JPH09256976A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent lubricating oil from being supplied excessively at the time of operation while preventing vibration and noise caused by oil compression at the time of re-start without employing the opening/closing valve mechanism of a complex structure. SOLUTION: A plain bearing 9 for rotatably supporting the rear side end part of a driving shaft 7 is housed in the bearing housing chamber 31 of a rear head 6. A guide passage 33 for guiding lubricating oil from the bearing hosing chamber 31 into a suction chamber 11 is arranged on the rear head 6. An annular groove communicated with the guide passage 32 and a spiral groove for supplying lubricating oil into a back pressure groove 60 only when the driving shaft 7 is rotated, are arranged on the inner circumferential surface of the plain bearing 9.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane type compressor, and more particularly to a vane type compressor which does not cause so-called liquid compression (oil compression) at startup.

[0002]

2. Description of the Related Art A vane type compressor includes a cam ring, a rotor rotatably housed in the cam ring, a drive shaft of the rotor, a front side block fixed to a front end surface of the cam ring, and a rear side of the cam ring. A rear side block fixed to the end surface, a front head fixed to the front side end surface of the front side block, a rear head fixed to the rear side end surface of the rear side block, and a plurality of vane grooves provided on the outer peripheral surface of the rotor, And a plurality of vanes slidably inserted into the vane grooves.

The front end of the drive shaft of the rotor is rotatably supported by the front side block via a bearing.

The rear end of the drive shaft of the rotor is rotatably supported by the rear side block via bearings.

The front side block and the front head form a discharge chamber in which the high-pressure refrigerant gas discharged from the compression chamber is stored.

At the rear side end surface of the front side block and the front side end surface of the rear side block, from the start of suction to the end of compression, the inner part of the vane groove (vane back pressure chamber).
A back pressure groove communicating with each is provided.

[0007]

When the operation of the compressor is stopped, the lubricating oil is supplied to the gap between the rear end surface of the rotor and the rear end surface of the front side block in the process of balancing the pressure inside the compressor. Then, the vane back pressure chamber is filled with the lubricating oil through the back pressure groove.

Therefore, when the compressor is restarted, oil compression occurs, and the pressure in the back pressure chamber of the vane is high, so that the vane is difficult to retract into the vane groove, and there is a problem that large vibration and noise are generated. .

As a conventional technique for solving this problem, there is a vane type compressor having the following opening / closing valve mechanism.

In the on-off valve mechanism of the vane type compressor, the front side block is provided with a passage for communicating the front side back pressure groove with the discharge chamber. An on-off valve is provided in the middle of the passage to close the passage when the pressure in the discharge chamber reaches a predetermined value and open the passage when the pressure in the discharge chamber does not reach the predetermined value.

However, the structure of this on-off valve mechanism is complicated, which is one of the causes of increasing the cost of the compressor.

Further, there is a problem that the lubricating oil may be excessively supplied during the operation of the compressor.

The present invention has been made in view of such circumstances, and its object is to prevent vibration and noise due to oil compression at the time of restart without adopting an opening / closing valve mechanism having a complicated structure. It is an object of the present invention to provide a vane compressor capable of preventing excessive supply of lubricating oil during operation of the compressor.

[0014]

In order to solve the above-mentioned problems, a vane type compressor according to a first aspect of the present invention comprises a rotor rotatably housed in a cam ring and a vane provided on an outer peripheral surface of the rotor. A groove, a vane slidably inserted in the vane groove, first and second side members fixed to both end surfaces of the cam ring, and a drive shaft of the rotor provided on the first side member. Bearing housing for accommodating a first bearing that rotatably supports one end of the rotor, and a second bearing that is provided in the second side member and rotatably supports the other end of the drive shaft of the rotor. A second bearing accommodating chamber, a first guide path for guiding the lubricating oil from the high pressure chamber to the first bearing accommodating chamber, and a rotor-side end surface of the first side member, from the start of suction to the end of compression. Between the back of the vane groove In a vane compressor having a back pressure groove for communicating lubricating oil from the first bearing accommodating chamber to the inner portion of the vane groove, the first bearing is a plain bearing, and the first bearing is a plain bearing. A second guide passage that guides the lubricating oil from the bearing housing chamber to the low pressure chamber is provided in the first side member, and an annular groove that communicates with the first guide passage, and an annular groove that communicates with the annular groove and the drive shaft. Is provided on the inner peripheral surface of the plain bearing or on the outer peripheral surface of one end of the drive shaft, the spiral groove feeding lubricating oil only to the back pressure groove side.

Lubricating oil in the high-pressure chamber passes through the first guide passage to the first
The pressure difference between the rotor side and the non-rotor side of the first bearing is large during the operation of the compressor, which is constantly fed into the bearing accommodating chamber, but due to the effect of the viscosity of the lubricating oil accompanying the rotation of the drive shaft due to the spiral groove , The lubricating oil in the first bearing housing chamber flows from the annular groove of the plain bearing to the rotor side through the gap between the outer peripheral surface of the drive shaft and the inner peripheral surface of the plain bearing, and the back pressure groove and the front side of the first side member. It is supplied to the gap between the end surface and the rear end surface of the rotor. The supply of the lubricating oil at this time does not become excessive due to the pressure difference.

When the operation of the compressor is stopped, the pressure in the compressor gradually balances, but during this time, most of the high pressure lubricating oil flows from the spiral groove of the first bearing to the side opposite to the rotor, and through the second guide passage. It is sent to the low pressure chamber. As a result, in the process of balancing the pressure inside the compressor, the lubricating oil is not fed into the inner part of the vane groove through the back pressure groove, and the inner part of the vane groove is not filled with the lubricating oil.

[0017]

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

FIG. 1 is a vertical sectional view of a vane type compressor according to an embodiment of the present invention, and FIG. 2 is a horizontal sectional view of a rotor.
Thick line arrows in FIG. 1 indicate the flow of the lubricating oil.

This vane type compressor has a cam ring 1,
A front side member (second side member) 25 and a rear side member (first side member) 20 respectively arranged on both end surfaces of the cam ring 1, a rotor 2 rotatably housed in the cam ring 1, and a drive of the rotor 2. And a shaft 7. The drive shaft 7 is a needle bearing (second bearing) described later.
It is rotatably supported by 8 and a plain bearing (first bearing) 9.

The front side member 25 is composed of a front side block 3 fixed to the front end surface of the cam ring 1 and a front head 5 fixed to the front end surface of the front side block 3.

A bearing accommodating chamber (second bearing accommodating chamber) 30 is provided in the center of the front side block 3, and a needle bearing 8 is accommodated in the bearing accommodating chamber 30.
Rotatably supports the front end of the drive shaft 7.

A discharge port 5a for high pressure refrigerant gas is formed in the front head 5, and the discharge port 5a communicates with a discharge chamber (high pressure chamber) 10 formed by the front head 5 and the front side block 3. Lubricating oil separated from the refrigerant gas is accumulated at the bottom of the discharge chamber 10. The front side block 3 is provided with a discharge passage 3a that connects the compression space 12 of the cam ring 1 described later and the discharge chamber 10 to each other. Further, a pair of back pressure grooves 50 communicating with the inner part of the vane groove 13 (vane back pressure chamber) described later is provided on the rear end surface of the front side block 3 from the start of suction to the end of compression. . The back pressure groove 50 and the bearing housing chamber 30 are separated by a seal member 51.

The rear side member 20 is the cam ring 1
It is composed only of the rear head 6 fixed to the rear side end surface of the via a O-ring 22. The rear head 6 is formed with a suction port 6a for the refrigerant gas, and the suction port 6a communicates with a suction chamber (low pressure chamber) 11.

A bearing accommodating chamber (first bearing accommodating chamber) 31 is provided in the center of the rear head 6, and a plain bearing 9 is accommodated in the bearing accommodating chamber 31. The plain bearing 9 is an end of the drive shaft 7 on the rear side. Rotatably supported.

A pair of back pressure grooves 60, which communicate with the inner part of the vane groove 13 from the start of suction to the end of compression, are provided on the cam ring side end surface of the rear head 6. Back pressure groove 60
Communicate with the bearing accommodating chamber 31.

The bottom portion of the discharge chamber 10 and the bearing accommodating chamber 31 communicate with each other through a guide passage (first guide passage) 32. The guide passage 32 includes a passage (not shown) of the front head 5, a passage 1b of the cam ring 1 communicating with the passage, and a passage 1b.
and a passage 6b of the rear head 6 communicating with b.

The bearing accommodating chamber 31 and the suction chamber 11 communicate with each other through a guide passage (second guide passage) 33 provided in the rear head 6.

FIG. 3 is a perspective view showing the plain bearing 9.

The plain bearing 9 is formed by forming a sintered layer and a resin layer on the surface of a steel plate. An annular groove 9a and two spiral grooves 9b communicating with the annular groove 9a are provided on the inner peripheral surface of the plain bearing 9. Further, the plain bearing 9 is provided with a hole 9c for guiding the lubricating oil from the passage 6b to the annular groove 9a, and a hole 9d for feeding the lubricating oil in the bearing housing chamber 31 to the guide passage 33.

FIG. 4 (a) is a development view of the plain bearing of FIG. 3, FIG. 4 (b) is a sectional view taken along line AA of FIG. 4 (a),
FIG. 5A is a diagram for explaining the function of the plain bearing during operation, and FIG. 5B is a diagram for explaining the function of the plain bearing when the operation is stopped.

In order to manufacture the plain bearing 9, a sintered layer and a resin layer are previously formed on the surface of a rectangular steel plate, and the sintered layer and the resin layer are pressed or machined into one annular shape. Grooves 9a, two spiral grooves 9b, etc. are formed, and finally the steel plate is made cylindrical. In this way, the plain bearing 9 of FIG. 3 is completed.

Two compression spaces 12 are formed between the inner peripheral surface of the cam ring 1 and the outer peripheral surface of the rotor 2 as shown in FIG. 2 (one compression space in FIG. 1). Space 1
Only 2 is visible). Rotor 2 has multiple vane grooves 1
3 are provided, and vanes 14 are provided in these vane grooves 13.
Are slidably inserted. Compression space 12 is vane 1
A plurality of compression chambers are formed by being partitioned by 4, and the volume of each compression chamber is changed by the rotation of the rotor 2.

Further, the cam ring 1 is provided with a discharge space 1a for discharging the high pressure refrigerant gas in the compression chamber.
Only one discharge space 1a is visible in FIG. A discharge valve (not shown) that opens and closes a discharge port 16 described later is housed in the discharge space 1a.

The partition wall 1c for partitioning the discharge space 1a and the compression space 12 is provided with discharge ports 16 corresponding to the two compression spaces 12 (one discharge port 16 in FIG. 1).
Only visible). When the discharge port 16 is opened, the high-pressure refrigerant gas in the compression chamber is discharged into the discharge port 16 and the discharge space 1.
A is discharged from the discharge port 5a through the discharge passage 3a and the discharge chamber 10.

The rear end surface of the cam ring 1 is provided with a suction port (not shown) for sending low-pressure refrigerant gas from the suction chamber 11 to the compression chamber in the suction process.

Next, the operation of the vane compressor will be described.

The rotational power of the engine (not shown) is driven by the drive shaft 7.
, The rotor 2 rotates. The refrigerant gas flowing out from the outlet of the evaporator (not shown) enters the suction chamber 11 through the suction port 6a and is sucked into the compression space 12 through the suction port from the suction chamber 11. The compression space 12 is partitioned by the vanes 14 to form five compression chambers, and the volume of each compression chamber changes with the rotation of the rotor 2. Therefore, the refrigerant gas trapped between the vanes 14 is compressed and compressed. The discharged refrigerant gas flows from the discharge port 16 through the discharge valve to the discharge space 1a, and then flows from the discharge space 1a to the discharge chamber 10 through the discharge passage 3a.

The high pressure refrigerant gas flowing into the discharge chamber 10 is separated into oil, and the lubricating oil is collected at the bottom of the discharge chamber 10. The lubricating oil collected at the bottom of the discharge chamber 10 is sent into the bearing housing chamber 31 through the guide passage 32.

During operation of the compressor, there is a difference (Pk>) between the pressure Pk in the inner part of the vane groove 13 and the pressure Pb in the bearing accommodating chamber 31.
Since there is Pb), the lubricating oil tends to flow in the direction of the arrow a in FIG. 5A, but due to the effect of the viscosity of the lubricating oil due to the rotation of the drive shaft 7 due to the spiral groove 9b, the lubricating oil has a differential pressure. 5 (a) in the direction of the arrow b (high pressure side), and through the gap between the outer peripheral surface of the drive shaft 7 and the inner peripheral surface of the plain bearing 9, the back pressure groove 60 and the side block 6 It is supplied to the gap between the front end surface and the rear end surface of the rotor 2.

On the other hand, when the operation of the compressor is stopped, the pressure in the compressor gradually balances, but most of the high-pressure lubricating oil during this time is the plain bearing as shown by the arrow a in FIG. 5 (b). From the annular groove 9a and the spiral groove 9b of 9 to the low pressure side, it is sent to the suction chamber 11 through the guide passage 33.

According to the vane type compressor of this embodiment,
In the process of balancing the pressure in the compressor, the back part of the vane groove 13 is not filled with the lubricating oil through the back pressure groove 60. Therefore, when the compressor is restarted, oil compression does not occur, and a large vibration and noise are generated. Can be prevented.

Further, since a complicated on-off valve mechanism is not required to prevent oil compression, the manufacturing cost of the compressor can be reduced.

Further, the amount of lubricating oil supplied during the operation of the compressor does not become excessive.

In the first embodiment described above, the case where the annular groove 9a and the spiral groove 9b are provided on the inner peripheral surface of the plain bearing 9 has been described, but instead of this, the annular groove 9a and the spiral groove 9b are provided. It may be provided on the outer peripheral surface of the rear end of the drive shaft 7. By doing so, the same effect as that of the first embodiment can be obtained.

Further, even if the annular groove 9a and the spiral groove 9b are provided on the outer peripheral surface of the drive shaft 7, the same effect as in the first embodiment can be obtained.

[0046]

As described above, according to the vane type compressor of the present invention, most of the high pressure lubricating oil flows from the spiral groove of the first bearing to the side opposite to the rotor when the compressor is stopped, and the second guide is provided. Since the lubricating oil flows through the passage to the low pressure chamber and the lubricating oil is not sent to the inner portion of the vane groove through the back pressure groove, when the compressor is restarted, oil compression does not occur, and large vibration and noise do not occur. Further, during the operation of the compressor, the supply of lubricating oil to the rotor side does not become excessive and proper lubrication is performed.

Furthermore, since a complicated on-off valve mechanism is not required to prevent oil compression, the manufacturing cost of the compressor can be reduced.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of a vane type compressor according to one embodiment of the present invention.

FIG. 2 is a cross-sectional view of a rotor.

FIG. 3 is a diagram showing a perspective view of a plain bearing.

FIG. 4 is a diagram for explaining a plain bearing.

FIG. 5 is a diagram for explaining the function of a plain bearing.

FIG. 6 is a longitudinal sectional view of a conventional vane type compressor.

[Explanation of symbols]

 1 cam ring 2 rotor 3 front side block 5 front head 6 rear head 7 drive shaft 8 needle bearing 9 plain bearing 9a annular groove 9b spiral groove 9c, 9d hole 20 rear side member 25 front side member 30, 31 bearing accommodating chamber 32, 33 guide path 50,60 Back pressure groove

Claims (1)

[Claims] 1. A rotor rotatably housed in a cam ring, a vane groove provided on an outer peripheral surface of the rotor, a vane slidably inserted in the vane groove, and both end surfaces of the cam ring, respectively. A first and a second side member that are fixed, and a first bearing that is provided on the first side member and that rotatably supports one end of the drive shaft of the rotor
A bearing accommodating chamber and a second bearing that is provided in the second side member and accommodates a second bearing that rotatably supports the other end of the drive shaft of the rotor.
A bearing accommodating chamber and a first for guiding lubricating oil from the high pressure chamber to the first bearing accommodating chamber
A guide path and a rotor-side end surface of the first side member, which communicates with the inner part of the vane groove from the start of suction to the end of compression, and extends from the first bearing housing chamber to the inner part of the vane groove. A vane type compressor having a back pressure groove for feeding lubricating oil to the second bearing, wherein the first bearing is a plain bearing, and the second bearing guides the lubricating oil from the first bearing housing chamber to the low pressure chamber.
A guide passage is provided in the first side member, an annular groove that communicates with the first guide passage, and a lubricating oil that communicates with the annular groove and is provided to the back pressure groove side only when the drive shaft rotates. A vane type compressor, wherein a spiral groove for feeding the oil is provided on the inner peripheral surface of the plain bearing or the outer peripheral surface of one end of the drive shaft.