JPH09250480A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate processing of the holes and pores of the rotor drive shaft and reduce the cost. SOLUTION: A front side block 3 is provided with a guide route 30 for guiding the coolant gas in a compression chamber at the initial stage of a compression process, therefore, a great differential pressure is generated between a shaft seal chamber 60 and the compression chamber at the initial stage of the compression process, the coolant gas is certainly introduced into the shaft seal chamber 60, and the inside of the shaft seal chamber is sufficiently lubricated. The coolant gas to be introduced into the shaft seal chamber 60 through the guide route 30 is low-pressure coolant gas at the initial stage of the compression process, therefore, the volume efficiency is hardly lowered. Since the guide route 30 is a short linear simple pore, it can be processed for a short time and no burring occurs.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane compressor, and more particularly to a vane compressor used in an air conditioner for automobiles.

[0002]

2. Description of the Related Art FIG. 4 is a vertical sectional view of a conventional vane compressor, and FIG. 5 is a sectional view taken along the line VV of FIG.

This vane type compressor has a cam ring 101.
A rotor 102 rotatably housed in the cam ring 101, a drive shaft 107 of the rotor 102, a front side block 103 fixed to the front end surface of the cam ring 101, and a rear end surface of the cam ring 101. A rear side block 104, a front head 105 fixed to the front side end surface of the front side block 103, and a rear head 106 fixed to the rear side end surface of the rear side block 104 are provided.

The front end of the drive shaft 107 of the rotor 102 is rotatably supported by the front side block 103 via a bearing 108.

A shaft seal 150 is mounted on the front end of the drive shaft 107, and a shaft seal chamber 160 is formed between the shaft seal 150 and the bearing 108.

The rear end of the drive shaft 107 of the rotor 102 is rotatably supported by the rear side block 104 via a bearing 109.

The drive shaft 107 of the rotor 102 has a hole 107a in the center line direction and a hole 10 in the direction orthogonal to the center line direction.
7b are provided. The hole 107a is the rotor 102
The drive shaft 107 extends from the rear end surface to the front end portion and communicates with the intermediate portion of the hole 107b. Both ends of the hole 107b are desired in the shaft seal chamber 160.

The inner peripheral surface of the cam ring 101 and the rotor 102
Two upper and lower compression spaces 112 are formed between the outer peripheral surface and the outer peripheral surface (only one compression space 112 is visible in FIG. 4). The rotor 102 is provided with a plurality of vane grooves 113, and the vanes 114 are slidably inserted in the vane grooves 113. The compression space 112 is partitioned by a vane 114 and divided into a plurality of compression chambers, and the volume of each compression chamber changes as the rotor 102 rotates.

In the front side block 103, the shaft seal chamber 1 is provided in the compression chamber of the suction stroke among the plurality of compression chambers.
A front head 105 and a front side block 103 are provided with a guide passage 131 for guiding the low pressure refrigerant gas of 60.
The discharge chamber 110 is formed by the above and stores the discharge gas discharged from the compression chamber.

Rear head 106 and rear side block 1
The suction chamber 111 is formed by 04 and accommodates the suction gas sent to the compression chamber.

The refrigerant gas flowing into the suction chamber 111 from the suction port 106a of the rear head 106 is sent to the compression chamber through the suction port 104a provided in the rear side block 104. A part of the refrigerant gas flowing into the suction chamber 111 advances to the front side in the hole 107a of the drive shaft 107 of the rotor 102, and from the hole 107b to the shaft seal chamber 160.
It flows in and is sent to the compression chamber in the suction stroke through the guide passage 131 of the front side block 103.

[0012]

As described above, in the conventional vane type compressor, the refrigerant gas in the rear suction chamber 111 is supplied to the holes 107a and 107 of the drive shaft 107 of the rotor 102.
A structure is adopted that leads to the shaft seal chamber 160 on the front side through b. As a result, the front shaft seal chamber 160 is lubricated.

However, since it takes time to process the holes 107a and 107b of the drive shaft 107, there is a problem that the manufacturing cost increases.

Further, since the hole 107a and the hole 107b are orthogonal to each other, a so-called burr is generated in the orthogonal portion when the hole 107a and the hole 107b are processed, and a work for removing this burr is required, which also increases the cost. There was a problem.

The present invention has been made in view of the above circumstances, and a problem thereof is to provide a vane type compressor which does not require machining of a hole and a hole of a drive shaft of a rotor and can reduce the cost. It is to be.

[0016]

In order to solve the above problems, a vane type compressor according to a first aspect of the present invention is provided with a rotor rotatably housed in a cam ring and a plurality of rotors provided on an outer peripheral surface of the rotor. Fixed to one end surface of the cam ring and a plurality of vanes slidably inserted into the plurality of vane grooves, so that one end of the drive shaft of the rotor can rotate via a first bearing. A first side member that supports the second side member that is fixed to the other end surface of the cam ring and that rotatably supports the other end portion of the drive shaft of the rotor via a second bearing; and the first bearing. A shaft seal chamber formed between any one of the second bearings and a shaft seal mounted on the outer peripheral surface of the drive shaft,
Low pressure operation of the shaft seal chamber in the compression chamber surrounded by the cam ring, the rotor, the vanes, the first and second side members, and the compression chamber in the intake stroke of the compression chambers. In a vane compressor in which a first guide path for guiding a fluid is provided in either one of the first and second side members, a compression at an initial stage of a compression stroke among the plurality of compression chambers is performed. A second guide passage for guiding the low-pressure working fluid in the chamber to the shaft seal chamber is provided in the one side member.

As described above, the second guide passage for guiding the low pressure working fluid in the compression chamber in the early stage of the compression stroke among the plurality of compression chambers to the shaft seal chamber is provided in the side member provided with the first guide passage. Since it is provided, a large pressure difference is generated between the shaft seal chamber and the compression chamber in the initial stage of the compression stroke, the low-pressure working fluid is reliably introduced into the shaft seal chamber, and the shaft seal chamber is sufficiently lubricated. Further, since the low-pressure working fluid introduced into the shaft seal chamber through the second guide passage is the low-pressure working fluid in the early stage of the compression stroke, the volumetric efficiency is hardly reduced.

Since the second guide path may be a short straight straight hole, the second guide path can be processed in a short time and no burr is generated.

A vane type compressor according to a second aspect of the present invention is
In the vane type compressor according to the first aspect of the present invention, the initial stage of the compression stroke is an arbitrary time point between the time point of starting compression and the time point of rotating by approximately 30 degrees.

Since the low-pressure working fluid introduced into the shaft seal chamber through the second guide passage is the low-pressure working fluid at the beginning of the compression stroke, that is, at any time between the start of compression and the point of rotation of approximately 30 degrees, Volume efficiency is hardly reduced.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION 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, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is a compression closing angle, volume efficiency and discharge temperature. It is a curve figure which shows the relationship of. Thick line arrows in FIGS. 1 and 2 indicate the flow of the refrigerant.

This vane type compressor includes a cam ring 1 and
A front side member (first side member) 25 and a rear side member (second 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 includes a bearing (first bearing) 8 and a bearing (second bearing).
It is rotatably supported by a bearing 9. Cam ring 1, front side member 25 and rear side member 20
Are integrally connected in the axial direction with through bolts 40.

The front side member 25 comprises a front side block 3 fixed to the front end surface of the cam ring 1 via an O-ring 21, and a front head 5 fixed to the front end surface of the front side block 3. Has been done.

A discharge port 5a for high-pressure refrigerant gas (working fluid) is formed in the front head 5, and the discharge port 5a communicates with a discharge chamber 10 formed by the front head 5 and the front side block 3. The front side block 3 is provided with a passage 3a that communicates a discharge space 1a described later with a discharge chamber 10.

The rear side member 20 is a cam ring 1
The rear side block 4 is fixed to the rear end surface of the rear side block via an O-ring 22, and the rear head 6 is fixed to the rear side end surface of the rear side block 3. The rear side block 4 is provided with a suction port 4a for sucking low-pressure refrigerant gas from the suction chamber 11 in the suction stroke to the compression chamber.

A suction port 6a for low-pressure refrigerant gas is formed in the rear head 6, and the suction port 6a communicates with a suction chamber 11 formed by the rear head 6 and the rear side block 4.

Between the inner peripheral surface of the cam ring 1 and the outer peripheral surface of the rotor 2, two upper and lower compression spaces 12 are defined 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.
Is slidably inserted. Compression space 12 is vane 1
A plurality of compression chambers are formed by being partitioned by 4. That is, the compression chambers are a plurality of chambers surrounded by the inner peripheral surface of the cam ring 1, the outer peripheral surface of the rotor 2, the five vanes 14, the rear side end surface of the front side block 3, and the front side end surface of the rear side block 4. The volume of each compression chamber changes with the rotation of the rotor 2.

The outer peripheral wall of the cam ring 1 is provided with two discharge ports 16 corresponding to the two compression spaces 12 (only one discharge port 16 is visible in FIG. 1). Further, on the outer peripheral wall of the cam ring 1, the valve stopper 1
A discharge valve cover 17 having 7a is fixed by a bolt 18. The discharge space 1a is formed by the outer peripheral wall of the cam ring 1 and the valve stop portion 17a. The high-pressure refrigerant gas discharged from the compression chamber is discharged into the discharge space 1a through the discharge port 16. A discharge valve 19 that opens and closes the discharge port 16 is housed in the discharge space 1a, and the discharge valve 19 includes a discharge valve cover 17
It is fixed to the inner wall surface of the with bolts 20. Discharge port 1
When 6 is opened, the high pressure refrigerant gas in the compression chamber is discharged from the discharge port 5a through the discharge port 16, the discharge space 1a, the passage 3a and the discharge chamber 10.

A shaft seal chamber 60 is provided between the bearing 8 supporting the front end of the drive shaft 7 and the shaft seal 50 mounted on the outer peripheral surface of the front end of the drive shaft 7.
Are formed.

The front side block 3 is provided with a linear guide path (first guide path) 31 for connecting the compression chamber of the intake stroke of the plurality of compression chambers with the shaft seal chamber 60. A linear guide path (second guide path) 30 that connects the compression chamber in the initial stage of the compression stroke and the shaft seal chamber 60 among the plurality of compression chambers is provided.

As shown in FIG. 2, the opening 30a on the rear side of the guide path 30 extends approximately 30 clockwise from the compression start position A.
It is located at α until rotated to position B, and in this first embodiment it is at position C of approximately 15 °, which is desired in the compression chamber. On the other hand, the opening 31a on the rear side of the guide path 31 is desired in the compression chamber in the suction stroke. The front openings of both guide passages 30 and 31 are desired in the shaft seal chamber 60.

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

The rotational power of the engine (not shown) is driven by the drive shaft 7.
When transmitted to the rotor 2, 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 each compression chamber from the suction chamber 11 through the suction port 4a. Since the volume of each compression chamber changes with the rotation of the rotor 2, the refrigerant gas trapped between the vanes 14 is compressed, and the compressed refrigerant gas passes from the discharge port 16 through the discharge valve 19 to the discharge space 1a. It flows out, flows into the discharge chamber 10 through the passage 3a, and is discharged from the discharge port 5a.

Further, as described above, the refrigerant gas flowing into the suction chamber 11 from the suction port 6a of the rear head 6 is sent to the compression chamber through the suction port 4a of the rear side block 6, but the refrigerant gas sent to the compression chamber is A part of the shaft seal chamber 60 passes through the guide passage 30 at the beginning of the compression stroke.
Pour into. Since a large pressure difference is generated between the shaft seal chamber 60 and the compression chamber at the beginning of the compression stroke, the refrigerant gas is reliably introduced into the shaft seal chamber 60, and the inside of the shaft seal chamber 60 is protected by the lubricating oil in the refrigerant. Well lubricated. Since the refrigerant gas introduced into the shaft seal chamber 60 through the guide passage 30 is the refrigerant gas at the initial stage of the compression stroke, for example, at the time when it is rotated about 15 degrees from the compression start time, the volumetric efficiency is hardly reduced. The initial stage of the compression stroke refers to an arbitrary time point α between the time point when the compression is started and the time point when it is rotated by about 30 degrees, and as shown in FIG. The temperature of the refrigerant gas introduced into the shaft seal chamber 60 also depends on the compression closing angle (the rotation angle of the vane 14 from the compression start position A).
Is almost the same as when it is 0 degrees.

The refrigerant gas introduced into the shaft seal chamber 60 is sent to the compression chamber in the suction stroke through the guide passage 31.

According to the first embodiment, since the guide passage 30 for guiding the refrigerant gas in the compression chamber at the initial stage of the compression stroke to the shaft seal chamber 60 is provided in the front side block 3, the shaft seal chamber 60 and A large pressure difference is generated between the compression chamber and the compression chamber at the beginning of the compression stroke, and the shaft seal chamber 60
Refrigerant gas is reliably introduced into the shaft seal chamber 60
The inside is well lubricated. Further, since the refrigerant gas introduced into the shaft seal chamber 60 through the guide passage 30 is a low-pressure refrigerant gas in the initial stage of the compression stroke (in this embodiment, at the time point C when it rotates about 15 degrees from the compression start point), the volumetric efficiency is almost zero. Does not fall.

Further, since the guide passage 30 is a simple straight hole having a short length, it can be processed in a short time and burrs do not occur, so that the cost can be reduced.

In the above-described embodiment, the shaft seal chamber 60 is guided to the shaft seal chamber 60 through the guide passage 30 from the time when the compression is started to about 1
The case where the refrigerant gas is fed at the time of rotating 5 degrees has been described, but the present invention is not limited to this case, and any time from the start of compression in the compression stroke to the time of rotating about 30 degrees can be used. Point of time (eg 5 degrees, 10
Refrigerant gas of 20 degrees or the like) may be fed.

Further, in the above-described embodiment, the case where one guide passage 30 is provided in the front side block 3 has been described, but a plurality of guide passages 30 may be provided.

Further, in the above-described embodiment, the case where the suction chamber 11 is located on the rear side and the shaft seal chamber 60 is located on the front side has been described, but the opposite case, that is, the suction chamber 11 is located on the front side and the shaft seal is located. When the chambers 60 are located on the rear side, the guide passage may be provided on the rear side block.

[0042]

As described above, according to the vane type compressor of the present invention, a large differential pressure is generated between the shaft seal chamber and the compression chamber in the early stage of the compression stroke, and the low pressure working fluid is generated in the shaft seal chamber. It is reliably introduced and the shaft seal chamber is sufficiently lubricated.

Further, since the second guide path may be a short straight straight hole, it can be processed in a short time and burrs do not occur, so that the cost can be reduced.

According to the vane type compressor of the second aspect of the present invention, the low pressure working fluid introduced into the shaft seal chamber through the second guide passage is at the beginning of the compression stroke, that is, at the time when the low pressure working fluid rotates by about 30 degrees from the compression start time. Since it is the low-pressure working fluid at any point between and, the shaft seal chamber can be lubricated while surely preventing a decrease in volume efficiency and an increase in discharge temperature.

[Brief description of the drawings]

FIG. 1 is a vertical cross-sectional view of a vane compressor according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a curve diagram showing the relationship between the compression closing angle and the volumetric efficiency and discharge temperature.

FIG. 4 is a vertical cross-sectional view of a conventional vane compressor.

5 is a cross-sectional view taken along the line VV of FIG.

[Explanation of symbols]

 1 Cam Ring 2 Rotor 3 Front Side Block 4 Rear Side Block 5 Front Head 6 Rear Head 7 Drive Shaft 8, 9 Bearing 20 Rear Side Member 25 Front Side Member 30, 31 Guideway 60 Shaft Seal Chamber

Claims (2)

[Claims] 1. A rotor rotatably housed in a cam ring, a plurality of vane grooves provided on an outer peripheral surface of the rotor, a plurality of vanes slidably inserted in the plurality of vane grooves, A first member fixed to one end surface of the cam ring and rotatably supporting one end portion of the drive shaft of the rotor via a first bearing.
Second side member fixed to the other end surface of the cam ring and rotatably supporting the other end portion of the drive shaft of the rotor via a second bearing.
A side seal member, a shaft seal chamber formed between one of the first bearing and the second bearing and a shaft seal mounted on the outer peripheral surface of the drive shaft, the cam ring, the rotor A plurality of compression chambers surrounded by the plurality of vanes, the first and second side members, and a low pressure working fluid of the shaft seal chamber being guided to a compression chamber in a suction stroke of the plurality of compression chambers. The guideway of 1
In the vane compressor provided on any one of the first and second side members, the low-pressure working fluid in the compression chamber at the beginning of the compression stroke of the plurality of compression chambers is supplied to the shaft seal chamber. A vane type compressor characterized in that a second guide path for guiding is provided in the one side member. 2. The vane type compressor according to claim 1, wherein the initial stage of the compression stroke is an arbitrary time point between the time point when the compression is started and the time point when the rotation is performed by about 30 degrees.