JPH0528396Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Field of Application] This invention relates to a vane compressor used in vehicle air conditioners and the like, and more specifically to a vane chattering prevention mechanism in the compressor.

[Conventional technology]

Generally, in vane compressors, conventionally,
A vane compressor as shown in FIGS. 6 and 7 has been proposed. This vane compressor has vane grooves 14 in the rear side plate 3 from the compression chamber 16 during the suction stroke to the compression chamber 16 in the middle of the compression stroke.
A pair of back pressure grooves 2 communicating with the back pressure passage 15 at the bottom
8, 28, and an intermediate pressure oil supply passage 29 in which a back pressure groove 28 and an oil separation chamber 7 are provided in the rear side plate.
The back pressure groove 28 is connected to the back pressure groove 28 to supply oil at an intermediate pressure between the discharge pressure and the suction pressure. In addition, an oil separation chamber 7 is provided in the rear side plate 3.
The oil corresponding to the discharge pressure from the back pressure grooves 28, 2 is
8, that is, in the confinement section D of the back pressure passage 15 corresponding to the end of the compression stroke, a high pressure oil supply passage 30 is provided that constantly supplies sliding contact to the rear side sliding end surface of the rotor 11, and the oil at the discharge pressure is The back pressure groove 28
The vane back pressure is increased by supplying the vane to the back pressure passage 15 located in the confinement section D.

However, since the oil in this vane compressor has high viscosity, the oil flows into the back pressure passage 1 at the beginning of startup.
During this time, the pressure P1 acting on the tip 13a of the vane 13 (hereinafter referred to as "vane tip pressure P1") is higher than the pressure P1 acting on the tip 13a of the vane 13.
There was a problem in that the back pressure P2 (hereinafter referred to as "vane back pressure P2") acting on the inner end surface of the vane 13 became small, causing the vane 13 to chattering. That is,
When the pressure in the compression chamber 16 is high and the vane tip pressure P1 is high, such as at the end of the compression stroke, the vane back pressure P2 becomes insufficient as shown in FIG. is slightly spaced from the inner circumferential surface 1a. As a result, compressed gas leaks from the leading side compression chamber 16 to the trailing side compression chamber 16, so the pressure in the leading side compression chamber 16 decreases, and as a result, the vane back pressure P2 increases at the vane tip. The pressure becomes relatively larger than the pressure P1, and the vane 13 is pressed against the inner circumferential surface 1a of the cylinder 1. This repeated protruding and retracting operation of the vane 13, that is, chattering occurs, causing the vane 13 and rotor 11 to
wear is accelerated and compression efficiency decreases.

On the other hand, in order to solve this problem, a vane compressor ( Actual public school 54
-Refer to Publication No. 33604) has also been proposed. This vane compressor, as shown in Figures 9 and 10,
A high pressure gas supply passage 32 is provided in the upper part of the rear side plate 3 and communicates between the upper part of the oil separation chamber 7 and the back pressure groove 28.
A valve chamber 32a is provided in the middle of the valve chamber 32a, and the valve chamber 32a accommodates a spherical check valve 33 which is normally biased in the closing direction by a coiled compression spring 34. Immediately after the vane compressor is started, refrigerant gas equivalent to the discharge pressure is supplied from the upper part of the oil separation chamber 7 to the back pressure passage 15 via the high pressure gas supply passage 32, which urges the vane 13 in the projecting direction. The back pressure P2 was optimized to prevent chattering and reduce compression efficiency.

In the case of a vane compressor equipped with this back pressure applying mechanism, when the check valve 33 is in an open state, the back pressure groove 28 is filled with refrigerant gas corresponding to the discharge pressure, and the
As shown by the chain line in the figure, the vane back pressure P2 is higher than the vane tip pressure P1, so the problems that occur in the vane compressor shown in FIGS. 6 and 7 are eliminated.

[The problem that the idea attempts to solve]

However, even in the vane compressor equipped with the back pressure applying mechanism, the compression operation continues,
When the pressure in the oil separation chamber 7 increases and the force due to the pressure difference before and after the check valve 33 becomes small, and the check valve 33 is closed by the biasing force of the compression spring 34, the back pressure passage 15 and The high-pressure refrigerant gas trapped in the vane groove 14 is likely to leak to the low-pressure compression chamber 16 through gaps such as the sliding surfaces between the rotor 11 and the vane 13, and the intermediate pressure from the intermediate-pressure oil supply passage 29 is likely to leak. Since the oil is supplied to the same back pressure groove 28 as the high pressure refrigerant gas, the oil is supplied to the back pressure passage 1 due to the pressure of the refrigerant gas and the viscosity of the oil itself.
5 will be delayed. As a result, for a predetermined period of time after the check valve 33 is closed, the vane back pressure P2 is higher than the vane tip pressure P1, as shown by the broken line in FIG. There is a problem that there is a section where P2 decreases, and chattering of the vane 13 occurs in this section.

This invention prevents the occurrence of vane chattering in a certain section immediately after the compressor is started and the check valve in the high-pressure gas supply passage is closed, which has been a problem in vane compressors equipped with the above-mentioned back pressure applying mechanism. That is the purpose.

[Means to solve the problem]

In order to achieve the above object, this invention relates to a vane chattering prevention mechanism in a vane compressor, which includes an elliptical cylinder having an inlet and an outlet, and a front and rear cylinder fixed to both front and rear end surfaces of the cylinder. a side plate, a rotor rotatably supported by a rotating shaft so as to form a pair of working chambers within the cylinder, and a rotor slidable within a plurality of radial vane grooves formed in the rotor. a housing provided to cover at least the rear side plate and forming an oil separation chamber between the inserted vane and a side surface of the rear side plate; a housing that extends through the rear side plate and includes a discharge chamber and the oil separation chamber; and a pair of back pressure passages carved in the rotor side sliding contact surface of the rear side plate and communicating with the back pressure passage formed at the bottom of the vane groove from the beginning to the middle of the compression stroke. a pressure groove, an intermediate pressure oil supply passage formed in the rear side plate and for reducing the oil in the oil separation chamber to an intermediate pressure and supplying it to the back pressure groove; and an intermediate pressure oil supply passage formed in the rear side plate and having one end. is opened into the oil separation chamber, and the other end is arranged so as to always correspond to the rear side sliding end surface of the rotor in the closed section of the back pressure passage provided between the pair of back pressure grooves and corresponding to the end of the compression stroke. A high-pressure oil supply passage that is open and supplies oil equivalent to the discharge pressure between the sliding surfaces of the rear side plate and the rotor, and each of the oil supply passages that supply oil to the rear side plate are independent of each other. a high-pressure gas supply passage for supplying refrigerant gas in the oil separation chamber from the oil separation chamber to the back pressure groove; A spherical check valve energized by the valve is adopted.

[Effect]

When the vane compressor is stopped, the pressure in the oil separation chamber and the pressure in the back pressure passage are balanced, so the check valve is opened by the biasing member. When the compressor is started in this state, the high-pressure refrigerant gas that has just been discharged from the discharge port to the oil separation chamber is quickly supplied from the high-pressure gas supply passage to the back pressure passage, so the back pressure of the vane at the time of startup is The upward movement is ensured, and the sliding surfaces between the rotor and the vanes are lubricated by the mist-like oil contained in the refrigerant gas, and proper compression operation is performed.

Shortly after starting the compressor, the pressure in the oil separation chamber increases and the pressure acting on the check valve exceeds the biasing force of the biasing means, the check valve is closed and from then on, the high pressure gas supply passage is The refrigerant gas supply is cut off.

When this refrigerant gas supply is cut off, first, high-pressure oil from the high-pressure oil supply passage is supplied to the back pressure passage and the back pressure passage of the confinement section through the sliding surface of the rear side plate and the rotor. This oil provides a back pressure higher than the vane tip pressure in the back pressure passage. Thereafter, intermediate pressure oil is also supplied from the intermediate pressure oil supply passage to the back pressure passage, and a back pressure higher than the vane tip pressure is always applied. Therefore, chattering of the vanes is prevented during startup and in the operating state after startup, and compression efficiency does not decrease.

〔Example〕

Hereinafter, an example that embodies this idea will be described.
FIG. 5 will be explained.

As shown in Figures 1 and 4, a front side plate 2 and a rear side plate 3 are joined to both end surfaces of a cylinder 1 having an elliptical hollow part, and these form an elliptical cylindrical space for accommodating the rotor. has been done. A front housing 5 having a suction chamber 4 is provided on the front side of the front side plate 2 . A rear housing 6 is joined to the rear surface of the front housing 5 so as to enclose the cylinder 1 and the rear side plate 3, and an oil separation chamber 7 is formed in the rear part thereof in cooperation with the rear side plate 3.

A rotating shaft 8 is supported by a radial needle bearing 9 and a radial plain bearing 10 in shaft holes 2a and 3a extending through the center of the front side plate 2 and rear side plate 3, and is fitted into the rotating shaft 8. fixed rotor 1
1 is housed in the elliptical cylindrical hollow part of the cylinder 1,
A pair of crescent-shaped working chambers 12 are formed (see FIG. 4).

On the circumference of the rotor 11, vane grooves 14 are formed with a required depth over the entire width and into which a plurality of vanes 13 (in this embodiment, five vanes are shown) are slidably fitted. At the inner end of the vane groove 14, there is a back pressure passage 15 for applying back pressure by oil and/or refrigerant gas to the inner end surface of the vane 13 to press the vane 13 against the inner circumferential surface 1a of the cylinder 1. It is formed.

The pair of working chambers 12 are each divided into a plurality of compression chambers 16 by the vanes 13, and the compression chambers 16 each have a suction passage 17 extending through the front side plate 2 and the cylinder 1, and a suction port 18.
It is communicated with the suction chamber 4 by. Further, the compression chamber 16 is communicated with a discharge chamber 20 through a discharge port 19, and the discharge chamber 20 is further communicated with the oil separation chamber 7 through a communication hole 21. In addition, 22
23 is a discharge valve, 23 is a retainer, 24 is an oil separation plate, and 25 is a cover for the plain bearing 10 fitted on the back side of the rear side plate 3, and an oil separation plate 25a is also integrally formed on the back side. .

An annular passage 3b is formed in the rear side plate 3 so as to surround the plain bearing 10, and the passage 3b and the bottom of the oil separation chamber 7 communicate with each other through an oil passage 26 formed in the rear side plate 3. In addition, each of the sliding contact surfaces of the front side plate 2 and the rear side plate 3 on the rotor 11 side is provided with a pair of back pressure grooves each having an arcuate shape when viewed from the axial direction of the rotor 11, as shown in FIGS. 3 and 2. 27 and 28 are carved, and these are provided so as to communicate with the back pressure passage 15 from the beginning to the middle of the compression stroke. Note that the back pressure grooves 27 on the front side shown in FIG.
The back pressure grooves 28 on the rear side shown in the figure are communicated with each other by a narrow groove 3c cut out in the inner peripheral edge of the shaft hole 3a of the rear side plate 3, and the back pressure groove 28 and the narrow groove 3c are connected to the plane by the shaft hole 3a. It communicates with the slit of the bearing 10. In this embodiment, the oil at the discharge pressure from the oil separation chamber 7 is reduced to an intermediate pressure into the back pressure groove 28 by the oil passage 26, the annular passage 3b, the slit of the plain bearing 10, the shaft hole 3a, etc. It constitutes an intermediate pressure oil supply passage 29 for supplying the oil. When the compressor is in operation, the intermediate pressure oil supply passage 29 is connected to the oil separation chamber 7.
Oil reduced to an intermediate pressure is supplied to the back pressure passage 15, and the vane 13 is urged in the direction of protrusion (into pressure contact with the inner circumferential surface 1a of the cylinder 1).

The rear side plate 3 has one end opened to the annular passage 3b, and the other end opened between the pair of back pressure grooves 28, 28, that is, when the vane 13 enters the final stage of the compression stroke, the back pressure passage 15 is closed. A back pressure passage 15 provided in the rotor 11 is located in the center of the section (hereinafter referred to as "confinement section D").
The rotor 11 is placed in a position that does not interfere with the rotation locus of
An oil passage 3d, which is always open, is provided through the rear side sliding end surface. In this embodiment, the oil passage 26, the annular passage 3b, and the oil passage 3d are used to supply high pressure oil equivalent to the discharge pressure from the bottom of the oil separation chamber 7 between the sliding surfaces of the rear side plate 3 and the rotor 11. It constitutes an oil supply passage 30. This high-pressure oil supply passage 30 supplies oil equivalent to the discharge pressure from the oil separation chamber 7 to the rear side plate 3 and the rotor 1.
At the same time, some of the oil is supplied to the back pressure groove 28, and the remaining oil is supplied to the back pressure groove 28 near the oil passage 3d of the high pressure oil supply passage 30 at the end of the compression stroke. It is supplied to the pressure passage 15 to increase the back pressure of the vane 13.

As shown in FIG. 3, the sliding surface of the front side plate 2 on the rotor 11 side has back pressure grooves 27,
A recess 2b is formed so as to be located in the center of the confinement section D formed between 27 and 27, and communicates with the back pressure passage 15 at the end of the compression stroke to suppress an excessive increase in vane back pressure. However, depending on the cylinder profile, it may not be necessary. In addition, the front side plate 2 has a shaft hole 2a.
an annular groove 2 that engages a seal ring 31 in close proximity to
engraved with c.

Next, a high-pressure gas supply mechanism that supplies refrigerant gas equivalent to the discharge pressure to the back pressure passage 15 will be explained.

An oil separation chamber 7 is located above the rear side plate 3.
A high-pressure gas supply passage 32 is formed that communicates the upper part, that is, the refrigerant gas atmosphere, with the upper back pressure groove 28 on the rear side. A spherical check valve 33 that can open and close the valve hole 32b is housed in a large-diameter valve chamber 32a formed on the oil separation chamber 7 side of the high-pressure gas supply passage 32, and a small-diameter spring of the high-pressure gas supply passage 32 Containment room 3
2c is a compression spring 3 in a coil shape as a biasing member that always biases the check valve 33 in the opening direction.
4 is accommodated. The check valve 33 is prevented from separating from the valve chamber 32a by the cover 25.

Further, the biasing force of the compression spring 34 is set such that the check valve 33 closes the valve hole 32b when the pressure in the oil separation chamber 7 exceeds a predetermined value after the compressor is started.

Next, the operation of the vane compressor configured as described above will be explained.

When the rotor 11 is rotated in the direction of the arrow in FIG. When the preceding vane 13 passes the starting end of the suction port 18 , the refrigerant gas in the suction chamber 4 flows into the compression chamber 16 from the suction port 18 .

When the succeeding vane 13 of the pair of vanes 13 forming the compression chamber 16 finishes passing through the suction port 18, a compression stroke begins in this compression chamber 16, and after the preceding vane 13 passes through the discharge port 19,
During the discharge stroke, the compressed refrigerant gas opens the discharge valve 22 due to the pressure difference and flows from the compression chamber 16 to the discharge port 1.
9 and is discharged into the discharge chamber 20. Then, the refrigerant gas discharged to the discharge chamber 20 enters the oil separation chamber 7 from the communication hole 21, collides with the oil separation plate 24 here and moves downward, and then the oil separation plate 25
The oil contained in the refrigerant gas is thus separated and stored at the bottom of the oil separation chamber 7, and the refrigerant gas is discharged to the external circuit.

By the way, when the compressor is stopped, the pressure in the oil separation chamber 7 and the pressure in the back pressure passage 15 of the vane 13 are balanced, so the check valve 33 is opened by the compression spring 34. When the vane compressor is started in this state, the refrigerant gas corresponding to the discharge pressure supplied from the discharge port 19 to the oil separation chamber 7 via the communication hole 21 flows from the high-pressure gas supply passage 32 to the back pressure groove 28 and backs up. Since the pressure is supplied to the pressure passage 15, the vanes 13 are brought into pressure contact with the inner circumferential surface 1a of the cylinder 1 by appropriate back pressure, and the compression operation at the time of startup and the rotor 11 and the vanes 13 are
Proper lubrication of sliding surfaces, etc.

As the internal pressure of the oil separation chamber 7 increases, oil is supplied to the high-pressure oil supply passage 30 which is not throttled, and the end surface of the rotor is lubricated.

After a predetermined period of time has passed after the compressor is started, the pressure in the oil separation chamber 7 increases and the differential pressure acting before and after the check valve 33 exceeds the biasing force of the compression spring 34. will be closed. At this time, the gas in the back pressure groove 28 escapes from between the sliding surfaces of the rear side plate 3 and the rotor 11 to the compression chamber 16 side, so the pressure in the back pressure groove 28 decreases by that amount. However, check valve 3
3, the high pressure oil supply passage 30 is closed.
Since high-pressure oil is supplied to the back pressure passage 15, the drop in back pressure caused by the gas leak is compensated for by the supply of this high-pressure oil.

Thereafter, intermediate-pressure oil is supplied from the intermediate-pressure oil supply passage 26 to the back-pressure passage 15, and high-pressure oil continues from the high-pressure oil supply passage 30, causing the rear side plate 3 and rotor 11 to come into sliding contact. It is supplied to the back pressure passage 15 through the back pressure groove 28 and the like between the surfaces. As a result, the pressure in the back pressure passage 15 is maintained at a high level both when the back pressure passage 15 is in a position corresponding to the back pressure groove 28 and when in the confinement section D. Therefore, as shown by the solid line in FIG. 5, the vane back pressure P2 is always maintained higher than the vane tip pressure P1, and the vane 13
chattering is prevented.

[Effect of idea]

As detailed above, according to this invention, not only when starting the vane compressor, but also after starting the compressor.
Even in a certain section immediately after the check valve in the high-pressure gas supply passage is closed, the high-pressure oil supply is formed independently of the high-pressure gas supply passage, and its oil supply action is not affected by the high-pressure refrigerant gas. The oil supply from the passage quickly compensates for the leakage of the high-pressure refrigerant gas supplied from the high-pressure gas supply passage to the compression chamber, etc., and reliably prevents the vane back pressure from falling below the vane tip pressure. This has the excellent effect of reliably preventing chattering of the vanes during startup and in the operating state after startup, thereby increasing compression efficiency.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of the central part of the vane compressor according to this invention showing a mechanism for preventing chattering movement of the vanes, Figs. 2 and 3 are front views showing the front and rear side plates, respectively, and Fig. 4 is a sectional view of the vane. A cross-sectional view of the compressor, FIG. 5 is a graph showing the relationship between vane tip pressure and vane back pressure, FIG. 6 is a vertical cross-sectional view of the central part of a conventional vane compressor, and FIG. 7 is a cross-sectional view of the same. FIG. 8 is a graph showing the relationship between vane tip pressure and vane back pressure in the conventional example, FIG. 9 is a longitudinal cross-sectional view of the central part showing another conventional example, and FIG.
The figure is a front view of another conventional rear side plate. 1...Cylinder, 2...Front side plate, 3...Rear side plate, 11...Rotor, 12...Working chamber, 13...Vane, 14...
Vane groove, 15... Back pressure passage, 16... Compression chamber,
18...Suction port, 19...Discharge port, 20...Discharge chamber, 21...Communication hole, 26...Oil passage, 27,2
8... Back pressure groove, 29... Oil passage 26 and annular passage 3
b, an intermediate pressure oil supply passage consisting of a gap in the plain bearing 10 and the shaft hole 3a, 30... a high pressure oil supply passage consisting of an oil passage 26, an annular passage 3b and an oil passage 3d, 32... a high pressure gas supply passage; 33...Check valve, 34...Compression spring as a biasing member, D...
Confinement section of back pressure passage 15.

Claims (1)

[Claims for Utility Model Registration] An elliptical cylinder 1 having an inlet 18 and an outlet 19; front and rear side plates 2 and 3 fixed to both front and rear end surfaces of the cylinder 1; and the cylinder. a rotor 11 rotatably supported by a rotating shaft 8 so as to form a pair of working chambers 12 within the rotor 11; and a rotor 11 slidably inserted into a plurality of radial vane grooves 14 formed in the rotor 11. a housing 6 which is provided to cover at least the rear side plate 3 and forms an oil separation chamber 7 between the side surface of the rear side plate 3; and a housing 6 which is provided through the rear side plate 3 and a discharge chamber. 20 and the oil separation chamber 7 communicate with each other.
1, and a pair of back pressures carved on the sliding contact surface of the rear side plate 3 on the rotor 11 side and communicating with the back pressure passage 15 formed at the bottom of the vane groove 14 from the beginning to the middle of the compression stroke. grooves 28, 28; an intermediate pressure oil supply passage 29 formed in the rear side plate 3 and for reducing the oil in the oil separation chamber 7 to an intermediate pressure and supplying the oil to the back pressure grooves 28, 28; The back pressure passage 15 is formed in the rear side plate 3 and has one end open to the oil separation chamber 7 and the other end provided between the pair of back pressure grooves 28 and 28 in a closed section of the back pressure passage 15 corresponding to the end of the compression stroke. , a high-pressure oil supply passage 30 that is always open so as to correspond to the rear side sliding end surface of the rotor 11 and for supplying oil equivalent to the discharge pressure between the sliding surface of the rear side plate 3 and the rotor 11; It is formed independently of the oil supply passages 29 and 30 for supplying oil to the plate 3, and supplies refrigerant gas from the oil separation chamber 7 to the back pressure grooves 28 and 28. A vane compressor comprising: a high-pressure gas supply passage 32 for the purpose of discharging the air; and a spherical check valve 33 accommodated in the high-pressure gas supply passage 32 and normally biased to the open position by a biasing member 34. Vane chattering prevention mechanism.