JP2964193B2 - Vane type compressor - Google Patents

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 used for compressing a medium to be compressed such as a refrigerant.

[0002]

2. Description of the Related Art As a conventional vane-type compressor, for example, a compressor disclosed in Japanese Patent Application Laid-Open No. 170787/1990 is provided with a rotor having vanes extending and retracting in a radial direction in a cylinder closed at both ends by side blocks. The vane slides on the inner surface of the cylinder due to the centrifugal force due to the rotation of the rotor and the hydraulic pressure received from the back pressure chamber at the lower portion of the vane groove, and a compression chamber is formed in a space surrounded by the vane, the rotor, and the side block. ing. In the back pressure chamber, high-pressure oil is guided through an oil guide passage provided in the front side block and a slight clearance between the rotor and the front side block, and the direction in which the vanes always project. Is pressed.

[0003]

However, the suction hole for sucking the medium to be compressed is formed in the rear side block, and a part of the high-pressure lubricating oil in the back pressure chamber is a vane and a vane groove. Through the clearance between the rotor and the rear side block. For this reason, the pressure in the back pressure chamber becomes slightly lower on the suction hole side, and the suction hole side is delayed when the vane projects from the vane groove, so that the corner of the vane on the suction hole side protrudes toward the suction hole. In some cases, this corner may come into contact with the end of the suction hole and be damaged.

In order to avoid this, it is conceivable to chamfer the vanes and the suction holes, but when the discharge pressure is high, such as when compressing a liquid refrigerant, the effect is not sufficient.

Accordingly, an object of the present invention is to provide a vane-type compressor which can prevent breakage caused by inclination of the vane when projecting and can cope with a high discharge pressure.

[0006]

SUMMARY OF THE INVENTION The gist of the present invention resides in that a rotor that rotates with the rotation of a shaft and a cylinder inner surface slide in a cylinder closed on both sides by side blocks. And a vane forming a compression chamber.The vane is fitted in a vane groove formed in the rotor so as to be able to protrude and retract, and a back pressure chamber for pressing the vane is formed in the vane groove. In the vane type compressor, an oil guide passage for guiding high-pressure lubricating oil from the suction hole side of the rotor for sucking the medium to be compressed to the back pressure chamber is formed, and in a state where the vane is fully immersed in the back pressure chamber. There is provided a partition section for partitioning the back pressure chamber in the longitudinal direction.

[0007]

Therefore, high-pressure lubricating oil is introduced from the suction hole side to the back pressure chamber, so that the bias of the pressure distribution in the back pressure chamber is reduced even near the suction hole in the back pressure chamber, and at the same time, the vane In the maximum immersion state, the partition prevents the pressure on the side opposite to the suction port from moving to the suction port side, keeps the overall back pressure uniform, and does not tilt the vane when the vane jumps out of the vane groove. Can be pushed up evenly,
Therefore, the above object can be achieved.

[0008]

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

As shown in FIGS. 1 and 2, a vane type compressor 1 according to an embodiment of the present invention closes a cylinder 2 having a substantially elliptical inner peripheral surface and both ends of the cylinder 2. It has a front side block 3 and a rear side block 4. A perfect circular rotor 5 is provided in the cylinder 2.
Are arranged with a small gap in the short diameter portion in the cylinder 2, and the rotor 5 divides the two spaces 6 a and 6 b in the cylinder 2 into symmetrical positions. This row
A vane 7 is slidably provided outwardly in a vane groove 8 formed in a substantially radial direction of the rotor 5, and a front side block 3, a rear side block 4, a rotor 5,
A compression chamber 9 is formed by the vanes 7, 7 adjacent to each other.

The shaft 10 is fitted along the center line of the rotor 5 and is rotatably supported by radial bearings 11 and 12 provided on the front side block 3 and the rear side block 4, respectively. I have. The shaft 10 has a front head 1 described below.
7, a shaft seal 13 is provided to prevent leakage of the refrigerant. A communication hole 15 is formed in the shaft 10 along the center axis thereof. A low-pressure refrigerant is divided from the rear side by the communication hole 15 from the rear side into the shaft seal and the bearing chamber. 16.

The front head 17 is fixed to the front side block 3, and a high-pressure chamber 18 is formed between the front head 17 and the high-pressure chamber 18. The high-pressure chamber 18 communicates with a discharge port 19. The high-pressure chamber 18 has an oil reservoir 18a formed at a lower portion thereof, and stores high-pressure lubricating oil.

The first passage 21 communicates the oil sump chamber 18a with the lubricating groove 24 formed in a rectangular shape on the side surface of the rotor and the sliding surface of the rotor 5 of the front side block 3. A first orifice 22 is fitted into the first passage 21, and high-pressure lubricating oil in the oil sump chamber 18 a is supplied to the rotor 5 and the front side block 3 through a throttle hole 25.
Is supplied directly to the sliding surface through the lubrication groove 24. Further, the high-pressure lubricating oil is also supplied to an arc groove 29 formed around the shaft via a clearance between the rotor 5 and the front side block 3,
It is sent to the back pressure chamber 38 formed in the rotor 5 through the clearance and the arc groove 29.

A second passage 23 is formed in the front side block 3, one of which is open to the shaft seal bearing chamber 16 and the other is open to a position corresponding to the suction hole 37a, and the compression chamber 9 expands. The suction pressure is applied to the refrigerant in the shaft seal bearing chamber 16 by the negative pressure generated in the process, and the flow of the refrigerant can be generated.

The rear head 26 is fixedly mounted on the rear side block 4 and forms a low pressure chamber 27 with the rear side block 4. The low pressure chamber 27 communicates with a suction port 28. The low-pressure chamber 27 communicates with suction holes 37a and 37b described below and the hole 31, and the hole 31 communicates with the communication hole 15 formed in the shaft 10. Below the rear head 26 and the rear side block 4, the high-pressure chamber 1
An oil sump chamber 18b communicating with the oil sump chamber 18a of No. 8 and a communication hole 30 formed in the cylinder 2 is provided to store high-pressure lubricating oil.

A third passage 32 is formed in the rear side block 4 and has an orifice 33 therein. One is in the oil sump chamber 18b and the other is in the radial bearing 1.
2 is connected to a bearing chamber 36 defined by a seal ring 34 disposed on one side and a thrust bearing 47 for a control plate described below.

The suction holes 37a and 37b are opened on the rotor side surface of the rear side block 4, and are formed by cutouts 43a and 43b formed on a control plate 42 of a variable capacity mechanism 41 which rotates one surface thereof. The compression start position is changed by rotating the control plate 42 in the circumferential direction, and the compression amount is changed.

As shown in FIGS. 3 to 5, the variable displacement mechanism 41 has a control plate 42 rotatably fitted in a variable displacement mechanism chamber 44 formed in the rear side block 4. The control plate 42 has notches 43a and 43b formed at symmetrical positions on the outer periphery thereof as described above, and a hole 45 is formed at the center thereof, and the shaft 10 penetrates the hole 45.

The thrust direction of the control plate 42 is rotatably supported by the rear side block 4 by a thrust bearing 47, and from the bearing chamber 36 through a clearance between the thrust bearing, the bush and the rear side block. The high-pressure lubricating oil sent is supplied to the back pressure chamber 38 through the throttle hole 39. Thus, the third passage 32, the bearing chamber 36, the thrust bearing, the bush, the clearance between the rear side blocks, and the throttle hole 39 form the oil guide passage 35 that guides the high-pressure oil to the back pressure chamber 38. . The amount of high-pressure lubricating oil supplied from the suction side depends on the diameter of the orifice,
By changing the resistance of the passage, it is set more than the front side.

The control plate 42 is constantly pressed in a predetermined direction by a coil spring 48 (shown in FIG. 1), and the control plate 42 has a tongue-shaped pressure receiving portion 4.
9a and 49b are protruded. These pressure receiving parts 49a, 4
9b is a sliding groove 50a formed in the rear side block 4,
50b, and one of the sliding grooves 50a, 50b defined by the pressure receiving portions 49a, 49b is inserted into one of the pressure chambers 51.
a, 51b.

The pressure chambers 51a and 51b communicate with each other through a through hole (not shown), and one of the pressure chambers 51a and 51b is connected to the other.
b, the pressure on the high pressure side is supplied through a through hole 53, and the other pressure chamber 51a is connected to the low pressure side through a through hole 54, and a control valve 55 is provided in the through hole 54. The control valve 55 has a bellows that operates in accordance with the pressure of the gas in the low-pressure chamber 27, a valve body that is moved by the bellows, and a valve seat. Pressure chamber 51a,
The pressure with respect to 51b is adjusted.

The discharge holes 59a and 59b are provided in the cylinder 2
Are provided on the reduced end side in the rotational direction of the spaces 6a, 6b.
60b are provided.

As shown in FIGS. 6 and 7, the back pressure chamber 38 is formed in a lower portion of the vane groove 8 for slidably fitting a vane formed in the rotor 5, and has a cross section. A partition 61 is formed in a circular shape, and about one third from the rear side block, which partitions the back pressure chamber 38 in the longitudinal direction when the vane is in the maximum immersion state. In this embodiment, the length of the vane groove 8 and the length of the vane 7 substantially coincide with each other, so that the partition 61 rises from the inner surface of the back pressure chamber 38 and matches the cross-sectional shape of the base peripheral edge of the vane 7. In particular, the arc-shaped partitioning pieces 62a, 62 shown in FIG.
2b and 62c.

The partition portion 61 is formed integrally with the rotor 5, and it is preferable to form the partition portion 61 by casting, unlike conventional extrusion.

In the above construction, when the rotor 5 rotates, the tip of the vane 7 slides on the inner peripheral surface of the cylinder 2 to change the volume of the compression chamber 9 defined by the vane 7 to a high pressure. The discharged refrigerant is discharged to the high-pressure chamber 18 through the discharge holes 59a and 59b. In this case, the amount of the refrigerant introduced from the low-pressure chamber 27 is changed by changing the compression start position in the variable capacity mechanism chamber 44, so that the supply amount to the compression chamber 9 is controlled and the discharge amount is changed. .

For example, when the pressure in the low-pressure chamber 27 is relatively high, such as during low-speed operation, the opening area through which the refrigerant passes is reduced by the control valve 55, so that the amount of escape to the low-pressure side is reduced, and the pressure chamber is reduced. The pressure at 51a, 51b rises and the control plate 42 rotates counterclockwise in FIG. 4 to move the compression start position counterclockwise. As a result, the time for trapping gas in the compression chamber 9 is advanced, so that a large capacity operation is performed.

Conversely, when the pressure in the low-pressure chamber 27 decreases, as in the case of high-speed operation, the opening area of the control valve 55 increases, so that the relief amount on the low-pressure side increases, and the pressure chamber 51a,
The pressure of 51b is reduced. Therefore, control plate 4
2 rotates clockwise to move the compression start position clockwise, delaying the time of trapping gas in the compression chamber, and reducing the volume of gas compressed in the compression chamber. Therefore, it is operated with a small capacity.

Next, the supply of the lubricating oil will be described.
First, a radial bearing 11 supporting a shaft 10,
For lubrication of the shaft 12 and the shaft seal 13, low-pressure refrigerant (including lubricating oil) flows from the low-pressure chamber 27 to the hole 29 to lubricate the radial bearing on the rear side from between the shaft 10 and the rear side block 4. The refrigerant reaches the shaft seal bearing chamber 16 through the communication hole 15 of the shaft 10. Then, the shaft seal 13 and the radial bearing 11 on the front side are lubricated. The shaft seal bearing chamber 16 has a suction function in the second passage 23,
A low-pressure, low-temperature refrigerant can always flow.

The lubrication between the front side block 3 and the rotor 5 is performed by high-pressure lubricating oil flowing through the first passage 21, and the lubrication between the rear side block 4 and the rotor 5 and the variable displacement mechanism 41. For lubrication, the lubricating oil supply passage 35, the bush 46 near the thrust bearing 47 and the shaft 1
This is carried out by using a high-pressure lubricating oil that is sent during the interval between 0 and the control plate 42 and through the throttle hole 39.

Next, the supply of high-pressure lubricating oil to the back pressure chamber 38 will be described. On the front side, high-pressure oil is supplied through the clearance between the front side block 3 and the rotor 5 and the circular arc groove 29. On the rear side, high-pressure lubricating oil is supplied via a throttle hole 39 in addition to the clearance between the rear side block 4 and the rotor 5, and positive high pressure oil is supplied from the rear side. By supplying the lubricating oil, the hydraulic pressure on the rear side of the back pressure chamber 38 is adjusted to be slightly higher.

The back pressure chamber 38 is partitioned by a partition 61 in the longitudinal direction when the vane is in the maximum immersion state.
8 is blocked from moving between the high-pressure lubricating oil supplied to the suction hole side (rear side) and the non-suction hole side (front side) of the back pressure chamber 38, the suction holes 37a and 37b are moved to the suction hole side of the back pressure chamber 38. Although the leaked high-pressure lubricating oil increases, when the vane 7 jumps out of the vane groove 8, the bias of the back pressure chamber pressure is eliminated, and the vane 7 is pushed up with a uniform pressing force without tilting.

The refrigerant and the lubricating oil used for lubrication are discharged from the discharge holes together with the refrigerant and collected in the high-pressure chamber 18.
Some flows to the cooling cycle.

[0032]

As described above, according to the present invention,
The high-pressure lubricating oil is guided from the suction hole side to the back pressure chamber, and the back pressure chamber is partitioned by a partition in the longitudinal direction. Even if the high-pressure lubricating oil leaks into the suction hole, the pressure in the back pressure chamber is reduced. And the vane can be pushed up uniformly, thereby preventing damage caused by the inclination of the vane. Therefore, it is possible to cope with a high discharge pressure without chamfering the vanes and the suction holes.

[Brief description of the drawings]

FIG. 1 is a sectional view taken along the line II in FIG. 2 showing an embodiment of a vane type compressor according to the present invention.

FIG. 2 is a cross-sectional view of the vane type compressor shown in FIG. 1 taken along the line II-II.

FIG. 3 is a sectional view of the vane type compressor shown in FIG. 1 taken along line III-III.

FIG. 4 is a sectional view of the vane type compressor shown in FIG. 1 taken along line IV-IV.

FIG. 5 is a perspective view of a control plate used in the vane type compressor according to the present invention.

FIG. 6 is a partially cutaway sectional view showing a shaft and a rotor of the vane compressor according to the present invention.

FIG. 7 is a perspective view showing a relationship between a vane groove and a partition portion according to the present invention.

[Explanation of symbols]

 2 Cylinder 3 Front side block 4 Rear side block 5 Rotor 7 Vane 9 Compression chamber 10 Shaft 35 Oil guide passage 38 Back pressure chamber 61 Partition part

Claims (1)

(57) [Claims] 1. A cylinder, both sides of which are closed by side blocks, including a rotor that rotates with the rotation of a shaft, and a vane that slides on the inner surface of the cylinder to form a compression chamber. A vane compressor which is fitted in a vane groove formed in the rotor such that the back pressure chamber presses the vane is formed in the vane groove. Along with forming an oil guide passage for guiding high-pressure lubricating oil from the suction hole side to the back pressure chamber,
A vane-type compressor, wherein the back pressure chamber is provided with a partition for partitioning the back pressure chamber in a longitudinal direction when the vane is in a maximum immersion state.