JPH10122170A - Vane compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the deterioration of the sliding property of a rotor due to machining errors and reduce the cost and weight. SOLUTION: A ring-like spacer made of iron or Teflon and having the outer diameter smaller than that of a rotor 2 is fitted between the rotor side end face of a rear head 6 and the rear side end face of a cam ring 1. Fixed gaps are maintained between the end face of the cam ring 1 and the rotor side end face of the rear head 6 and between the end face of the cam ring 1 and the rotor side end face of a front side block 3, the machining errors on the end face of the rotor 2 and the rotor side end face of the rear head 6 and the assembling errors of the rotor 2 and the rear head 6 are absorbed, and the abrasion on the end face of the rotor 2 can be suppressed. The gap between the end face of the rotor 2 and the rotor side end face of the rear head 6 and the gap between the end face of the rotor 2 and the rotor side end face of the front side block 3 become narrower respectively than those when no spacer 70 is used, and performance is improved.

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 in which rotor seizure hardly occurs.

[0002]

2. Description of the Related Art A conventional vane type compressor is disclosed in
There is one disclosed in Japanese Patent Application Laid-Open No. 7-151091.

This vane type compressor includes a cam ring, a rotor rotatably housed in the cam ring, a drive shaft of the rotor, a vane slidably inserted in a vane groove of the rotor, and a front side of the cam ring. A front side block is provided on the end face, and a rear side block is provided on the rear end face of the cam ring. The rotor and both side blocks are formed of an aluminum-based material.

The cam ring, the front side block and the rear side block are integrally connected in the axial direction by through bolts.

A thin plate made of an iron-based material is provided between the rear end surface of the cam ring and the rotor end surface of the rear side block, and between the front end surface of the cam ring and the rotor end surface of the front side block. ing. Therefore, since the end face of the rotor does not directly contact the end face of the side block on the rotor side, seizure of the rotor is suppressed.

[0006]

However, in the vane type compressor described above, when the processing accuracy (particularly, flatness) of the rotor end face or the rotor side end face of the side block is low, or when the precision at the time of assembly is low. (For example, the fall of the drive shaft of the rotor) has a problem that the end face of the rotor comes into strong contact with the thin plate partially, so that the slidability of the rotor is reduced and the end face of the rotor is worn.

Further, since the thin plate has a size enough to cover the entire end face of the side block on the rotor side, the amount of iron-based material used for forming the thin plate increases, the cost increases, and the weight increases. was there.

The present invention has been made in view of such circumstances, and an object of the present invention is to prevent a decrease in the slidability of a rotor due to a processing error and to reduce the cost and weight.

[0009]

According to a first aspect of the present invention, there is provided a vane-type compressor comprising: a rotor rotatably housed in a cam ring; and a plurality of vane grooves formed in the rotor. A vane slidably inserted into the plurality of vane grooves, and a side member fixed to an end surface of the cam ring, wherein at least the rotor and the side member are formed of an aluminum-based material. In the compressor, an iron or Teflon ring spacer smaller than an outer diameter of the rotor is mounted between an end surface of the cam ring and an end surface of the side member on a rotor side.

As described above, an iron-based or Teflon-based ring-shaped spacer smaller than the outer diameter of the rotor is mounted between the end face of the cam ring and the rotor-side end face of the side member. Since a certain gap is maintained between the side end surface, machining errors in the rotor end surface and the rotor side end surface of the side members, and assembly errors in the rotor and side members are absorbed, and wear on the rotor end surface is suppressed. And when not using spacers,
Since the gap between the end face of the rotor and the end face of the side member on the rotor side is narrowed, the performance is improved.

Also, since the spacer is smaller than the outer diameter of the rotor, the amount of material used for forming the spacer is reduced as compared with the conventional example.

The vane compressor according to a second aspect of the present invention is the vane compressor according to the first aspect of the present invention, wherein a back pressure groove for sending a first fluid to a back surface of the vane is provided on a rotor-side end surface of the side member. A low-pressure chamber that is provided and sends a second fluid having a lower pressure than the first fluid to a compression chamber that is formed between the vanes that are successive in the rotation direction is provided outside the back pressure groove, The spacer is located between the back pressure groove and the low pressure chamber.

Since the spacer is located between the back pressure groove and the low pressure chamber as described above, the first fluid can be prevented from escaping from the back pressure groove to the low pressure chamber, and the spacer can be provided on the back surface of the vane. Such pressure is kept high.

According to a third aspect of the present invention, there is provided the vane type compressor according to the first aspect of the present invention, wherein a back pressure groove for sending a first fluid to a back surface of the vane is provided on a rotor-side end surface of the side member. A low-pressure chamber that is provided and sends a second fluid having a lower pressure than the first fluid to a compression chamber that is formed between the vanes that are successive in the rotation direction is provided outside the back pressure groove, The spacer is located inside the back pressure groove.

In addition to the fact that the spacer is smaller than the outer diameter of the rotor, the diameter of the spacer is smaller because the spacer is located inside the back pressure groove, and the amount of material used to form the spacer is greatly increased. decrease.

A vane type compressor according to a fourth aspect of the present invention is the vane type compressor according to the first aspect of the present invention, wherein the first fluid is supplied to the rotor-side end face of the side member on the rear side to send the first fluid to the back surface of the vane. A pressure groove is provided, and the first chamber is formed in a compression chamber formed between the vanes successively in the rotation direction.
A low-pressure chamber for sending a second fluid having a pressure lower than that of the second fluid is provided outside the back pressure groove, and the spacer is located inside the back pressure groove.

During operation of the compressor, the rotor tends to move rearward due to the spring force of the electromagnetic clutch. However, the rotor is maintained substantially at the center of the cam ring in the axial direction by the action of the spacer. The gap between the rotor side end face and the rear end face of the cam ring, and the gap between the rotor side end face of the front side member and the front end face of the cam ring are kept substantially equal, and refrigerant leakage is suppressed as a whole.

[0018]

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

FIG. 1 is a longitudinal sectional view of a vane type compressor according to a first embodiment of the present invention, FIG. 2 is a view showing a front end surface of a rear head, FIG. 3 is an enlarged sectional view of the rear head, and FIG.
FIG. 4 is an arrow view along the line IV-IV in FIG. 1.

This vane type compressor has a cam ring 1,
A rotor 2 rotatably housed in the cam ring 1, a drive shaft 7 of the rotor 2, a front head 5 fixed to a front end face of the cam ring 1, and an O-ring 22 on a rear end face of the cam ring 1. The vehicle includes a fixed rear head (rear side member) 6 and a front side block (side member) 3 housed in the front head 5. The cam ring 1, the front side block 3, the front head 5, and the rear head 6 are axially connected by through bolts (not shown). The front end of the drive shaft 7 is connected to the front side block 3 via a bearing 8.
The rear end of the drive shaft 7 is rotatably supported by the rear head 6 via a bearing 9.

Parts such as the cam ring 1, the rotor 2, the front head 5 and the rear head 6 are made of an aluminum-based material.

The rear end face of the front side block 3 is fixed to the front end face of the cam ring 1 and closes the front opening of the cam ring 1. The front end of the front side block 3 is fitted to the boss 5b of the front head 5 via an O-ring 51. A discharge chamber 10 into which a high-pressure refrigerant gas discharged from a compression chamber described later flows flows is formed in the front head 5.

The rear head 6 has a refrigerant gas inlet 6a.
And a suction chamber (low-pressure chamber) 11 for accommodating low-pressure refrigerant gas introduced from the suction port 6a, and a pair of suction ports 11a for sending the refrigerant gas (second fluid) in the suction chamber 11 to the compression chamber.
And a high-pressure chamber 61 into which a high-pressure refrigerant gas is introduced from the discharge chamber 10.

A pair of back pressure grooves 60 for sending back pressure (first fluid) to the back surface of the later described vane 14 are formed on the rotor side end face of the rear head 6. High-pressure oil is introduced into the back pressure groove 60 from a high-pressure chamber 61 through a high-pressure introduction path 62. The high pressure chamber 61 of the rear head 6 communicates with a high pressure chamber (not shown) formed in the cam ring 1, and the high pressure chamber of the cam ring 1 communicates with the discharge chamber 10.

Between the rotor-side end surface of the rear head 6 and the rear-side end surface of the cam ring 1, a ring spacer 70 of iron or Teflon smaller than the outer diameter of the rotor 2 is mounted. As shown in FIG. 2, the spacer 70 is
And the back pressure groove 60 is located between the back pressure groove 60 and the suction port 11a.
1a. A stopper 71 is provided on the inner peripheral edge of the spacer 70, and the stopper 71 is engaged with one back pressure groove 60. Thus, rotation of the spacer 70 is prevented.

Between the inner peripheral surface of the cam ring 1 and the outer peripheral surface of the rotor 2, as shown in FIG.
2 are formed. The rotor 2 has a plurality of vane grooves 13.
Are provided, and a vane 14 is slidably inserted into these vane grooves 13. The compression space 12 is a vane 14
To form a plurality of compression chambers, and the volume of each compression chamber changes with the rotation of the rotor 2.

The cam ring 1 has a discharge valve chamber 1c in which a discharge valve 19 described later is stored.
The front side of the discharge valve housing chamber 1c is open to the discharge chamber 10. In FIG. 1, only one ejection space 1c is visible. Partition walls that partition the discharge space 1c and the compression space 12 include:
Discharge ports 16 corresponding to the two compression spaces 12 are provided (only one discharge port 16 is visible in FIG. 1). When the discharge port 16 is opened, the high-pressure refrigerant gas in the compression chamber flows into the discharge chamber 10 through the discharge port 16 and the discharge space 1c.

The discharge space 1c has a valve retainer 32 having a circular cross section.
And an arc-shaped discharge valve 19 mounted on the outer periphery of the valve presser 32 are accommodated. Discharge valve 19 and valve retainer 32
Are held in the discharge space 1c by bolts 33 screwed into the screw holes of the valve presser 32 in the discharge space 1c through the bolt holes from the outside of the cam ring 1.

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

The rotational power of the engine (not shown) is
, The rotor 2 rotates. The refrigerant gas flowing out of the outlet of the evaporator (not shown) enters the suction chamber 11 through the suction port 6a, and is sucked from the suction chamber 11 into the compression space 12 through the suction port 11a.

The compression space 12 is partitioned by vanes 14 to form five compression chambers. Since the volume of each compression chamber changes with the rotation of the rotor 2, the refrigerant trapped between the vanes 14 The gas is compressed, and the compressed refrigerant gas flows from the discharge port 16 through the discharge valve 19 to the discharge space 1c.

The high-pressure refrigerant gas flowing into the discharge space 1c from the discharge port 16 flows into the discharge chamber 10 and is discharged from the discharge port 5a.

According to the first embodiment, an iron-based or Teflon-based ring-shaped spacer 70 smaller than the outer diameter of the rotor 2 is mounted between the rotor-side end face of the rear head 6 and the rear-side end face of the cam ring 1. Therefore, a certain gap is maintained between the end face of the cam ring 1 and the rotor-side end face of the rear head 6, and a certain gap is maintained between the end face of the cam ring 1 and the rotor-side end face of the front side block 3. Processing errors in the end face of the rotor 2 and the rear side of the rotor 6 and assembly errors in the rotor 2 and the rear head 6 are absorbed.
Of the end face of the rotor 2 and the end face of the rear head 6 on the rotor side, the end face of the cam ring 1 and the end face of the rotor of the front side block 3 as compared with when the spacer 70 is not used. Are narrowed, so that the performance is improved.

Since the spacer 70 is smaller than the outer diameter of the rotor 2, the cost can be reduced and the weight can be reduced.

Further, since the spacer 70 surrounds the back pressure groove 60 and separates the back pressure groove 60 from the suction port 11a, it is possible to prevent the refrigerant from escaping from the back pressure groove 60 to the suction port 11a. The back pressure can be stably supplied to the back surface of the base 14.

FIG. 5 is a view showing a front end surface of a rear head of a vane type compressor according to a second embodiment of the present invention.
FIG. 6 is an enlarged sectional view of the rear head.

Portions common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted. In the first embodiment described above, the case where the spacer 70 is mounted outside the back pressure groove 60 has been described. However, in the second embodiment, as shown in FIG. Attached inside.

A stopper 171 is provided on the outer peripheral edge of the spacer 170.
60 is engaged. Thus, rotation of the spacer 170 is prevented.

The spacer 170 projects slightly forward from the rotor-side end face of the rear head 6, and the rotor-side end face of the rear head 6 does not contact the rear-side end face of the rotor 2.

According to the second embodiment, the back pressure groove 16
Except that the refrigerant cannot be prevented from escaping from 0 to the suction port 11a, the same effect as in the first embodiment can be obtained.

Further, since the spacer 70 has a centering function of holding the rotor 2 at the center position, the amount of refrigerant leakage is reduced and the performance is improved. That is, during operation of the compressor, the rotor 2 moves rearward due to the spring force of the electromagnetic clutch. However, since the spacer 70 is provided, the gap between the rotor-side end face of the rear head 6 and the rear-side end face of the rotor 2 and the front head 5 The gap between the rotor-side end face and the front-side end face of the rotor 2 is kept substantially equal, and the leakage of the refrigerant is suppressed as a whole.

FIG. 7 is a view showing a front end surface of a rear head of a vane type compressor according to a modification of the second embodiment of the present invention, and FIG. 8 is an enlarged sectional view of the rear head.

Parts common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted.

In this modification, a bearing 9 made of an iron-based material and a rear head 2 made of an aluminum-based material are used.
A space 206a surrounding the bearing 9 is formed in the rear head 206 so that the bearing 9 is not loosened due to a difference in thermal expansion from the space 06, and an iron bush 231 is cast into the space 206a. A part of the iron bush 231 (abutment portion 27)
0) slightly protrudes from the rotor-side end face of the rear head 6 toward the rotor 2. The butting portion 270 is annular as shown in FIG. 7, and as in the second embodiment, the butting portion 270 is located inside the back pressure groove 260.

According to this modification, the same effects as those of the second embodiment can be obtained, and the loosening of the bearing 9 can be prevented.

In each of the above embodiments, the case where the spacer 170 is mounted only on the rear side has been described. However, the spacer may be mounted on the front side.

In each of the above embodiments, the case where the spacer is provided so as not to rotate by providing the stopper is described. However, the spacer may be rotated together with the rotor without providing the stopper.

[0048]

As described above, according to the vane-type compressor of the first aspect of the present invention, machining errors in the end face of the rotor and the end face of the side member on the rotor side and assembly errors in the rotor and the side member are absorbed. Thus, the wear of the end face of the rotor can be suppressed, and the gap between the end face of the rotor and the end face on the rotor side of the side member is narrower than when the spacer is not used, so that the performance is improved.

Further, since the spacer is smaller than the outer diameter of the rotor, the amount of material used for forming the spacer is reduced, the cost can be reduced, and the weight can be reduced as compared with the conventional example.

According to the vane type compressor of the second aspect of the present invention, the first fluid can be prevented from escaping from the back pressure groove to the low pressure side, and the pressure applied to the back surface of the vane can be kept high. , Vane chattering can be prevented.

According to the vane type compressor of the third aspect of the present invention, the spacer is smaller than the outer diameter of the rotor, and the spacer is located inside the back pressure groove, so that the diameter of the spacer is smaller. As a result, the material used for forming the spacer is significantly reduced, and the spacer can be further reduced in size and weight, and the cost can be further reduced.

According to the vane type compressor of the fourth aspect of the present invention, the gap between the rotor side end surface of the rear side member and the rear end surface of the cam ring, the rotor side end surface of the front side member and the front side of the cam ring. The gap with the side end face
It is kept substantially equal, and the leakage of the refrigerant is suppressed as a whole, so that the performance is improved.

[Brief description of the drawings]

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

FIG. 2 is a diagram showing a front end surface of a rear head.

FIG. 3 is an enlarged sectional view of a rear head.

FIG. 4 is an arrow view along the line IV-IV in FIG. 1;

FIG. 5 is a diagram showing a front end surface of a rear head of a vane type compressor according to a second embodiment of the present invention.

FIG. 6 is an enlarged sectional view of a rear head.

FIG. 7 is a view showing a front end surface of a rear head of a vane type compressor according to a modification of the second embodiment of the present invention.

FIG. 8 is an enlarged sectional view of a rear head.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cam ring 2 Rotor 3 Front side block 5 Front head 6 Rear head 13 Vane groove 14 Vane 70,170 Spacer 60,160,260 Back pressure groove

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Ryuichiro Kai 39, Higashihara, Chiyo, Odai-gun, Osato-gun, Saitama

Claims (4)

[Claims] A rotor rotatably housed in a cam ring; a plurality of vane grooves formed in the rotor; a vane slidably inserted into the plurality of vane grooves; and an end face of the cam ring. A vane type compressor having at least the rotor and the side member formed of an aluminum-based material, wherein the rotor is disposed between an end surface of the cam ring and a rotor-side end surface of the side member. A vane-type compressor provided with an iron-based or Teflon-based ring-shaped spacer smaller than the outer diameter of the vane-type compressor. 2. A back pressure groove for feeding a first fluid to a back surface of the vane is provided on an end face of the side member on a rotor side, and a compression chamber formed between the vanes which are successive in the rotation direction is provided. A low-pressure chamber for sending a second fluid having a lower pressure than the first fluid is provided outside the back pressure groove, and the spacer is located between the back pressure groove and the low pressure chamber. The vane type compressor according to claim 1, wherein 3. A back pressure groove for sending a first fluid to a back surface of the vane is provided on an end surface of the side member on a rotor side, and a compression chamber formed between the vanes which are arranged in front and rear in a rotation direction is provided. 2. A low-pressure chamber for sending a second fluid having a lower pressure than the first fluid is provided outside the back pressure groove, and the spacer is located inside the back pressure groove. A vane-type compressor as described. 4. A back pressure groove for sending a first fluid to a back surface of the vane is provided on a rotor side end surface of the side member on a rear side, and is formed between the vanes which are successive in a rotational direction. A low-pressure chamber that sends a second fluid having a lower pressure than the first fluid to the compression chamber is provided outside the back pressure groove;
The vane type compressor according to claim 1, wherein the spacer is located inside the back pressure groove.