JPH1113662A - Vane rotary type variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce bypass loss of low temperature refrigerant gas by providing a specified number of vanes capable of advancing in the rotary radial direction, on a rotary circumferential part. SOLUTION: Seven vanes 12 of a rotor 9 are arranged. AS a result, a suction capacity of low pressure refrigerant gas in one compressing chamber 13 formed between adjacent vanes 12 is reduced comparing with that of three to five vanes, a bypass rate for bypassing from one compressing chamber 13 is reduced at the time of high speed operation, bypass loss is reduced, and it is solved that excessive load is applied on a driving means of the rotor 9. A delivery temperature of high pressure refrigerant gas is not raised, cooling performance is improved, and the damage of a pipe for connecting a compressor and a condenser to each other is prevented. In the case where the elliptic shape of a cylinder 7 is the same, the delivery rate of the high pressure refrigerant gas is maximized when the number of the vanes 12 is seven pieces, and vibration of a two cylinder type compressor is prevented by forming an odd number of vanes 12.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane rotary type variable displacement compressor used in an air conditioner system such as a car cooler, and more particularly to a small, high-performance vane rotary type variable displacement compressor.

[0002]

2. Description of the Related Art Conventionally, as shown in FIGS. 3 and 4, an open end of a casing 1 is closed by a front head 2 and an electromagnetic clutch 3 is provided in the casing 1 as shown in FIGS. The compressor main body 4 connected to is accommodated.

[0003] The compressor body 4 includes a front side block 5.
A cylinder 7 having a substantially elliptical cylindrical inner circumference is provided between the cylinder 7 and the rear side block 6.
A rotor 9 is rotatably suspended in a cylinder chamber 8 formed by the above.

A rotor shaft 10 is provided integrally with the rotor 9 so as to penetrate between end faces thereof, and the rotor shaft 10 is rotatably supported by both side blocks 5 and 6.

[0005] A slit-shaped vane groove 11 is formed in the rotor 9 in the radial direction.
Five vanes 12 are mounted so as to be able to advance and retreat, and when the rotor 9 rotates, the vanes 12 are urged toward the inner wall side of the cylinder 7 by centrifugal force and oil pressure at the bottom of the vane groove.

The small chamber of the cylinder chamber 8 partitioned by the rear side block 6, the cylinder 7, the rotor 9, the vane 12, and a control plate, which will be described later, is called a compression chamber 13. The rotation of the rotor 9 repeatedly changes the capacity.

[0007] A suction chamber 18 and a suction port 19 are formed in the front head 2, and low-pressure refrigerant gas from the air conditioning system is sucked into the suction chamber 18 through the suction port 19.

A discharge chamber 14 is formed in the casing 1 on the downstream side of the compressor body 4 to discharge the high-pressure refrigerant gas compressed by the rotation of the rotor 9 in the compression chamber 13. A discharge port 15 for discharging the high-pressure refrigerant gas to the air-conditioning system side is opened, and an oil separator 16 for separating the lubricating oil A from the high-pressure refrigerant gas is disposed below the discharge port 15.

An oil storage chamber 17 for storing lubricating oil A to be supplied to a sliding portion of the compressor body 4 is formed below the discharge chamber 14.

[0010] Between the front side block 5 and the cylinder 7, that is, on the inner side of the front side block 5,
A substantially disk-shaped control plate 20 is mounted on the shaft. The control plate 20 is rotatable within a predetermined angle.
0 supported. 18 at the periphery of the control plate 20
A pair of recesses 21 are formed at the 0 ° facing position, and the suction chamber 18 and the compression chamber 13 communicate with each other through the recesses 21.

That is, the control plate 20 controls the suction capacity of the low-pressure refrigerant gas in the compression chamber 13 so as to keep the output of the compressor constant during high-speed operation and low-speed operation.

In such a vane rotary type variable displacement compressor, when the rotor 9 rotates and the capacity of the compression chamber 13 changes, the low pressure refrigerant gas in the suction chamber 18 is sucked and compressed by the change in capacity.

In this case, during high-speed operation of the compressor, the control plate 20 causes the low-pressure refrigerant gas sucked into the compression chamber 13 to bypass the suction chamber 18. That is, a part of the low-pressure refrigerant gas in the compression chamber 13 is returned from the recess 21 of the control plate 20 to the suction chamber 18 so that the discharge amount of the high-pressure refrigerant gas after compression per unit time of the compressor becomes constant. Is controlled.

The compressed high-pressure refrigerant gas passes from the compression chamber 13 through the discharge hole 22 of the cylinder 7, the discharge communication path of the rear side block 6, the oil separator 16, and the discharge chamber 14 in this order. To the air conditioning system side.

[0015]

In the vane rotary type variable displacement compressor as proposed above, when the control plate 20 controls the suction capacity of the compression chamber 13, one of the low-pressure refrigerant gas sucked into the compression chamber 13 is removed. A so-called bypass loss that consumes power to return the section to the suction chamber 18 occurs.

For this reason, the rotational power of the rotor 9 increases,
There is a problem that an excessive load is applied to an engine, a motor, and the like, which are driving means of the rotor 9, and that the cooling temperature of the air conditioner system decreases because the discharge temperature of the high-pressure refrigerant gas discharged to the air conditioner system side increases. .

There is also a problem that a pipe (hose) connecting the compressor and the condenser is damaged due to an increase in the discharge temperature of the high-pressure refrigerant gas.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a vane rotary type variable displacement compressor capable of reducing a bypass loss of a low-pressure refrigerant gas. Is to do.

The above and other objects and novel features of the present invention will become apparent from the description of the present specification and the accompanying drawings.

[0020]

In order to achieve the above object,
The vane rotary type variable displacement compressor of the present invention,
A cylinder provided between a front member and a rear side block, a cylinder chamber formed by the front member, the rear side block, and the cylinder; a rotor rotatably suspended in the cylinder chamber; Seven or more vanes mounted on the periphery so as to be able to advance and retreat in the radial direction of the rotor, and a compression formed between adjacent vanes rotatably mounted on the inner surface side of the front member so as to be rotatable within a predetermined angle. A control plate that varies the volume of the chamber according to the rotation angle.

Therefore, according to the present invention, since the number of vanes is set to 7 or more, one compression formed between adjacent vanes in the cylinder chamber is compared with the conventional case where the number of vanes is 3 to 5 sheets. The suction capacity of the low-pressure refrigerant gas in the chamber is reduced. Therefore, the amount of bypass that must be bypassed from one compression chamber is reduced, and as a result, bypass loss is reduced.

[0022]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a sectional view of a main part of a vane rotary type variable displacement compressor according to one embodiment of the present invention, and FIG. 2 is a high pressure refrigerant of the vane rotary type variable displacement compressor according to one embodiment of the present invention. FIG. 4 is a characteristic diagram of a gas discharge amount and the number of vanes.

As shown in FIG. 3, the basic structure of the vane rotary type variable displacement compressor is such that, for example, a compressor body 4 is housed in a casing 1, and the compressor body 4 is provided between a front side block 5 and a rear side block 6. A cylinder 9 formed by the side blocks 5, 6 and the cylinder 7. A rotor 9 is rotatably suspended in a cylinder chamber 8. A vane 12 is mounted to be able to move forward and backward, and a control plate 20 is provided between the front side block 5 and the cylinder 7.
The control plate 20 controls the suction capacity of the low-pressure refrigerant gas in the compression chamber 13 so as to keep the output of the compressor constant during high-speed operation and low-speed operation. The compressed, compressed high-pressure refrigerant gas passes from the compression chamber 13 through the discharge hole 22 of the cylinder 7, the discharge communication path of the rear side block 6, the oil separator 16, and the discharge chamber 14 in this order. Is the same as that of the conventional example, and therefore, the same members are denoted by the same reference numerals and detailed description thereof will be omitted.

As shown in FIG. 1, the vane rotary type variable displacement compressor according to the present embodiment has seven vanes 12 mounted on the periphery of a rotor 9 so as to be able to move forward and backward.

When the operation of such a vane rotary type variable displacement compressor is started, the rotor 9 rotates and the capacity of the compression chamber 13 changes.
8 low-pressure refrigerant gas is taken in and compressed.

The compressed high-pressure refrigerant gas passes from the compression chamber 13 through the discharge hole 22 of the cylinder 7, the discharge communication path of the rear side block 6, the oil separator 16, and the discharge chamber 14 in this order. Is discharged to the air conditioning system side.

In this case, the vane 1 provided on the rotor 9
By setting the number of sheets 2 to seven, the suction capacity of the low-pressure refrigerant gas in one compression chamber 13 formed between the adjacent vanes 12 is reduced as compared with the case where the number of vanes is 3 to 5 as in the conventional case. Decrease. Therefore, during high-speed operation, the amount of bypass that must be bypassed from one compression chamber 13 is reduced, and the bypass loss is reduced accordingly.

As a result, the problem that the rotational power of the rotor 9 is reduced and an excessive load is applied to an engine, a motor, or the like which is a driving means of the rotor 9 is solved.

Also, the discharge temperature of the high-pressure refrigerant gas discharged to the air conditioner system side does not increase, so that the cooling capacity of the air conditioner system can be improved and the pipe (hose) connecting the compressor and the condenser. Damage can be prevented.

When the cylinders 7 have the same elliptical shape,
The relationship between the number of vanes and the discharge amount of the high-pressure refrigerant gas is as shown in FIG. 2, and the discharge amount of the high-pressure refrigerant gas discharged from the compressor to the air conditioning system side is represented by 7 vanes.
It can be seen that it becomes the maximum when it is made into sheets. That is, when the number of vanes is 7, the size and performance of the compressor can be reduced.

Further, by setting the number of vanes to an odd number such as seven, it is effective in preventing vibration when high-pressure refrigerant gas is discharged from the compression chamber 13 in a two-cylinder compressor.

By setting the number of vanes to 7, the thickness of the rotor 9 between the vane grooves 11 is reduced.
Is not so much as to decrease the durability.

Although the vane rotary type variable displacement compressor according to the embodiment of the present invention has been described in detail, the present invention is not limited to the vane rotary type variable displacement compressor described in the above embodiment. Various changes can be made in the design without departing from the spirit of the invention described in the appended claims.

For example, in this embodiment, the number of vanes is limited to seven. However, even if eight or more vanes are provided, the bypass loss in the compressor can be reduced.

In the present embodiment, the front side block and the front head are provided, and the control plate is axially mounted on the inner side of the front side block. Instead, the control plate is mounted on the inner side of the front head. The same effect can be expected even with a shaft attached.

[0037]

As will be understood from the above description, the vane rotary type variable displacement compressor of the present invention has one compression chamber because seven or more vanes are mounted on the periphery of the rotor so as to be able to move forward and backward. , Suction capacity is reduced, and bypass loss is reduced.

Therefore, it is possible to prevent a problem that the rotational power of the rotor is reduced and an excessive load is applied to the engine and the motor.

Further, the discharge temperature of the high-pressure refrigerant gas discharged to the air conditioner system does not increase, so that the cooling capacity of the air conditioner system can be prevented from lowering.

Further, it is possible to prevent damage to a pipe (hose) connecting the compressor and the condenser.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of a vane rotary type variable displacement compressor showing an embodiment of the present invention.

FIG. 2 is a characteristic diagram showing the relationship between the discharge amount of high-pressure refrigerant gas and the number of vanes in a vane rotary variable displacement compressor according to an embodiment of the present invention.

FIG. 3 is a sectional view of a conventional vane rotary type variable displacement compressor.

FIG. 4 is a sectional view taken along line XX of FIG. 3;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Casing 2 Front head 3 Electromagnetic clutch 4 Compressor body 5 Front side block 6 Rear side block 7 Cylinder 8 Cylinder chamber 9 Rotor 10 Rotor shaft 11 Vane groove 12 Vane 13 Compression chamber 14 Discharge chamber 15 Discharge port 16 Oil separator 17 Oil storage Chamber 18 Suction chamber 19 Suction port 20 Control plate 21 Recess 22 Discharge hole A Lubricating oil

Claims (1)

[Claims] A cylinder provided between a front member and a rear side block; a cylinder chamber formed by the front member, the rear side block and the cylinder; and a rotor rotatably suspended in the cylinder chamber. And seven or more vanes mounted on the periphery of the rotor so as to be able to advance and retreat in the radial direction of the rotor; and between the adjacent vanes rotatably mounted at a predetermined angle on the inner surface side of the front member. And a control plate that varies the capacity of the compression chamber formed in accordance with the rotation angle.