 18 d and flows so as to approach the outer periphery of the rotating shaft 16. The lubricating oil that has flowed so as to approach the outer periphery of the rotating shaft 16 by the oil guide groove 18d is supplied to the sliding portion between the shaft hole 13h of the bottom wall portion 13p and the rotating shaft 16.

  As shown in FIG. 1, a discharge port 34 is formed on the peripheral wall 12 a of the rear housing 12. A joint portion 38 is connected to the discharge port 34. A discharge pipe 39 extending toward the outside of the vane compressor 10 is connected to the joint portion 38.

  A discharge region 35 is defined by a rear side plate 15 on the rear side of the rear housing 12. An oil separator 36 is disposed in the discharge region 35. The oil separator 36 is provided to separate the lubricating oil contained in the refrigerant gas. The oil separator 36 has a bottomed cylindrical case 36a. A cylindrical oil separation cylinder 36b is fitted and fixed to the opening side of the case 36a.

  An oil passage 36c is formed in the lower part of the case 36a. The oil passage 36c communicates the inside of the case 36a with the bottom side of the discharge region 35. As shown in FIGS. 1 and 3, a communication passage 37 is formed in the rear side plate 15 and the case 36a. The communication path 37 communicates the discharge chamber 30 and the inside of the case 36a. An oil supply passage 15 d is formed in the rear side plate 15.

  An intermediate chamber 40 is defined at the rear end of the rotary shaft 16 by the rear side plate 15 and the case 36a. A rotation path 42 is formed on the outer peripheral surface of the rotation shaft 16. An annular groove 43 is recessed in the bearing surface of the shaft hole 15h. A back pressure supply hole 15 e is formed in the rear side plate 15 along the axial direction of the rotary shaft 16 so as to communicate with the annular groove 43. The oil supply passage 15 d, the intermediate chamber 40, the rotation path 42, the annular groove 43, and the back pressure supply hole 15 e serve as a back pressure supply path that supplies back pressure to the back pressure chamber 41. The lubricating oil stored on the bottom side of the discharge region 35 is guided to the back pressure chamber 41 through the back pressure supply path.

  The inside of each of the discharge chamber 30, the communication path 37, the discharge area 35, and the back pressure supply path is a discharge pressure atmosphere area that is higher than the suction pressure atmosphere area. The rear side plate 15 defines a discharge pressure atmosphere region.

  Hereinafter, the operation of the vane compressor 10 will be described. When the rotating shaft 16 rotates, the rotor 18 rotates and the refrigerant gas is sucked into the suction space 20 from the outside of the vane compressor 10 via the suction port 22. The refrigerant gas sucked into the suction space 20 is sucked into the compression chamber 21 during the suction stroke via the suction hole 23. The refrigerant gas sucked into the compression chamber 21 is compressed as the volume of the compression chamber 21 decreases as the rotor 18 rotates. The compressed refrigerant gas is discharged from the compression chamber 21 to the discharge chamber 30 via the discharge port 31.

  The refrigerant gas in the discharge chamber 30 flows out into the case 36a through the communication passage 37 and is sprayed on the outer peripheral surface of the oil separation cylinder 36b, and in the case 36a while turning around the outer peripheral surface of the oil separation cylinder 36b. Guided downward. At this time, the lubricating oil is separated from the refrigerant gas by centrifugation. The lubricating oil separated from the refrigerant gas moves to the bottom side of the case 36a and is stored at the bottom of the discharge region 35 through the oil passage 36c.

  The lubricating oil stored at the bottom of the discharge region 35 is guided to the back pressure chamber 41 from the oil supply passage 15d through the back pressure supply hole 15e. The vane 19 is pushed out to the outer peripheral side by the pressure of the lubricating oil in the back pressure chamber 41. The compression chamber 21 is partitioned by the vane 19 pushed to the outer peripheral side. The sliding portion between the vane 19 and the vane groove 18 a is lubricated by the lubricating oil guided to the back pressure chamber 41. The lubricating oil guided to the back pressure chamber 41 is supplied to the sliding portion between the bottom wall portion 13p and the rotating shaft 16 through the oil passage groove 13a and the oil guiding groove 18d. The sliding portion between the rotor 18 and the bottom wall portion 13p is lubricated by the lubricating oil supplied into the oil passage groove 13a. The sliding portion is lubricated by the lubricating oil supplied to the sliding portion between the bottom wall portion 13p and the rotating shaft 16.

  In the oil separator 36, the refrigerant gas from which the lubricating oil has been separated moves upward in the oil separation cylinder 36 b and is discharged to the outside of the vane type compressor 10 through the discharge port 34.

  In the vane compressor 10 of the present embodiment, as shown in FIG. 1, an oil passage groove 13 a is formed on the end surface 13 s of the bottom wall portion 13 p, and an oil guide groove 18 d is formed on the front end surface 18 f of the rotor 18. . The lubricating oil in the back pressure chamber 41 can be supplied to the sliding portion between the bottom wall portion 13p and the rotating shaft 16 through the oil passage groove 13a and the oil guide groove 18d.

  The rotor 18 is pressed in the axial direction by a differential pressure between the front side and the rear side of the rotor 18, and a gap between the rotor 18 and the rear side plate 15 or a gap between the rotor 18 and the bottom wall portion 13 p is generated. In some cases, the supply path of the lubricating oil to the rotating shaft 16 becomes narrow. In particular, when the vane compressor 10 is restarted from a stopped state, the rotor 18 is pressed forward mainly by the discharge pressure of the discharge region 35, and the gap between the rotor 18 and the bottom wall portion 13p is reduced. There is. Even in such a case, the vane compressor 10 of the present embodiment can sufficiently supply lubricating oil to the rotating shaft 16 by providing the oil guide groove 18d.

  In particular, since the sliding portion between the bottom wall portion 13p and the rotating shaft 16 is located away from the discharge region 35 where the lubricating oil is stored, it is a place where the lubricating oil is difficult to be supplied. By providing 18d, the lubricity of the sliding part between the bottom wall part 13p and the rotating shaft 16 can be ensured.

  When the pressing force pressing the tip of the vane 19 against the inner peripheral surface of the cylinder chamber 14d is too weak, leakage of refrigerant gas or chattering from the gap between the cylinder chamber 14d and the vane 19 to the adjacent compression chamber 21 occurs. There is. On the contrary, when the pressing force of the vane 19 is too strong, an increase in power consumption of the vane compressor 10 or wear of the inner peripheral surface 14c of the cylinder portion 14 or the vane 19 may occur. Therefore, the pressing force of the vane 19 needs to be maintained at an appropriate strength.

  In a state where the pressure in the compression chamber 21 is low, for example, in the initial stage of the suction stroke or the compression stroke, the pushing back force received by the vane 19 is low, so the pushing force of the vane 19 becomes high, and the power consumption of the vane compressor 10 is increased. Becomes larger.

  A suction stroke or compression connected to the oil passage groove 13a by guiding the lubricating oil in the oil passage groove 13a to the sliding portion between the bottom wall portion 13p and the rotating shaft 16 by the oil guide groove 18d. The back pressure of the back pressure chamber 41 in the process can be lowered. Thereby, it can suppress that the power consumption of the vane type compressor 10 becomes large.

  As another means for ensuring the lubricity of the sliding portion between the bottom wall portion 13p and the rotating shaft 16, the end surface 13s of the bottom wall portion 13p is provided in a concave curved surface shape, or the width of the oil passage groove 13a is increased. It is also possible to do. In these cases, the recessed portion of the end surface 13s of the bottom wall portion 13p and the back pressure chamber 41 always face each other, and the lubricating oil easily leaks from the back pressure chamber 41 into the gap between the rotor 18 and the bottom wall portion 13p. Therefore, it is difficult to obtain a high back pressure necessary during the discharge stroke, which is not preferable.

  In the vane type compressor 10 according to the present embodiment, by providing the oil guide groove 18d on the front end face 18f of the rotor 18, the reduction of the back pressure to the vane 19 in the discharge stroke is suppressed while improving the lubricity. It is possible to reduce the back pressure to the vane 19 in the intake stroke or the compression stroke. Thus, the vane type compressor 10 can achieve both proper adjustment of the back pressure and lubrication of the sliding portion around the rotating shaft 16.

  The oil guide groove 18 d extends while being inclined with respect to the radial direction of the rotor 18 so that the lubricating oil is drawn from the rotor 18 toward the center of the rotary shaft 16 by the rotation of the rotary shaft 16. Therefore, the lubricating oil drawn into the oil guiding groove 18d from the oil passage groove 13a by the rotation of the rotor 18 is effectively supplied to the sliding portion between the bottom wall portion 13p and the rotating shaft 16.

  The oil guide groove 18 d is provided so as to have a state of facing the back pressure chambers 41 and a state of not facing the back pressure chambers 41 by the rotation of the rotor 18. The oil guide groove 18 d is provided so as to have a state of facing the oil passage groove 13 a and a state of not facing the oil passage groove 13 a by the rotation of the rotor 18.

  That is, the back pressure chamber 41, the oil guide groove 18d, and the oil passage groove 13a are intermittently connected. The oil passage groove 13a has a state in which it is periodically blocked from the back pressure chamber 41, and the oil guide groove 18d has a state in which it is periodically cut off from the oil passage groove 13a. Compared to the case where the back pressure chamber 41 is always connected and the oil guide groove 18d is always connected to the oil passage groove 13a, excessive outflow of lubricating oil into the oil guide groove 18d is suppressed, and the vane type compression is performed. The power consumption of the machine 10 can be reduced.

  In the description so far, the example in which the bottom wall portion 13p and the cylinder portion 14 are integrally formed has been described. Instead of this example, the bottom wall portion 13p is formed as a front side plate separately from the cylinder portion 14, and the cylinder portion 14 is provided between the front side plate and the rear side plate 15 that are spaced apart in the axial direction. It is good also as a structure to arrange.

  The oil guide groove 18d is not limited to the case where the oil guide groove 18d is open to the shaft hole 13h of the bottom wall portion 13p, and the oil guide groove 18d may be separated from the shaft hole 13h. Since a differential pressure is generated between the shaft hole 13h that is the suction pressure atmosphere region and the back pressure chamber 41, the oil guide groove 18d toward the sliding portion between the bottom wall portion 13p and the rotary shaft 16 is provided. Should be extended.

  Further, the oil guide groove 18 d may extend from the outer edge of the oil passage groove 13 a to the outer peripheral side in the range inside the outer edge of the rotor 18. In this case, more lubricating oil can be supplied between the bottom wall portion 13p and the front end face 18f of the rotor 18. A bearing may be provided in a sliding portion between the bottom wall portion 13p and the rotary shaft 16.

  It should be thought that embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  10 vane type compressor, 11 housing, 12 rear housing, 12a peripheral wall, 13 front housing, 13a oil passage groove, 13b, 37 communication path, 13c, 15c sliding layer, 13h, 15h shaft hole, 13p bottom wall, 13r Communication space, 13s, 15s end face, 13t accommodation space, 14 cylinder part, 14a, 14b recess, 14c inner peripheral face, 14d cylinder chamber, 15 rear side plate, 15d oil supply passage, 15e back pressure supply hole, 16 rotating shaft, 17a Shaft seal device, 18 rotor, 18a vane groove, 18ab bottom, 18c outer peripheral surface, 18d oil guide groove, 18f front end surface, 18r rear end surface, 18s fixing part, 19 vane, 20 suction space, 21 compression chamber, 22 suction port, 23 Suction hole, 24, 38 Joint part, 25 Suction pipe, 30 Discharge chamber , 31 Discharge port, 32 Discharge valve, 34 Discharge port, 35 Discharge area, 36 Oil separator, 36a Case, 36b Oil separation cylinder, 36c Oil passage, 39 Discharge piping, 40 Intermediate chamber, 41 Back pressure chamber, 42 Rotation path , 43 annular groove, 141b extending surface, 142b mounting surface, O axis, R direction of rotation.

Claims (6)

A housing that forms a cylinder chamber and has a partition wall that partitions the cylinder chamber;
A rotating shaft supported by the partition wall and rotatably provided in the cylinder chamber;
A rotor fixed to the rotating shaft and having a plurality of vane grooves formed on the outer periphery;
A vane attached to each of the plurality of vane grooves so as to be able to appear and disappear,
In the cylinder chamber, a plurality of compression chambers are partitioned by the rotor and the vane,
In the rotor, a back pressure chamber is defined by the bottom of the vane groove and the vane,
In the partition wall, an oil passage groove extending in a circumferential direction of the rotating shaft is formed on an end surface facing the rotor so as to face the rotor.
The oil passage groove can be simultaneously opposed to the plurality of back pressure chambers, and is provided so as to have a state of facing the back pressure chambers and a state of not facing the back pressure chambers by rotation of the rotating shaft. ,
In the rotor, an oil guide groove extending in an outer peripheral region direction from a fixed portion to the rotating shaft is formed in at least one of the back pressure chambers on an end surface facing the partition wall. ,
The oil guide groove is a vane type compressor provided so as to have a state of facing the oil passage groove and a state of not facing the oil passage groove by rotation of the rotor.   2. The vane-type compression according to claim 1, wherein the oil guide groove has a groove shape inclined toward the front in the rotation direction of the rotor so as to draw lubricating oil from the rotor toward the center of the rotation shaft. Machine. A communication space is provided between the partition wall and the rotation shaft;
The vane type compressor according to claim 1 or 2, wherein the oil guide groove is always opposed to the communication space. A plurality of the oil guiding grooves are provided,
4. The vane type compressor according to claim 1, wherein the oil passage groove is always opposed to any one of at least one of the plurality of oil guide grooves. 5.   5. The oil guiding groove according to claim 1, wherein one oil guiding groove is formed between all the back pressure chambers adjacent to each other in a circumferential direction of the rotating shaft. The vane type compressor as described.   The vane type compressor according to any one of claims 1 to 5, wherein a plurality of the oil passage grooves are formed and extend in an arc shape.

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