JPH0258479B2 - - 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 and deflect the throttle plate.

Therefore, since the actuator, which is the driving means, deflects 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 machining 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. A control member configured to be defined by the side block, the rotor, and the vanes, comprising a plurality of vanes, a control member detachably attached to the suction port of the one side block, and a driving means for driving the control member. The vane-type compression is configured such that the fluid is compressed by changing the volume of the compression chamber, and the discharge capacity can be variably controlled by changing the compression start position of the suction port using the control member. In the machine, teeth for being driven are carved in the control member, teeth that mesh with the teeth are provided on the output shaft of the drive means, and the control member is directly driven by the drive means. This is what I did.

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. .

(Object 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 having a simple, compact structure, low cost, and a variable capacity control mechanism with high control reliability.

(Means for Solving the Problems) In order to achieve the above object, the present invention provides a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a vane of the rotor. A vane-type compression device comprising a vane slidably fitted in a groove, and compressing the fluid by varying the volume of a cavity defined by the side block, cam ring, rotor, and vane. In the machine, a bypass port provided in the side block having the suction port of the both side blocks, and a pressure operating chamber provided in the side block having the suction port and communicating with the low pressure chamber side and the high pressure chamber side. , slidably fitted into the pressure working chamber so as to divide the pressure working chamber into a first chamber communicating with the low pressure chamber side and a second chamber communicating with the high pressure chamber side via an orifice. a control member having a pressure receiving part equipped therein and controlling the opening angle of the bypass port; and a bypass bored in the side block in parallel with the orifice to communicate the high pressure chamber side and the second chamber. a bypass valve disposed in the bypass hole that opens the bypass hole when the high pressure chamber side pressure is below a predetermined value and closes the bypass hole when the high pressure chamber side pressure is above a predetermined value; , a communication path that communicates the second chamber with the low pressure chamber side; and a communication path provided in the communication path that closes the communication path and controls the low pressure chamber side pressure when the pressure on the low pressure chamber side is equal to or higher than a predetermined value. is less than a predetermined value,
an on-off valve mechanism that opens the communication passage, and the control member rotates in accordance with a pressure difference between the first chamber and the second chamber to control the opening angle of the bypass port. The present invention is characterized in that the discharge capacity can be variably controlled by controlling the compression start timing.

(Example) Hereinafter, one example of the present invention will be described based on the accompanying drawings. FIG. 1 is a partially cutaway side view of a vane type compressor according to the present invention. In the figure, 1 is a housing, which is a cylindrical case 2 with an open end surface, and an opening surface on one end surface of the case 2. It consists of a front head 3 attached with bolts (not shown) so as to close the front head. A discharge port 4 for refrigerant gas, which is a heat medium, is provided on the upper surface of the rear side of the case 2, and an inlet port 5 for refrigerant gas is provided on the upper surface of the front head 3, respectively. 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 main 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, and the rotating shaft 11 is rotated by bearings 12 (only the front side block 8 side is shown) provided on both side blocks 8 and 9. Supported as possible.

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, 4 vane grooves 14) arranged at equal intervals in the circumferential direction along the radial direction of the rotor 10.
Vanes 15 ₁ to 15 ₄ are fitted into these vane grooves 14 so as to be freely retractable along the radial direction.

The front side block 8 has a
Intake ports 16, 16 are provided symmetrically with an offset of 180 degrees (see FIGS. 2 to 7). 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 ₄ is maximized. The suction port 16, 16
penetrates the front side block 8 in the thickness direction, and connects the front head 3 and the front side block 8 through these suction ports 16.
The suction chamber (low pressure side chamber) 17 and the void chamber 1 between
3 are in communication.

Discharge ports 1 are provided on both side peripheral walls of the cam ring 7.
8 and 18 are provided, and a discharge chamber (high pressure side chamber) 19 in the case 2 is provided through these discharge ports 18.
and the void chamber 13 are in communication. As shown in FIG. 2, these discharge ports 18, 18 are provided with a discharge valve 20 and a discharge valve stop 21, respectively.

As shown in FIG. 7, the front side block 8 is provided with an annular recess 22 on its one side (rotor 10 side) surface, and arc-shaped bypass ports 23, 23 are provided in the recess 22 in the circumferential direction. They are arranged symmetrically with an offset of 180 degrees (Fig. 5), and the suction chamber 17 and the cavity chamber 1 are connected via these bypass ports 23.
3 communicates with each other. 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. Further, on one side of the control member 24, protruding pressure receiving portions 26, 26 are integrally provided in a symmetrical manner and are offset by 180 degrees in the circumferential direction. These pressure receiving parts 26, 26 are slidably fitted into arc-shaped pressure operating chambers 27, 27 provided continuously with the bypass ports 23, 23, as shown in FIG. The inside of these pressure working chambers 27 is divided into a first chamber 27 ₁ by the pressure receiving section 26 .
The first chamber ₂₇₁ is connected to the suction chamber ₁₇ via the suction port 16 and the bypass port 23, and the second chamber ₂₇₂ is connected to the orifice 28.
They each communicate with the discharge chamber 19 via. The one second chamber 27 ₂ and the other second chamber 27 ₂ communicate with each other through a communication hole 29 bored in the control member 24, and the one second chamber 27 ₂ and the discharge chamber 19 The orifice 28 is interposed between the two.

Further, a bypass hole 3 is provided between the second chamber 27 ₂ and the discharge chamber 19 in parallel with the orifice 28 .
9 is bored, and the bypass hole 39 is provided with a bypass valve 40. The bypass valve 40 is
It opens and closes in response to the pressure on the discharge chamber 19 side (high pressure chamber side), and includes a ball valve body 41, a spring 42 that always biases the ball valve body 41 in the valve opening direction, and a ball valve body 41. It consists of a supporting stopper pin 43. When the pressure on the side of the discharge chamber 19 is lower than a predetermined value, the ball valve body 41 opens the bypass hole 39 by the urging force of the spring 42, and when the pressure is higher than the predetermined value, the pressure causes the ball valve body 41 to open the bypass hole 39. The ball valve body 41 is configured to close the bypass hole 39 against the biasing force of the spring 42.

As shown in FIG. 3, the other second chamber ₂₇₂ communicates with the suction chamber 17 via a communication passage 32, and the communication passage 32 is provided with an on-off valve mechanism 33. The opening/closing valve mechanism 33 opens and closes in response to pressure on the suction chamber 17 side (low pressure chamber side), and includes a bellows 34, a case 35, a ball valve body 36,
A spring 37 that urges the ball valve body 36 in the valve closing direction.
It consists of When the pressure on the suction chamber 17 side is higher than a predetermined value, the bellows 34 is in a contracted state, and the ball valve body 36 is closed to the communication passage 3 by the biasing force of the spring 37.
2 is blocked. Further, when the pressure on the side of the suction chamber 17 is below a predetermined value, the bellows 34 is expanded and the ball valve body 36 is pressed by the rod 34a at its tip against the biasing force of the spring 37. Open. An O-ring 38 is interposed between the case 35 and the front side block 8.

The control member 24 is biased by a coil spring 31, which is a biasing member, in a direction that increases the opening angle of the bypass port 23 (counterclockwise in FIG. 5). This coil spring 31 is wound around the outer circumferential side of the central boss portion 8a of the front side block 8 extending toward the suction chamber 17 side, and has one end attached to the central boss portion 8a and the other end attached to the control member 24. They are each connected to the pressure receiving section 26.

Note that a specially shaped sealing member 30 as shown in FIG. 7 is attached to the front side block 8 side of the control member 24, which allows the first chamber 27 ₁ and the second chamber 27 ₂ to be separated from each other. and between the vane back pressure side and the suction pressure side are airtightly sealed.

(Operation) Next, the operation of the vane type compressor of the present invention having the above structure will be explained.

When the rotary shaft 11 is rotated in relation to the engine of the vehicle, and the rotor 10 rotates clockwise in FIG.
The vanes 15 ₁ to 15 ₄ protrude in the radial direction from the vane groove 14 due to centrifugal force and vane back pressure, and rotate integrally with the rotor 10 while their tip surfaces slide against the inner peripheral surface of the cam ring 8, and each vane 15 ₁ ~15 ₄
In the suction stroke to expand the volume of the void chamber 13 divided by
The refrigerant gas is compressed in the compression stroke to reduce the volume of the
In the discharge stroke at the end of the compression stroke, the discharge valve 20 is opened by the pressure of the compressed refrigerant gas, and the compressed refrigerant gas passes sequentially through the discharge port 18, the discharge chamber 19, and the discharge port 4 to the air conditioner (not shown). Supplied to the heat exchange circuit.

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 the pressure in the discharge chamber 19, which is the high pressure side, is introduced into the second chamber 2 of both pressure working chambers 27, 27 through the orifice 28 and the communication hole 29.
7 ₂ , introduced within 27 ₂ . Therefore, the first chamber 2
7 The sum of the pressure inside ₁ and the biasing force of the coil spring 31 (the force that presses the control member 24 in the direction that increases the opening angle of the bypass port 23, that is, the force that rotates it in the direction of arrow B in FIG. 5) ) and the pressure in the second chamber 27 ₂ (the force that presses the control member 24 in the direction that the opening angle of the bypass port 23 becomes smaller, that is, the force that rotates it in the direction of arrow A in FIG. 5). The control member 24 rotates in accordance with the bypass port 2.
By controlling the opening angle of No. 3, 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 refrigerant gas (suction pressure) in the suction chamber 17 is relatively high, so the bellows 34 of the on-off valve mechanism 33 contracts, and the ball valve body 36 closes the communication path 32. In the closed state, the pressure inside the second chamber ₂₇₂ is lower than that of the first chamber 2.
7. Overcoming the sum of the pressure inside ₁ and the biasing force of the coil spring 31, the control member 24 moves in the direction indicated by the arrow A in FIG.
The control member 24 closes the entire bypass port 23 as shown by the two-dot chain line in FIG. 5 (the opening angle is zero). Therefore, all of the refrigerant gas sent into the void chamber 13 from the suction port 16 is compressed and discharged, so that 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 on-off valve mechanism 3
The bellows 34 of No. 3 expands and the rod 34a presses the ball valve body 36 against the biasing force of the spring 37 to open the valve, so that the communication passage 32 opens. As a result, the pressure in the second chamber 27 ₂ leaks through the communication path 32 into the suction chamber 17 on the low pressure side, so the pressure in the second chamber 27 ₂ decreases, and as a result, the control member 24 rotates in the direction of arrow B in FIG. 5, and the notch 25 of the control member 24 matches the bypass port 23, thereby opening the bypass port 23 as shown by the solid line in FIG. Therefore, since the refrigerant gas sent from the suction port 16 into the cavity chamber 13 leaks into the suction chamber 17 through the bypass port 23, the compression start timing is delayed by the amount that the bypass port 23 opens, and the Since the amount of compressed refrigerant gas in the compressor decreases, the discharge capacity of the compressor decreases and the compressor becomes partially operational.

By the way, when starting up the compressor or changing from the above-mentioned partial operating state to full operating state, the discharge chamber 1
The pressure on the 9 side (high pressure chamber side) has decreased (e.g.
10Kg/cm2 or ^less ), and the pressure is
Since the pressure in _the second chamber 27 ₂ does not rise quickly and the control member 2
However, in the present invention, as described above, the bypass valve 40 may not operate quickly and accurately.
Since the bypass hole 39 is provided, the control member 24 has excellent responsiveness. That is, the discharge chamber 1
When the pressure on the 9 side is lower than a predetermined value, the ball valve body 41 is pushed by the biasing force of the spring 42 as shown in FIG.
opens the bypass hole 39, the pressure on the discharge chamber 19 side passes through the bypass hole 39 and is transferred to the second chamber 27.
₂ , and the pressure in the chamber ₂₇₂ quickly rises. Therefore, the control member 24 operates quickly and accurately to smoothly start the compressor and change from a partially running state to a fully operating state.

Next, when the fully operating state is reached and the pressure on the discharge chamber 19 side becomes higher than a predetermined value, this pressure overcomes the biasing force of the spring 42 and the ball valve body 41 closes the bypass hole 39. is introduced into the second chamber 27 ₂ through.

Note that the bypass valve 40 may be a solenoid valve, and the solenoid valve may be opened and closed by detecting the pressure in the discharge chamber 19 with an appropriate sensor. Also,
Although the pressure of the discharge chamber 19, that is, the discharge pressure is introduced into the second chamber ₂₇₂ , the present invention is not limited to this.
You may make it introduce the pressure which acts to press _51-154 in the discharge direction, ie, vane back _pressure .

The opening angle of the bypass port 23 is determined by the balance between the pressure in the first chamber 27 ₁ and the biasing force of the spring 37 and the pressure in the second chamber 27 ₂ . , suction chamber 1 on the low pressure side
Control member 2 according to changes in pressure (suction pressure) in 7.
Since the rotational position of the compressor 4 changes continuously, continuous variable displacement control of the compressor is possible.

(Effects of the Invention) As explained above, 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 slidably fitted into a vane groove of the rotor. In the vane type compressor, the vane type compressor is equipped with a vane equipped with a rotor, and compresses a fluid by changing the volume of a cavity defined by the side block, the cam ring, the rotor, and the vane. a bypass port provided in the side block having the suction 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; A pressure receiving part slidably fitted so as to partition the pressure working chamber into a first chamber communicating with the low pressure chamber side and a second chamber communicating with the high pressure chamber side via an orifice. a control member for controlling the opening angle of the bypass port; a bypass hole bored in the side block in parallel with the orifice to communicate the high pressure chamber side and the second chamber; and the bypass hole. a bypass valve disposed in the second chamber that opens the bypass hole when the pressure on the high pressure chamber side is below a predetermined value and closes the bypass hole when the pressure on the high pressure chamber side is above the predetermined value; and a communication path that communicates between the communication path and the low pressure chamber side, and is arranged in the communication path and closes the communication path when the pressure on the low pressure chamber side is above a predetermined value and when the pressure on the low pressure chamber side is below a predetermined value. , further comprising an on-off valve mechanism that opens the communication passage, and the control member rotates in accordance with the differential pressure between the first chamber and the second chamber to control the opening angle of the bypass port. The present invention is characterized in that the compression start timing is controlled and the discharge capacity 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, low in cost, and highly reliable.

In addition, the second chamber of the pressure working chamber and the high pressure chamber side are communicated through a bypass hole having an orifice and a bypass valve, so when the pressure on the high pressure chamber side is low, the bypass valve opens and the high pressure chamber side is connected to the high pressure chamber side. Since the pressure is quickly introduced into the second chamber, the control member always operates smoothly and the reliability of the control is further improved.

[Brief explanation of drawings]

The figures show one embodiment of the vane type compressor of the present invention, FIG. 1 is a cutaway side view of the vane type compressor, and FIG.
The figure is a sectional view taken along the - line in Fig. 1, Fig. 3 is a sectional view taken along the - line in Fig. 1, Fig. 4 is a sectional view taken along the - line in Fig. 1, and Fig. 5 is a sectional view taken along the - line in Fig. 1. of-
6 is a sectional view taken along the - line in FIG. 4, and FIG. 7 is an exploded perspective view of the main parts. 7...Cam ring, 8...Front side block, 9...Rear side block, 10...Rotor. 1
3... Void chamber, 14... Vane groove, 15 ₁ to 15 ₄ ... 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 part, 27...
Pressure operation chamber, 27 ₁ ... first chamber, 27 ₂ ... second chamber, 28 ... orifice, 32 ... communication passage, 33 ... opening/closing valve mechanism, 39 ... bypass hole, 40 ... bypass valve.

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 control member that controls the opening angle of the bypass port and has a pressure receiving part that is slidably fitted so as to partition the first chamber and the second chamber that communicates with the high pressure chamber through an orifice; ,
a bypass hole bored in the side block in parallel with the orifice to communicate the high pressure chamber side and the second chamber; and a bypass hole provided in the bypass hole when the high pressure chamber side pressure is below a predetermined value. , a bypass valve that opens the bypass hole and closes the bypass hole when the pressure on the high pressure chamber side is equal to or higher than a predetermined value, a communication passage that communicates the second chamber with the low pressure chamber side, and the communication passage. When the low pressure chamber side pressure is above a predetermined value,
and an on-off valve mechanism that closes the communication passage and opens the communication passage when the pressure on the low pressure chamber side is below a predetermined value, and the valve mechanism opens the communication passage according to the pressure difference between the first chamber and the second chamber. A vane type compressor, characterized in that the control member rotates to control the opening angle of the bypass port, thereby controlling compression start timing and variable control of discharge capacity.