JPS63280883A - Variable volume type vane compressor - Google Patents

Abstract

PURPOSE:To prevent vanes from chattering by opening and closing as gas flow path for affording and interruption communication between a vane groove and a discharge chamber according to the discharge volume in response to the pivotal position of a pivotable plate. CONSTITUTION:A pivotable plate 15 as a volume controlling plate is provided between a cylinder 2, a rotor 5 and a front side plate 3 to controllably afford and interrupt communication between gas flow paths 45, 46, 47. A discharge chamber 9 and a vane groove 6 can communicate to each other through said paths 45, 46, 47 and an annular groove 28 and the back pressure of vane is varied with the rotational position of pivotable plate 15 according to the volume. Thus, discharge pressure acts on the back surface of vane in starting or small cooling load to prevent the vane from chattering.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a variable capacity vane compressor used in a refrigerant gas compressor for an automobile cabin cooling system, and in particular,
This invention relates to a structure for preventing vane chattering that occurs during startup or under low load.

[Prior Art] A conventional general vane compressor has front and rear side plates 3.4 at both open ends of a cylinder 2 housed in a housing 1, as shown in FIGS. 1 to 3, for example.
is fixed to form a sealed space, and a rotor 5 rotatably supported by both side plates 3.4 is accommodated in this space. A plurality of (four in this example) vane grooves 6 are formed in the rotor 5 over its entire width at equal intervals in the circumferential direction and with a required depth. A vane 7 that comes into sliding contact with is slidably fitted. The vane 7 divides the space inside the cylinder 2 into a plurality of compression chambers 8 .

A space surrounded by the rear side plate 4 and the rear housing 1a communicates with a discharge chamber 9, and serves as an oil separation chamber 10 for separating oil mist in the refrigerant gas discharged from the compression chamber 8. .

The rear side plate 4 is formed with an oil passage 12 for guiding the oil in the oil separation chamber 10 to the plain bearing 11 supporting the rotor 5, and the vane groove 6 is formed on the end surface of the rear side plate 4 on the rotor side. An annular groove 13 is formed to communicate with the bottom. Therefore, the oil in the oil separation chamber 10 not only lubricates the brain bearing 11, etc.
By applying a predetermined hydraulic pressure to the bottom of the vane groove 13, the vane 7 can be urged in a direction in which it comes into pressure contact with the inner peripheral surface of the cylinder.

Also, while the air conditioner is operating in a cooling mode that lowers the temperature of the passenger compartment, the compressor is required to have a large discharge capacity, but when the room temperature reaches a comfortable temperature, the operating mode of the air conditioner When shifting to the heat retention mode, the compressor only needs to be operated at a small discharge capacity. Some devices are equipped with a variable capacity mechanism that varies the discharge capacity. This variable capacity m-tank consists of a rotary plate 15 interposed between the cylinder 2 and the front side plate 2, and includes a first through hole 6 provided in the front side plate 2 and The amount of refrigerant gas sucked through these can be controlled by the degree of overlap with the second through holes 17.

[Problems to be solved by the invention] In the conventional variable displacement vane compressor as described above, the pressure in the oil separation chamber 10 is low at startup, and the vane 7
Since the pressure applied to the back of the vane (vane back pressure) is also small,
The pressure within the compression chamber 8 during the compression stroke attempts to push the vane 7 into the vane groove 6 by competing with the vane back pressure. Therefore, in such a case, there is a problem in that the vane 7 vibrates back and forth along the vane groove 6, resulting in vane chattering.

Furthermore, when the temperature inside the vehicle becomes comfortable and the cooling load on the air conditioner becomes smaller, the discharge pressure decreases due to the action of the rotary plate 15, and the pressure in the oil separation chamber 10 decreases accordingly.
Vane chattering may occur as during startup.

An object of the present invention is to solve such problems. [Means for Solving the Problems/:Means for Solving the Problems] Therefore, in the conventional variable displacement vane compressor described above, the discharge capacity is set to a required value. A rotary plate is installed between the vane groove and the discharge chamber so that the vane groove and the discharge chamber communicate with each other in the following cases, and cut off between the vane groove and the discharge chamber when the value exceeds the required value. It is characterized by forming a gas flow path that opens and closes depending on the rotational position.

[Function] In the variable capacity vane compressor of the present invention configured as described above, high pressure refrigerant gas is supplied from the discharge chamber to the vane groove even in a state where vane chattering would occur in the past. Therefore, the vane back pressure does not become smaller than the force acting on the vane due to the pressure inside the compression chamber, and vane chattering can be prevented.

[Embodiments] Hereinafter, preferred embodiments of the variable displacement vane compressor according to the present invention will be described in detail with reference to the drawings. Incidentally, since FIGS. 1 to 3 showing the conventional configuration are common to the embodiment of the present invention, these drawings will also be referred to.

In FIGS. 1 to 3, a disk-shaped front side plate 3 and a rear side plate 4 are joined to both end surfaces of a cylinder 2 having an elliptic cylindrical hollow portion of a compressor. A space is formed. A front housing 1b having a suction chamber 14 is provided on the front side of the front side plate 3.
is in communication with an external circuit via a compressor inlet 18.

A rear housing 1a is joined to the rear surface of the front housing 1b so as to surround the outer periphery of the barrier side plate 4 and the cylinder 2, and an oil separation chamber 10 is formed in a space surrounded by the rear side plate 4 and the rear housing 1a. This oil separation chamber 10 is communicated with an external circuit via one compressor outlet.

Front side plate 3 and rear side plate 4
At the center of the rotating shaft 20 is a brane bearing 11.
As shown in FIG. The cylinder chamber is divided into a pair of crescent-shaped chambers 22 that are point symmetrical with respect to the central axis of the rotor 5. A plurality of vane grooves 6 are formed with a required depth over the entire width on the circumference of the rotor 5, and each vane groove 6
The vane 7, which is slidably fitted into the cylinder 2, partitions the crescent-shaped chamber 22 into a plurality of compression chambers 8 by abutting the inner circumferential surface of the cylinder 2 at its tip.

A first through hole 16 is formed in the front side plate 3 in the thickness direction of the front side plate for guiding refrigerant gas in the suction chamber 14 to the compression chamber 8 during the suction stroke (volume increase). The first through holes 16 are provided at two points symmetrically with respect to the center of the rotating shaft 20, and are located at two points symmetrically with respect to the center of the rotating shaft 20.
is the top position ffT closest to the inner peripheral surface in the cylinder 2
It is formed in an arc shape toward the rotation direction of the rotor 5 with a starting point slightly away from the rotation direction of the rotor 5 .

A suction passage 23 extends through the cylinder 2 at a position corresponding to the first through hole 16, and a main suction port 24 that communicates the suction passage 23 with the compression chamber 8 is provided. Refrigerant gas is sucked from the first through hole 16 into the compression chamber 8 through the suction passage 23 and the main suction port 24 via the second through hole 17 formed in the rotating plate 15 .

Further, the compression chamber 8 is communicated with a discharge chamber 9 formed in a notch in the cylinder 2 through a discharge port 25 provided through the cylinder 2.
A discharge valve 26 and a retainer 27 are provided at the discharge port 25. The discharge chamber 9 communicates with an oil separation chamber 10 via a communication passage 50 provided in the rear side plate 4.

An oil passage 12 is formed in the rear side plate 4 to guide oil in the oil separation chamber 10 to the brain bearing 11.
Similarly, an annular groove 13 is formed on the end surface of the rotor side of the rear side plate 4 so as to communicate with the bottom of the vane groove 6, and an annular groove 28 that communicates with the vane groove 6 is also formed on the end surface of the front side plate 3 on the rotor side. . Then, the brain bearing 11, the rotor 5 and both side plates 3.4
The sliding surface of the vane 7 is lubricated, and a predetermined pressure is applied to the bottom of the vane groove 6 to urge the vane 7 in a direction in which it comes into pressure contact with the inner circumferential surface of the cylinder 2.

A rotating plate 15 serving as a capacity control plate is provided between the front end surfaces of the cylinder 2 and rotor 5 and the front side plate 3.
is provided. The rotary plate 15 is rotatably held around the central axis of the cylinder 2 by a shallow annular groove 29 formed on the inner surface of the front side plate 3 in communication with the annular groove 28, and then The surface forms a continuous plane with the inner surface of the front side plate 3,
The rotor 5 and the vane 7 are brought into contact with or very close to their front end surfaces. The rotary plate 15 is provided with two first through holes 16 that penetrate through the rotary plate 15 in the thickness direction so as to correspond to the first through holes 16 .

As shown in FIG. 2 and FIGS. 4 to 6, the second through hole 17 allows suction from the first through hole 16 to the suction passage 23 by adjusting the rotational position of the rotating plate 15. The cross-sectional area of the refrigerant gas passage can be changed, and the front side of the compression chamber 8 is opened to form a sub-intake port 30, from which refrigerant gas is also drawn into the compression chamber 8 during the suction stroke. I try to do that.

The second through hole 17 also functions as a bypass passage that communicates the leading compression chamber 8 on the front side of the vane 6 during the compression stroke with the trailing compression chamber 8 on the rear side during the suction stroke. do. That's what I do.

As shown in FIG. 1.3, the rotor 5 is mounted on the rotating plate 15.
A bottle 31 protruding on the opposite side is screwed into the hole 31 through an arcuate hole 32 formed in the front side plate 3.
It is loosely inserted into a long hole 34 formed in the spool 33. The spool 33 is installed in a spool chamber 36 formed by closing the opening of a bottomed hole formed near the boss portion that supports the rotating shaft 22 of the front side plate 3 with a seal plug 35, in the same direction as the tangential direction of the rotating plate 15. It is housed so that it can move back and forth in the direction. The spool chamber 36 is partitioned into a first pressure chamber 37 and a second pressure chamber 38 by the spool 33.
It houses three springs that bias it to the side.

A gas passage 40 that communicates the discharge chamber 9 and the first pressure chamber 37 passes through the cylinder 2 and the front side plate 3, and supplies refrigerant gas pressure equivalent to the discharge pressure from the discharge chamber 9 into the first pressure chamber 37. Then, this is applied to the first pressure of the spool 33.
1.

On the other hand, the cylinder 2 and the front and rear side plates 3.4 are provided with a communication passage 42 that communicates the bottom of the oil separation chamber 10 with the second pressure chamber 38, and a hydraulic pressure equivalent to the discharge pressure is transmitted through the communication passage 42. Supplied to the second pressure chamber 38, sealed plug 35
The pressure is reduced to an intermediate pressure by a leak passage 43 provided through the spool 33, and the pressure is applied to the second pressure receiving surface 44 of the spool 33. Although not shown, the communication passage 42 is provided with an on-off valve that opens when the cooling load becomes small.

Further, according to the present invention, as shown in FIGS. 4 to 7, the annular groove 2 formed in the front side plate 3
The bottom surface of 9, that is, the surface in sliding contact with the front surface of the rotating plate 15, has a circular arc shape extending from one end of the circular arc hole 32 in a counterclockwise direction in FIGS. A first gas flow path 45 is formed between the rotary plate 15 and the front surface of the rotary plate 15. Further, an arc-shaped groove having the same center and radius as the first gas flow passage 45 is cut on the front surface of the rotary plate 15, and a second gas flow path is formed in cooperation with the front side plate 3.
A gas flow passage 46 is formed. Furthermore, as clearly shown in FIG. 7, the front side plate 3 has one end opened into the annular groove 28 and the other end spaced apart from the end of the first gas flow passage 45 in the circumferential direction. Annular groove 29 at the position
A third gas flow passage 47 opening inward is bored.
The second gas flow passage 46 moves in the circumferential direction depending on the rotational position of the rotation plate 15, but the relationship of first, second and third gas flow passages 45 = 46.47 is such that the fourth ) to the intermediate capacity (Fig. 5), and from the intermediate capacity to the maximum capacity (Fig. 6), the third gas flow passage 47 communicates with the first and second gas flow passages. It has been blocked since 45.46.

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

In this compressor, the rotating shaft 20 is equipped with an electromagnetic clutch (not shown).
It is used by being connected to the engine, which is the drive source of the car, through the compressor, but if the compressor is left in a stopped state for a long time, the pressure in all the spaces inside the compressor becomes equal, and the rotating plate The spool 33 connected to the spool 15 is moved toward the first pressure chamber 37 by the spring 39 until it comes into contact with the end surface of the first pressure chamber 37 . At this time, as shown in FIG. 4, the second through hole 17 formed in the rotating plate 15 is at the most different position from the first through hole 16 of the front side plate 3 and the suction passage 23 of the cylinder 2, and , first, second and third gas flow passages 45.46
．． 47 are in communication with each other.

In this state, the clutch is connected, and the rotating shaft 20 and rotor 5
When the vane 7 starts rotating, the refrigerant gas in the suction chamber 14 is transferred from the main suction port 24 and the sub suction port 30 through the communication portion between the first through hole 16 and the second through hole 17 to the compression chamber where the volume is increasing. 8, but both through holes】6.17
Since a throttling effect is given at the communication part of the compression chamber 8
The amount of refrigerant gas absorbed by the sub suction port 3 is small.
The refrigerant gas in the compression chamber 8 which is in the middle of the compression stroke is located in a position where the discharge port side end P of 0 is moved to the side of the discharge port 25, and the refrigerant gas in the compression chamber 8 is in the middle of the suction stroke on the trailing side] Since the compressor is bypassed to No. 4 and the compression start time is delayed, the compressor operates at the minimum capacity at the beginning of startup.

When compression is started in this way, the refrigerant gas reaches the first pressure chamber 37 from the discharge chamber 9 via the gas passage 40. Furthermore, this refrigerant gas is supplied to the bottom of the vane groove 6 via the arc hole 32, the first, second, and third gas flow passages 45, 46, 47, and the annular vortex 28, and the vane back pressure is The refrigerant gas pressure is equivalent to the discharge pressure. As a result, the vane 7 is not pushed back by the pressure within the compression chamber 8, and vane chattering is prevented from occurring.

When the above-mentioned minimum capacity operation is carried out for a short time and the pressure in the discharge chamber 9 and oil separation chamber 10 rises sufficiently, the high pressure gas in the discharge chamber 9 is force-fed to the first pressure chamber 37, and the spool 33 is moved by the three springs. It is moved toward the second pressure chamber 38 against the urging force. As a result, the rotating plate 15 is rotated, and as shown in FIG. 6, the first through hole 16 and the second through hole 17 almost coincide with each other, and the communication area between them becomes the maximum. The machine is in maximum capacity operation. In this state, the third gas flow passage 47 is cut off from the discharge chamber 9, so the vane back pressure is due to the throttled hydraulic pressure from the oil separation chamber 10, but the pressure inside the oil separation chamber 10 is is also sufficiently large, so that the vane 7 is not pushed back into the vane groove 6 by the pressure within the compression chamber 8.

By maintaining such a large-capacity operating state for a certain period of time, the room temperature gradually approaches a comfortable temperature and the cooling load decreases, the on-off valve provided in the communication passage 42 opens, and discharge is discharged through the communication passage 42. Hydraulic pressure equivalent to the pressure is supplied to the second pressure chamber 38, and cooperates with the biasing force of the spring 39 to push the spool 3
3 is moved toward the first pressure chamber 37, and the rotating plate 15 rotates until it reaches the state shown in FIG. At this time, the intake amount of refrigerant gas decreases and becomes intermediate capacity operation, and the vane back pressure due to the oil pressure from the oil separation chamber 10 decreases, but the first, second and third gas flow passages 45, 46, 47 communicates again, and the refrigerant gas from the discharge chamber 9 is supplied to the vane groove 6 without being depressurized, so that no vane chattering occurs.

[Effects of the Invention] As described above, according to the present invention, high-pressure refrigerant gas from the discharge chamber acts on the back surface of the vane at startup or when the cooling load is small, and vane chattering can be prevented. . Therefore, noise caused by vane chatter is reduced, and damage caused by wear between the vane and the vane groove and collision between the vane and the inner circumferential surface of the cylinder is prevented.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view showing the present invention and a conventional variable displacement vane compressor, and FIGS. 2 and 3 are cross-sectional views taken along lines A-A and B-B in FIG. 1, respectively. 4 to 6 are cross-sectional views taken along line C-C in FIG. 1, showing one embodiment of the variable capacity vane according to the present invention, and FIG. Figure 5 shows the state during intermediate capacity operation, Figure 6 shows the state during maximum capacity operation, and Figure 7 is a cross-sectional view taken along line D-D in Figure 4. Front side plate 4: Rear side plate 5: Rotor 6: Vane groove 7: Vane 8: Compression chamber 9: Discharge chamber 10: Oil separation chamber 13.28: Tubular groove 14: Suction chamber 15: Rotating plate 16: First penetration Hole 17: Second through hole 23: Suction passage 29: Annular groove 31: Bottle 32: Arc hole 33 Varnish spool 36: Spool chamber 42: Communication passage 45: First gas flow passage 46: Second gas flow passage 47 :Third gas flow path patent applicant Toyota Industries Corporation:,l,'
I'l', i Fig. 1 r Fig. 4 Fig. 5

Claims (1)

[Claims] A rotor is rotatably supported inside a front side plate and a rear side plate fixed to both open ends of a cylinder housed in a housing, and a plurality of rotors are provided on the rotor at equal intervals in the circumferential direction. A vane is slidably fitted into each of the vane grooves, and hydraulic pressure is supplied from an oil separation chamber to the bottom of the vane groove to bring the vane into sliding contact with the inner circumferential surface of the cylinder, thereby rotating the rotor. A vane compressor that sucks refrigerant gas in a suction chamber into a compression chamber from a suction port and discharges it from a discharge port to a discharge chamber,
A rotating plate is interposed between the cylinder and the front side plate, and the suction amount of refrigerant gas supplied from the suction chamber to the compression chamber during the suction stroke is adjusted according to the rotating position of the rotating plate. In the variable capacity type vane compressor in which the discharge capacity is varied by controlling A variable capacity type characterized in that a gas flow path is formed between the vane groove and the discharge chamber, and the gas flow path is opened and closed according to the rotational position of the rotation plate so as to isolate the flow path between the vane groove and the discharge chamber. vane compressor.