JPH0337393A - Variable capacity type vane compressor - Google Patents

Abstract

PURPOSE:To improve the controllability by controlling each pressure in two pressure chambers partitioned by the pressure receiving part of a control member by a control valve, in the constitution in which the discharge quantity is controlled by revolving the control member installed onto the rotor side edge surface of a side block on one side in the normal and reverse directions according to a thermal load. CONSTITUTION:On one between the side blocks 3 and 4 arranged on the both sides, having a cylindrical rotor 2 interposed, an annular recessed part 40 is formed on a rotor side edge surface 4a, and a ring-shaped control member 50 is fitted in turnable manners inside the annular recessed part 40. In the annular recessed part 40, flat surfaces 41 and 42 at the shallow positions are formed on the both sides of one suction port 15, and pressure acting chambers 43 and 44 at the deep positions are formed on the both sides of the other suction port 15. Pressure receiving parts 53 and 54 which are fitted in slidable manners in the pressure acting chambers 43 and 44 are formed on the other edge surface of a control member 50, and the first pressure chambers 431 and 441 partitioned by the pressure receiving parts 53 and 54 allowed to communicate to a suction chamber 11, and the second pressure chambers 432 and 442 are allowed to communicate to the suction chamber 11 or discharge chamber 10 by a control valve 60 which is controlled according to the variation of a thermal load.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention comprises a control member that has a pair of pressure receiving parts on one side and that rotates forward and backward depending on the heat load to control the discharge amount. This invention relates to a variable capacity vane compressor.

(Prior Art) Conventionally, as a variable capacity vane compressor equipped with such a control member, there is, for example, a technique disclosed in Japanese Utility Model Application Publication No. 63-99005.

That is, this prior art includes a cylinder whose both ends are closed by side blocks, a rotor rotating within the cylinder, and an 11〆1n provided in the end surface of the rotor side of one side block so as to move together. A pair of pressure receiving portions Il are provided at substantially symmetrical positions on the anti-rotor side surface of the control member.
1, 112 (see FIG. 11) are formed, and the control member controls the suction pressure Ps, which is a low pressure, introduced into the low pressure chamber 113 on one side of each pressure receiving part 111, 112, and the coil spring. The resultant force of the urging forces of 114 and each pressure receiving part Ill.

Hyperbaric chamber on the other side of 112! Due to the difference between the high discharge pressure 1) d and the control pressure Pc formed by introducing the high pressure into the 1) through the orifice 116, the operating position is set to 1 where the discharge amount is the minimum, and the full operation position is where the discharge amount is the maximum. It can be rotated forward and backward between positions. And one high pressure chamber 115 and 131
Opening/closing J "mechanism 7" installed in the passageway communicating with the passenger room
The control member 111 changes the control pressure Pc by opening and closing in response to changes in the suction pressure Ps depending on the thermal load, and the difference between the changing control pressure Pc and the resultant force causes the control member 111 to reduce the discharge amount. Rotate in the direction or increase direction and emit 11 + J song l! ill W
be done.

(Problem to be Solved by the Invention) Generally, in the conventional variable capacity vane compressor as described above, in order to reduce the shock at startup, it is started at a half-operating position where the discharge amount is minimum. It is.

However, in the above-mentioned conventional technology, a coil spring is provided that biases the control member toward the half-operated position, and the preset force of the spring is large enough to overcome the rotational resistance of the control member. In order to increase the amount, it is necessary to apply a force to the control member that is greater than the sum of the rotational resistance of the control member and the biasing force of the coil spring. However, at startup, the compression ratio is small and the discharge pressure Pd does not rise much, so ^
:j The control pressure [)c also does not increase very much, so there is a problem that the control member is difficult to smoothly rotate in the direction of increasing the discharge amount at the time of startup, and the startup performance is not very good.

The present invention was made by focusing on such conventional problems, and is a variable capacity vane type compression system that improves starting performance and controllability by eliminating the spring member that biases the control member. The purpose is to provide equipment.

(Means for Solving the Problems) In order to achieve the above object, a variable capacity vane compressor according to the present invention includes a cylinder whose both ends are closed with side blocks, and a rotor rotating within the cylinder. , a control member rotatably provided in the rotor-side end face of one side block and having a pair of pressure-receiving parts on the side face opposite to the rotor, and the control member rotates in forward and reverse directions according to heat and negative conditions. In the variable displacement claw type vane type compressor that controls the discharge amount by moving, each first pressure chamber on one side of each pressure receiving part communicates with the low pressure side, and the other side of each pressure receiving part described in 81j. A control valve is provided to alternately communicate the second pressure chambers on the high pressure side or the low pressure side depending on changes in heat load, and the second pressure chamber on the other side of one pressure receiving part communicates with the high pressure side. When this happens, the torque generated on the one pressure receiving part causes the control member to decrease the discharge amount.
The two pressure chambers are arranged such that when the second pressure chamber on the other side of the other pressure receiving part communicates with the high pressure side, the control member is rotated in the direction of increasing the discharge amount by the torque generated on the other pressure receiving part side. A first pressure chamber and two second pressure chambers are arranged.

In addition, in order to achieve the above object, each m 1 jE force chamber on one side of each pressure receiving part communicates with the low pressure side, and an intermediate pressure chamber is provided in a second pressure chamber on the other side of one pressure receiving part. is formed, and a control pressure that changes from high pressure to low jE according to the heat load is formed in the second pressure chamber on the other side of the other pressure receiving part, and the above I111 member Due to the almost constant torque generated on one pressure receiving part side, the discharge amount is reduced, and the nsI is generated on the rising pressure receiving part side and 61
Preferably, the pumps are configured to be rotated in the direction of increasing the discharge amount by a torque that changes depending on the control value.

Furthermore, in order to achieve the above object, one of the pressure receiving parts has a smaller pressure receiving area than the other, and each first pressure chamber on one side of each pressure receiving part communicates with the low pressure side. ,
The second focusing chamber on the other side of the one pressure receiving part communicates with the high pressure side, and the second pressure chamber on the other side of the other pressure receiving part has a pressure ranging from high pressure to low pressure depending on the heat load. A changing control pressure is formed, and 1); the control member i is moved in the direction of reducing the discharge amount by the almost constant torque generated on the one pressure receiving part side, and 51! on the other pressure receiving part side. Raw 0. Preferably, the tM is configured to rotate in the direction of increasing the discharge amount by a torque that changes according to the control pressure.

(Function) In the vane type compressor described above, which is provided with a control valve that alternately communicates each second focusing chamber with the high pressure side or the low pressure side depending on the heat load, the second pressure chamber of one pressure receiving part is connected to the high pressure side. When the second E force chamber of the other pressure receiving part communicates with the high pressure side, torque is generated on the one pressure receiving part side, and this torque causes the control member to rotate in the direction of reducing the discharge amount. Torque is generated on the other pressure receiving part side, and this torque rotates the control member in the direction of increasing the discharge amount.

In addition, in the vane type compressor described above in which intermediate pressure is formed in the second pressure chamber of one pressure receiving part, an almost constant torque is generated on the one pressure receiving part side due to the difference between the intermediate pressure and the low pressure, and this torque If the torque on the other pressure receiving part side changes according to the control pressure, the control member rotates in the direction of decreasing the discharge amount, and in the opposite case, the control member rotates in the direction of increasing the discharge amount. move.

In this vane type compressor, even if the control member rotates to the full operating position of the maximum discharge amount, intermediate pressure acts on one pressure receiving part side. ,
The control member is prevented from tilting due to the pressure of the compression chamber acting on its rotor-side side surface.

In addition, one of the pressure receiving parts has a smaller pressure receiving area than the other. 1. In a vane type compressor, the difference between the pressure difference between the high pressure and low pressure and the pressure receiving area on the side of the pressure receiving part with the smaller pressure receiving area. When a certain approximately constant torque is generated and this torque is larger than the torque on the other pressure receiving part side which changes according to the control pressure, the control member rotates in the direction of reducing the discharge amount, and vice versa. In this case, the control member rotates in the direction of increasing the discharge amount. Also in this vane type compressor, even if the control member rotates to the full operating position of the maximum discharge amount, high IJ is acting on one pressure receiving part side. On the side, the control member is prevented from being pushed under the pressure of the compression chamber acting on its rotor-side side.

(Example) Each example of Kuniaki Kuniaki will be described below based on the accompanying drawings. In addition, in the description of each embodiment, the same parts are designated by the same reference numerals 11 and redundant description will be omitted.

Figures 1 to 6 show a variable capacity vane type compressor according to the first embodiment of Kochomei, and Figure 1 shows the discharge amount control mechanism provided in this vane type compressor. The approximate xm diagram and FIG. 4 are longitudinal cross-sectional views of this vane type compressor.

As shown in FIG. 4, the variable displacement vane type compressor includes a cam ring 1 having an elliptical inner circumferential surface 1a, and a cylindrical rotor 2 rotatably housed within the cam ring 1.
And cam ring! A front side block 3 and a rear side block 4 are respectively fixed to both side ends so as to close both sides of the block, and a front head 5 is fixed to the outer ends of both side blocks 3.4, respectively. The rear head 6 and the co-rotating shaft 7 of the rotor 2 are the main components, and the rotation axis 7
is rotatably supported by bearings 8 and 9 provided on both side blocks 3 and 4, respectively.

A discharge port Lj 5A for refrigerant gas, which is a heat medium, is formed on the upper surface of the front head 5, and a refrigerant gas suction port 6a is formed on the upper surface of the rear head 6. The discharge port 1'' 5a communicates with a discharge chamber 10 defined by the front head 5 and the front side block 3, and the suction port 6a communicates with a suction chamber 11 defined by the rear head 6 and the rear side block 4. .

Two compression chambers 12 are defined between the inner peripheral surface ra of the cam ring 1 and the outer peripheral surface of the rotor 2 at substantially symmetrical positions offset by 180 degrees in the circumferential direction 1fiJ. The rotor 10 is provided with a plurality of vane grooves 13 along its radial direction at equal intervals in the circumferential direction, and vanes 14 are installed in these vane grooves 13.
are respectively fitted into the recessed and recessed openings 7r along the radial direction.

As shown in FIGS. 4 and 6, the rear side block 4 is provided with suction bows 115.15 at approximately symmetrical positions offset by 180 degrees in the circumferential direction (in FIG. 4, one suction boat Only 15 is visible). Each suction boat I5 passes through the rear side block 4 in the thickness direction, and the suction chamber II and the compression chamber 12 are communicated with each other via each suction boat 1-15.

The outer peripheral wall of the cam ring l has 1801 mm in the circumferential direction. & 2v4 discharge boats 16°16 are bored at approximately symmetrical positions (only one discharge boat I6 is visible in FIG. 4). Cam ring 1 with the discharge boat 16
A valve stop portion 17a is provided on the outer peripheral wall of the valve.

A discharge valve cover 17 having a diameter 17a is fixed with bolts 18. The outer peripheral wall of the cam ring l and the valve stop portion 17a
A discharge valve 1 held on the discharge valve cover 17 side is provided between
9.19 is interposed, and each discharge valve 19 opens when receiving discharge pressure to separate the respective discharge boats I6. Further, the cam ring 1 is formed with a communication passage 20 that communicates with the discharge boat 16 when the discharge valve 19 is opened, and the front side block 3 is formed with a communication passage 21 that communicates with the communication passage 20. When the valve is opened and the waste discharge boat 16 is opened 1", the compressed refrigerant gas in the compression chamber 12 is sequentially discharged through the discharge boat 16, the communication passages 20 and 21, the discharge chamber IO and the discharge 115a. It has become so.

As shown in FIGS. 4 and 6, the rear side block 4
is provided with an annular recess 40 on its rotor-side end surface 4a, and a ring-shaped control member 50 shown in FIG. 5 is rotatably mounted within the annular recess 40.

Inside the annular portion 40, flat surfaces 41.42 are formed on both sides of one suction bow 15 at a shallow position from the rotor side end surface 4a, and pressure working chambers 43.42 are formed at a deep position from the end surface 4a. 44 are formed on both sides of the other suction boat 15.

As shown in FIG. 5, the outer peripheral edge of the control member 50 has notches 51 at approximately symmetrical positions offset by 180 degrees in the circumferential direction.
52 are provided. Further, on the side surface of the m-control member 50 on the side opposite to the rotor, as shown in FIG.
A pair of pressure receiving parts 5 each slidably fitted into 44.
3 and 54 are provided on both sides of the notch 51,
Tail portions 55.5 slidingly contact the flat surfaces 41, 42, respectively.
6 each pressure receiving part 53 provided on both sides of the notch 52
．． Seal structures 53a and 54a are formed around the periphery of 54, into which the l1IIIf/l seal member S and the resin seal member S are fitted as shown in FIG. Seal grooves 55a and 56a into which seal members S++S are fitted are also formed in the tail portions 55 and 56.

As shown in FIG. 1, each pressure working chamber 43,44 has a first pressure chamber 43,44 located on one side thereof by each pressure receiving part 53,54. , /14. and a second pressure chamber 43 on the other side. ．．
44. It is divided into two parts. Each first pressure chamber 43. ．． 44
．． is the suction chamber 11 on the low pressure side via each suction boat 15.
in communication with each first pressure chamber 43. ,44. A low suction pressure Ps is introduced into the chamber.

On the other hand, the second pressure chamber 43. ．． 44. is alternately communicated with the suction chamber 11 on the low JE side or the discharge chamber 10 on the high pressure side by displacing the spool valve (control valve) 60 in response to changes in heat load. In other words, Suburb “6
0 can be slid in a hole 61 provided in the rear side block 4 between a first position shown in FIG. 2 and a second position shown in FIG. 3. Further, this spool valve 60 is equipped with a spring 6
2 toward the first position, and a bellows 63 provided in the suction chamber ti toward the second position (note that the spool valve 60, bellows 63, etc. are not shown in FIG. 4). be). This bellows 63 expands against the biasing force of the spring 62 when the thermal load becomes small and the suction pressure Ps reaches a predetermined level (under direct weight), and the thermal load increases and the suction pressure Ps
When s becomes larger than a predetermined value (11), the spool valve 60 is set to contract.
When the bellows 3 contracts, it is displaced toward the first position by the biasing force of the spring 62, and when the bellows 63 expands, it is displaced toward the second position against the biasing force of the spring 62. and,
When the spool valve 60 is displaced to the first position (in the state shown in FIGS. 1 and 2), one of the second pressure chambers 43
．． is the communication path 64 and the first boat 60a of Sbourble r 60
, and the suction chamber 11 via the low pressure passage 65, and the other second pressure chamber 44 communicates with the discharge chamber 10 via the communication passage 66, the second boat 60b of the spool valve 60, and the high first king passage 67. It is designed to communicate with At this time, the second pressure chamber 44. The pressure inside 1'c becomes high pressure and the second
Since the focus Pc in the 1st power chamber 431 becomes low pressure, Uke 1
Torque is generated on the working part 54 side by the pressure difference between the high pressure Pc and the low pressure Ps, and this torque causes the control member 50 to rotate in the direction of increasing the discharge amount (counterclockwise n1 direction in FIG. 1). There is. Further, when the spool valve 60 is displaced to the second position (in the state shown in FIG. 3), one of the second pressure chambers 43. communicates with the discharge chamber 10 via the communication passage 64, the first boat 60a, and the high pressure passage 67, and the other second pressure chamber 44o communicates with the discharge chamber 10 via the communication passage 66, the second boat 60b, and the low pressure passage 68. It communicates with the suction chamber 11. At this time, the pressure inside the second pressure chamber 431 is Pc.

becomes high pressure and the second pressure chamber 44. The pressure inside Pc.

is low) I:, so torque is generated on the pressure receiving part 53 side due to the pressure difference between the high pressure Pc and the low pressure Ps, and this torque causes the control member 50 to move in the direction of reducing the discharge amount (in Fig. It is designed to rotate in the direction of force.

Hereinafter, the operation of the first embodiment will be explained.

It is now assumed that the compressor is started, and at the time of starting, the control member 50 is at a position close to the full operating position, as shown in FIG. 1, for example. During this start-up, the heat load is usually large;
Since the suction II P s is larger than the predetermined 1 shift, the bellows 63 contracts, and the Sbourble r 60 is displaced to the first ablation side shown in FIGS. 1 and 2 by the force of the spring 62.

When the spool valve 60 is displaced to the first position, one of the second pressure chambers 43. communicates with the suction chamber 11, and the other second pressure chamber 44° communicates with the discharge chamber 10. As a result, the other second pressure chamber 44. Since the internal pressure Pc becomes high, torque is generated on the pressure receiving part 54 side due to the pressure difference between the high pressure Pc and the low pressure Ps, and this torque causes the control member 50 to
is further rotated in the direction of increasing the output from the starting position shown in FIG. 1, and the ljl output of the compressor increases. The position where the 111 control member 50 moves to the maximum lli+ in the direction of increasing the discharge amount is the full operation position, and at this position the discharge amount is maximum.

Furthermore, when the thermal load is small at startup and the suction pressure Ps is below a predetermined value, the bellows 63 expands against the biasing force of the spring 62, and the spool valve 6o is displaced to the second position shown in FIG. do. When Sbourbe 6° is displaced to the second position, one 21F power chamber 438 communicates with the discharge chamber 10, and the other 2J mocha chamber 441 communicates with the suction chamber 11. Pressure P inside pressure chamber 43.
c, becomes high pressure, a torque is generated on the pressure receiving part 53 side due to the pressure difference between the high pressure Pc and the low pressure Ps, and this torque causes the control member 50 to move in the direction of decreasing the discharge amount from the starting position shown in FIG. The discharge amount of the compressor decreases. When the compressor is started, the control member 50 rotates to the maximum in the direction of reducing the discharge amount (the 3/ position is the half-operation position, and the discharge amount is at its minimum in this position). ,
The control member 50 is rotated in the direction of decreasing or increasing the discharge amount by the torque generated by the pressure difference between the high pressure Pc or 1) c and the low pressure Ps on the pressure receiving part 53 or 54 side. Since the force of the coil spring ζ1 is not acting, the control member 50 can smoothly rotate from the starting position, and has good starting performance.

Further, after startup, the bellows 63 expands and contracts in response to changes in the suction pressure Ps depending on the thermal load, and this expansion and contraction causes the spool valve 60 to vibrate between the first position and the second position. This vibration causes one of the second pressure chambers 43. internal pressure P
c, and the pressure Pc in the other pressure chamber 44 are controlled by duty ratio.

That is, the time the spool valve 60 is in the first position is the second
<If the time is longer than 1'l, the pressure Pc.

The force 1) becomes higher than C1, and the torque generated on the pressure receiving part 54 side becomes larger than the torque generated on the pressure receiving part 53 side, so +I, II 111 member 50 rotates in the direction of increasing the discharge amount. Conversely, if the time that the spool valve 60 is in the second position is longer than the time that it is in the first position, the pressure Pc
becomes higher than jmocha1)cl, and the torque generated on the pressure receiving part 53 side becomes larger than the torque generated on the receiver 11:, part 54 side, so the control member 50 rotates in the direction of decreasing the discharge amount.

In this way, during operation of the compressor, the control member 50 rotates forward and backward depending on the difference between the torque on the pressure receiving part 53 side and the torque on the pressure receiving part 54 side in response to changes in thermal load. System t
Since the biasing force of the coil spring does not act on the i11 member 50 as in the above-mentioned prior art, the control member 50 can move smoothly in response to changes in thermal load, providing good controllability.

Furthermore, when the compressor is stopped, the torque on the pressure receiving part 53 side and the torque on the pressure receiving part 54 side disappear, so the control member 5
0 will stop at the position at which it stopped.

In the first embodiment, a solenoid valve is used in place of the bellows 63, and the spool valve 6 is opened by this solenoid valve.
0 can also be configured to be displaced toward the second position.

Next, a second embodiment of the present invention will be described with reference to FIG.

In this second embodiment, each of the first pressure chambers 43. .

This is the same as the first embodiment described above in that a low suction pressure Ps is introduced into the second embodiment. However, the one second pressure chamber 43. An intermediate pressure Pc is formed within the second pressure chamber 44. Control pressure Pc changes from high pressure to low pressure depending on the heat load.

By forming the control member 50, the control pressure P is generated on the other pressure receiving part 54 side in the direction of discharge amount reduction due to the almost constant torque generated on the negative pressure receiving part 53 side, and
The second embodiment differs from the first embodiment described in ``2'' in that it is configured to rotate in the direction of increasing the discharge amount by a torque that changes according to c. For other configurations,
Second example and the above! This is the same as the example.

Specifically, one second LE force chamber 43. simultaneously communicates with the suction chamber 11 and the discharge chamber 10 via orifices 70 and 71.

The other second pressure chamber 44. is in communication with the discharge chamber IO via the orifice 72, and can also communicate with the suction chamber 11 via the communication path 73. The communication passage 73 is interposed with an opening/closing Jr. machine TL180 that opens and closes the communication passage 73 according to the suction pressure Ps that changes depending on the heat load to control the control pressure Pc within the second pressure chamber 44°. ing. This opening/closing block “Il”
The structure 80 includes a bellows 81 that is provided in the suction chamber 1 and that expands and contracts according to the suction pressure Ps, and a bellows 81 that expands and contracts according to the suction pressure Ps, and a communication path 7 that is opened and closed by this expansion and contraction.
It consists of a ball valve body 82 that opens and closes the valve body 82, and a spring 83 that biases the valve body 82 in the valve closing direction by τ1. When the suction pressure Ps is below a predetermined elevation f, the on-off valve device 4M80 lowers the control pressure Pc by expanding the bellows 81 and opening the communication passage 73, so that the suction pressure Ps becomes larger than the predetermined value. When this happens, the bellows 81 contracts and the communication path 7
3, the IT control pressure Pc is increased.

The operation of the second embodiment will be explained below.

During operation of the compressor, +I11 f is generated on one pressure receiving part 53 side due to the difference between the same pressure Pc and the suction pressure Ps.
A substantially constant torque is generated to rotate the IT member 50 in the direction of reducing the discharge amount, and at the same time, on the other 15 pressure receiving parts 54 side,
The difference between the control 1JTEPc and the suction pressure Ps generates a torque that rotates the control fTB material 50 in the direction of increasing the discharge amount.

Now, as the heat load becomes smaller and the suction pressure Ps becomes less than the predetermined value, the control pressure 1)c decreases, and Ω;I is almost constant]・Ruk is generated on the receiving part 54 side. When the torque becomes larger than that, the control member 50 rotates in the direction of decreasing the discharge amount, and the discharge amount decreases.

On the contrary, when the thermal load increases, the suction pressure Ps becomes larger than the predetermined value, and the control pressure Pc increases, and the above-mentioned almost constant torque becomes smaller than the torque generated on the pressure receiving part 54 side. , the control member 50 rotates in the direction of increasing the discharge amount, and the discharge amount increases.

When the compressor is stopped, the torque on the pressure receiving part 53 side and the torque on the pressure receiving part 54 side disappear, so the control member 50 stops at its stop position.

According to the second embodiment, when the compressor is started up and is in operation, the control member 50 operates in the direction of decreasing or increasing the discharge amount depending on the difference between the torque on the pressure receiving section 53 side and the torque on the pressure receiving section 54 side. Since the force of the coil spring τ1 does not act on the control member 50 as in the above-mentioned prior art, the startability and control are the same as in the first embodiment described in Section 1. Good sex.

Further, according to the second embodiment, when the control member 50 rotates to the maximum extent in the counterclockwise i1t/j direction in FIG. Although the high pressure within the compression chamber 12 acts on the side surface 50a (see FIG. 4), the second pressure chamber 44.071.
The control pressure Pc in the second pressure chamber 43. Since the internal pressure Pc does not become a low pressure and is always at an intermediate pressure, the control member 50 does not succumb to the high pressure within the compression chamber 12 and move in the direction opposite to the rotor (rightward in FIG. 4).
That is, the control member 50 does not tilt on the one pressure receiving part 53 side. Therefore, even in the full operating position, a predetermined gap is maintained between the rotor 2 and both side blocks 3 and 4, preventing airtightness and deterioration of performance. In this respect, the second embodiment is more practical than the first embodiment.

Next, a third embodiment of the present invention will be described using FIGS. 8 to 10.

This ff13f embodiment generates a substantially constant torque on one pressure receiving part 53 (in this third embodiment, the pressure receiving part 53') using a method different from the second embodiment described in 1. The other configurations are the same as in the second embodiment described in section 1.

Specifically, one pressure receiving part 53 shown in FIGS. 8 and 9
The pressure receiving part 53' is made lower than the external force receiving part B 54.
The pressure receiving surface 1 is smaller than the pressure receiving portion 54, and
The second pressure chamber 43 of one pressure receiving part 53'. There is a discharge chamber I inside.
A discharge pressure Pd in O is introduced via a communication path 84. As a result, in one pressure receiving part 53', the discharge pressure Pd
A substantially constant torque is generated, which is the product of the force difference between the low pressure Ps and the pressure receiving area of the pressure receiving portion 53', and this torque causes the control member 50 to rotate in the direction of reducing the discharge amount. In addition, it is r1! that the height of one pressure receiving part 53' is lower than the other receiving JTE part 54, and one pressure working chamber 43' of the rear side block 4 shown in Fig.
The depth of the pressure working chamber 44 is made shallower than that of the other pressure working chamber 44.

First, the pressure receiving part 5 has a larger pressure receiving part 1ff than the pressure receiving part 53'.
On the 4 side, as in the second embodiment described in 1., a torque is generated which is the product of the pressure difference between the control pressure Pc and the suction pressure Ps, which changes according to the heat load, and the pressure receiving area of the pressure receiving portion 54. This torque causes the control member 50 to rotate in the direction of decreasing the discharge amount.

Therefore, this third embodiment operates in the same manner as the second embodiment described above. In other words, the heat load becomes smaller and the suction pressure P s
becomes less than a predetermined value and the control pressure PC decreases, and when the almost constant torque becomes larger than the torque generated on the pressure receiving part 54 side, the control 11 member 50 rotates in the direction of reducing the discharge amount. Discharge amount decreases.

On the contrary, as the heat load increases, the suction pressure Ps becomes larger than the predetermined value, and the control pressure Pc increases, and the above-mentioned almost constant torque becomes smaller than the torque generated on the pressure receiving part 54 side. Then, the control member 50 rotates in the direction of increasing the discharge amount, and the discharge amount increases.

According to the third embodiment, the startability and controllability are good as in the case of the second embodiment.

Further, according to the second embodiment, the control member 50 is 011
When the control member 5o is in the fully operating position, the high pressure in the compression chamber 12 acts on the rotor-side side surface 50a of the control member 5o.
Since the control pressure Pc in the pressure chamber 441 is high and the pressure in the second pressure chamber 433 is always high (discharge pressure 1) d), the control member 50 is succumbed to the high pressure in the compression chamber 12. It does not move in the anti-rotor direction, that is, one pressure receiving part 53'
On the side, the control member 50 does not tilt. Therefore, even in the full operating position, a predetermined gap is maintained between the rotor 2 and both side blocks 3 and 4, as in the second embodiment, and there is no airtightness. /j +l-, which has the advantage of preventing performance deterioration. In this respect, the third embodiment is more practical than the first embodiment.

<Effects of the Invention> As described in detail below, according to the variable capacity vane compressor according to the present invention, each of the eleventh power chambers on one side of each pressure receiving part communicates with the low pressure side. At the same time, a control brake r is provided that alternately connects the second pressure chambers on the other side of each pressure receiving part to the high pressure side or the low pressure side according to changes in heat load, and When a certain second pressure chamber communicates with the high pressure side, the control member is caused to decrease the discharge amount due to the torque generated on the one pressure receiving part side, and the second pressure chamber on the other side of the other pressure receiving part is directed to the high pressure side. The two first pressure chambers and the two second pressure chambers are arranged so that the control members move together in the direction of increasing the discharge amount due to the torque generated on the other pressure receiving part side when communicating with each other. As a result, when the second pressure chamber of one of the receiving fittings communicates with the high pressure side, torque is generated on the pressure receiving part side of the force, and this torque causes the control member to rotate in the direction of reducing the discharge amount. When the second pressure chamber of the other pressure receiving part communicates with the high pressure side, torque is generated on the other pressure receiving part side, and this torque rotates the control member in the direction of increasing the discharge amount. Therefore, when the compressor is started, the control member is rotated in the direction of decreasing or increasing the discharge amount by the torque generated on one or the other pressure receiving part side, and the control member is equipped with a coil spring as in the above-mentioned prior art. Since no biasing force is applied, the control member can smoothly rotate from the starting position, resulting in good starting performance. Also,
Even during operation of the compressor, the g1m member rotates in the direction of decreasing or increasing the discharge amount due to the torque generated on one side or the other side of the pressure receiving section in response to changes in thermal load, and the control member has the above-mentioned conventional technology. Since the coil spring's 1° force is not generated as shown in FIG.

Furthermore, each first pressure chamber on one side of each pressure receiving part communicates with the low pressure side, and an intermediate pressure is formed in a second pressure chamber on the other side of one pressure receiving part. In the second pressure chamber on the other side of the pressure receiving part, a control pressure that changes from a high pressure to a low pressure according to the heat negative neck is formed, and the control member controls the pressure generated on the one pressure receiving part side to be almost constant. One pressure receiving section is configured to move in the direction of decreasing the discharge amount due to the torque of the other pressure receiving section, and in the direction of increasing the discharge amount due to the torque generated on the other pressure receiving section side and changing according to the control pressure. If a substantially constant torque is generated on the pressure receiving part side due to the difference between the intermediate pressure and the low pressure, and this torque is larger than the torque on the other pressure receiving part side which changes depending on the control pressure, the control 11 member will cause the discharge ffi to stop. In the case of inward movement and vice versa, the control member rotates in the direction of increasing the discharge amount. Therefore, the control member can rotate smoothly from the starting position, and has good starting performance. During operation, the control member can also smoothly move in response to changes in thermal load, and the control uv rl is good. In addition, even if the control member rotates to the full operating position of the maximum discharge amount, intermediate pressure is generated on one pressure receiving part side, so in the one order receiving part side, the 1li11a11 member is on the rotor side. The pressure of the compression chamber acting on the sides prevents it from tilting. Therefore, even in the full operating position, a predetermined gap is maintained between the rotor and both side blocks, preventing poor airtightness and reducing performance.

In addition, one of the two pressure receiving parts has a smaller pressure receiving area than the other, and each first pressure chamber on one side of each pressure receiving part communicates with the low pressure side. The second pressure chamber on the other side communicates with the high pressure side, and the second pressure chamber on the other side of the pressure receiving part of the other force has a high The pressure changes to low; I11 pressure is formed, and the control member is generated on the one receiver I side. Due to the almost constant torque generated by the
It occurred on the pressure receiving part side on the nt la side.
j1: By being configured to rotate in the direction of increasing the discharge amount by a torque that changes according to , the pressure difference between high pressure and low pressure and the receiving JIE surface are When a nearly constant torque is generated, which is the product of the control pressure, and this torque is larger than the torque at the other pressure receiving part that changes depending on the control pressure, the control member rotates in the direction of reducing the discharge amount, In the opposite case, the control member rotates in the direction of increasing the discharge amount. Therefore, the control member can be smoothly rotated from the starting position and has good starting performance, and during operation, the control member can be smoothly rotated in response to changes in thermal load, providing good controllability. In addition, even if the control rotor material rotates to the full operating position of the maximum discharge amount, high pressure is still acting on one pressure receiving part side, so the control member on the one pressure receiving part side The force of the compression chamber acting on the side surface prevents it from becoming I'l+ and expanding. Therefore, even in the full operating position, a predetermined gap is maintained between the rotor and both side blocks, and poor airtightness is prevented, thereby preventing poor performance.

[Brief explanation of drawings]

1 to 6 show a first embodiment of the present invention,
Figure 1 is a schematic configuration diagram showing the variable capacity vane type compression (discharge amount 1 + NJ control mechanism provided in the
Figure 3 is an explanatory diagram showing the spool valve in the first position, Figure 4 is an explanatory diagram showing the spool valve in the second position, and Figure 4 is a longitudinal section showing the variable displacement vane compressor. Figure 5 is a plan view of the control member viewed from the side opposite to the rotor;
Figure 7 is a plan view of the rear side block viewed from the rotor side, Figure 7 is a schematic configuration diagram showing the discharge amount control mechanism of a variable displacement vane type compressor according to a second embodiment of the present invention, and Figures 8 to 8. FIG. 10 shows a third embodiment of the present invention, FIG. 8 is a schematic configuration diagram showing the discharge amount control mechanism, FIG. 9 is a plan view of the control member viewed from the side opposite to the rotor, and FIG. FIG. 1t, which is a plan view of the side block viewed from the rotor side, is a schematic configuration diagram showing a discharge amount control mechanism provided in a conventional variable capacity vane type compressor. ! ...Cam ring (cylinder), 2...Rotor, 3
゜4...Side block, 43. ．． 44. ...First
Pressure chamber, 43□441...21'JF, force chamber, 50.
... Control member, 60... Suburb f' (control valve).

Claims (1)

[Claims] 1. A cylinder whose both ends are closed with side blocks;
The control member includes a rotor that rotates within the cylinder, and a control member that is rotatably provided within the rotor-side end surface of one side block and has a pair of pressure-receiving portions on the side surface opposite to the rotor, and the control member is configured to handle thermal loads. In a variable capacity vane type compressor that controls the discharge amount by rotating forward or backward according to
A control valve is provided to alternately communicate the second pressure chambers on the other side of each of the pressure receiving parts with the high pressure side or the low pressure side according to changes in heat load, and the second pressure chamber on the other side of one of the pressure receiving parts When the pressure chamber communicates with the high pressure side, the control member decreases the discharge amount due to the torque generated on the side of one pressure receiving part, and the second pressure chamber on the other side of the other pressure receiving part communicates with the high pressure side. The two first pressure chambers and the two
A variable capacity vane type compressor characterized in that two second pressure chambers are arranged. 2. A cylinder whose both ends are closed with side blocks,
The control member includes a rotor that rotates within the cylinder, and a control member that is rotatably provided within the rotor-side end surface of one side block and has a pair of pressure-receiving portions on the side surface opposite to the rotor, and the control member is configured to handle thermal loads. In a variable capacity vane type compressor that rotates forward and backward depending on the pressure, the discharge amount is controlled, each first pressure chamber on one side of each pressure receiving section communicates with the low pressure side, and one pressure receiving section An intermediate pressure is formed in the second pressure chamber on the other side, and a control pressure that changes from high pressure to low pressure depending on the heat load is formed in the second pressure chamber on the other side of the other pressure receiving part. The control member is configured to reduce the discharge amount by a substantially constant torque generated on the one pressure receiving part side, and to reduce the discharge amount by a torque generated on the other pressure receiving part side and varying according to the control pressure. A variable capacity vane type compressor, characterized in that it is configured to rotate in the direction of increasing volume. 3. A cylinder whose both ends are closed with side blocks,
The control member includes a rotor that rotates within the cylinder, and a control member that is rotatably provided within the rotor-side end surface of one side block and has a pair of pressure-receiving portions on the side surface opposite to the rotor, and the control member is configured to handle thermal loads. In a variable capacity vane type compressor that controls the discharge amount by rotating forward or backward according to Each first pressure chamber communicates with the low pressure side, a second pressure chamber on the other side of the one pressure receiving part communicates with the high pressure side, and a second pressure chamber on the other side of the other pressure receiving part communicates with the second pressure chamber on the other side of the other pressure receiving part.
A control pressure that changes from a high pressure to a low pressure depending on the heat load is formed in the pressure chamber, and the control member controls the discharge amount in the direction of reducing the discharge amount by a substantially constant torque generated on the one pressure receiving part side. A variable capacity vane type compressor, characterized in that it is configured to rotate in a direction to increase the discharge amount by a torque generated on the other pressure receiving part side and varying according to the control pressure.