JP3598155B2 - Gas compressor - Google Patents

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity gas compressor used for a car air conditioner and the like, and in particular, has a small external appearance of the apparatus and has an excellent capacity control start-up.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, this kind of gas compressor has a front head 1 and a rear side block 2 as first and second blocks as shown in FIG. It becomes.
[0003]
A rotor 5 is rotatably suspended in a cylinder chamber 4 formed by the front head 1, the rear side block 2 and the cylinder 3, and the rotor 5 has a slit-shaped vane in the radial direction as shown in FIG. Grooves 6, 6... Are formed, and vanes 7, 7. Are urged toward the inner wall side of the cylinder 1 by the centrifugal force generated by the rotation of the rotor 5 and the oil pressure at the bottom of the vane groove.
[0004]
The vanes 7, 7 partition the cylinder chamber 4 into a plurality of small chambers. These small chambers are referred to as compression chambers 8, 8,... To compress the low-pressure refrigerant gas. The compressed high-pressure refrigerant gas is discharged to the discharge chamber 11 through the discharge ports 9, 9, the discharge valves 10, 10, and the like.
[0005]
As shown in FIG. 2, a control plate 12 is rotatably provided between the front head 1 and the cylinder 3, and the control plate 12 controls the compression capacity of the refrigerant gas by adjusting the suction amount of the refrigerant gas. I do.
[0006]
That is, the low-pressure refrigerant gas to be compressed is sucked into the cylinder chamber 4 side from the suction chamber 13 through the notches 12a, 12a (see FIG. 4) of the control plate 12 and the intake passage 14 of the cylinder 3. When the control plate 12 rotates in the rotation direction of the rotor 5, the position of the notch 12a changes, and the volume at the start of compression of the compression chamber 8 partitioned by the control plate 12, the rear side block 2, the cylinder 3, the rotor 5, and the vane 6. Becomes smaller, that is, the refrigerant gas to be sucked in decreases, and the compression capacity decreases.
[0007]
On the other hand, when the control plate 12 rotates in the opposite direction to the rotor 5 from this state and the positions of the notches 12a return to the original position, the volume of the compression chamber 8 at the start of compression increases, and the refrigerant gas to be sucked in , The compression capacity increases.
[0008]
The rotation driving of the control plate 12 is performed by the plate driving means 15 shown in FIG.
[0009]
The plate drive means 15 has a drive shaft 16 slidably disposed in the front head 1, and the pressure of the suction chamber 13 (suction pressure P 1) and the force of a spring 17 act on the tip end surface 16 a of the drive shaft 16. On the other hand, the rear end face 16b is provided so that the pressure (discharge pressure P2) on the discharge chamber 11 side acts. Strictly speaking, the front end surface 16a of the drive shaft 16 is acted upon by a pressing force at the front end of the drive shaft composed of the force of the suction pressure P1 × the area of the front end surface 16a and the spring force, and the discharge pressure is applied to the rear end surface 16b. A drive shaft rear end pressing force having an area of P2 × the rear end surface 16b is applied. The discharge pressure P2 acting on the rear end face 16b of the drive shaft is obtained by adjusting the oil pressure supplied from the oil reservoir 18 of the discharge chamber 11 via the oil passage 19 by the throttle passage 20 and the control adjustment valve 21.
[0010]
The distal end side concave portion 22 of the drive shaft 16 is engaged with a drive pin 23, and the drive pin 23 stands on the control plate 12.
[0011]
In such a plate driving means 15, the drive shaft 16 slides by the balance of the suction pressure P1, the discharge pressure P2, and the force of the spring 17, and the slide stop position is determined. When the drive shaft 16 slides, the propulsive force is transmitted to the control plate 12 via the drive pin 23, whereby the control plate 12 and the drive pin 23 rotate integrally with the slide of the drive shaft 16. .
[0012]
[Problems to be solved by the invention]
However, in the conventional gas compressor, (1) the diameter of the drive shaft 16 is at least a minimum for the rotational movement of the drive pin 23 from the viewpoint of avoiding an increase in the size of the front head 1 in order to reduce the external appearance of the device. There is only a required diameter. {Circle around (2)} When the operation of the compressor is stopped, there is no difference between the discharge pressure P2 and the suction pressure P1 and the internal pressure is constant, so that the drive shaft 16 is pushed by the force of the spring 17 and moves to the bottom of the slide range. Position, whereby the control plate 12 is rotated clockwise to the maximum and the compression capacity is set to the minimum, so that the following problems occur.
[0013]
When the operation of the compressor is restarted, the compressor starts from the minimum compression capacity, so that a large pressure difference between the suction pressure P1 and the discharge pressure P2 hardly occurs. Further, since the drive shaft 16 has a small diameter, the difference is small. During this period, a sufficient propulsion force is hardly generated on the drive shaft 16, and even if it is generated, it is smaller than the force of the spring 17. Therefore, the slide of the drive shaft 16 from the position where the compression capacity is minimized to the position where the compression capacity is maximized (slide of the drive shaft 16 in the direction indicated by the arrow A in the figure) and the control plate 12 in the direction where the compression capacity increases. (The rotational movement of the control plate 12 in the direction indicated by the arrow B in the figure) is not performed, so that the compression capacity does not increase, and the rise of the capacity control by the control plate 12 is poor, and the necessary cooling capacity is obtained. I can't.
[0014]
Further, such a poor start-up is not limited to only when the compressor is started, and the same is true when the compression capacity shifts from the minimum to the maximum during the operation of the compressor.
[0015]
The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas compressor which has a small external appearance of a device and which is excellent in capacity control startup.
[0016]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a cylinder interposed between first and second blocks, a rotor rotatably suspended in a cylinder chamber formed by the two blocks and the cylinder, A vane mounted on the rotor so as to freely advance and retreat in a vane groove, a control plate rotatably disposed between the block and the cylinder, and plate driving means for rotating the control plate. A variable-capacity gas in which the volume of the refrigerant gas sucked from the intake chamber into the cylinder chamber by the rotation of the rotor is adjusted by the control plate, and the adjusted refrigerant gas is compressed and discharged to the discharge chamber side. in the compressor, the plate drive means, the drive shaft distal end pushing force consisting of the force and the spring force of the pressure × distal end surface area of the suction chamber side acts on the distal end surface, above the rear end surface A drive shaft drive shaft rear end pushing force of the pressure × rear end surface area of the outlet chamber side acts engage the front end side recess of the drive shaft, and a drive for rotating the control plate in conjunction with the sliding of the drive shaft A pin and a rear end side outer periphery of the drive shaft are formed to have a larger diameter than the front end surface of the drive shaft, and the pressure of the suction chamber side and the pressure of the pressure receiving section tip of the pressure receiving section area and the pressure of the discharge chamber side × A pressure receiving portion on which a pressure receiving portion rear end pressing force of a pressure receiving portion area acts, a front end pressing force including the drive shaft front end pressing force and the pressure receiving portion front end pressing force, the drive shaft rear end pressing force, and The drive shaft slides due to a difference from a rear end pressing force formed by the pressure receiving unit rear end pressing force .
[0017]
According to the present invention, the pressure receiving surface of the suction pressure and the discharge pressure of the drive shaft is enlarged by the pressure receiving portion. Therefore, even when the difference between the suction pressure and the discharge pressure is small, such as immediately after the start of operation of the compressor, a large propulsive force is generated on the drive shaft that is not defeated by the spring force. The rotational movement of the control plate is performed quickly.
[0018]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of a gas compressor according to the present invention will be described in detail with reference to FIG.
[0019]
A cylinder 3 is interposed between the basic structure of the gas compressor, for example, a front head 1 and a rear side block 2, and a rotor 5 is provided in a cylinder chamber 4 formed by the front head 1, the rear side block 2 and the cylinder 3. Are rotatably mounted, and vanes 7, 7,... Are mounted on the vane grooves 6, 6,. Since the control plate 12 is rotatably driven by the plate driving means 15 as in the related art, the same members are denoted by the same reference numerals, and detailed description thereof will be omitted.
[0020]
This gas compressor has a drive shaft 16 as plate driving means 15 as shown in FIG. 1, and the drive shaft 16 is slidably disposed in the front head 1.
[0021]
A concave portion 22 is provided on the distal end side 16 a of the drive shaft 16, the concave portion 22 is engaged with a drive pin 23, and the drive pin 23 stands on the control plate 12.
[0022]
A pressure receiving portion 30 is integrally provided on an outer periphery 16 c of the rear end side 16 b of the drive shaft 16, and the pressure receiving portion 30 is formed to have a larger diameter than a diameter at which the distal end concave portion 22 of the drive shaft 16 is formed.
[0023]
The pressure (suction pressure P1) of the suction chamber 13 is applied to the front face 30a (boundary of the drive shaft 16) of the pressure receiving section 30, and the discharge chamber 11 is provided to the rear face 30b of the pressure receiving section 30 in the same manner as the rear end face 16b of the drive shaft 16. Pressure (discharge pressure P2) acts on the tip end surface 16a of the drive shaft 16, and the suction pressure P1 and the force of the spring 17 act.
[0024]
That is, from the viewpoint of improving the propulsive force of the drive shaft 16, the pressure receiving portion 30 is provided with a large diameter by expanding the rear end side 16b of the drive shaft 16. The diameter of the distal end 16a of the drive shaft 16 is formed to a minimum diameter necessary for the rotational movement of the drive pin 23 from the viewpoint of avoiding an increase in the size of the front head 1.
[0025]
The discharge pressure P2 acting on the rear surface portion 30b of the pressure receiving portion 30 is obtained by adjusting the oil pressure supplied from the oil reservoir 18 of the discharge chamber 11 via the oil passage 19 by the throttle passage 20 and the control adjustment valve 21.
[0026]
Next, the operation of the gas compressor configured as described above will be described.
[0027]
When the operation of the compressor is started and the rotor 5 rotates, the volume of the compression chambers 8, 8,... Changes, whereby the notches 12a, 12a of the control plate 12 and the intake air of the cylinder 3 from the suction chamber 13. The low-pressure refrigerant gas is sucked into the cylinder chamber 4 through the passage 14 and compressed, and the compressed high-pressure refrigerant gas is discharged into the discharge chamber 11 through the discharge ports 9 and 9 and the discharge valves 10 and 10. Since it is the same as the conventional one, its detailed description is omitted (see FIGS. 2 to 4).
[0028]
According to this gas compressor, when the operation is stopped, there is no difference between the discharge pressure P2 and the suction pressure P1, and the internal pressure is constant. It is located at the bottom, whereby the control plate 12 is set to rotate clockwise to the maximum and to minimize the compression capacity.
[0029]
That is, at the start of operation, the volume of the compression chamber 8 at the start of compression is the minimum, and the notches 12a, 12a of the control plate 12 are located at positions beyond the elliptical major axis of the cylinder 3. Part of the refrigerant gas sucked into the chamber 4 is discharged from the notches 12a, 12a into the suction chamber 13, and the compression capacity is reduced.
[0030]
When the operation of the compressor is started from such a state, the pressure of the suction chamber 13 (suction pressure P1) acts on the distal end face 16a of the drive shaft 16 and the front face part 30a of the pressure receiving part 30 immediately after the start of the operation. The pressure of the discharge chamber 11 (discharge pressure P2) also acts on the rear end face 16b of the drive shaft 16 and the rear face part 30b of the pressure receiving part 30. Strictly speaking, the front end face 16a of the drive shaft 16 is acted on by the front end portion 30a of the pressure receiving portion, which is composed of the force of the suction pressure P1 × the area of the front end face 16a and the spring force. The pressing force of the pressure receiving portion at the suction pressure P1 × the area of the pressure receiving portion acts on the rear end surface 16b of the drive shaft 16, and the pressing force at the rear end of the driving shaft having the area of the discharge pressure P2 × the rear end surface 16b acts on the pressure receiving portion. A rear-end pressing force of the pressure receiving portion of the discharge pressure P2 × the pressure receiving portion area acts on the rear surface portion 30b.
[0031]
That is, even when the difference between the suction pressure P1 and the discharge pressure P2 is small, such as when the compression capacity shifts from the minimum to the maximum immediately after the start of the operation or during the operation, the suction pressure P1 and the discharge pressure P2 are driven. Pressure is received not only at the front end surface 16a and the rear end surface 16b of the shaft 16 but also at the front surface portion 30a and the rear surface portion 30b of the pressure receiving portion 30, and the pressure receiving area is large. As a result, a large propulsive force is generated on the drive shaft 16 which is not inferior to the force of the spring 17, and the drive shaft 16 is moved in the direction of the spring 17 as shown by the arrow A in FIG. Slide to maximum position.
[0032]
As described above, when the drive shaft 16 slides, the propulsive force is transmitted to the control plate 12 via the drive pin 23, whereby the control plate 12 and the drive pin 23 are interlocked with the slide of the drive shaft 16 in the figure. Rotate counterclockwise as indicated by arrow B.
[0033]
When the control plate 12 rotates counterclockwise to return the positions of the notches 12a, 12a, the volume of the compression chamber 8 at the start of compression increases, and the control chamber 12 passes through the notches 12a, 12a as described above. There is no discharge (bypass) of the refrigerant gas, and the compression capacity increases.
[0034]
In the gas compressor of this embodiment, a pressure receiving portion 30 is provided on the outer periphery of the rear end side of the drive shaft 16, and the pressure receiving portion 30 is also configured to receive the suction pressure P1 and the discharge pressure P2. For this reason, the pressure receiving surface of the suction pressure P1 and the discharge pressure P2 of the drive shaft 16 is expanded by the pressure receiving portion 30, so that the compression capacity shifts from the minimum to the maximum immediately after the start of operation of the compressor or during the operation. In addition, even when the difference between the suction pressure P1 and the discharge pressure P2 is small, a large propulsive force is generated on the drive shaft 16 which is not defeated by the force of the spring 17, and the slide of the drive shaft 16 and the control plate 12 The rotational movement is performed quickly, and the rise of the capacity control by the control plate 12 is improved.
[0035]
Further, in this gas compressor, the pressure receiving portion 30 is provided by enlarging only a part of the drive shaft 16 instead of the entire drive shaft 16, so that the front head 1 housing the drive shaft 16 does not become large. In addition, the appearance of the device is small.
[0036]
【The invention's effect】
In the gas compressor according to the present invention, the pressure receiving portion is provided on the outer periphery of the rear end side of the drive shaft as described above, and the pressure receiving portion also receives the pressure of the suction chamber and the discharge chamber. For this reason, the pressure receiving surface of the suction pressure and the discharge pressure of the drive shaft is enlarged by the pressure receiving portion. A large propulsive force is generated on the drive shaft, and the slide of the drive shaft and the rotational movement of the control plate in conjunction therewith are performed quickly, so that the rise of capacity control by such a control plate is improved.
[0037]
Further, according to the present invention, since the pressure receiving portion is provided by enlarging only a part of the drive shaft, not the entire drive shaft, it is not necessary to apply a large front head for housing the drive shaft, It is also suitable for miniaturizing the external shape of the device.
[Brief description of the drawings]
FIG. 1 is an explanatory diagram of an embodiment of a gas compressor according to the present invention.
FIG. 2 is a cross-sectional view of a conventional gas compressor.
FIG. 3 is a sectional view taken along line AA of FIG. 2;
FIG. 4 is an explanatory diagram of capacity control in a conventional gas compressor.
[Explanation of symbols]
REFERENCE SIGNS LIST 1 front head 2 rear side block 3 cylinder 4 cylinder chamber 5 rotor 6 vane groove 7 vane 11 discharge chamber 12 control plate 13 intake chamber 15 plate driving means 20 drive shaft 22 recess 23 drive pin 30 pressure receiving part

Claims (1)

A cylinder interposed between the first and second blocks, a rotor rotatably suspended in a cylinder chamber formed by the two blocks and the cylinder, and a vane groove provided in the rotor so as to be movable forward and backward. It has a mounted vane, a control plate rotatably disposed between the block and the cylinder, and plate driving means for rotating the control plate. The rotation of the rotor causes the cylinder chamber to move from the intake chamber to the cylinder chamber. In the variable capacity gas compressor, the volume of the refrigerant gas sucked into the side is adjusted by the control plate, and the adjusted volume of the refrigerant gas is compressed and discharged to the discharge chamber side.
The plate driving means,
The driving shaft tip pressing force, which is composed of the pressure of the suction chamber side × the force of the tip end surface area and the spring force, acts on the tip end surface, and the driving shaft rear end pushing of the discharge chamber side pressure × the rear end surface area acts on the rear end surface. A drive shaft on which force acts,
A drive pin that engages with the tip-side recess of the drive shaft and rotates the control plate in conjunction with the slide of the drive shaft;
On the rear end side outer periphery of the drive shaft, a diameter is formed larger than the tip end surface of the drive shaft, and the pressure on the suction chamber side × the pressure on the tip end of the pressure receiving section and the pressure on the discharge chamber side × the pressure receiving section Pressure-receiving part on which the pressure-receiving part rear end pressing force of the area acts ,
The drive shaft is driven by a difference between a front end pressing force consisting of the driving shaft front end pressing force and the pressure receiving unit front end pressing force and a rear end pressing force consisting of the driving shaft rear end pressing force and the pressure receiving unit rear end pressing force. A gas compressor characterized by sliding .

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