JP2018168801A - Vane type compressor - Google Patents

Abstract

To obtain a vane type compressor which enables reduction of power loss and improvement of quietness.SOLUTION: A vane type compressor includes: a housing formed with a discharge chamber and a cylinder chamber; a rotary shaft 19 rotatably provided in the housing; a rotor 41 which is provided in the cylinder chamber and formed with multiple vane grooves 41A and in which a housing part 42 which is recessed while including the rotary shaft is formed on at least one axial end surface; vanes 51 which are provided at each of the multiple vane grooves so as to extend and retract; and a ring part which is disposed in the housing part so as to surround a periphery of the rotary shaft and deflects to elastically press the vanes. The ring part includes: an outer ring-like member 62 which contacts with the vanes; and an inner ring-like member 61 which is formed by a member made of a material different from the outer ring-like member 62 and disposed at the inner periphery side of the outer ring-like member 62. The inner ring-like member 61 has an elastic pressing force larger than the outer ring-like member 62.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vane type compressor.

  As disclosed in Patent Document 1 below, in a vane type compressor, a cylinder chamber is formed in a housing, and a rotor is rotatably disposed in the cylinder chamber. A plurality of vane grooves are formed around the rotor, and the vanes are arranged in the vane grooves so as to be able to appear and disappear. A compression chamber is defined between the outer peripheral surface of the rotor, the inner peripheral surface of the cylinder chamber, and two vanes adjacent in the rotational direction.

  When the rotor rotates, the vane moves radially outward under the action of centrifugal force, and the radially outer end of the vane comes into sliding contact with the inner peripheral surface of the cylinder chamber. During the compression stroke and the discharge stroke, a high compression pressure acts on the vane, and a part of the compression pressure urges the vane toward the inside in the radial direction. If a gap is formed between the radially outer end of the vane and the inner peripheral surface of the cylinder chamber, pressure loss and chattering occur, which causes noise and a decrease in discharge capacity. On the other hand, if the vane is in contact with the inner peripheral surface of the cylinder chamber with excessive pressure, the vane and the inner peripheral surface are worn, and the power loss increases.

  In the vane type compressor disclosed in Patent Document 1, a recess is formed on the end surface in the axial direction of the rotor, and a ring made of a spring material is disposed in the recess. The ring is in contact with the radially inner end of the vane and biases the vane radially outward. Patent Document 1 states that since the ring always urges the vane radially outward, a good seal is always provided between the radially outer end of the vane and the inner circumferential surface of the cylinder chamber.

JP 61-065086 A

  If the contact pressure between the radially outer end of the vane and the inner peripheral surface of the cylinder chamber is too small, chattering will occur and the discharge capacity will decrease, and if it is too large, wear and power loss will occur on the vane and inner peripheral surface. Increase. Assuming that the contact pressure that can satisfy both of these conditions is the required contact pressure, the compression pressure acting on the vane gradually increases as it advances from the compression stroke toward the discharge stroke (increases until the discharge pressure is reached). Therefore, the necessary contact pressure gradually increases.

  It is assumed that the necessary contact pressure that varies depending on the stroke is realized by one ring made of a spring material as in the configuration disclosed in Patent Document 1, for example. Here, the elastic pressing force generated in one ring increases and decreases in a substantially linear function. Therefore, the spring constant of the ring needs to be adjusted to the highest value of the required contact pressure (for example, the required contact pressure immediately before the transition from the compression stroke to the discharge stroke) from the viewpoint of preventing the discharge capacity from being lowered.

  The required contact pressure immediately after the start of the suction stroke is small. When a ring having a high spring constant is adopted, there is a possibility that the vane forming the compression chamber is pressed against the inner peripheral surface of the cylinder chamber with a contact pressure more than necessary during the suction stroke. On the other hand, from the viewpoint of preventing wear on the vane and the inner peripheral surface, when the spring constant of the ring is adjusted to a low value of the required contact pressure, sufficient sealing performance is obtained immediately before the transition from the compression stroke to the discharge stroke. It may not be obtained.

  An object of the present invention is to provide a vane-type compressor that has been created in view of the above circumstances and has a configuration capable of preventing chattering and reducing power loss.

  A vane type compressor according to the present invention includes a housing in which a discharge chamber and a cylinder chamber are formed, a rotating shaft that is rotatably provided in the housing, and a rotating shaft that is rotatable with the rotating shaft in the cylinder chamber. Each of the plurality of vane grooves, and a vane provided so as to be able to appear and retract in each of the plurality of vane grooves, and at least one end face in the axial direction. And a ring part that elastically presses the vane by being bent, and is provided so as to contact the vane and give a pressing force. The outer ring-shaped member and the outer ring-shaped member are made of different materials and are arranged on the inner peripheral side of the outer ring-shaped member. To include an inner ring-shaped member which gives a pressing force to the outer ring-shaped member in contact with the outer ring member, the inner ring-shaped member has a large elastic pressing force than the outer ring member.

  In the vane compressor, preferably, the outer ring-shaped member is made of resin, and the inner ring-shaped member is made of metal.

  In the vane compressor, preferably, the inner ring-shaped member has a C-shape.

  In the vane type compressor, preferably, a back pressure chamber is formed between the radially inner end of the vane and the vane groove, and the housing portion is connected to the back pressure chamber.

  Preferably, in the vane compressor, a back pressure flow path that connects the discharge chamber and the back pressure chamber is formed in the rotating shaft and the rotor.

  According to the vane type compressor, when the vane is deeply buried in the vane groove, the elastic pressing force of the inner ring-shaped member acts on the vane so as to be superimposed on the elastic pressing force of the outer ring-shaped member. Thus, chattering can be prevented and power loss can be reduced.

It is sectional drawing which shows the vane type compressor 100 in embodiment. It is arrow sectional drawing along the II-II line in FIG.

  Hereinafter, embodiments will be described with reference to the drawings. The same parts and corresponding parts are denoted by the same reference numerals, and redundant description may not be repeated.

(Vane type compressor 100)
FIG. 1 is a cross-sectional view showing a vane type compressor 100 in the embodiment. The vane compressor 100 includes a motor housing 1, a motor mechanism 3, side plates 4 and 5, a cylinder block 7, a cover 9, and a compression mechanism 13. The motor housing 1, the side plates 4, 5, the cylinder block 7, and the cover 9 constitute a vane compressor 100 housing.

  In the following description, the motor housing 1 side that is the left side of FIG. 1 is the front side, and the cover 9 side that is the right side of FIG. 1 is the rear side. The upper side in FIG. 1 is the upper side, and the lower side in FIG. 1 is the lower side. These front and rear directions and up and down directions are examples. The mounting posture of the vane compressor 100 is appropriately changed in accordance with a vehicle or the like to be mounted.

  The motor housing 1 has a bottom wall 1A and a cylindrical portion 1D, and an opening 1B is formed on the rear end side of the cylindrical portion 1D. The cylindrical portion 1D forms a motor chamber 1C that also serves as a suction chamber, and a bulging portion 1E is formed on the upper portion of the cylindrical portion 1D. A suction port 1F is formed on the front side and the lower side of the cylindrical portion 1D. An evaporator of a vehicle air conditioner is connected to the suction port 1F by a pipe (not shown).

  The motor mechanism 3 includes a stator 15 and a motor rotor 17. Lead wire 16C and cluster block 16 are accommodated in bulging portion 1E. The cluster block 16 has connection terminals 16A and 16B. The front end side of the lead wire 16C is connected to the cluster block 16 via the connection terminal 16B, and the rear end side is connected to the stator 15. The motor rotor 17 is inserted with a rotation shaft 19 that can rotate about the rotation axis X1. A shaft support portion 1G protrudes from the bottom wall 1A, and a bearing device 21 that supports the rotary shaft 19 is provided on the shaft support portion 1G.

  A cover 9 is fixed to the rear end of the motor housing 1. The cover 9 has a bottomed cylindrical shape, the rear end side is closed by the bottom wall 9D, and the opening 9E is formed on the front end side. The opening 9E of the cover 9 contacts the opening 1B of the motor housing 1, and the motor housing 1 and the cover 9 are closed. A gasket 22 is provided between the openings 1B and 9E. A step 9F is formed on the opening 9E side of the cover 9, and a step 1H is formed on the opening 1B side of the motor housing 1.

  The side plate 4 has a flat plate shape, and the outer peripheral edge of the side plate 4 is sandwiched from the front and rear by the step portions 9F and 1H. An O-ring 23 is provided between the outer peripheral surface of the side plate 4 and the inner peripheral surface of the step portion 9F. The side plate 4 is provided with a shaft hole 4A through which the rotary shaft 19 is inserted. Plating for sliding the rotating shaft 19 is formed in the shaft hole 4A.

  In the cover 9, the cylinder block 7, the side plate 5, and the block 35 are accommodated. The cylinder block 7 and the side plate 5 are assembled to the rear surface of the side plate 4 by a plurality of bolts 25 shown in FIG. As shown in FIG. 1, the cylinder block 7 is sandwiched from the front and rear by the side plate 4 and the side plate 5.

  The side plate 5 is fitted to the inner peripheral surface of the cover 9. An O-ring 24 is provided between the outer peripheral surface of the side plate 5 and the inner peripheral surface of the cover 9. The side plate 5 is provided with a shaft hole 5A through which the rotary shaft 19 is inserted. In the shaft hole 5A, plating for suitably sliding the rotating shaft 19 is formed. The rear end portion of the rotation shaft 19 is supported by the shaft hole 5A. A discharge chamber 9A is formed between the bottom wall 9D of the cover 9 and the rear surface of the side plate 5. The discharge chamber 9A is connected to the condenser of the vehicle air conditioner via the discharge port 9B and a pipe (not shown).

  The block 35 has an oil separation chamber 35 </ b> A and is fixed to the rear surface of the side plate 5. A cylinder member 59 is fixed to the oil separation chamber 35A, the upper end of the cylinder member 59 is open to the discharge chamber 9A, and the lower end of the oil separation chamber 35A is open to the discharge chamber 9A through the oil discharge port 35B. In the side plate 5 and the block 35, passages 5B and 35C are formed.

  The passages 5B and 35C communicate between the oil separation chamber 35A and a discharge space 37 described later. The portion surrounding the shaft hole 5 </ b> A on the rear surface of the side plate 5, the rear end surface of the rotary shaft 19, and the front surface of the block 35 form an oil supply chamber 210. The side plate 5 has passages 5E and 5F, and the discharge chamber 9A communicates with the oil supply chamber 210 through the passages 5E and 5F.

  As shown in FIG. 1, the cylinder block 7 has a cylindrical shape extending in the direction of the rotation axis X1. The cylinder block 7 forms a cylinder chamber 31 together with the side plates 4 and 5. FIG. 2 is a cross-sectional view taken along the line II-II in FIG.

  The cross-sectional shape of the inner peripheral surface 31S of the cylinder chamber 31 is a perfect circle centered on the eccentric axis X2 that is eccentric with respect to the rotation axis X1. The side plate 4 (FIG. 1) 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 that communicates with the suction passage 33A. The suction passage 33 </ b> B communicates with the cylinder chamber 31 through a suction port 33 </ b> C that is recessed in the cylinder block 7.

  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 through a discharge port 37 </ b> 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 </ b> A and a retainer 39 </ b> A that restricts the opening degree of the discharge reed valve 39 are fixed to the cylinder block 7.

  As shown in FIG. 2, the compression mechanism 13 includes a cylinder chamber 31, a rotor 41, and a plurality of (three in this embodiment) vanes 51. The rotor 41 is provided in the cylinder chamber 31 so as to be able to rotate synchronously with the rotary shaft 19. The cross-sectional shape of the outer peripheral surface 41S of the rotor 41 is a perfect circle centered on the rotation axis X1. In this embodiment, the rotation direction R1 of the rotor 41 is counterclockwise toward the paper surface of FIG.

  The rotor 41 is formed with three vane grooves 41A. The three vane grooves 41A are formed at intervals of 120 ° around the rotation axis X1. A vane 51 is provided in each vane groove 41A so as to be able to appear and disappear. The vane 51 is formed with a plating (not shown) so as to slide on the front surface, the inner peripheral surface 31S and the rear surface of the cylinder chamber 31 and the rotor 41 described later. As the rotor 41 rotates, the vane 51 appears and disappears with respect to the vane groove 41 </ b> A, with the radially outer tip thereof slidingly contacting the inner peripheral surface 31 </ b> S of the cylinder chamber 31.

  As shown in FIGS. 1 and 2, a compression chamber is formed by the front surface of the cylinder chamber 31, the inner peripheral surface 31S of the cylinder chamber 31, the rear surface of the cylinder chamber 31, the outer peripheral surface 41S of the rotor 41, and a pair of adjacent vanes 51. Is done. In the vane type compressor 100 of the present embodiment, the three compression chambers 30A, 30B, and 30C are formed by the three vanes 51.

(Ring part)
A housing portion 42 is formed on the front end surface of the rotor 41 in the axial direction. The accommodating part 42 is dented toward the rear, with the rotating shaft 19 inside. In the accommodating portion 42, an inner ring-shaped member 61 and an outer ring-shaped member 62 are accommodated. As shown in FIG. 1, a housing portion 43 is formed on the rear end surface in the axial direction of the rotor 41. The accommodating part 43 is recessed toward the front while the rotation shaft 19 is contained. In the accommodating portion 43, an inner ring-shaped member 71 and an outer ring-shaped member 72 are accommodated.

  The front-side accommodation portion 42, the inner ring-shaped member 61 and the outer ring-shaped member 62, and the rear-side accommodation portion 43, the inner ring-shaped member 71 and the outer ring-shaped member 72 have the same configuration. In the following description, the accommodating portion 42, the inner ring-shaped member 61, and the outer ring-shaped member 62 will be mainly described, and the descriptions of the accommodating portion 43, the inner ring-shaped member 71, and the outer ring-shaped member 72 will not be repeated as appropriate.

  As shown in FIGS. 1 and 2, the accommodating portion 42 is a bottomed round hole centered on the rotation axis X <b> 1 and is shallowly recessed. The radially outer portion of the accommodating portion 42 overlaps the radially inner ends of the three vane grooves 41A, and the interior of the accommodating portion 42 is connected to the interior of the vane groove 41A (back pressure chamber 49 described later). ing. Part of the lubricating oil in the vane groove 41 </ b> A flows into the accommodating portion 42 and lubricates the inner ring-shaped member 61 and the outer ring-shaped member 62. The inner ring-shaped member 61 is formed by bending a metal plate-shaped member, and has a substantially C-shape when viewed from the direction of the rotation axis X1. The inner ring-shaped member 61 is disposed so as to surround the periphery of the rotation shaft 19 in the accommodating portion 42, and functions as a leaf spring.

  The outer ring-shaped member 62 is made of a member made of a material different from that of the inner ring-shaped member 61 and is disposed so as to surround the inner ring-shaped member 61 in the accommodating portion 42. The outer ring-shaped member 62 is provided so as to contact the vane 51 and apply a pressing force. The inner ring-shaped member 61 is disposed on the inner peripheral side of the outer ring-shaped member 62 and is in contact with the outer ring-shaped member 62 to apply a pressing force to the outer ring-shaped member 62. When the inner ring-shaped member 61 is made of metal, the outer ring-shaped member 62 is made of resin, for example. As the outer ring-shaped member 62, a so-called O-ring made of rubber can be used. The inner ring-shaped member 61 and the outer ring-shaped member 62 function as ring portions that elastically press the vane 51 by bending.

  A back pressure chamber 49 is formed between the radially inner end 52 of the vane 51 and the vane groove 41A. As shown in FIG. 1, a communication path 5 </ b> G is formed in the rotating shaft 19 and the rotor 41. The communication path 5G extends from the rear end surface of the rotation shaft 19 to the front side along the rotation axis X1, then bends radially outward of the rotation axis X1 and communicates with the back pressure chamber 49. The passages 5E and 5F, the oil supply chamber 210, and the communication passage 5G constitute a back pressure flow path. The lubricating oil that has passed through the back pressure flow channel acts as a back pressure on the radially inner end 52 of the vane 51 and urges the vane 51 outward in the radial direction.

(Intake stroke, compression stroke, discharge stroke)
When the stator 15 shown in FIG. 1 is supplied with power, the motor mechanism 3 operates, and the rotating shaft 19 rotates about the rotating shaft X1. The compression mechanism 13 operates and the rotor 41 rotates in the cylinder block 7. The compression chambers 30A, 30B, and 30C (FIG. 2) repeat the expansion and contraction of the volume.

  The compression chambers 30A, 30B, and 30C perform a suction stroke for sucking low-pressure refrigerant gas from the motor chamber 1C through the suction passages 33A and 33B and the suction port 33C. After the suction stroke, the refrigerant is compressed in the compression chambers 30A, 30B, and 30C. A compression stroke for compressing the gas is performed. After the compression stroke, a high-pressure refrigerant gas in the compression chambers 30A, 30B, 30C is discharged to the discharge chamber 9A through the discharge port 37A, the discharge space 37, and the passages 5B, 35C. Do. The refrigerant gas is discharged from the discharge chamber 9A to a refrigerant circuit (not shown), circulates in the refrigerant circuit, and air conditioning of the passenger compartment is performed.

  The operation of the vane 51 (51A) will be described in detail with reference to FIG. 2. If the rotor 41 rotates in the rotation direction R1 from the state shown in FIG. Also rotate in the same direction around the rotation axis 19. The vane 51 (51A) is pushed by the inner peripheral surface 31S of the cylinder chamber 31 and rotates while being buried in the vane groove 41A. In the compression chamber formed forward of the vane 51 (51A) in the rotational direction shown in FIG. 2, the compression pressure reaches the discharge pressure, and the discharge reed valve 39 (FIG. 1) is expanded to perform the discharge stroke. ing.

  At this time, a part of the compression pressure acts on the vane 51 (51A), and the compression pressure urges the vane 51 (51A) toward the radially inner side. On the other hand, the vane 51 (51A) buried in the vane groove 41A elastically deforms the inner ring-shaped member 61 and the outer ring-shaped member 62. That is, in addition to the radially inward biasing force generated by the compression pressure, the elastic pressing force of the inner ring-shaped member 61, the elastic pressing force of the outer ring-shaped member 62, the back pressure from the back pressure chamber 49, and the vane The centrifugal force generated by the rotation of 51 (51A) acts on the vane 51 (51A). The two elastic pressing forces, back pressure, and centrifugal force all urge the vane 51 (51A) toward the radially outer side.

  When the discharge stroke is performed, a high contact pressure is required to prevent pressure leakage between the radially outer end of the vane 51 (51A) and the inner peripheral surface 31S of the cylinder chamber 31. However, in the present embodiment, these two elastic pressing forces, back pressure and centrifugal force are opposed to the compression pressure. The radially outer end of the vane 51 (51A) and the inner peripheral surface 31S of the cylinder chamber 31 are kept in contact with each other, and noise caused by chattering and a decrease in discharge capacity (pressure loss) occur. Is prevented.

  After the discharge stroke is completed with the rotation of the vane 51 (51A), the suction stroke is performed. The vane 51 (51A) moves outward in the radial direction. When the pressing force applied to the inner ring-shaped member 61 by the vane 51 (51A) via the outer ring-shaped member 62 is gradually reduced, the vane 51 (51A) further moves toward the radially outer side as it rotates. The inner ring-shaped member 61 returns to the no-load state (natural state). The vane 51 (51A) bends only the outer ring-shaped member 62, and elastic pressing force, back pressure, and centrifugal force by the outer ring-shaped member 62 act on the vane 51 (51A).

  When the vane 51 (51A) further moves radially outward along with the rotation, the pressing force applied to the outer ring-shaped member 62 by the vane 51 (51A) gradually decreases, and the vane 51 (51A) rotates. If the outer ring-shaped member 62 is further moved toward the radially outer side along with this, the outer ring-shaped member 62 returns to the no-load state (natural state). In this state, back pressure and centrifugal force act on the vane 51 (51A).

  As described at the beginning, if the contact pressure between the radially outer end of the vane 51 and the inner peripheral surface 31S of the cylinder chamber 31 is too small, chattering will occur and the discharge capacity will be reduced. 51 and inner peripheral surface 31S wear and power loss of the compressor. Assuming that the contact pressure that can satisfy both of these conditions is the required contact pressure, the compression pressure that acts on the vane 51 gradually increases as it progresses from the compression stroke toward the discharge stroke (increases until the discharge pressure is reached). Therefore, the necessary contact pressure gradually increases.

  In the present embodiment, the necessary contact pressure that varies depending on the stroke is realized by the two outer ring-shaped members 62 and the inner ring-shaped member 61 that are made of different materials. When the pressing force toward the radially inner side of the vane 51 is small, the outer ring-shaped member 62 bends, and when the pressing force toward the radially inner side of the vane 51 is large, both the outer ring-shaped member 62 and the inner ring-shaped member 61 are Bend. The elastic pressing force generated in one ring increases and decreases almost linearly (Patent Document 1). On the other hand, when two outer ring-shaped members 62 and inner ring-shaped member 61 made of different materials are used, the elastic pushing force that increases or decreases in a substantially linear function while the elastic pushing force of the outer ring-shaped member 62 is acting. Although pressure is generated, the vane 51 is deeply buried in the vane groove 41 </ b> A so that the elastic pressing force of the inner ring-shaped member 61 is superimposed on the elastic pressing force of the outer ring-shaped member 62. To do.

  Therefore, by using the two outer ring-shaped members 62 and the inner ring-shaped member 61 of different materials, the elastic pressing force of the entire elastic system of the outer ring-shaped member 62 and the inner ring-shaped member 61 can be reduced, for example, in the suction stroke. Can be configured to increase or decrease slowly, and can be configured to increase or decrease steeply in the compression stroke and the discharge stroke. The elastic pressing force as a whole of the elastic system can be matched to both the suction stroke where the required contact pressure is small, and the compression stroke and the discharge stroke where the required contact pressure is large.

  As a result, it is possible to suppress the inner ring-shaped member 61 and the outer ring-shaped member 62 from pressing the vane forming the compression chamber on the inner peripheral surface of the cylinder chamber during the suction stroke with an excessive contact pressure. It is possible to prevent wear of the vane and the inner peripheral surface. On the other hand, the inner ring surface 61 and the outer ring member 62 of the vane forming the compression chamber during the compression stroke and the discharge stroke are subjected to an appropriate contact pressure together with the back pressure and the centrifugal force. Therefore, sufficient sealing performance can be obtained, power loss does not increase, chattering does not occur, and discharge capacity does not decrease.

(Modification 1)
In the above-described embodiment, the accommodating portion 42 is formed on the front end surface in the axial direction of the rotor 41, and the inner ring-shaped member 61 and the outer ring-shaped member 62 are accommodated in the accommodating portion 42. A housing part 43 is formed on the rear end surface in the axial direction of the rotor 41, and the inner ring-shaped member 71 and the outer ring-shaped member 72 are housed in the housing part 43. The configuration is not limited to such a configuration, and a housing portion may be formed on at least one end surface in the axial direction of the rotor 41, and the outer ring-shaped member and the inner ring-shaped member may be housed in the housing portion. Absent.

(Modification 2)
In the above-described embodiment, the inner ring-shaped member 61 is made of metal, and the outer ring-shaped member 62 is made of resin. The configuration is not limited to this, and it is sufficient that the inner ring-shaped member 61 has a larger elastic pressing force than the outer ring-shaped member 62. The inner ring-shaped member 61 may be molded from a relatively hard resin, and the outer ring-shaped member 62 may be molded from a relatively soft resin.

(Modification 3)
In the above-described embodiment, the inner ring-shaped member 61 has a C-shape. The inner ring-shaped member 61 may have a continuous annular shape. Even in this configuration, when the vane 51 is shallowly buried in the vane groove 41A, the elastic pressing force of the outer ring-shaped member 62 acts on the end 52, and the vane 51 is deeply buried in the vane groove 41A. In this case, the elastic pressing force of the inner ring-shaped member 61 is applied to the vane 51 so as to be superimposed on the elastic pressing force of the outer ring-shaped member 62, so that the same operation and effect as in the above-described embodiment are obtained. be able to.

(Modification 4)
In the above-described embodiment, the back pressure chamber 49 is formed between the radially inner end 52 of the vane 51 and the vane groove 41A. A part of the discharge pressure acts on the radially inner end 52 of the vane 51 through the back pressure flow path, and biases the vane 51 toward the radially outer side. The configuration of biasing the vane 51 radially outward using the back pressure is not essential. For example, the elastic pressing force of the outer ring-shaped member 62, the elastic pressing force of the inner ring-shaped member 61, and the centrifugal force are used. Then, the vane 51 may be urged radially outward, or the vane 51 may be urged radially outward using the elastic pressing force and centrifugal force of the outer ring-shaped member 62.

(Modification 5)
In the embodiment described above, the outer ring-shaped member 62 and the inner ring-shaped member 61 are arranged so as to be coaxial with the rotary shaft 19. The outer ring-shaped member 62 and the inner ring-shaped member 61 are not limited to such a configuration, and may be disposed at positions eccentric with respect to the rotation shaft 19 as long as they surround the rotation shaft 19. .

(Modification 6)
In the above-described embodiment, two of the outer ring-shaped member 62 and the inner ring-shaped member 61 are accommodated in the accommodating portion 42, but three or more ring-shaped members are accommodated in the accommodating portion 42. May be. In that case, at least one of the plurality of ring-shaped members is configured to be different in material from the other ring-shaped members of the plurality.

(Modification 7)
In the above-described embodiment, the inner ring-shaped member 61 is arranged so as to be in an unloaded state (natural state) when the pressing force applied by the vane 51 is small. The inner ring member 61 may always support the outer ring member 62 without being limited to such a configuration. In this case, when the vane 51 is shallowly buried in the vane groove 41A, the outer ring-shaped member 62 bends, and the elastic pressing force of the outer ring-shaped member 62 mainly acts on the end portion 52, and the vane 51 becomes the vane groove 41A. When deeply buried in the inner ring-shaped member 61, both the inner ring-shaped member 61 and the outer ring-shaped member 62 are bent so that the elastic pressing force of the inner ring-shaped member 61 is superimposed on the elastic pressing force of the outer ring-shaped member 62. Acts on the vane 51.

  Although the embodiment has been described above, the above disclosure is illustrative in all respects and is not restrictive. The technical scope of the present invention is defined by the terms of the claims, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  1 Motor housing, 1A, 9D bottom wall, 1B, 9E opening, 1C motor chamber, 1D cylindrical part, 1E bulging part, 1F suction port, 1G shaft support part, 1H, 9F step part, 3 motor mechanism, 4, 5 side Plate, 4A, 5A Shaft hole, 5B, 5E, 5F, 35C passage, 5G communication passage, 7 Cylinder block, 9 cover, 9A Discharge chamber, 9B Discharge port, 13 Compression mechanism, 15 Stator, 16 Cluster block, 16A, 16B Connection terminal, 16C lead wire, 17 Motor rotor, 19 Rotating shaft, 21 Bearing device, 22 Gasket, 23, 24 O-ring, 25 Bolt, 30A, 30B, 30C Compression chamber, 31 Cylinder chamber, 31S Inner peripheral surface, 33A, 33B Suction passage, 33C Suction port, 35 block, 35A Oil separation chamber, 35B Oil discharge port, 37 Discharge Space, 37A discharge port, 39 discharge reed valve, 39A retainer, 41 rotor, 41A vane groove, 41S outer peripheral surface, 42, 43 accommodating portion, 49 back pressure chamber, 51 vane, 52 end, 59 cylindrical member, 61, 71 Inner ring-shaped member, 62, 72 Outer ring-shaped member, 100 vane compressor, 210 oil supply chamber, R1 rotation direction, X1 rotation axis, X2 eccentric axis.

Claims (5)

A housing in which a discharge chamber and a cylinder chamber are formed;
A rotating shaft rotatably provided in the housing;
A rotor that is rotatably provided with the rotating shaft in the cylinder chamber, has a plurality of vane grooves, and has a housing portion that is recessed while the rotating shaft is contained in at least one end surface in the axial direction;
A vane provided in each of the plurality of vane grooves so as to be able to appear and disappear,
A ring portion that is arranged so as to surround the periphery of the rotation shaft in the housing portion and elastically presses the vane by bending;
The ring part is
An outer ring-shaped member provided so as to give an elastic pressing force in contact with the vane;
An inner side made of a material different from that of the outer ring-shaped member, disposed on the inner peripheral side of the outer ring-shaped member, and in contact with the outer ring-shaped member to give an elastic pressing force to the outer ring-shaped member A ring-shaped member,
The inner ring member has a larger elastic pressing force than the outer ring member,
Vane type compressor. The outer ring-shaped member is made of resin,
The inner ring-shaped member is made of metal.
The vane type compressor according to claim 1. The inner ring-shaped member has a C-shape,
The vane type compressor according to claim 1 or 2. A back pressure chamber is formed between the radially inner end of the vane and the vane groove,
The accommodating portion is connected to the back pressure chamber;
The vane type compressor according to any one of claims 1 to 3. A back pressure flow path that connects the discharge chamber and the back pressure chamber is formed in the rotating shaft and the rotor.
The vane type compressor according to claim 4.

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