JP6753336B2 - Vane compressor - Google Patents

Description

The present invention relates to a vane type compressor.

Japanese Patent Application Laid-Open No. 2004-353591 (Patent Document 1) discloses a gas compressor provided with a suction check valve. In the gas compressor described in Patent Document 1, the valve closes due to the attractive force of the magnet when the operation is stopped, and the gas suction input of the gas compressor overcomes the attractive force of the magnet and opens the valve during operation.

Japanese Unexamined Patent Publication No. 2004-353591

The pressure inside the vane type compressor during operation is higher on the discharge side than on the suction side. Even after the operation is stopped, the pressure difference inside the vane type compressor remains, and the pressure difference causes the lubricating oil to flow out from the discharge side to the suction side. As a result, the amount of lubricating oil stored on the discharge side becomes small, and when the operation is restarted, the lubricating oil may not be sufficiently supplied to the back pressure chamber of the vane type compressor.

The present invention has been made in view of the above problems, and suppresses a decrease in the lubricating oil on the discharge side while the operation is stopped, and promptly supplies a sufficient lubricating oil to the back pressure chamber when the operation is restarted. The purpose is to provide a vane type compressor that can be used.

A vane-type compressor based on the present invention includes a housing, a rotating shaft, a rotor, and a vane. The housing has a cylinder chamber, an oil separation chamber, and a discharge chamber formed therein. The rotating shaft is supported by the housing 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 circumference of the rotor. The vanes are habitably attached to each of the plurality of vane grooves. The rotor is provided with a back pressure chamber that applies back pressure to the vane. The refrigerant gas compressed in the cylinder chamber is discharged to the discharge chamber after the lubricating oil is separated in the oil separation chamber. The lubricating oil separated from the refrigerant gas is delivered to the bottom of the discharge chamber. Inside the housing, a back pressure supply path is provided that opens toward the bottom of the discharge chamber and communicates the bottom of the discharge chamber with the back pressure chamber to supply lubricating oil to the vanes. The vane type compressor further includes a valve mechanism for opening and closing the opening of the back pressure supply path. The valve mechanism has a first pressure receiving portion that receives a pressing force due to the pressure in the oil separation chamber and a second pressure receiving portion that is provided opposite to the first pressure receiving portion and receives the pressing force due to the pressure in the discharge chamber. Includes a valve body that opens and closes the opening of the back pressure supply path by the differential pressure between the and the oil separation chamber.

In one embodiment of the present invention, the first pressure receiving portion is located in the oil separation chamber. The second pressure receiving portion is located at the bottom of the discharge chamber.

In one embodiment of the present invention, the valve body further includes a connecting rod portion that connects the first pressure receiving portion and the second pressure receiving portion to each other. The connecting rod portion is inserted into a guide hole that opens at the bottom of the oil separation chamber. The opening of the guide hole is parallel to the opening of the back pressure supply path.

In one embodiment of the invention, the cylinder chamber is partitioned by a partition wall. The back pressure supply path is provided on the partition wall.

In one embodiment of the present invention, each of the first pressure receiving portion and the second pressure receiving portion is composed of a plate-shaped member. The pressure receiving area of the first pressure receiving portion is larger than the pressure receiving area of the second pressure receiving portion.

In one embodiment of the present invention, the vane type compressor further includes a spring that applies an urging force in the closing direction of the valve body to the valve body.

According to the present invention, it is possible to suppress a decrease in the lubricating oil on the discharge side while the operation is stopped, and to quickly supply a sufficient lubricating oil to the back pressure chamber when the operation is restarted.

It is sectional drawing which shows the structure of the vane type compressor which concerns on Embodiment 1 of this invention. It is a partial cross-sectional view which shows the valve mechanism of the vane type compressor which concerns on Embodiment 1 of this invention in an enlarged manner. It is sectional drawing which saw the vane type compressor of FIG. 1 from the direction of the arrow of line III-III. It is sectional drawing which saw the vane type compressor of FIG. 1 from the direction of the arrow of line IV-IV. It is sectional drawing which shows the structure of the vane type compressor which concerns on Embodiment 2 of this invention. It is a partial cross-sectional view which shows the valve mechanism of the vane type compressor which concerns on Embodiment 2 of this invention in an enlarged manner. It is sectional drawing which shows the structure of the vane type compressor which concerns on Embodiment 3 of this invention. FIG. 5 is an enlarged partial cross-sectional view showing a state in which the valve mechanism of the vane type compressor according to the third embodiment of the present invention is open. FIG. 5 is an enlarged partial cross-sectional view showing a state in which the valve mechanism of the vane type compressor according to the third embodiment of the present invention is closed. It is sectional drawing which shows the structure of the vane type compressor which concerns on Embodiment 4 of this invention. It is a partial cross-sectional view which shows the valve mechanism of the vane type compressor which concerns on Embodiment 4 of this invention in an enlarged manner.

Hereinafter, the vane type compressor according to each 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 designated by the same reference numerals, and the description will not be repeated.

(Embodiment 1)
FIG. 1 is a cross-sectional view showing the configuration of a vane type compressor according to the first embodiment of the present invention. FIG. 2 is an enlarged partial cross-sectional view showing the valve mechanism of the vane type compressor according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view of the vane type compressor of FIG. 1 as viewed from the direction of the arrow line III-III. FIG. 4 is a cross-sectional view of the vane type compressor of FIG. 1 as viewed from the direction of the arrow along line IV-IV. FIG. 1 shows a state in which the valve mechanism is open. FIG. 2 shows a state in which the valve mechanism is closed. In each figure, the amount of lubricating oil is schematically shown. The vane type compressor according to the first embodiment of the present invention is mounted on a vehicle and used as an air conditioner for the vehicle.

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

As shown in FIGS. 1 to 4, the housing 11 of the vane type compressor 10 according to the first embodiment of the present invention has a bottomed cylindrical rear housing 12 and a front housing coupled to the front end surface of the rear housing 12. It is formed from 13. The rear housing 12 constitutes the first housing according to the present embodiment. The front housing 13 constitutes the second housing according to the present embodiment. 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 tubular cylinder portion 14 extends from the bottom wall portion 13p. The inner peripheral surface 14c of the cylinder portion 14 is formed in an elliptical shape. The cylinder portion 14 has an open end portion opened on 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 the first partition wall. The bottom wall portion 13p is provided with a hole 13h that slides on the rotating shaft 16.

The cylinder portion 14 and the rear side plate 15 are housed in the rear housing 12. The rear housing 12 has a peripheral wall 12a. The rear side plate 15 is arranged so as 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 by using bolts (not shown). The rear side plate 15 constitutes the second partition wall.

The front housing 13 and the rear side plate 15 rotatably support the rotating shaft 16. The rotating shaft 16 penetrates the inside of the cylinder portion 14. A lip seal type shaft sealing device 17a is provided between the rotating shaft 16 and the front housing 13. The shaft sealing device 17a prevents the refrigerant gas from leaking along the peripheral surface of the rotating shaft 16.

The bottom wall portion 13p has one end surface 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 forward. One end face 13s and the other end face 15s are provided in parallel with a gap and face each other.

The cylinder chamber 14d is partitioned by the tubular cylinder portion 14, the bottom wall portion 13p, and the rear side plate 15. A rotor 18 having a cylindrical shape is provided in the cylinder chamber 14d. The rotor 18 is integrally rotatably attached to the rotating shaft 16.

As shown in FIG. 1, 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 plurality of vane grooves 18a are formed so as to extend radially on the outer peripheral surface 18c of the rotor 18. Inside each of the plurality of vane grooves 18a in the radial direction, a bottom portion 18ab having a widened groove is formed. The bottom portion 18ab of the vane groove 18a is formed in a substantially circular shape when viewed in the axial direction.

Each of the plurality of vane grooves 18a is provided with one vane 19 so as to appear and disappear. Lubricating oil in the discharge chamber 35, which will be described later, is supplied to each of the plurality of vane grooves 18a.

As the rotating shaft 16 rotates, the rotor 18 rotates, and some 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, a pair of adjacent vanes 19, and the end surface of the bottom wall portion 13p. The compression chamber 21 is partitioned between the 13s and the end surface 15s of the rear side plate 15. As shown in FIGS. 3 and 4, a plurality of compression chambers 21 are partitioned.

The outer peripheral surface 18c of the rotor 18 forms a wall surface on the inner peripheral side of the compression chamber 21. The inner peripheral surface 14c of the cylinder portion 14 forms a wall surface on the outer peripheral side of the compression chamber 21. The end surface 13s of the bottom wall portion 13p forms a wall surface on the front side of the compression chamber 21. The end surface 15s of the rear side plate 15 forms a wall surface on the rear side of the compression chamber 21.

The compression chamber 21 is formed in the cylinder chamber 14d. With respect to 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 reduces the volume is the compression stroke.

As shown in FIGS. 1 and 3, the rear housing 12 is formed with a suction port 22 that penetrates 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. 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 recess 14a is formed on the outer peripheral surface of the cylinder portion 14 over the entire circumference of the cylinder portion 14 in the circumferential direction. The suction space 20 is partitioned by the recess 14a 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 to partition the 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 rotating shaft 16.

As shown in FIG. 3, 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.

In the axial direction of the rotating shaft 16, the suction space 20 and the suction port 22 are arranged at positions overlapping with the compression chamber 21. A pair of suction holes 23 communicating with the suction space 20 are formed in the cylinder portion 14. 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 is open to the inner peripheral surface 14c of the cylinder portion 14 and is open to the suction space 20.

The suction hole 23, the suction space 20, and the suction port 22 are formed radially outward with respect to the compression chamber 21.

As shown in FIGS. 1 and 4, a pair of recesses 14b are provided on 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 recess 14b is formed from an extension surface 141b extending from the outer peripheral surface of the cylinder portion 14 toward the rotation shaft 16 and a mounting surface 142b intersecting the extension surface 141b and extending toward the outer peripheral surface of the cylinder portion 14. It is formed.

The discharge space 30 is provided by the extending surface 141b, the mounting surface 142b, and the inner peripheral surface of the rear housing 12. The discharge space 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 into the mounting surface 142b and communicates the compression chamber 21 and the discharge space 30. The discharge port 31 is opened and closed by a discharge valve 32 mounted on the mounting surface 142b. The refrigerant gas compressed in the compression chamber 21 pushes away the discharge valve 32 and is discharged to the discharge space 30 via the discharge port 31.

The suction space 20 and the discharge space 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 space 30.

As shown in FIGS. 3 and 4, a back pressure chamber 41 is formed between the bottom surface of each vane 19 housed in each vane groove 18a and the bottom surface of each vane groove 18a. A plurality of back pressure chambers 41 are partitioned by one end surface 13s of the bottom wall portion 13p, the other end surface 15s of the rear side plate 15, each bottom portion 18ab of the plurality of vane grooves 18a, and the vane 19.

The strength of the force with which the vane 19 is pressed against the inner peripheral surface 14c of the cylinder portion 14 is mainly the back pressure of the back pressure chamber 41 and the centrifugal force acting on the vane 19 to push the vane 19 to the outer peripheral side. The difference between the push-back force in which the vane 19 is pushed back toward the center of the rotating shaft 16 by the pressure of the refrigerant gas in the compression chamber 21, and the balance between the push-back force and the push-back force causes the vane 19 to move against the vane groove 18a. Haunt.

Each of the plurality of back pressure chambers 41 is provided so as to be able to communicate with the back pressure supply holes 15e, which will be 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 rotation shaft 16 rotates. Lubricating oil is supplied to each of the plurality of back pressure chambers 41 from the back pressure supply holes 15e when facing the back pressure supply holes 15e.

As shown in FIGS. 1 and 3, a plurality of oil passage grooves 13a are formed on the end surface 13s of the bottom wall portion 13p so as to be separated from each other in the circumferential direction. Each of the plurality of oil passage grooves 13a extends in the circumferential direction so as to connect between the back pressure chambers 41 adjacent to each other.

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

A cover body 36 is provided on the side of the rear side plate 15 opposite to the cylinder chamber 14d side. An intermediate chamber 70, which is a space communicating with the back pressure supply hole 15e described later, is provided between the rear side plate 15 and the cover body 36. The cover body 36 is housed in the rear housing 12. The discharge chamber 35 is partitioned by the rear side plate 15, the cover body 36, and the rear housing 12.

The cover body 36 has an oil separation chamber 36a which is a substantially cylindrical space forming a part of a communication passage between the compression chamber 21 and the discharge chamber 35. The oil separation chamber 36a separates the lubricating oil 60 from the refrigerant gas compressed in the compression chamber 21, and delivers the lubricating oil 60 to the bottom of the discharge chamber 35. A cylindrical oil separation cylinder 36b is fitted and fixed to one end side of the oil separation chamber 36a. An oil passage 36c is formed on the other end side of the oil separation chamber 36a. The oil passage 36c communicates the inside of the oil separation chamber 36a with the bottom side of the discharge chamber 35. A guide hole 36e is provided on the bottom surface of the oil separation chamber 36a. The guide hole 36e extends in the extending direction of the oil separation cylinder 36b.

As shown in FIGS. 1 and 4, a compressed refrigerant passage 37 is formed in the rear side plate 15 and the cover body 36. The compressed refrigerant passage 37 communicates the discharge space 30 with the inside of the oil separation chamber 36a.

The cover body 36 is provided with a communication passage 36d for communicating the bottom of the discharge chamber 35 and the intermediate chamber 70. The communication passage 36d is open toward the bottom of the discharge chamber 35. The opening of the communication passage 36d is on the same plane as the opening of the guide hole 36e, and the communication passage 36d and the guide hole 36e are opened in parallel. The rear side plate 15 is formed with a back pressure supply hole 15e for supplying back pressure to the vanes 19 by communicating with each of the plurality of vane grooves 18a. The communication passage 36d, the intermediate chamber 70, and the back pressure supply hole 15e serve as a back pressure supply passage for guiding the lubricating oil 60 stored in the bottom of the discharge chamber 35 to the back pressure chamber 41.

The vane type compressor 10 further includes a valve mechanism A for opening and closing the opening of the back pressure supply path. The valve mechanism A includes a valve body 50 that is brought into contact with and separated from the opening of the back pressure supply path. The valve body 50 is provided so as to face the first pressure receiving portion 53 that receives the pressing force due to the pressure in the oil separation chamber 36a and the first pressure receiving portion 53, and receives the pressing force due to the pressure in the discharge chamber 35. It has a pressure receiving unit 51.

Specifically, the valve body 50 has a first pressure receiving portion 53 located in the bottom of the oil separation chamber 36a and receiving a pressing force P1 due to a pressure including dynamic pressure and static pressure in the oil separating chamber 36a, and a discharge chamber. It has a second pressure receiving portion 51 that is located in the bottom of the 35 and receives a pressing force P2 due to a pressure including dynamic pressure and static pressure in the discharge chamber 35. Each of the first pressure receiving portion 53 and the second pressure receiving portion 51 is composed of a plate-shaped member. The pressure receiving area of the first pressure receiving unit 53 is larger than the pressure receiving area of the second pressure receiving unit 51.

The valve body 50 further includes a connecting rod portion 52 that connects the first pressure receiving portion 53 and the second pressure receiving portion 51 to each other. The connecting rod portion 52 is inserted into the guide hole 36e. The connecting rod portion 52 can move up and down along the guide hole 36e provided in the cover body 36.

A part of the second pressure receiving portion 51 faces the open end of the communication passage 36d. A part of the second pressure receiving portion 51 receives a pulling force P3 due to a differential pressure of pressure including dynamic pressure and static pressure in the discharge chamber 35 and the intermediate chamber 70.

An upward force and a downward force act on the valve body 50. The magnitude of the upward force acting on the valve body 50 is the sum of the pressing force P2, the buoyancy of the valve body 50, and the pulling force P3. The magnitude of the downward force acting on the valve body 50 is the sum of the pressing force P1 and the own weight of the valve body 50. The valve body 50 descends when the downward force is greater than the upward force and rises when the upward force is greater than the downward force. When the valve body 50 is lowered, the second pressure receiving portion 51 opens the communication passage 36d, and when the valve body 50 is raised, the second pressure receiving portion 51 closes the communication passage 36d.

The operation of the vane type compressor 10 will be described below. 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 type 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 by reducing the volume of the compression chamber 21 as the rotor 18 rotates. The compressed refrigerant gas is discharged from the compression chamber 21 to the discharge space 30 via the discharge port 31.

The refrigerant gas in the discharge space 30 flows out into the oil separation chamber 36a through the compressed refrigerant passage 37, is sprayed on the outer peripheral surface of the oil separation cylinder 36b, and is oil while swirling the outer peripheral surface of the oil separation cylinder 36b. It is guided downward in the separation chamber 36a. At this time, the lubricating oil 60 is separated from the refrigerant gas by centrifugation. The lubricating oil 60 separated from the refrigerant gas moves to the bottom side of the oil separation chamber 36a, passes through the oil passage 36c, and is stored in the bottom of the discharge chamber 35.

During the operation of the vane type compressor 10, the pressure in the oil separation chamber 36a is higher than the pressure in the discharge chamber 35, and the downward force acting on the valve body 50 is larger than the upward force. Therefore, the valve body 50 is lowered and the second pressure receiving portion 51 opens the communication passage 36d. As a result, the lubricating oil 60 stored in the bottom of the discharge chamber 35 is guided from the communication passage 36d to the back pressure chamber 41 through the intermediate chamber 70 and 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 vanes 19 extruded to the outer peripheral side. A part of the lubricating oil guided to the intermediate chamber 70 is supplied to the sliding portion between the rear side plate 15 and the rotating shaft 16.

The sliding portion is lubricated by the lubricating oil supplied to the sliding portion between the rear side plate 15 and the rotating shaft 16. The sliding portion between the vane 19 and the vane groove 18a is lubricated by the lubricating oil guided to the back pressure chamber 41. 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 separation chamber 36a, the refrigerant gas from which the lubricating oil 60 has been separated moves upward inside the oil separation cylinder 36b and is discharged to the discharge chamber 35, and is discharged to the outside of the vane type compressor 10 via the discharge port 34. It is discharged.

While the vane type compressor 10 is stopped, the pressure in the discharge chamber 35 becomes substantially equal to the pressure in the oil separation chamber 36a, and the upward force acting on the valve body 50 is larger than the downward force. Therefore, the valve body 50 rises and the second pressure receiving portion 51 closes the communication passage 36d.

In this way, the valve body 50 opens and closes according to the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the back pressure chamber 41. When the communication passage 36d is closed, the inflow of the lubricating oil into the intermediate chamber 70 is stopped. As a result, the amount of lubricating oil stored in the bottom of the discharge chamber 35 is maintained.

In the vane type compressor 10 of the present embodiment, the communication passage 36d is opened and closed by the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the back pressure chamber 41. By providing the valve body 50 that operates, it is possible to suppress a decrease in the lubricating oil 60 stored in the bottom of the discharge chamber 35 during the operation stop. Therefore, by opening the communication passage 36d when the operation is restarted, sufficient lubricating oil can be quickly supplied to the back pressure chamber 41 to increase the back pressure, and it is possible to suppress the occurrence of chattering.

Further, in the vane type compressor 10 of the present embodiment, since the outflow of the lubricating oil through the back pressure supply path is prevented during the operation stop, if the airtightness of the discharge valve 32 is maintained, the airtightness is maintained. There is no need to provide a check valve on the suction side. Further, it is possible to suppress the occurrence of oil compression that occurs when the operation is restarted in a state where the lubricating oil is accumulated on the suction side.

The communication passage 36d and the guide hole 36e are opened in parallel. Therefore, the entire valve mechanism A can be miniaturized by providing the second pressure receiving portion 51 of the valve body 50 so as to face the opening of the communication passage 36d and the opening of the guide hole 36e. Therefore, in order to provide the valve mechanism A, it is not necessary to increase the size of the discharge chamber 35 or change the arrangement of the members in the discharge chamber 35.

Further, in the vane type compressor 10 of the present embodiment, the first pressure receiving portion 53 and the second pressure receiving portion 51 are composed of plate-shaped members, and the pressure receiving area of the first pressure receiving portion 53 is the second pressure receiving portion. It is set larger than the pressure receiving area of 51. Therefore, even when the flow of the lubricating oil in the discharge chamber 35 becomes a dynamic pressure and acts as an upward force on the second pressure receiving unit 51 during the operation of the vane type compressor 10, the first pressure receiving unit 53 Due to the large pressure receiving area, the downward force acting on the first pressure receiving portion 53 can be increased, and the valve body 50 can be prevented from closing the communication passage 36d during the operation of the vane type compressor 10.

In the vane type compressor 10 according to the present embodiment, the bottom wall portion 13p and the cylinder portion 14 are integrally formed, but in the vane type compressor 10, the cylinder portion 14 uses the bottom wall portion 13p as the front side plate. The cylinder portion 14 may be arranged between the front side plate and the rear side plate 15 which are formed separately from the above and are arranged at intervals in the axial direction. Although the oil separation chamber 36a is shown so as to extend in the vertical direction, the oil separation chamber 36a may be arranged so as to be inclined with respect to the vertical direction. Even in this case, the guide hole 36e may be opened toward the bottom of the discharge chamber 35.

(Embodiment 2)
Hereinafter, the vane type compressor according to the second embodiment of the present invention will be described with reference to the drawings. The vane-type compressor according to the second embodiment of the present invention is different from the vane-type compressor 10 according to the first embodiment mainly in that it further includes a spring for applying an urging force to the valve body. The description of the configuration similar to that of the vane type compressor 10 will not be repeated.

FIG. 5 is a cross-sectional view showing the configuration of the vane type compressor according to the second embodiment of the present invention. FIG. 6 is an enlarged partial cross-sectional view showing the valve mechanism of the vane type compressor according to the second embodiment of the present invention. FIG. 5 shows a state in which the valve mechanism is open. FIG. 6 shows a state in which the valve mechanism is closed.

As shown in FIGS. 5 and 6, the vane type compressor 10a according to the second embodiment of the present invention includes a valve mechanism B for opening and closing the opening of the back pressure supply path. The valve mechanism B includes a valve body 50 that comes into contact with and separates from the opening of the back pressure supply path, and a spring 90 that applies an urging force P4 in the closing direction of the valve body 50 to the valve body 50.

In the cover body 36 according to the present embodiment, a storage recess 36f that houses a part of the spring 90 and supports the spring 90 is provided on the inner peripheral wall of the guide hole 36e on the oil separation chamber 36a side. The spring 90 is arranged in a compressed state between the bottom surface of the accommodating recess 36f and the first pressure receiving portion 53. The spring 90 is a compression coil spring. Therefore, the urging force P4 of the spring 90 is applied to the first pressure receiving portion 53.

Also in this embodiment, an upward force and a downward force act on the valve body 50. The magnitude of the upward force acting on the valve body 50 is the sum of the pressing force P2, the buoyancy of the valve body 50, the pulling force P3, and the urging force P4. The magnitude of the downward force acting on the valve body 50 is the sum of the pressing force P1 and the own weight of the valve body 50. The valve body 50 descends when the downward force is greater than the upward force and rises when the upward force is greater than the downward force. When the valve body 50 is lowered, the second pressure receiving portion 51 opens the communication passage 36d, and when the valve body 50 is raised, the second pressure receiving portion 51 closes the communication passage 36d. Since the urging force P4 of the spring 90 acts upward on the valve body 50, the valve body 50 can close the communication passage 36d even when the pulling force P3 is low.

During the operation of the vane type compressor 10a, the pressure in the oil separation chamber 36a is higher than the pressure in the discharge chamber 35, and the downward force acting on the valve body 50 is larger than the upward force. Therefore, the valve body 50 is lowered, the second pressure receiving portion 51 opens the communication passage 36d, and the lubricating oil is guided to the back pressure chamber 41 via the back pressure supply path. While the vane type compressor 10 is stopped, the pressure in the discharge chamber 35 becomes substantially equal to the pressure in the oil separation chamber 36a, and the upward force acting on the valve body 50 is larger than the downward force. Therefore, the valve body 50 rises and the second pressure receiving portion 51 closes the communication passage 36d, so that the lubricating oil is not guided to the back pressure supply path and is stored in the discharge chamber 35.

In this way, the valve body 50 opens and closes according to the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the back pressure chamber 41. When the communication passage 36d is closed, the inflow of the lubricating oil into the back pressure chamber 41 is stopped. As a result, the amount of lubricating oil stored in the bottom of the discharge chamber 35 is maintained.

In the vane type compressor 10a of the present embodiment, since the urging force P4 of the spring 90 is applied to the valve body 50, as compared with the vane type compressor 10 according to the first embodiment, the valve body 50 communicates the passage. The 36d can be opened and closed more stably.

(Embodiment 3)
Hereinafter, the vane type compressor according to the third embodiment of the present invention will be described with reference to the drawings. The vane type compressor according to the third embodiment of the present invention is related to the second embodiment because the structure of the valve body and the position where the valve body is provided are mainly different from the vane type compressor 10a according to the second embodiment. The description of the configuration similar to that of the vane type compressor 10a will not be repeated.

FIG. 7 is a cross-sectional view showing the configuration of the vane type compressor according to the third embodiment of the present invention. FIG. 8 is a partial cross-sectional view showing an enlarged state in which the valve mechanism of the vane type compressor according to the third embodiment of the present invention is open. FIG. 9 is an enlarged partial cross-sectional view showing a state in which the valve mechanism of the vane type compressor according to the third embodiment of the present invention is closed. FIG. 7 shows a state in which the valve mechanism is open.

As shown in FIGS. 7 to 9, in the vane type compressor 10b according to the third embodiment of the present invention, a storage portion 36g for movably accommodating the valve body 80 is provided on the side wall of the oil separation chamber 36a. There is. A reduced diameter opening 36h is provided on one end side of the accommodating portion 36g. The accommodating portion 36g communicates with the oil separation chamber 36a through the opening 36h. The other end of the accommodating portion 36g is open so as to face the rear end surface 15r of the rear side plate 15.

The vane type compressor 10b includes a valve mechanism C that opens and closes the opening of the back pressure supply path. The valve mechanism C includes a valve body 80 that comes into contact with and separates from the opening of the back pressure supply path, and a spring 91 that applies an urging force P4 in the closing direction of the valve body 80 to the valve body 80.

Specifically, the valve body 80 has a prismatic outer shape. The valve body 80 has a first pressure receiving portion 83 on which the pressure in the oil separation chamber 36a acts, and a second pressure receiving portion 82 on the other end side on which the pressure in the discharge chamber 35 acts. The valve body 80 is provided with a hole 81 extending in the radial direction of the valve body 80 and capable of communicating with the communication passage 36d.

A spring 91 that applies an urging force P4 in the closing direction of the valve body 80 to the valve body 80 is attached to the second pressure receiving portion 82 of the valve body 80. The spring 91 is arranged in a compressed state between the second pressure receiving portion 82 of the valve body 80 and the rear end surface 15r of the rear side plate 15. The spring 91 is a compression coil spring. Therefore, the urging force P4 of the spring 91 is applied to the second pressure receiving portion 82 of the valve body 80.

A forward force, a backward force, an upward force, and a downward force act on the valve body 80. The magnitude of the forward force acting on the valve body 80 is the pressing force P1. The magnitude of the backward force acting on the valve body 80 is the sum of the pressing force P2 and the urging force P4. The magnitude of the upward force acting on the valve body 80 is the pull-in force P3. The magnitude of the downward force acting on the valve body 80 is the weight of the valve body 80 itself. A frictional force proportional to the differential pressure between the upward force and the downward force acting on the valve body 80 is generated between the outer peripheral surface of the valve body 80 and the inner wall surface of the accommodating portion 36 g.

The valve body 80 moves forward when the forward force is greater than the sum of the frictional force and the backward force. The valve body 80 moves backward when the backward force is greater than the sum of the frictional force and the forward force. When the valve body 80 is moved forward, the hole 81 communicates with the communication passage 36d to open the communication passage 36d, and when the valve body 80 is moved backward, the hole 81 communicates with the communication passage 36d. The passage 36d is blocked by the absence.

During the operation of the vane type compressor 10b, the pressure in the oil separation chamber 36a is higher than the pressure in the discharge chamber 35, and the forward force acting on the valve body 80 is the sum of the frictional force and the backward force. It's getting bigger. Therefore, the valve body 80 moves forward and the hole 81 opens the communication passage 36d. While the vane type compressor 10 is stopped, the pressure in the discharge chamber 35 becomes substantially equal to the pressure in the oil separation chamber 36a, and the backward force acting on the valve body 80 is larger than the sum of the frictional force and the forward force. It has become. Therefore, the valve body 80 moves rearward and closes the communication passage 36d.

In this way, the valve body 80 opens and closes according to the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the back pressure chamber 41. When the communication passage 36d is closed, the inflow of the lubricating oil into the back pressure chamber 41 is stopped. As a result, the amount of lubricating oil stored in the bottom of the discharge chamber 35 is maintained.

Also in the vane type compressor 10b of the present embodiment, since the urging force P4 of the spring 91 is applied to the valve body 80, the valve body 80 is connected to the vane type compressor 10b as compared with the vane type compressor 10 of the first embodiment. The passage 36d can be opened and closed more stably.

(Embodiment 4)
Hereinafter, the vane type compressor according to the fourth embodiment of the present invention will be described with reference to the drawings. The vane type compressor according to the fourth embodiment of the present invention is different from the vane type compressor 10 according to the first embodiment mainly in that a communication passage is provided in the rear side plate, and therefore the vane type compressor according to the first embodiment. The description of the configuration similar to that of the compressor 10 will not be repeated.

FIG. 10 is a cross-sectional view showing the configuration of the vane type compressor according to the fourth embodiment of the present invention. FIG. 11 is an enlarged partial cross-sectional view showing the valve mechanism of the vane type compressor according to the fourth embodiment of the present invention. FIG. 10 shows a state in which the valve mechanism is open. FIG. 11 shows a state in which the valve mechanism is closed.

As shown in FIGS. 10 and 11, in the vane type compressor 10c according to the fourth embodiment of the present invention, the rear side plate 15 is provided with a communication passage 15d for communicating the bottom of the discharge chamber 35 and the intermediate chamber 70. ing. A communication passage for communicating the bottom of the discharge chamber 35 and the intermediate chamber 70 may be provided between the cover body 36 and the rear side plate 15.

The vane type compressor 10c includes a valve mechanism D that opens and closes the opening of the back pressure supply path. The valve mechanism D includes a valve body 50 that is brought into contact with and separated from the opening of the back pressure supply path. A part of the second pressure receiving portion 51 of the valve body 50 faces the open end of the communication passage 15d. A part of the second pressure receiving portion 51 receives a pulling force P3 due to a differential pressure of pressure including dynamic pressure and static pressure in the discharge chamber 35 and the intermediate chamber 70.

An upward force and a downward force act on the valve body 50. The magnitude of the upward force acting on the valve body 50 is the sum of the pressing force P2, the buoyancy of the valve body 50, and the pulling force P3. The magnitude of the downward force acting on the valve body 50 is the sum of the pressing force P1 and the own weight of the valve body 50. The valve body 50 descends when the downward force is greater than the upward force and rises when the upward force is greater than the downward force. When the valve body 50 is lowered, the second pressure receiving portion 51 opens the communication passage 15d, and when the valve body 50 is raised, the second pressure receiving portion 51 closes the communication passage 15d.

During the operation of the vane type compressor 10c, the pressure in the oil separation chamber 36a is higher than the pressure in the discharge chamber 35, and the downward force acting on the valve body 50 is larger than the upward force. Therefore, the valve body 50 is lowered and the second pressure receiving portion 51 opens the communication passage 15d. As a result, the lubricating oil stored in the bottom of the discharge chamber 35 is guided from the communication passage 15d to the back pressure chamber 41 through the intermediate chamber 70 and the back pressure supply hole 15e, and rotates with the bottom wall portion 13p through the oil passage groove 13a. It is supplied to the sliding portion with the shaft 16. 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 vanes 19 extruded to the outer peripheral side. A part of the lubricating oil guided to the intermediate chamber 70 is supplied to the sliding portion between the rear side plate 15 and the rotating shaft 16.

While the vane type compressor 10c is stopped, the pressure in the discharge chamber 35 becomes substantially equal to the pressure in the oil separation chamber 36a, and the upward force acting on the valve body 50 is larger than the downward force. Therefore, the valve body 50 rises and the second pressure receiving portion 51 closes the communication passage 15d.

In this way, the valve body 50 opens and closes according to the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the back pressure chamber 41. When the communication passage 15d is closed, the inflow of the lubricating oil into the back pressure chamber 41 is stopped. As a result, the amount of lubricating oil stored in the bottom of the discharge chamber 35 is maintained.

In the vane type compressor 10c of the present embodiment, the opening and closing operation of the communication passage 15d is performed by the differential pressure fluctuation between the discharge chamber 35 and the oil separation chamber 36a and the differential pressure fluctuation between the discharge chamber 35 and the intermediate chamber 70. By providing the valve body 50 for performing the above, it is possible to suppress the decrease of the lubricating oil stored in the bottom of the discharge chamber 35 during the operation stop, and when the operation is restarted, the communication passage 15d is opened to promptly open the back pressure chamber. Sufficient lubricating oil can be supplied to 41 to increase the back pressure, and it is possible to suppress the occurrence of chattering.

It should be considered that the embodiments disclosed this time are exemplary in all respects and not restrictive. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

10,10a, 10b, 10c vane type compressor, 11 housing, 12 rear housing, 12a peripheral wall, 13 front housing, 13a oil flow groove, 13h, 81 holes, 13p bottom wall part, 13s, 15s end face, 14 cylinder part, 14a, 14b recess, 14c inner peripheral surface, 14d cylinder chamber, 15 rear side plate, 15d, 36d communication passage, 15e back pressure supply hole, 15r, 18r rear end surface, 16 rotation shaft, 17a shaft sealing device, 18 rotor, 18a vane Groove, 18ab bottom, 18c outer peripheral surface, 18f front end surface, 19 vanes, 20 suction space, 21 compression chamber, 22 suction port, 23 suction hole, 24, 38 joint part, 25 suction pipe, 30 discharge space, 31 discharge port, 32 Discharge valve, 34 Discharge port, 35 Discharge chamber, 36 Cover body, 36a Oil separation chamber, 36b Oil separation cylinder, 36c Oil passage, 36e guide hole, 36f storage recess, 36g storage part, 36h opening, 37 Compressed refrigerant passage , 39 Discharge piping, 41 Back pressure chamber, 50,80 Valve body, 51,82 Second pressure receiving part, 52 Connecting rod part, 53,83 First pressure receiving part, 60 Lubricating oil, 70 Intermediate chamber, 90,91 Spring, 141b extension surface, 142b mounting surface, A, B, C, D valve mechanism.

Claims (5)

A housing in which a cylinder chamber, an oil separation chamber and a discharge chamber are formed inside,
A rotating shaft supported by the housing 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 circumference,
Each of the plurality of vane grooves is provided with a vane that is attached so as to appear.
The rotor is provided with a back pressure chamber that applies back pressure to the vane.
The oil separation chamber is a substantially cylindrical space formed in a cover body that partitions the discharge chamber.
A cylindrical oil separation cylinder is fixed to one end side of the oil separation chamber.
An oil passage is formed on the other end side of the oil separation chamber.
The oil passage communicates the bottom side of the oil separation chamber with the bottom side of the discharge chamber.
The refrigerant gas compressed in the cylinder chamber swirls around the outer peripheral surface of the oil separation cylinder in the oil separation chamber to separate the lubricating oil, and the lubricating oil is discharged into the discharge chamber and separated from the refrigerant gas. The oil is delivered to the bottom of the discharge chamber and
Inside the housing, a back pressure supply path is provided that opens toward the bottom of the discharge chamber and communicates the bottom of the discharge chamber with the back pressure chamber to supply lubricating oil to the vane. Ori,
Further provided with a valve mechanism for opening and closing the opening of the back pressure supply path,
The valve mechanism is provided at a first pressure receiving portion located in the oil separation chamber and receiving a pressing force due to the pressure in the oil separating chamber, and at the bottom portion of the discharge chamber facing the first pressure receiving portion. It is, and a second pressure receiving portion for receiving a pressing force by the pressure of the discharge chamber, viewed contains a valve body,
The valve body further has a connecting rod portion that connects the first pressure receiving portion and the second pressure receiving portion to each other.
The connecting rod portion is inserted into a guide hole that opens at the bottom of the oil separation chamber.
Said valve body, said opening and closing the opening of the back pressure supply passage by the differential pressure between the oil separation chamber and the discharge chamber, base over emission type compressor. Opening before Symbol guide holes are in parallel with the opening of the back pressure supply passage, the vane type compressor according to claim 1. The cylinder chamber is partitioned by a partition wall and is partitioned by a partition wall.
The vane-type compressor according to claim 1 or 2 , wherein the back pressure supply path is provided on the partition wall. Each of the first pressure receiving portion and the second pressure receiving portion is composed of a plate-shaped member.
The vane type compressor according to any one of claims 1 to 3 , wherein the pressure receiving area of the first pressure receiving unit is larger than the pressure receiving area of the second pressure receiving unit. The vane-type compressor according to any one of claims 1 to 4 , further comprising a spring that applies an urging force in a closing direction to the valve body.

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