JPH0563634B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a vane type rotary compressor, particularly a vane type rotary compressor having a variable capacity mechanism, which is used, for example, in an automobile air conditioner.

(Prior Art) Various mechanisms for varying the capacity of vane-type rotary compressors are known, but for example, the applicant proposed an internally controlled mechanism in Japanese Patent Application No. 142,600/1982. There is. This is configured such that a rotatable adjustment member is provided on the side block, and the adjustment member is rotated based on the balance between the biasing force of the spring and the pressing force of the pressure chamber to adjust the compression start position. The high-pressure gas is throttled and introduced into the pressure chamber, and the gas is communicated with the low-pressure chamber via a communication path, and the degree of communication between the pressure chamber and the low-pressure chamber is adjusted according to the pressure in the low-pressure chamber. A control valve is provided. When the rotation speed of the compressor increases, the pressure in the low pressure chamber decreases, a communication passage is opened by the control valve, the pressure in the pressure chamber decreases, and the spring rotates the adjustment member in the direction of increasing capacity, and vice versa. When the rotational speed of the compressor decreases, the adjusting member rotates in the opposite direction to reduce the capacity.

(Problem to be solved by the invention) However, in the case of the above-mentioned prior application, since the capacity is controlled according to the pressure of the low pressure chamber, for example, when the car accelerates, the capacity is reduced. Regardless of the desire to reduce the load on the engine and improve acceleration, the pressure in the low pressure chamber does not decrease until after acceleration, so the capacity does not decrease, and it is difficult to control the engine appropriately in response to external changes. There was a problem that I couldn't do it.

Therefore, this invention solves the above problems and
It is an object of the present invention to provide a vane-type rotary compressor that can control capacity not only in response to internal changes but also in response to external changes, thereby optimally controlling capacity.

(Means for Solving the Problems) Therefore, the gist of the present invention is to insert a rotor into which vanes are slidably inserted into a space surrounded by a cylinder and a side block, In a vane-type rotary compressor in which a compression chamber surrounded by a rotor, a side block, and a vane changes in volume as the rotor rotates, the side block is rotatably provided to adjust the compression start position. an adjustment member, an elastic means for biasing the adjustment member in one rotational direction, and a pressure chamber communicating with a high pressure chamber via an orifice so as to generate pressure for pressing the adjustment member in a direction opposite to the biasing direction of the elastic means. a first control valve that adjusts the degree of communication between the pressure chamber and the low pressure chamber in accordance with the pressure in the low pressure chamber; and a first control valve that adjusts the degree of communication between the pressure chamber and the low pressure chamber in accordance with a signal from the outside. and a second control valve.

(Function) Therefore, as the pressure in the low pressure chamber increases or decreases, the first control valve operates to adjust the pressure in the pressure chamber and internally control the capacity, while increasing or decreasing the pressure in the pressure chamber in response to an external signal. Since the second control valve that adjusts the pressure is provided, the capacity can also be controlled from the outside using the second control valve, and therefore the above object can be achieved.

(Example) In FIGS. 1 to 4, a vane type rotary compressor has a cylinder 1 having a substantially elliptical inner surface, and a rotor 2 is installed inside the cylinder 1.
It is inserted so that it contacts near both short diameter parts,
Two operating spaces 3a and 3b are symmetrically defined within the cylinder 1 by the rotor 2. The rotor 2 has a drive shaft 4 fixedly attached to the center of the rotor 2, and has, for example, a drive shaft 4 extending approximately radially from the rotor 2.
Vane grooves 5 are formed, and a vane 6 is slidably inserted into each of the vane grooves 5.

The side blocks 7a, 7b are fixed to both sides of the cylinder 1, and the rotor 2 and vane 6 are in contact with the side blocks 7a, 7b.
Rotor 2, vane 6 and side blocks 7a, 7
Five compression chambers 8 are constructed from b.

The open ends of the shells 9a and 9b fit into each other and surround the periphery of the cylinder 1 and the side blocks 7a and 7b. Rear side block 7b
A low pressure chamber 10 is connected to the front side block 7a and the shell 9b, and a high pressure chamber 11 is connected to the front side block 7a and the shell 9a. The low pressure chamber 10 is connected to an inlet 12 formed in the shell 9b,
Further, the high pressure chamber 11 is connected to a discharge port 13 formed in the shell 9a.

The aforementioned drive shaft 4 is connected to the side blocks 7a, 7.
b is rotatably supported via radial bearings 14a and 14b, and extends to a cylindrical center hole formed in the front side shell 9a, and receives torque from the engine through this extended portion. There is. A mechanical seal 15 is provided between the drive shaft 4 and the shell 9a.

The suction holes 16a and 16b are symmetrically formed so that they communicate with the low pressure chamber 10 when the compression chamber 8 expands in the rear side block 7b. However, the opening rear end positions of the suction holes 16a and 16b relative to the compression chamber 8, that is, the compression start positions, are adjusted by an adjustment member described later. Discharge hole 1
A plurality of valve openings 7a and 17b are formed on both sides of the cylinder 1, and communicate with the valve insertion spaces 18a and 18b when the compression chamber 8 is contracted. Valve insertion space 18a,
18b is composed of a cylinder 1 and covers 19a and 19b attached to the cylinder 1, and includes roll-shaped discharge valves 20a and 20b, and stoppers 21a and 21a for regulating the discharge valves 20a and 20b, respectively.
21b are arranged, and the discharge valves 20a, 20b and stoppers 21a, 21b are arranged in the covers 19a, 19.
It is supported by b. In addition, the valve insertion space 18a,
18b communicates with the high pressure chamber 11 via a discharge communication hole 50 formed in the front side block 7a.

As shown in FIG. 5, a ring-shaped adjustment member 2
2 is rotatably fitted into an annular groove 23 formed in the rear side block 7b. This adjustment member 22 is formed with notches 24a and 24b that are constantly in communication with the suction holes 16a and 16b of the side block 7b described above. Therefore, when the adjustment member 22 is rotated, the notch 24
The circumferential positions of a and 24b change, and therefore,
The suction hole 16 of the compression chamber 8 is opened by the vane 6 mentioned above.
The position where communication with a and 16b is cut off, ie, the compression start position, is adjusted.

A coil-shaped spring 25 constituting a biasing means is elastically mounted between the rear side block 7b and the adjustment member 22, and the adjustment member 22 is moved as shown in FIGS.
It is pressed clockwise as shown in the figure. In addition, the adjustment member 2
2 is provided with tongue-shaped pressure receiving parts 26a, 26b which are fitted into sliding grooves 27a, 27b formed in the side block 7b following the suction holes 16a, 16b. The sliding grooves 27a, 27b and the adjusting member 22 define pressure chambers 28a, 28b. These pressure chambers 28a, 28b are located at the inner periphery of the adjustment member 22,
Airtightness is maintained by a sealing member 29 fitted to the outer periphery and the periphery of the receiving portion. Further, the pressure chambers 28a and 28b are connected to the side block 7b.
A connection space 3 surrounded by connection holes 30a and 30b formed in the side block 7b and shell 9b.
They communicate with each other via 1. Further, one of the pressure chambers 28a, 28b is connected to a first high pressure introduction path 32 formed between the cylinder 1, the side blocks 7a, 7b, and the shells 9a, 9b, and a second high pressure introduction path 32 formed in the side block 7b. The second high pressure introduction path 33 communicates with the high pressure chamber 11 through the high pressure introduction part 33.
The discharge gas is introduced in a restricted manner through an orifice 34 provided in the exhaust gas.

The first control valve 35 is shown in FIGS. 1, 4, and 5.
As shown in the figure, this is for adjusting the degree of communication between the low pressure chamber 10 and the pressure chambers 28a, 28b according to the pressure in the low pressure chamber 10.
A ball-shaped valve 37 and a first valve seat 3 on which the valve body 37 is seated in a first communication path 36 that communicates with the valve body 28b.
8. The valve body 37 is pressed in the seating direction by a valve spring 39 and is connected to a bellows 41 via a valve stem 40 . This bellows 41 is arranged in the low pressure chamber 10, and contracts when the pressure in the low pressure chamber 10 is high, and expands when the pressure in the low pressure chamber 10 is low. The setting force of this bellows 41 can be adjusted using an adjusting screw 42.

The second control valve 43 is composed of an electromagnetic valve as shown in FIG. 6, and includes an excitation coil 45 that is energized according to a control signal from a control unit 44, a stator 46 in which a magnetic pole is generated by the excitation coil 45, and a stator 46 that generates a magnetic pole. It has a needle valve 47. A first communication passage 48 that communicates the low pressure chamber 10 and the pressure chamber 28b is formed in the side block 7b opposite to the needle valve 47. The tip of the needle valve 47 is seated on the second valve seat 49. The acceleration Ap of the vehicle, the temperature Tr inside the vehicle, and the outside temperature Ta are input to the control unit 44, and a control signal is calculated from these input factors.

In the above configuration, when the drive shaft 4 rotates, the vane 5 rotates together with the rotor 2 along the inner surface of the cylinder 1, and the volume of the compression chamber 8 changes. When the compression chamber 8 expands, the compression chamber 8 and the low pressure chamber 10 are connected to the suction holes 16a, 16b and the notch 2 of the adjustment member 22.
4a, 24b, so the suction port 12
Gas entering the low pressure chamber 10 from the suction holes 16a, 1
6b and the notches 24a, 24b into the compression chamber 8. Next, the volume of the compression chamber 8 is reduced, but the rear vane 5 is cut out at the notch 24.
a, 24b, the gas in the compression chamber 8 flows back into the low pressure chamber 10 via the notches 24a, 24b and the suction holes 16a, 16b.
Compression has not started yet. Then, when the rear vane 5 passes through the notches 24a and 24b, the gas in the compression chamber 8 is trapped and compression starts. Further, the rotor 2 rotates and the vane 5 moves forward.
When the gas passes through the discharge holes 17a and 17b, the discharge valves 20a and 20b are opened by the pressure in the compression chamber 8, the compression chamber 8 and the valve insertion spaces 18a and 18b communicate with each other, and the gas in the compression chamber 8 is discharged through the discharge hole. 17a, 17b
is discharged into the valve insertion spaces 18a, 18b through the
It reaches the high pressure chamber 11 via the discharge communication hole 50 and is discharged from the discharge port 13 to the outside of the compressor.

Next, I will explain the operation of the variable capacity mechanism.
When the pressure Ps in the low pressure chamber 10 is high, such as during low speed operation, the bellows 41 of the first control valve 35 contracts to reduce the opening area between the valve body 37 and the first valve seat 38. Therefore, as long as the second communication path 48 is constricted by the second control valve 43, the pressure Pc in the pressure chambers 28a and 28b is equal to the pressure in the high pressure chamber 11.
As a result, the adjustment member 22 rotates counterclockwise against the spring 25, and the timing at which the vane 5 closes the notches 24a and 24b at the rear, that is, the compression start timing, is advanced. The compressor will be operated at high capacity.

Conversely, during high-speed operation, the pressure in the low pressure chamber 10 Ps
Since the bellows 41 of the first control valve 35 expands to increase the opening area between the valve body 37 and the first valve seat 38, the second communication path by the second control valve 43 is reduced. 48 is constricted to a certain level, the pressure Pc in the pressure chambers 28a, 28b decreases to approach the pressure Ps in the low pressure chamber 10, and the adjustment member 22 rotates clockwise due to the pressing force of the spring 25.
The timing at which the rear vanes close the notches 24a and 24b is delayed, and the compressor is operated at a small capacity.

In the second control valve 43, under normal conditions, a small current is passed through the excitation coil 45, the needle valve 47 is slightly separated from the second valve seat 49, and a small amount of gas flows into the pressure chamber 28.
a, 28b to leak into the low pressure chamber 10,
Pc<Pd is always maintained. For example, when the automobile accelerates, the control unit 44 receives the acceleration signal Ap and increases the energization of the excitation coil 45, thereby increasing the opening degree of the second communication path 48.
Therefore, even if the first communication passage 36 is closed by the first control valve 41, the pressure Pc in the pressure chambers 28a, 28b decreases, the adjustment member 22 rotates clockwise, and the capacity becomes small, and the engine It is possible to reduce the load on the vehicle and improve acceleration.

Further, when the outside temperature Ta is low and the inside temperature Tr is high, the control unit 44 turns off the energization to the excitation coil 45 so that the second control valve 43 completely closes the second communication path 48.
Under these conditions, the compressor is driven for the purpose of dehumidification during heating, so the heat load on the evaporator is small and the first control valve 35 is opened to reduce pressure in the pressure chambers 28a and 28b. The pressure is reduced to approximately equal to the pressure in the low pressure chamber 10, resulting in a state close to no-load operation, and the dehumidification function cannot be performed, but the second communication path 48 is completely closed by the second control valve 43. Possibly pressure chamber 28
By increasing the pressures of the compressors a and 28b, the compressor can be driven at a predetermined capacity, thereby making it possible to dehumidify.

In addition to the above-mentioned conditions, the conditions for controlling the second control valve 43 include, for example, reducing the capacity when climbing a hill;
The capacity is increased when the brake is applied to decelerate, and the capacity is decreased when the belt transmission device that transmits the driving force from the engine to the compressor slips, or when the temperature of the discharged gas from the compressor becomes abnormally high. In some cases, known control methods such as setting a small capacity are included.

(Effects of the Invention) As described above, according to the present invention, when the pressure in the low pressure chamber increases or decreases, the first control valve operates to adjust the pressure in the pressure chamber, and rotates the adjustment member. While the capacity is controlled internally by changing the compression start position, a second control valve is provided that adjusts the pressure in the pressure chamber according to an external signal, so the capacity can also be controlled externally using this second control valve. Although the internal control is simple, the drawback of insufficient control can be compensated for, and an optimal system can be obtained. In addition, the second control valve uses the pressure of the high pressure chamber generated inside the compressor to move the adjustment member, so the second control valve operates similarly to the first control valve. The valve can also be made smaller.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing a vane type rotary compressor according to an embodiment of the present invention, FIG. 2 is a sectional view taken along the line -- in FIG. 1, FIG. These figures are a sectional view taken along the line -- in FIG. 1, FIG. 5 is an exploded perspective view of the main parts of the same, and FIG. 6 is a sectional view showing the second control valve used in the same. 1... Cylinder, 2... Rotor, 6... Vane, 7a, 7b... Side block, 8... Compression chamber, 10... Low pressure chamber, 11... High pressure chamber, 22...
Adjustment member, 25...Spring, 28a, 28b
...Pressure chamber, 34...Orifice, 35...1st
control valve, 43... second control valve.

Claims (1)

[Scope of Claims] 1. A rotor into which vanes are slidably inserted is inserted into a space surrounded by a cylinder and a side block, and the compression chamber surrounded by the cylinder, rotor, side block, and vanes is In a vane-type rotary compressor whose volume changes as the rotor rotates,
an adjustment member rotatably provided on the side block to adjust the compression start position; an elastic means for biasing the adjustment member in one rotational direction; and an elastic means for biasing the adjustment member in a direction opposite to the biasing direction of the elastic means. a pressure chamber that communicates with the high pressure chamber via an orifice to generate pressing pressure; a first control valve that adjusts the degree of communication between the pressure chamber and the low pressure chamber in accordance with the pressure of the low pressure chamber; 1. A vane-type rotary compressor having a variable capacity mechanism, characterized by comprising a second control valve that adjusts the degree of communication between the chamber and the low-pressure chamber in accordance with an external signal. 2. A vane type rotary compressor having a variable capacity mechanism according to claim 1, wherein the second control valve is a solenoid valve.