JP7272310B2 - vane compressor - Google Patents

Description

This specification relates to vane-type compressors.

As disclosed in Japanese Patent Application Laid-Open No. 62-248891 (Patent Document 1), in a vane compressor, a cylinder chamber and a discharge area are formed in a housing, and a rotating shaft and a rotor are rotatable within the cylinder chamber. be provided. A plurality of vane grooves are formed in the rotor, and a plurality of vanes are provided in the plurality of vane grooves so as to be retractable. A plurality of compression chambers are formed by the rotor and the plurality of vanes. Refrigerant compressed in each compression chamber is discharged to the discharge area and separated, part of the refrigerant is discharged from the discharge area to the outside in the form of compressed gas, and part of the refrigerant is stored as lubricating oil in the discharge area.

A partition wall (also referred to as a side block or the like) that partitions the cylinder chamber is formed with a back pressure supply passage and a back pressure groove having a shape such as an arc shape (fan shape). A vane back pressure chamber is provided between the bottom surface of each vane and each vane groove. Since the vane back pressure chamber faces the back pressure supply passage, lubricating oil having a pressure equivalent to the discharge pressure is supplied from the discharge area to the vane back pressure chamber through the back pressure supply passage (high pressure hole in Patent Document 1). be. Alternatively, by having the vane back pressure chamber face the back pressure groove, the pressure in the vane back pressure chamber is adjusted according to the pressure in the back pressure groove, or lubricating oil is supplied from the back pressure groove to the vane back pressure chamber. or The pressure (back pressure) applied to the vane back pressure chamber is optimized by the lubricating oil from the back pressure groove and the lubricating oil from the back pressure supply passage, making it possible to reduce power consumption and suppress chattering.

JP-A-62-248891

In the vane-type compressor disclosed in Patent Document 1, the back pressure supply groove is formed in the partition wall (side block), and the back pressure groove extends over a predetermined angular range in the circumferential direction. It is In the case of this configuration, since the vane back pressure chamber communicates with the back pressure groove over a long section, high back pressure is applied in a section where the necessary back pressure is high, such as the section from the latter half of the compression stroke to the latter half of the discharge stroke. If it is set to supply to the vane back pressure chamber, back pressure more than necessary is supplied to the vane back pressure chamber in a section where the necessary back pressure is low, such as the section from the intake stroke to the beginning of the compression stroke. there is a possibility.

An object of the present specification is to disclose a vane compressor capable of reducing power consumption by suppressing the supply of excessive back pressure to the vane back pressure chamber.

A vane-type compressor according to the present disclosure includes a rotating shaft, a suction port for sucking refrigerant and a discharge port for discharging refrigerant, a housing that defines a cylinder chamber inside, supports the rotating shaft, and a housing that supports the rotating shaft. a rotor provided to rotate integrally with the rotating shaft and having a plurality of vane grooves; and a plurality of vanes provided in each of the vane grooves so as to be retractable, A plurality of compression chambers are formed in the cylinder chamber by the rotor, and vane back pressure chambers are provided between the bottom surfaces of the vanes and the vane grooves. and the refrigerant compressed in the compression chamber is discharged to the outside through the discharge region and the discharge port. It has a first partition wall having a first insertion hole that is open to insert and support the rotating shaft, and a second end face that partitions the cylinder chamber, and the second end face is open to receive the rotating shaft. a second partition wall provided with a second insertion hole for inserting and supporting the rotor, and arranged on the opposite side of the first partition wall in the axial direction across the rotor; A rear back pressure groove is formed which is radially spaced from the opening of the first insertion hole and communicates with the vane back pressure chamber at least in a suction stroke so as to face the back pressure chamber. A front back pressure groove extending radially from the opening of the insertion hole of the vane back pressure chamber is formed to face and communicate with the vane back pressure chamber. is larger, the rear end of the rear back pressure groove in the rotation direction of the rotating shaft is positioned rearward than the rear end of the front back pressure groove in the rotation direction of the rotating shaft, and the rear back pressure groove in the rotation direction of the rotating shaft The front end portion of the groove is positioned rearwardly of the front end portion of the front back pressure groove, and the rear back pressure groove and the front back pressure groove communicate with each other via the vane back pressure chamber.

In the vane compressor, when viewed in the axial direction of the rotating shaft, a portion of the rear back pressure groove on the front side in the rotating direction of the rotating shaft and a portion of the rotating shaft on the rear side in the rotating direction of the front back pressure groove may overlap with a part of

In the vane compressor, when viewed in the axial direction of the rotating shaft, a portion of the rear back pressure groove on the front side in the rotating direction of the rotating shaft and a portion of the rotating shaft on the rear side in the rotating direction of the front back pressure groove It does not have to overlap with a part of .

In the vane compressor, the second partition wall includes a first through hole that communicates between the lower portion of the discharge region and the second insertion hole and supplies lubricating oil to the second insertion hole. and a second through hole branching from the middle of the first through hole and communicating between the lower part of the discharge region and the vane back pressure chamber, and intermittently supplying back pressure to the vane back pressure chamber. and a back pressure supply passage is provided, and as the rotating shaft rotates, the vane back pressure chamber faces the rear back pressure groove and communicates with the rear back pressure groove, and and a first state in which the front back pressure groove and the back pressure supply passage are not opposed, and at a timing after the first state, the vane back pressure chamber faces the front back pressure groove and moves toward the front side. A second state in which the back pressure groove communicates with the back pressure groove and is not opposed to the rear back pressure groove and the back pressure supply passage, and at a timing after the second state, the vane back pressure chamber receives the back pressure. A third state may be formed in which the groove faces and communicates with the supply path and does not face the rear back pressure groove and the front back pressure groove.

In the vane compressor, as the rotating shaft rotates, the vane back pressure chamber is opened at a timing after the first state and before the second state. A state may be formed in which both the side back pressure groove and the front side back pressure groove face and communicate with each other.

In the vane compressor, the rear back pressure groove may be in communication with the vane back pressure chamber from suction to the initial compression stroke.

According to the above configuration, it is possible to obtain a vane compressor capable of reducing power consumption by suppressing the supply of back pressure more than necessary to the vane back pressure chamber.

It is a sectional view showing vane type compressor 10 in an embodiment. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1; 2 is a cross-sectional view taken along line III-III in FIG. 1; FIG. 2 is a cross-sectional view taken along line IV-IV in FIG. 1; FIG. 2 is a cross-sectional view taken along line VV in FIG. 1; FIG. It is a figure for demonstrating the 1st state S1, the state SC, the 2nd state S2, and the 3rd state S3 which are formed by the vane type compressor 10 in embodiment. FIG. 5 is a diagram showing the configuration of a bottom wall portion 13p (first partition wall) and back pressure grooves 13f1 and 13f2 in a vane compressor 10Z of a comparative example, and corresponds to FIG. 4 in the embodiment. FIG. 5 is a diagram showing the configuration of a rear side plate 15 (second partition wall) and back pressure grooves 15f1 and 15f2 of a vane compressor 10Z in a comparative example, and corresponds to FIG. 5 in the embodiment. 4 is a graph based on simulation results showing the relationship between the rotation angles of the rotating shaft 16 and the rotor 18 and the pressure in the vane back pressure chamber 41; FIG. 7 is a diagram showing the configuration of a back pressure groove applied to a vane compressor in a modified example of the embodiment, and corresponds to FIG. 6 in the embodiment;

Embodiments will be described below with reference to the drawings. In the following description, the same reference numerals are given to the same parts and equivalent parts, and redundant description may not be repeated.

[Embodiment]
(Vane compressor 10)
A vane compressor 10 according to an embodiment will be described with reference to FIGS. 1 to 6. FIG. FIG. 1 is a cross-sectional view showing a vane compressor 10. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1, and FIG. 3 is a cross-sectional view taken along line III-III in FIG.

The vane compressor 10 includes a housing 11 , a rotating shaft 16 , a rotor 18 and a plurality of vanes 19 . The housing 11 has a suction port 22 for sucking the refrigerant and a discharge port 34 for discharging the refrigerant. In this embodiment, housing 11 includes rear housing 12 , front housing 13 and rear side plates 15 .

The rear housing 12 has a peripheral wall 12a (FIGS. 2 and 3), and the front housing 13 has a cylinder portion 14 and a bottom wall portion 13p (FIG. 1) as a first partition wall. The cylinder portion 14 is formed integrally with the bottom wall portion 13p. The cylinder portion 14 is formed in a cylindrical shape and arranged inside the peripheral wall 12 a of the rear housing 12 . The front housing 13 is fixed to the rear housing 12 so that the bottom wall portion 13p closes the opening of the rear housing 12 .

A rear side plate 15 as a second partition wall has a substantially disk-like shape and is arranged inside the peripheral wall 12a of the rear housing 12 (FIG. 1). The rear side plate 15 has an end face 15s (second end face) perpendicular to the axial direction (the direction in which the axis O of the rotating shaft 16 extends), and is on the opposite side of the bottom wall portion 13p in the axial direction with the rotor 18 interposed therebetween. placed in By fixing the rear side plate 15 to the rear end of the cylinder portion 14, the end surface 15s of the rear side plate 15 defines the cylinder chamber 14d together with the cylinder portion 14. As shown in FIG.

The bottom wall portion 13p also has an end face 13s (first end face) perpendicular to the axial direction (the direction in which the axis O of the rotating shaft 16 extends). 13 s of end faces of the bottom wall part 13p also divide 14 d of cylinder chambers with the cylinder part 14. As shown in FIG. The cylinder chamber 14d is positioned between an end face 15s of the rear side plate 15 and an end face 13s (FIG. 1) of the bottom wall portion 13p.

The front housing 13 (bottom wall portion 13p) has a shaft hole 13h (first insertion hole), and the rear side plate 15 has a shaft hole 15h (second insertion hole). 13 h of shaft holes are opened to 13 s of end faces (the 1st end face), and insert and support rotating shaft 16 . The shaft hole 15h opens to the end face 15s (second end face), and supports the rotating shaft 16 by inserting it therein. The rotating shaft 16 extends into the cylinder chamber 14d. The rotating shaft 16 may be inserted through the shaft hole 15h formed in the rear side plate 15 so as to pass through the shaft hole 15h. 15h may be inserted.

The configuration of providing a shaft hole 13h for inserting the rotating shaft 16 in the front housing 13 and the configuration of providing a shaft hole 15h for inserting the rotating shaft 16 in the rear side plate 15 are not essential configurations. The rotating shaft 16 may be rotatably supported by other means. Front housing 13 and rear side plate 15 rotatably support rotating shaft 16 .

Between the rotating shaft 16 and the front housing 13, a lip seal type shaft sealing device 17a is provided. The rotating shaft 16 is arranged so as to pass through the cylinder chamber 14d. The rotor 18 is provided so as to be rotatable together with the rotating shaft 16 within the cylinder chamber 14d. The front end face of the rotor 18 faces the end face 13s of the bottom wall portion 13p on the cylinder chamber 14d side, and the rear end face of the rotor 18 faces the end face 15s of the rear side plate 15 on the cylinder chamber 14d side.

As shown in FIGS. 2 and 3, the inner peripheral surface 14c of the cylinder portion 14 has an elliptical shape, and the outer peripheral surface 18c of the rotor 18 has a circular shape. A plurality of vane grooves 18a are formed on the outer peripheral surface 18c of the rotor 18. As shown in FIG. Each of the plurality of vanes 19 is protrusively provided in each of the plurality of vane grooves 18a. A vane back pressure chamber 41 is provided between the bottom surface of each vane 19 and each vane groove 18a. Each of the plurality of vane grooves 18a (vane back pressure chambers 41) is supplied with lubricating oil within a discharge region 35 (FIG. 1), which will be described later.

As the rotating shaft 16 and the rotor 18 rotate, the tips of the vanes 19 come into contact with the inner peripheral surface 14c of the cylinder portion 14 . A plurality of compression chambers 21 are formed in the cylinder chamber 14d. By the outer peripheral surface 18c of the rotor 18, the inner peripheral surface 14c of the cylinder portion 14, the plurality of vanes 19, the end surface 13s of the bottom wall portion 13p (Fig. 1), and the end surface 15s of the rear side plate 15 (Fig. 1), a plurality of compression forces are generated. A chamber 21 is formed.

As shown in FIGS. 1 and 2, the rear housing 12 is formed with an intake port 22 . A check valve (not shown) is provided inside the suction port 22 . The cylinder portion 14 is formed with a concave portion 14a and a pair of suction holes 23 (FIG. 2). The recessed portion 14a extends over the entire circumference of the outer peripheral surface of the cylinder portion 14 in the circumferential direction. An intake space 20 is defined by the recess 14 a and the inner peripheral surface of the rear housing 12 . During the intake stroke, the compression chamber 21 and the intake space 20 communicate with each other through the intake hole 23 .

As shown in FIGS. 1 and 3, the cylinder portion 14 is formed with a pair of recesses 14b (FIG. 3). The pair of recesses 14b are located on opposite sides of the rotating shaft 16. As shown in FIG. A pair of discharge chambers 30 are defined by the pair of recesses 14 b and the inner peripheral surface of the rear housing 12 . A pair of discharge ports 31 (FIG. 3) are formed in the cylinder portion 14 . The discharge port 31 is opened and closed by a discharge valve 32 .

The refrigerant gas compressed in the compression chamber 21 pushes away the discharge valve 32 and is discharged to the discharge chamber 30 via the discharge port 31 . The discharge chamber 30 is located on the rear side of the suction space 20, and the suction space 20 and the discharge chamber 30 are formed at different positions in the axial direction. The suction space 20 is positioned closer to the bottom wall portion 13p than the discharge chamber 30, and the discharge chamber 30 is positioned closer to the rear side plate 15 than the suction space 20 is.

A discharge port 34 is formed in the rear housing 12 . A discharge region 35 is formed in the space within the housing 11 at a position opposite to the cylinder chamber 14 d with respect to the rear side plate 15 . The discharge region 35 is located on the opposite side of the cylinder portion 14 in the axial direction with respect to the rear side plate 15 . An oil separator 36 is provided in the discharge area 35 .

A communication hole 37 is formed in the rear side plate 15, and the communication hole 37 allows the discharge chamber 30 and the oil separator 36 to communicate with each other. The oil separator 36 separates lubricating oil contained in the refrigerant gas. Refrigerant in discharge chamber 30 (refrigerant compressed in compression chamber 21 ) is discharged to discharge region 35 through communication hole 37 and oil separator 36 . The discharge region 35 stores lubricating oil separated from the refrigerant compressed in the compression chamber 21 and discharges the refrigerant compressed in the compression chamber 21 to the outside through the discharge port 34 .

The rear side plate 15 is formed with an oil passage 15d1, an annular passage 15d2, and oil passages 15d3 and 15d4. The oil passage 15d1 communicates the lower portion of the discharge region 35 with the annular passage 15d2. The annular passage 15d2 is formed to surround the shaft hole 15h. The oil passage 15d1 and the annular passage 15d2 correspond to first through-holes, which connect the lower portion of the discharge region 35 and the shaft hole 15h (second insertion hole) to supply lubricating oil to the shaft hole 15h. The oil passage 15d3 communicates the annular passage 15d2 and the oil passage 15d4. The rear end of the rotary shaft 16 is positioned inside the oil passage 15d4. The oil passage 15d1, the annular passage 15d2, and the oil passages 15d3 and 15d4 can also function as first through holes, and communicate the lower portion of the discharge region 35 with the shaft hole 15h (second insertion hole) to provide lubrication. Oil is supplied to the shaft hole 15h.

(Vane back pressure chamber 41)
As described above, the space between the bottom surface of each vane 19 and each vane groove 18a is the vane back pressure chamber 41 (FIGS. 2 and 3). The vane 19 moves in and out with respect to the vane groove 18 a due to pressure changes in the vane back pressure chamber 41 .

(Rear side back pressure grooves 13a1 and 13a2)
4 is a cross-sectional view taken along line IV-IV in FIG. 1. FIG. For convenience of illustration, no hatching lines are shown in FIG. As shown in FIGS. 1, 2 and 4, rear back pressure grooves 13a1 and 13a2 are formed in an end face 13s of the bottom wall portion 13p of the front housing 13. As shown in FIG.

The rear back pressure grooves 13 a 1 and 13 a 2 are arranged on opposite sides of the axis O of the rotating shaft 16 . Both of the rear back pressure grooves 13a1 and 13a2 are opened on an end face 13s (first end face) of the bottom wall portion 13p on the cylinder chamber 14d side. Both of the rear back pressure grooves 13a1 and 13a2 are formed to extend in an arc shape having a predetermined circumferential length. The rear back pressure grooves 13a1 and 13a2 are radially separated from the shaft hole 13h (opening), and communicate with the vane back pressure chamber 41 at least during the suction stroke. The rear back pressure grooves 13a1 and 13a2 may communicate with the vane back pressure chamber 41 from intake to initial compression stroke.

The rear back pressure groove 13a1 has a front end portion 13en and a rear end portion 13st. The front end portion 13en is a portion of the rear back pressure groove 13a1 located at the front end in the rotation direction of the rotating shaft 16, and the rear end portion 13st is a portion of the rear back pressure groove 13a1 in the rotation direction of the rotating shaft 16. This is the part located at the end.

When the vane back pressure chamber 41 moves due to the rotation of the rotary shaft 16 and the rotor 18, the vane back pressure chamber 41 first faces the rear end portion 13st of the rear back pressure grooves 13a1, and moves toward the rear back pressure groove 13st. It finally faces the front end 13en of 13a1. The rear end portion 13st is the portion that the vane back pressure chamber 41 faces first, and the front end portion 13en is the portion that the vane back pressure chamber 41 faces last.

(Front side back pressure grooves 15c1 and 15c2)
5 is a cross-sectional view taken along line VV in FIG. 1. FIG. Based on the position and arrow direction of line VV shown in FIG. 1, the rear back pressure grooves 13a1, 13a2, rotor 18 and plurality of vanes 19, etc. do not inherently appear in FIG. For convenience of explanation, each of these elements is illustrated in FIG. For convenience of explanation, the front back pressure grooves 15c1 and 15c2 are also shown virtually in FIG. As shown in FIGS. 1, 3 and 5, the end surface 15s of the rear side plate 15 is formed with front back pressure grooves 15c1 and 15c2.

The front back pressure grooves 15c1 and 15c2 are arranged on opposite sides of the axis O of the rotary shaft 16. As shown in FIG. Both of the front back pressure grooves 15c1 and 15c2 open onto an end face 15s (second end face) of the rear side plate 15 on the cylinder chamber 14d side. Each of the front back pressure grooves 15c1 and 15c2 is formed to extend in an arc shape having a predetermined circumferential length. The front back pressure grooves 15c1 and 15c2 are connected to the shaft hole 15h (opening), extend radially outward from the shaft hole 15h, and communicate with the vane back pressure chamber 41 facing each other. The front back pressure grooves 15c1 and 15c2 communicate with each other through the shaft hole 15h.

The front back pressure groove 15c1 has a front end portion 15en and a rear end portion 15st. The front end portion 15en is located at the front end of the front back pressure groove 15c1 in the rotation direction of the rotating shaft 16, and the rear end portion 15st is located at the rear end of the front back pressure groove 15c1 in the rotation direction of the rotating shaft 16. It is the part that is located.

When the vane back pressure chamber 41 moves due to the rotation of the rotating shaft 16 and the rotor 18, the vane back pressure chamber 41 first faces the rear end portion 15st of the front back pressure groove 15c1, and then faces the rear end portion 15st of the front back pressure groove 15c1. It finally faces the front end portion 15en of them. The rear end portion 15st is the portion that the vane back pressure chamber 41 faces first, and the front end portion 15en is the portion that the vane back pressure chamber 41 faces last.

(Positional relationship between rear back pressure grooves 13a1 and 13a2 and front back pressure grooves 15c1 and 15c2)
As shown in FIGS. 4 and 5, in the rotation direction of the rotary shaft 16, the rear end portion 13st of the rear back pressure groove 13a1 is positioned rearward of the rear end portion 15st of the front back pressure groove 15c1. The front end portion 13en of the side back pressure groove 13a1 is located on the rear side of the front end portion 15en of the front side back pressure groove 15c1. These positional relationships are the same for the rear back pressure groove 13a2 and the front back pressure groove 15c2.

In the present embodiment, when the rear back pressure grooves 13a1 and the front back pressure grooves 15c1 are viewed from a direction parallel to the axial direction, the rear back pressure grooves 13a1 and the front back pressure grooves 15c1 overlap each other. are spaced apart from each other in the circumferential direction. These positional relationships are the same for the rear back pressure groove 13a2 and the front back pressure groove 15c2.

(Back pressure supply paths 15e1, 15e2)
1 and 5, the rear side plate 15 is also provided with a back pressure supply passage 15e1 and a back pressure supply passage 15e2. The back pressure supply paths 15e1 and 15e2 are provided at positions across the rotating shaft 16. As shown in FIG. The back pressure supply path 15 e 1 is located in front of the front back pressure groove 15 c 1 in the rotation direction of the rotor 18 , and the back pressure supply path 15 e 2 is located in front of the front back pressure groove 15 c 2 in the rotation direction of the rotor 18 .

When the back pressure supply passages 15e1, 15e2, etc. are viewed from a direction parallel to the axial direction, the back pressure supply passages 15e1, the front back pressure grooves 15c1, and the rear back pressure grooves 13a1 are arranged in the circumferential direction of the rotating shaft 16. The back pressure supply passage 15 e 2 , the front back pressure groove 15 c 2 and the rear back pressure groove 13 a 2 are also spaced apart from each other in the circumferential direction of the rotating shaft 16 .

Each of the back pressure supply passages 15e1 and 15e2 has a second through hole branching from the middle of the first through hole (here, the annular passage 15d2). and extends toward the front side. One end of this second through hole opens on the end face 15s (second end face) of the rear side plate 15, and the other end of this second through hole opens on the annular passage 15d2 (FIG. 1). ing. Each of the back pressure supply passages 15e1 and 15e2 communicates with the lower portion of the discharge region 35 via the annular passage 15d2 (FIG. 1) and the oil passage 15d1. The lubricating oil stored in the lower portion of the discharge region 35 is intermittently supplied to the vane back pressure chamber 41 through the back pressure supply passages 15e1 and 15e2.

(First state S1, second state S2, and third state S3)
Rear back pressure grooves 13a1 and 13a2 provided on the front side when viewed from the cylinder chamber 14d, front back pressure grooves 15c1 and 15c2 provided on the rear side when viewed from the cylinder chamber 14d, and back pressure supply paths 15e1, 15e2 communicates or disconnects with the vane back pressure chamber 41 by rotation of the rotary shaft 16. As shown in FIG.

As the rotating shaft 16 rotates together with the rotor 18, at least a first state S1, a second state S2 and a third state S3, which will be described below, are formed. FIG. 6 is a diagram for explaining a first state S1, a state SC, a second state S2 and a third state S3 formed by the vane compressor 10. FIG. For convenience of explanation, FIG. 6 shows the rear back pressure grooves 13a1 and 13a2, the rotor 18, and the plurality of vanes 19. As shown in FIG.

As shown in FIG. 6, in the first state S1, the vane back pressure chamber 41 faces the rear back pressure groove 13a1 and is in communication with the rear back pressure groove 13a1. It does not face the pressure supply path 15e1. This state is formed, for example, between the beginning of the intake stroke and the beginning of the compression stroke. In the first state S1, the vane back pressure chamber 41 faces only the rear back pressure groove 13a1, and the high pressure from the front back pressure groove 15c1 and the back pressure supply passage 15e1 acts as the vane back pressure. Little or no liquid is supplied to chamber 41 .

The second state S2 is formed at a timing after the first state S1. In the second state S2, the vane back pressure chamber 41 faces the front back pressure groove 15c1 and communicates with the front back pressure groove 15c1. Moreover, it does not face the rear back pressure groove 13a1 and the back pressure supply passage 15e1. This state is formed, for example, in the second half of the compression stroke. In the second state S2, the vane back pressure chamber 41 faces only the front back pressure groove 15c1, and the low pressure from the rear back pressure groove 13a1 is supplied to this vane back pressure chamber 41. Little or nothing.

The third state S3 is formed at a timing after the second state S2. In the third state S3, the vane back pressure chamber 41 faces the back pressure supply path 15e1. This state is formed, for example, from the latter half of the compression stroke to the discharge stroke. A high pressure is supplied to the vane back pressure chamber 41 from the back pressure supply passage 15 e 1 . In the third state S3, the vane back pressure chamber 41 may or may not face the front back pressure groove 15c1. Depending on whether these are communicated or not communicated, the high pressure from the vane back pressure chamber 41 is also supplied to the front side back pressure groove 15c1 or not supplied.

In the present embodiment, in one rotation of the vane back pressure chamber 41 about the rotary shaft 16, the angle range θA in which the vane back pressure chamber 41 faces the rear back pressure groove 13a1 is equal to the vane back pressure It is larger than the angular range θC in which the chamber 41 faces the front back pressure groove 15c1. The rear back pressure groove 13 a 1 and the front back pressure groove 15 c 1 communicate with each other via the vane back pressure chamber 41 . The rear back pressure groove 13 a 2 and the front back pressure groove 15 c 2 communicate with each other through the vane back pressure chamber 41 .

As shown in FIG. 6 , in the present embodiment, as the rotating shaft 16 rotates, at a timing after the first state S1 and before the second state S2, another State SC is formed. In another state SC, the vane back pressure chamber 41 faces both the rear back pressure groove 13a1 and the front back pressure groove 15c1 and communicates with both the rear back pressure groove 13a1 and the front back pressure groove 15c1. By connecting these, high pressure from the front side back pressure groove 15c1 is supplied to the rear side back pressure groove 13a1, or pressure movement in the opposite direction is performed.

(High pressure gas supply passage 15f)
As shown in FIG. 1, a high-pressure gas supply passage 15f is formed in the upper portion of the rear side plate 15. As shown in FIG. The high-pressure gas supply passage 15f communicates the upper portion of the discharge region 35 (refrigerant gas atmosphere) with, for example, the front back pressure groove 15c1. The high-pressure gas supply passage 15f has a large diameter portion 15g located on the discharge region 35 side and a small diameter portion 15j located on the front side back pressure groove 15c1 side. A valve hole is formed between the large diameter portion 15g and the small diameter portion 15j. A spherical valve element 33 is accommodated in the large diameter portion 15g so as to be able to open and close the valve hole. The valve body 33 is urged in the valve opening direction by a spring 33s. After the vane compressor 10 is started, the valve body 33 closes the high-pressure gas supply passage 15f (valve hole) when the pressure in the discharge region 35 reaches or exceeds a predetermined value.

(Action of vane compressor 10)
Referring to FIG. 2 , when rotor 18 rotates together with vanes 19 , leading vane 19 of the pair of vanes 19 forming compression chamber 21 passes through the beginning of suction hole 23 . At this time, the vane back pressure chamber 41, the rear back pressure groove 15a1, and the front back pressure groove 15c1 (or the vane back pressure chamber 41, the rear back pressure groove 13a1, and the front back pressure groove 15c1) are expanded to the extent that the vane 19 protrudes. 13c1), the pressure decreases due to the increased volume. Refrigerant gas in the suction space 20 flows into the compression chamber 21 through the suction hole 23 . When the trailing vane 19 of the pair of vanes 19 forming the compression chamber 21 finishes passing through the suction hole 23, the compression stroke starts in the compression chamber 21, and the refrigerant gas is compressed.

The discharge stroke is initiated by the leading vane 19 passing through the discharge port 31 (FIG. 3). The compressed refrigerant gas opens the discharge valve 32 and is discharged to the discharge chamber 30 through the discharge port 31 . The refrigerant gas discharged into the discharge chamber 30 flows through the communication holes 37 , and the oil contained in the refrigerant gas is separated by the oil separator 36 . The oil (lubricating oil) contained in the refrigerant gas is stored at the bottom of the discharge area 35, and the refrigerant gas is sent to the external circuit through the discharge port 34.

When the vane compressor 10 is stopped, the pressure in the discharge area 35 and the pressure in the vane back pressure chamber 41 are balanced. The valve body 33 is biased by a spring 33s and does not close (open) the high-pressure gas supply passage 15f. When the vane compressor 10 is started in this state, compressed gas corresponding to the discharge pressure is supplied to the discharge region 35 from the discharge port 31 through the communication hole 37 . Compressed gas corresponding to the discharge pressure is supplied to the vane back pressure chamber 41 via the high pressure gas supply passage 15f and the front side back pressure groove 15c1.

The vane 19 is pressed against the inner peripheral surface 14c of the cylinder portion 14 with proper back pressure. Immediately after starting, the vanes 19 are prevented from chattering, and the compression operation and the lubricating operation of the sliding surface between the rotor 18 and the vanes 19 are properly performed. After the vane type compressor 10 is started, the pressure in the discharge region 35 rises after a predetermined period of time has passed, and when the differential pressure acting on the front and rear of the valve body 33 exceeds the biasing force of the spring 33s, the valve body 33 reaches a high pressure. The gas supply passage 15f is closed.

Lubricating oil having a discharge pressure (high pressure) stored in the bottom of the discharge region 35 (FIG. 1) flows from the bottom of the discharge region 35 to the oil passage 15d1, the annular passage 15d2, the oil passages 15d3 and 15d4, and the shaft hole 15h. and flow. After that, the lubricating oil flows through the front side back pressure grooves 15c1 and 15c2 from the shaft hole 15h and is supplied to each back pressure groove.

Furthermore, the lubricating oil having a discharge pressure (high pressure) stored in the bottom of the discharge region 35 is supplied to the front back pressure grooves 15c1 and 15c2 via the back pressure supply passages 15e1 and 15e2. During operation of the vane compressor 10, the lubricating oil (back pressure) is thus supplied to the vane back pressure chamber 41, and the vanes 19 are urged in the protruding direction.

As shown in FIG. 6, in the present embodiment as described above, at least the first state S1, the second state S2 and the third state S3 are formed as the rotating shaft 16 rotates together with the rotor 18. . A particularly remarkable effect obtained by this will be described in comparison with the following comparative example.

[Comparative example]
FIG. 7 shows the configuration of the bottom wall portion 13p (first partition wall) and the back pressure grooves 13f1 and 13f2 in the vane compressor 10Z of the comparative example, and corresponds to FIG. 4 in the embodiment. FIG. 8 is a diagram showing the configuration of a rear side plate 15 (second partition wall) and back pressure grooves 15f1 and 15f2 of a vane compressor 10Z in a comparative example, and corresponds to FIG. 5 in the embodiment.

The back pressure groove 13f1 has a shape in which the rear back pressure groove 13a1 and the front back pressure groove 15c1 in the embodiment are combined on the bottom wall portion 13p. and the front back pressure grooves 15c1 are not two spaces separated from each other in the axial direction and the circumferential direction. The same applies to the back pressure groove 13f2, the back pressure groove 15f1, and the back pressure groove 15f2.

That is, in the comparative example shown in FIGS. 7 and 8, the back pressure groove is formed to extend in the circumferential direction over a predetermined angular range. In the case of this configuration, the vane back pressure chamber 41 communicates with these back pressure grooves over a long section. When the back pressure is set to be supplied to the vane back pressure chamber 41, the back pressure more than necessary is generated in the vane back pressure chamber 41 in a section where the necessary back pressure is low, such as the section from the intake stroke to the beginning of the compression stroke. 41 may be supplied.

On the other hand, in the vane compressor 10 according to the embodiment, a high back pressure is applied to the vane back pressure chamber 41 in a section where the necessary back pressure is high, such as a section from the latter half of the compression stroke to the latter half of the discharge stroke. When set to supply, the pressure in the front back pressure grooves 15c1 and 15c2 is increased.

The front back pressure groove 15c1 and the rear back pressure groove 13a1 are separated from each other in the axial direction and the circumferential direction. Very little is communicated. Therefore, it is possible to reduce the possibility that excessive back pressure is supplied to the vane back pressure chamber 41 in a section where the necessary back pressure is low, such as a section from the intake stroke to the beginning of the compression stroke. , the same applies to the front back pressure groove 15c2. Therefore, according to the vane-type compressor 10 of the present embodiment, it is possible to reduce power consumption by suppressing the supply of excessive back pressure to the vane back pressure chamber 41. there is

FIG. 9 is a graph based on simulation results showing the relationship between the rotation angles of the rotary shaft 16 and the rotor 18 and the pressure in the vane back pressure chamber 41 . In the example based on the embodiment, the pressure in the vane back pressure chamber 41 is increased in the range from 10° (initial stage of the intake stroke) to 110° (first half of the compression stroke) as compared to the case of the comparative example. It can be seen that it can be made smaller.

As described above, in the present embodiment (see FIG. 6), during one rotation of the vane back pressure chamber 41 about the rotation shaft 16, the vane back pressure chamber 41 faces the rear back pressure groove 13a1. The angular range .theta.A where the vane back pressure chamber 41 faces the front side back pressure groove 15c1 is larger than the angle range .theta.C. Setting a low pressure in the vane back pressure chamber 41 in the long first half of a series of cycles of suction, compression and discharge to suppress the supply of excessive back pressure to the vane back pressure chamber 41 Therefore, it is possible to reduce power consumption. Depending on the specifications, the magnitude relationship between the angle ranges θA and θC may be reversed.

As shown in FIG. 6 , in the present embodiment, as the rotating shaft 16 rotates, at a timing after the first state S1 and before the second state S2, another State SC is formed. In another state SC, the vane back pressure chamber 41 faces both the rear back pressure groove 13a1 and the front back pressure groove 15c1 and communicates with both the rear back pressure groove 13a1 and the front back pressure groove 15c1.

By connecting these, high pressure from the front side back pressure groove 15c1 is supplied to the rear side back pressure groove 13a1, or pressure movement in the opposite direction is performed. By suppressing the setting of an excessively low pressure in the vane back pressure chamber 41 during the long first half of the series of cycles of suction, compression, and discharge, an appropriate pressure higher than the required pressure is ensured. Also, chattering can be suppressed.

Further, in the present embodiment, the discharge region 35 is provided on the rear side, and the back pressure supply passages 15e1 and 15e2 are also provided on the rear side plate 15, thereby simplifying and simplifying the device in the axial direction. is possible. The back pressure supply path may be provided on the front side according to specifications.

FIG. 10 is a diagram showing the configuration of a back pressure groove applied to a vane compressor in a modified example of the embodiment, and corresponds to FIG. 6 in the embodiment. As shown in FIG. 10, when the rear back pressure groove 13a1 and the front back pressure groove 15c1 are viewed from a direction parallel to the axial direction (that is, when viewed in the axial direction of the rotating shaft 16), the rear back pressure groove A portion of the rotary shaft 16 of the 13a1 on the front side in the rotation direction and a portion of the front back pressure groove 15c1 on the rear side in the rotation direction of the rotary shaft 16 may overlap. By suppressing the setting of an excessively low pressure in the vane back pressure chamber 41 during the long first half of the series of cycles of suction, compression, and discharge, an appropriate pressure higher than the required pressure is ensured. Also, chattering can be suppressed.

In this embodiment, rear back pressure grooves 13a1 and 13a2 are provided on the front side, and front back pressure grooves 15c1 and 15c2 are provided on the rear side. The configuration is not limited to such a configuration, and the front side back pressure groove may be provided on the front side and the rear side back pressure groove may be provided on the rear side.

In the housing 11, the bottom wall portion 13p and the cylinder portion 14 are integrally formed, but instead of this configuration, the bottom wall portion 13p is formed separately from the cylinder portion 14 as a front side plate, and is axially mounted. , the cylinder portion 14 may be arranged between the front side plate and the rear side plate 15 which are arranged with a space therebetween. In this configuration, the front side plate constitutes the first partition wall, and the rear side plate constitutes the second partition wall.

Although the embodiments have been described above, the above disclosure is illustrative in all respects and is not restrictive. The technical scope of the present invention is indicated by the scope of claims, and is intended to include all modifications within the meaning and scope of equivalence to the scope of claims.

Reference Signs List 10, 10Z vane compressor, 11 housing, 12 rear housing, 12a peripheral wall, 13 front housing, 13a1, 13a2, 15a1 rear back pressure groove, 13c1, 15c1, 15c2 front back pressure groove, 13en, 15en front end portion, 13f1 , 13f2, 15f1, 15f2 back pressure groove, 13h, 15h shaft hole, 13p bottom wall portion, 13s, 15s end surface, 13st, 15st rear end portion, 14 cylinder portion, 14a, 14b recessed portion, 14c inner peripheral surface, 14d cylinder chamber 15 rear side plate 15d1, 15d3, 15d4 oil passage 15d2 annular passage 15e1, 15e2 back pressure supply passage 15f high pressure gas supply passage 15g large diameter portion 15j small diameter portion 16 rotary shaft 17a shaft seal device 18 Rotor 18a Vane groove 18c Peripheral surface 19 Vane 20 Suction space 21 Compression chamber 22 Suction port 23 Suction hole 30 Discharge chamber 31, 34 Discharge port 32 Discharge valve 33 Valve element 33s Spring 35 discharge area, 36 oil separator, 37 communication hole, 41 vane back pressure chamber, O axial center, S1 first state, S2 second state, S3 third state, SC state.

Claims (6)

a rotating shaft;
a housing having a suction port for sucking refrigerant and a discharge port for discharging refrigerant, partitioning a cylinder chamber therein, and supporting the rotating shaft;
a rotor provided to be integrally rotatable with the rotating shaft in the cylinder chamber and having a plurality of vane grooves;
a plurality of vanes each provided in each of the vane grooves so as to be retractable,
A plurality of compression chambers are formed in the cylinder chamber by the plurality of vanes and the rotor,
Between the bottom surface of each vane and each vane groove is a vane back pressure chamber,
The housing defines a discharge area inside the housing, and the refrigerant compressed in the compression chamber is discharged to the outside through the discharge area and the discharge port,
The housing is
a first partition wall having a first end surface that partitions the cylinder chamber and having a first insertion hole that is open to the first end surface and into which the rotating shaft is inserted and supported;
It has a second end face that defines the cylinder chamber, and is provided with a second insertion hole that is open to the second end face and into which the rotating shaft is inserted to support the rotating shaft. a second partition wall positioned opposite the wall;
The first end surface is formed with a rear back pressure groove that is radially spaced from the opening of the first insertion hole and communicates with the vane back pressure chamber at least during a suction stroke,
A front back pressure groove extending radially from the opening of the second insertion hole and communicating with the vane back pressure chamber is formed in the second end face,
The angle range of the rear back pressure groove is larger than the angle range of the front back pressure groove,
A rear end portion of the rear back pressure groove in the rotation direction of the rotating shaft is located rearward of a rear end portion of the front back pressure groove, and a front end of the rear back pressure groove in the rotation direction of the rotating shaft. is positioned rearward of the front end of the front back pressure groove,
the rear back pressure groove and the front back pressure groove communicate with each other via the vane back pressure chamber,
vane type compressor. When viewed in the axial direction of the rotating shaft, a portion of the rear back pressure groove on the front side in the rotation direction of the rotating shaft and a portion of the front back pressure groove on the rear side in the rotating direction of the rotating shaft overlap,
The vane compressor according to claim 1. When viewed in the axial direction of the rotating shaft, a portion of the rear back pressure groove on the front side in the rotation direction of the rotating shaft and a portion of the front back pressure groove on the rear side in the rotating direction of the rotating shaft do not overlap,
The vane compressor according to claim 1. The second partition wall includes a first through hole for communicating a lower portion of the discharge region and the second insertion hole and supplying lubricating oil to the second insertion hole, and the first through hole. A back pressure supply path is provided which branches from the middle and has a second through hole communicating between the lower portion of the discharge region and the vane back pressure chamber, and intermittently supplies back pressure to the vane back pressure chamber. and
As the rotating shaft rotates,
a first state in which the vane back pressure chamber faces the rear back pressure groove and communicates with the rear back pressure groove and does not face the front back pressure groove and the back pressure supply passage;
At a timing after the first state, the vane back pressure chamber faces the front back pressure groove and communicates with the front back pressure groove, and the rear back pressure groove and the back pressure supply passage. a second state not facing the
A third state, at a timing after the second state, in which the vane back pressure chamber faces and communicates with the back pressure supply passage and does not face the rear back pressure groove and the front back pressure groove. and are formed,
The vane compressor according to any one of claims 1 to 3. With the rotation of the rotating shaft, the vane back pressure chamber is moved to the rear side back pressure groove and the front side back pressure groove at a timing after the first state and before the second state. A state is formed in which both pressure grooves face and communicate with each other,
The vane compressor according to claim 4. The rear back pressure groove communicates with and faces the vane back pressure chamber from intake to initial compression stroke,
The vane compressor according to any one of claims 1 to 5.

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