JPH0259313B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used as a refrigerant compressor for, for example, an automobile air conditioner.

(Prior Art and its Problems) Conventionally, the so-called vane compressor has been designed to control the capacity of a vane compressor by adjusting the suction amount of gas to be compressed.
As a variable capacity vane type compressor, it was developed in 1982.
No. 2000 is publicly known.

Such conventional vane type compressors have an arc-shaped slot bored through the end plate on the side of the suction port provided in the lower part of the cylinder, and a throttle plate is slidably fitted into the slot. The throttle plate is slidably displaced within the slot, and the length of the suction port is restricted at the tip thereof, thereby changing the compression start position and varying the discharge capacity. Further, one end of a swinging lever is connected to the throttle plate via a shaft, the swinging lever is pivotally supported by a support shaft fixed to the end plate, and an actuator connected to the other end of the swinging lever is connected to the throttle plate via a shaft. rotates the swing lever to slide the throttle plate.

Therefore, since the actuator, which is the driving means, displaces the throttle plate, which is the control member of the suction port, through the swing lever, the hysteresis of the control member is large, and the processing and assembly are complicated. There was a problem.

Further, the present applicant has filed Japanese Patent Application No. 1984-71984 for a vane type compressor in which the hysteresis of the control member described above is reduced. The vane type compressor according to the application includes a cam ring whose both end faces are closed with side blocks, a rotor rotatably disposed within the cam ring, and a rotor slidably fitted into a vane groove of the rotor. The rotor is defined by the side block, the rotor, and the vanes, and includes a plurality of vanes, a control member displaceably attached to the suction port of the one side block, and a driving means for driving the control member. A vane type compressor which compresses fluid by changing the volume of a compression chamber, and whose discharge capacity can be variably controlled by changing the compression start position of the suction port using the control member. In this, the control member is provided with teeth for being driven, and teeth that mesh with the teeth are provided on the output shaft of the drive means, so that the control member is directly driven by the drive means. It is something.

However, since this vane type compressor has a step motor built into the housing as a driving means, it requires a large storage space, has a complicated structure, and is expensive. .

(Objective of the Invention) The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a vane type compressor equipped with a variable capacity control mechanism that has a simple and compact structure, is low in cost, and has high control reliability. With the goal.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention includes a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a rotor that is rotatably disposed within the cam ring. a vane slidably fitted in a vane groove of the vane, the vane compressing fluid by varying the volume of a cavity defined by the side block, cam ring, rotor, and vane. In the type compressor, a bypass port provided in the side block having the suction port of both the side blocks, and a pressure actuation device provided in the side block having the suction port and communicating with the low pressure chamber side and the high pressure chamber side. a chamber, and the pressure working chamber is airtightly divided into a first chamber communicating with the low pressure chamber side and a second chamber communicating with the low pressure chamber side and the high pressure chamber side. a control member having a pressure receiving member slidably fitted therein and controlling the opening angle of the bypass port; and a biasing member urging the control member in a direction in which the opening angle of the bypass port becomes larger. A low-pressure communication path that communicates between the second chamber and the low-pressure chamber side, a high-pressure communication path that communicates with the second chamber and the high-pressure chamber side, and a high-pressure communication path that is disposed astride both of these communication paths. When the side pressure is above a predetermined value, the low pressure communication passage is closed and at the same time the high pressure communication passage is opened, or after the low pressure communication passage is closed, the high pressure communication passage is opened and the low pressure chamber side pressure is below a predetermined value. a valve mechanism that opens the low-pressure communication passage and simultaneously closes or throttles the opening amount of the high-pressure communication passage, or closes the high-pressure communication passage and then opens the low-pressure communication passage; The control member rotates in accordance with the differential pressure between the bypass port and the second chamber to control the opening angle of the bypass port, thereby controlling the compression start timing and variably controlling the discharge volume. be.

(Function) The control member rotates according to the differential pressure between the first chamber and the second chamber of the pressure working chamber to control the opening angle of the suction port, thereby controlling the compression start timing and increasing the discharge volume. is variably controlled. Furthermore, when the pressure in the low pressure chamber is below a predetermined value, the pressure in the second chamber escapes to the low pressure chamber and at the same time, the inflow of high pressure into the second chamber is blocked or restricted. The pressure drops quickly and the discharge volume drops immediately. Furthermore,
The pressure working chamber also serves as a part of the passage for releasing high pressure to the low pressure chamber side.

(Example) Hereinafter, an example of the present invention will be described based on the accompanying drawings. FIG. 1 is a longitudinal cross-sectional view of a vane compressor according to the present invention, and in the figure, 1 is a housing, which is a cylindrical case 2 with one end open, and one end of the case 2 that closes the opening. Like bolt (not shown)
It consists of a rear head 3 attached at. A discharge port 4 for refrigerant gas, which is a heat medium, is provided on the front upper surface of the case 2, and an inlet port 5 for refrigerant gas is provided on the upper surface of the rear head 3. The discharge port 4 and the suction port 5 communicate with a discharge chamber and a suction chamber, respectively, which will be described later.

A pump body 6 is housed inside the housing 1. The pump body 6 has a cam ring 7
and front side blocks 8 mounted on both open ends of the cam ring 7 so as to close the opening surfaces.
and rear side block 9, and the cam ring 7.
A circular rotor 10 is rotatably housed inside the rotor 10.
and a rotating shaft 11 of the rotor 10. The rotating shaft 11 is rotatably supported by bearings 12, 12 provided on both side blocks 8, 9, respectively.

The inner circumferential surface of the cam ring 7 has an elliptical shape as shown in FIG. Cavity chambers 13, 13 are defined.

The rotor 10 has a plurality of vane grooves 14 (for example, 5 vane grooves 14 arranged at equal intervals in the circumferential direction) along the radial direction of the rotor 10.
Vanes 15 ₁ to 15 ₅ are fitted into these vane grooves 14 so as to be freely protrusive and retractable along the radial direction.

Suction ports 16, 16 are provided in the rear side block 9 symmetrically and offset by 180 degrees in the circumferential direction (see FIGS. 2 and 3). These suction ports 16, 16 are arranged at positions where the volume of the void chamber 13 divided by the vanes 15 ₁ to 15 ₅ is maximized. The suction port 16, 16
pass through the rear side block 9 in the thickness direction, and the suction chamber (low pressure side chamber) 17 between the rear head 3 and the rear side block 9 communicates with the void chamber 13 via these suction ports 16. ing.

As shown in FIGS. 1 and 2, a plurality of (for example, five) discharge ports 18 are provided on the circumferential walls at both ends of the cam ring 7, and the inner circumference of the case 2 is provided through these discharge ports 18. Discharge chamber (high pressure side chamber) 1 between the surface and the outer peripheral surface of the cam ring 7
9 and the void chamber 13 are communicated with each other. These discharge ports 18 include a discharge valve 20 and a discharge valve stop 2.
1 is provided for each.

As shown in FIGS. 3 and 5, the rear side block 9 is provided with an annular recess 22 on its one side (rotor 10 side) surface.
2, arc-shaped bypass ports 23, 23 are symmetrically provided with a circumferential offset of 180 degrees, and the suction chamber 17 and the cavity chamber 1 are connected via these bypass ports 23.
3 are communicated. Furthermore, a ring-shaped control member 24 for controlling the opening angle of the bypass ports 23, 23 is fitted in the recess 22 so as to be rotatable in the forward and reverse directions. The outer peripheral edge of the control member 24 is provided with circular arc-shaped notches 25, 25 symmetrically offset by 180 degrees in the circumferential direction. Furthermore, pressure receiving members 26, 26 in the shape of protrusions are integrally provided on one side of the control member 24 and symmetrically offset by 180 degrees in the circumferential direction. These pressure receiving members 26, 26 are slidably fitted into arcuate pressure operating chambers 27, 27 provided continuously with the bypass ports 23, 23. The inside of these pressure working chambers 27 is divided into a first chamber ₂₇₁ and a second chamber 2 by the pressure receiving member 26.
The _first chamber ₂₇₁ is the suction port 1.
6 and the inhalation chamber 17 via the bypass port 23
The second chamber 27 ₂ is connected to the suction chamber 17 and the discharge chamber 19 via the low pressure communication passage 28 and the high pressure communication passage 29.
are communicated with each other. The one second chamber 27
₂ and the other second chamber 27 ₂ are communicated with each other via a communication path 30 . As shown in FIGS. 1 and 2, the communication passage 30 includes a pair of communication holes 30 that are formed symmetrically across the center of a boss portion 9a that protrudes from the center of the side surface opposite to the rotor of the rear side block 9.
a, 30a, and an annular cavity 30b defined between the protruding end surface of the boss portion 9a and the inner surface of the rear head 3. The communication holes 30a, 30
One end of each a opens into the second chambers 27 ₂ and 27 ₂ , and each other end opens into the annular cavity chamber 30b.

By providing the communication passage 30 in the rear side block 9, which is a fixed member, the communication passage 30
0 is provided in the control member 24, which is a rotating member, the hole drilling is easier, and since the hole can be left open at both ends, foreign substances such as chips can be reliably removed during hole drilling. It becomes highly reliable. (When providing a communication path on the control member 24 side, it is necessary to fit a blind pin into each one end opening of two holes diagonally opened at both ends so as to intersect with each other, so that foreign substances such as chips Note that the low pressure communication passage 28 and the high pressure communication passage 29 are provided inside the rear side block 9.

A specially shaped seal member 31 is provided at the center of one side of the control member 24 and at both end faces of the pressure receiving member 26.
is installed. The third seal member 31
As shown in the figure, the first chamber 27 ₁ and the second chamber 27 ₂
Furthermore, as shown in FIG. 3, the inner and outer circumferential surfaces of the control member 24 and the inner and outer circumferential surfaces of the annular recess 22 of the rear side block 9 are hermetically sealed.

The control member 24 is biased by a coil spring 32, which is a biasing member, in a direction that increases the opening angle of the bypass port 23 (clockwise in FIG. 3). This coil spring 32 is fitted onto the outer circumferential side of the boss portion 9a of the rear side block 9 that extends toward the suction chamber 17 side. This coil spring 32 has one end connected to the boss portion 9a and the other end connected to the control member 24, respectively.

A valve mechanism 33 is provided across the low pressure communication path 28 and the high pressure communication path 29. The valve mechanism 33 switches in response to the pressure on the suction chamber 17 side (low pressure chamber side), and includes a bellows 34, a spool valve body 35, and a spring that biases the spool valve body 35 in the valve closing direction. It consists of 36. The bellows 34 is located within the suction chamber 17 and is extendably and retractably arranged with its axis parallel to that of the rotating shaft 11. The bellows 34 contracts when the pressure on the suction chamber 17 side is above a predetermined value, and expands when it is below a predetermined value. The spool valve body 35 is slidably fitted into a fitting hole 37 provided in the rear side block 9 so as to communicate orthogonally with the low pressure communication passage 28 and the high pressure communication passage 29. The spool valve body 3
5 has an annular groove 38 on the outer circumferential surface on one end side from the substantially intermediate portion in the axial direction, and has a small diameter portion 39 set to approximately the same diameter as the annular groove 38 on the outer circumferential surface on the other end side. Further, the spool valve body 35 is provided with a breathing passage 40 along its internal axis. Spring receiving step portion 35 inside one end side of the spool valve body 35
The coil spring 32 is fitted between a and the inner end surface of the fitting hole 37, and the other end surface of the spool valve body 35 is in contact with the inner end surface of the bellows 34. When the pressure on the suction chamber 17 side is higher than a predetermined value and the bellows 34 is in a contracted state, the annular groove 38 of the spool valve body 35 matches the high pressure communication passage 29, so that the high pressure communication passage 29 is opened. At the same time, the low pressure communication passage 28 is connected to the spool valve body 35.
It is closed by the surrounding wall of. In addition, the suction chamber 17
When the pressure on the side is below a predetermined set value, the bellows 34
When the annular groove 3 of the spool valve body 35 is in the extended state
8 does not match the high pressure communication path 29, and the high pressure communication path 2
9 is closed by the circumferential wall of the spool valve body 35, and at the same time, the low pressure communication passage 28 and the small diameter portion 39 of the spool valve body 35 match, so that the low pressure communication passage 28 is opened. Note that the pressure on the suction chamber 17 side acts on one end side (spring 36 side) of the spool valve body 35 via the breathing passage 40, and the pressure on the suction chamber 17 side acts on the other end side. The spool valve body 35 has only sliding resistance and little hiss. In addition, since the spool valve body 35 and the bellows 34 are separated from each other and merely contact each other, there is no fear that they will be damaged by vibration or the like.

In the above explanation, the low and high pressure communication passages 28 and 29 are opened and closed at the same time, but the present invention is not limited to this, and when the pressure on the suction chamber 17 side rises above a predetermined value, the low pressure communication passages The high pressure communication passage 29 may be opened after the passage 28 is closed, or the communication passage 28 may be opened after the high pressure communication passage 29 is closed when the pressure on the suction chamber 17 side drops below a predetermined value. good.

Next, the operation of the vane compressor of the present invention having the above structure will be explained. When the rotating shaft 11 is rotated in relation to the engine of the vehicle and the rotor 10 rotates clockwise in FIG. 2, the vanes 15 ₁ to 15 ₅ protrude radially from the vane groove 14 due to centrifugal force and vane back pressure. The suction port 16 rotates together with the rotor 10 while its tip surface slides on the inner circumferential surface of the cam ring 7, and during the suction stroke in which the volume of the cavity chamber 13 divided by each vane 15 ₁ to 15 ₅ is expanded. A refrigerant gas, which is a heat medium, is sucked into the cavity 13 from
The refrigerant gas is compressed in the compression stroke to reduce the volume of the void chamber 13, and the discharge valve 20 is opened by the pressure of the compressed refrigerant gas in the discharge stroke before the compression stroke, and the compressed refrigerant gas is discharged. It is supplied to a heat exchange circuit of an air conditioner (not shown) through the port 18, the discharge chamber 19, and the discharge port 4 in this order.

During operation of such a compressor, the pressure in the suction chamber 17, which is on the low pressure side, is transferred to the first chamber 27 ₁ of both pressure working chambers 27, 27 through the suction port 16.
27 ₁ and is also on the high pressure side
9 is introduced into the second chambers 27 ₂ , 27 ₂ of both pressure working chambers 27 , 27 via the high pressure communication passage 29 . Therefore, the force of the sum of the pressure in the first chamber 27 ₁ and the biasing force of the coil spring 32 (control member 24
The pressure in the second chamber 272 (the force that presses the bypass port 23 in the direction that increases its opening angle, that is, the force that rotates it clockwise in FIG. 3) and the pressure in the second chamber ₂₇₂ (the control member 24
The control member 24 rotates in response to the differential pressure between the bypass port 23 and the force that presses the bypass port 23 in a direction that reduces its opening angle, that is, the force that rotates the bypass port 23 counterclockwise in FIG. By controlling the opening angle of the cylinder, the compression start timing is controlled and the discharge capacity is controlled.

That is, when the compressor is operated at low speed, the pressure of the refrigerant gas in the suction chamber 17 (suction pressure) is relatively high, so the bellows 34 of the valve mechanism 33 contracts.
The spool valve body 35 opens the high-pressure communication passage 29 and simultaneously closes the low-pressure communication passage 28 (the state shown in FIG. 6), and the pressure in the discharge chamber ₁₉ is supplied to the second chamber 272. The pressure inside the second chamber ₂₇₂ is
Overcoming the force of the sum of the pressure in the first chamber ₂₇₁ and the biasing force of the coil spring 32, the control member 24
The bypass port 23 is held at the rotation limit position in the counterclockwise direction in the figure, and the entire bypass port 23 is closed by the control member 24 as shown by the solid line in FIG. 3 (the opening angle is zero). Therefore, from the suction port 16 to the cavity chamber 1
Since all of the refrigerant gas sent into the compressor 3 is compressed and discharged, the discharge capacity of the compressor becomes maximum and becomes fully operational.

Next, when the compressor enters a high-speed operation state, the suction pressure in the suction chamber 17 decreases, so the bellows 34 of the valve mechanism 33 expands and presses the spool valve body 35 against the biasing force of the spring 36. Low pressure communication path 2
At the same time as 8 opens, the high pressure communication path 29 is closed (the state shown in FIG. 7). As a result, the pressure supply in the discharge chamber 19 to the second chamber 27 ₂ is stopped, and at the same time, the pressure in the second chamber 27 ₂ is transferred to the suction chamber 17 on the low pressure side via the low pressure communication path 28. As a result, the pressure in the second chamber ₂₇₂ rapidly decreases, and as a result, the control member 24 immediately rotates clockwise in FIG. By matching with the port 23, the bypass port 23 opens as shown by the two-dot chain line in FIG. Therefore, the refrigerant gas sent into the cavity 13 from the suction port 16 leaks into the suction chamber 17 through the bypass port 23, so the compression start time is delayed by the amount that the bypass port 23 is opened.
Since the amount of compressed refrigerant gas in the void chamber 13 decreases, the discharge capacity of the compressor decreases and the compressor becomes partially operational.

The opening angle of the bypass port 23 is determined by the sum of the pressure in the first chamber 27 ₁ and the force of the spring 32;
It is determined when the pressure in the second chamber ₂₇₂ is balanced, and the rotational position of the control member 24 changes continuously according to changes in the pressure (suction pressure) in the suction chamber 17, which is the low pressure side. Therefore, continuous variable capacity control of the compressor is possible. Also, the second chamber 27 ₂
Although the pressure in the discharge chamber 19, that is, the discharge pressure, is introduced, the present invention is not limited to this, and the pressure that acts to press the vanes ₁₅₁ to ₁₅₅ in the projecting direction, that is, the vane back pressure may also be introduced. good.

Further, although the high pressure communication passage 29 is closed when the pressure on the suction chamber 17 side is below a predetermined value, the present invention is not limited to this, and the opening amount of the high pressure communication passage 29 may be reduced.

(Effects of the Invention) As detailed above, the vane compressor of the present invention has the following features:
A cam ring with both sides closed by side blocks, a rotor rotatably disposed within the cam ring, and a vane slidably fitted in a vane groove of the rotor, the side block, the cam ring, In a vane compressor that compresses fluid by changing the volume of a cavity defined by a rotor and vanes, a bypass provided in one of the two side blocks having a suction port is provided. a pressure working chamber provided in the side block having the suction port and communicating with the low pressure chamber side and the high pressure chamber side, and a first pressure working chamber within the pressure working chamber communicating with the low pressure chamber side. and a second chamber communicating with the low pressure chamber side and the high pressure chamber side, and a pressure receiving member slidably fitted so as to airtightly partition the chamber, and the opening angle of the bypass port is controlled. a control member; a biasing member that biases the control member in a direction in which the opening angle of the bypass port becomes larger;
a low-pressure communication path that communicates the second chamber with the low-pressure chamber side; a high-pressure communication path that communicates the second chamber with the high-pressure chamber side;
When the pressure on the low pressure chamber side is higher than a predetermined value by straddling both of these communication passages, the high pressure communication passage is closed simultaneously and the high pressure communication passage is opened, or after the low pressure communication passage is closed, the high pressure communication passage is closed. When the passage is opened and the pressure on the low pressure chamber side is below a predetermined value, the low pressure communication passage is opened and at the same time the high pressure communication passage is closed or the opening amount is throttled, or the high pressure communication passage is closed and then the low pressure communication passage is closed. and a valve mechanism that opens, and the control member rotates according to the pressure difference between the first chamber and the second chamber to control the opening angle of the bypass port, thereby controlling the compression start timing. This is characterized in that the discharge volume can be variably controlled.

Therefore, since the pressure of the compressor is used to control the control member, the structure of the variable displacement control mechanism is simple and compact, and its assembly is easy and inexpensive. Moreover, when the discharge capacity changes from large to small, the supply of high pressure to the second chamber is stopped and at the same time the pressure in the second chamber escapes to the low pressure chamber, resulting in good responsiveness. Improved controllability and high reliability. Furthermore, since the pressure working chamber also serves as a part of the passage for releasing high pressure to the low pressure side, space can be used effectively, making variable displacement control even more effective for this type of compressor, which is particularly space-constrained. The mechanism can be made more compact.

[Brief explanation of drawings]

The drawings show one embodiment of the vane type compressor of the present invention, FIG. 1 is a longitudinal sectional view of the vane type compressor, FIG. 2 is a sectional view taken along the line - in FIG. 1, and FIG.
4 is a sectional view taken along the - line in Figure 1, Figure 5 is an exploded perspective view of the main parts, and Figure 6 is an enlarged sectional view of the valve mechanism part in the fully operating state. , FIG. 7 is an enlarged sectional view similar to FIG. 6 in a partially operating state. 7...Cam ring, 8...Front side block, 9...Rear side block, 10...Rotor, 13...Gap chamber, 14...Vane groove, 15
₁ ~ 15 ₅ ... Vane, 16 ... Suction port, 17
... Suction chamber (low pressure side chamber), 19 ... Discharge chamber (high pressure side chamber), 23 ... Bypass port, 24 ... Control member, 26 ... Pressure receiving member, 27 ... Pressure operation chamber,
27 ₁ ...first chamber, 27 ₂ ...second chamber, 28...
...Low pressure communication path, 29...High pressure communication path, 32...Coil spring (biasing member), 33...Valve mechanism.

Claims (1)

[Claims] 1. A cam ring with both sides closed by side blocks, a rotor rotatably disposed within the cam ring, and a vane slidably fitted into a vane groove of the rotor, the side blocks and cam ring In a vane type compressor that compresses fluid by changing the volume of a cavity defined by a rotor and a vane, a compressor is provided in the side block having the suction port of both the side blocks. a bypass port, a pressure working chamber provided in the side block having the suction port and communicating with the low pressure chamber side and the high pressure chamber side, and a pressure working chamber in the pressure working chamber communicating with the low pressure chamber side. A pressure receiving member is slidably fitted to airtightly partition the first chamber and a second chamber communicating with the low pressure chamber side and the high pressure chamber side, and controls the opening angle of the bypass port. a control member that biases the control member in a direction in which the opening angle of the bypass port becomes larger; a low-pressure communication path that communicates the second chamber with the low-pressure chamber side; A high-pressure communication path that communicates between the chamber and the high-pressure chamber side, and a high-pressure communication path that is disposed across both of these communication paths to close the low-pressure communication path and simultaneously close the high-pressure communication path when the pressure on the low-pressure chamber side is higher than a predetermined value. When the high-pressure communication passage is opened or the low-pressure communication passage is closed after the low-pressure communication passage is opened and the pressure on the low-pressure chamber side is below a predetermined value, the low-pressure communication passage is opened and at the same time the high-pressure communication passage is closed or the opening amount is throttled. Alternatively, the control member may include a valve mechanism that opens the low pressure communication passage after closing the high pressure communication passage, and the control member rotates according to the pressure difference between the first chamber and the second chamber to close the bypass. A vane type compressor characterized in that the discharge capacity can be variably controlled by controlling the compression start timing by controlling the opening angle of the port.