JPH10311277A - Refrigerant compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high reliable refrigerant compressor to sufficiently feed oil to a thrust bearing and a radial bearing even under a high speed low load condition under which a circulation flow rate of refrigerant gas is decreased. SOLUTION: This refrigerant compressor comprises a rear head 3 arranged on one end face of a cylinder block 1 through a valve plate 2: a front head 4 arranged on the other end face of the cylinder block 1: a discharge chamber 12 formed in the rear head 3; a crank chamber 8 formed in the front head 4; a high pressure chamber 22 formed in the cylinder head 1 and communicated with the discharge chamber 12; and a discharge port 23 to feed refrigerant gas in a high pressure chamber 22 to an external part. In this case, the refrigerant compressor is additionally provided with a baffle plate 50 to separate oil from refrigerant gas flowing in the high pressure chamber 22; a small hole 83; and a communication passage 32 to feed oil, separated in the high pressure chamber 22 from a high pressure chamber 22, to the crank chamber 8.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant compressor, and more particularly to a refrigerant compressor in which a high-pressure chamber for reducing pulsation is provided on a side surface of a cylinder block.

[0002]

2. Description of the Related Art FIG. 8 is a longitudinal sectional view showing a conventional rocking plate compressor.

[0003] A shaft 1 is mounted on a cylinder block 101.
A plurality of cylinder bores 106 are provided at predetermined intervals in the circumferential direction around the center 05. Cylinder block 10
A rear head 103 is fixed to the rear side end face of the device 1 via a valve plate 102, and a discharge chamber 112 and a suction chamber 113 are formed in the rear head 103.

A front head 104 is fixed to a front end surface of the cylinder block 101. A crank chamber 108 is formed in the front head 104, and a swing plate 110 is housed in the crank chamber 108.

[0005] Rear head 103, cylinder block 10
The one and the front head 104 are integrally connected by a plurality of through bolts (not shown).

A high pressure chamber 122 for reducing high pressure pulsation is provided on the outer peripheral surface of the cylinder block 101. A concave portion 101a is provided on the outer peripheral surface of the cylinder block 101, and an O-ring 153 is
The cover 160 is fixed via the.

The high-pressure chamber 122 is formed by the cover 160 and the recess 101a of the cylinder block 101. The high-pressure chamber 122 communicates with the high-pressure chamber 122 through an oblique hole 135 extending outward from the discharge chamber 112 and a communication passage 134 extending in parallel with the shaft 105.

The valve plate 102 has a discharge port 1 for communicating the cylinder bore 106 with the discharge chamber 112.
16 and a suction port 115 for communicating the cylinder bore 106 with the suction chamber 113 are provided.

The discharge port 116 is opened and closed by a discharge valve 117. The discharge valve 117 is fixed to a rear head side end surface of the valve plate 102 by a rivet 119 together with a valve retainer 118.

In the vicinity of the rivet 119, a guide hole 127 is provided for communicating the discharge chamber 112 and the bearing receiving hole 125 of the cylinder block 101 through the orifice 126.

The high-pressure refrigerant gas in the discharge chamber 112 is supplied to the bearing receiving hole 125 of the cylinder block 101 through the guide hole 127 and the orifice 126, and is supplied to the bearing receiving hole 12.
5 to the crank chamber 108 through the bearing housing hole 128. Then, the oil in the refrigerant gas is supplied to the thrust bearings 145, 146, etc. and the radial bearings 147, 148, etc.

The high-pressure refrigerant gas sent from the compression chamber to the discharge chamber 112 expands in the discharge chamber 112, is narrowed by the oblique hole 135 and the passage 134, expands in the high-pressure chamber 122, is narrowed by the discharge port 123, and is compressed. The pulsation is reduced because the gas is discharged from the machine.

[0013]

By the way, when the refrigerant gas flows into the discharge chamber 112 and the high-pressure chamber 122, the speed of the refrigerant gas is reduced, and a part of the mist oil contained in the refrigerant gas is separated and the discharge chamber 112 and the high-pressure chamber 122 are separated. It accumulates in the lower part of the high-pressure chamber 122.

In particular, in the high-pressure chamber 122, the refrigerant gas is discharged upward due to the layout of the compressor, so that the oil is decelerated due to the difference in specific gravity with the refrigerant gas and the collision of the refrigerant gas with the wall surface of the cover 160, It is easily separated from the refrigerant gas.

Therefore, the oil contained in the refrigerant gas is gradually reduced during the circulation of the refrigerant gas.
5 and the radial bearing 148 may not be sufficiently cooled and lubricated. In particular, when the compressor is used under high-speed, low-load conditions, the compressor is in the minimum discharge state, and this tendency becomes remarkable when the flow rate of the refrigerant gas decreases.

SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and an object thereof is to provide a reliable oil supply to a thrust bearing and a radial bearing even under a high-speed and low-load condition in which a circulating flow rate of a refrigerant gas is reduced. It is to provide a refrigerant compressor having high performance.

[0017]

According to a first aspect of the present invention, there is provided a refrigerant compressor including a rear head provided on one end surface of a cylinder block via a valve plate, and a second end surface of the cylinder block. A first high-pressure chamber formed in the rear head, into which high-pressure refrigerant gas is sent from a compression chamber; a crank chamber formed in the front head; and a cylinder block formed in the cylinder block. A refrigerant compressor having a second high-pressure chamber communicating with the first high-pressure chamber, and a discharge port for sending refrigerant gas from the second high-pressure chamber to the outside; An oil separating member for separating oil from the refrigerant gas, and a throttle.
And a communication path for supplying the oil separated in the high-pressure chamber to the crank chamber.

In the second high-pressure chamber, oil is separated from the refrigerant gas by the oil separating member, and the separated oil accumulates in the lower part of the second high-pressure chamber. Since this oil is returned to the crank chamber through the communication passage, the amount of oil supplied to the crank chamber increases, and the thrust bearing and the radial bearing are sufficiently supplied with oil.

The refrigerant compressor according to the second aspect of the present invention provides the refrigerant compressor according to the first aspect.
Wherein the second high-pressure chamber is formed by a concave portion provided on an outer peripheral surface of the cylinder block, and a lid member fixed to an opening end of the concave portion, and the oil separating member is provided. And a plate having a hole mounted between the opening end of the recess and the lid member.

Since the amount of the refrigerant gas is reduced by the hole of the plate mounted between the opening end of the concave portion and the lid member, the pulsation generated in the space formed by the concave portion and the plate is further reduced. Also, the velocity of the refrigerant gas is reduced by the collision with the plate, and the oil separates from the refrigerant gas.

According to a third aspect of the present invention, there is provided a refrigerant compressor.
Alternatively, in the refrigerant compressor described in 2, the throttle is formed in a gasket mounted between the other end surface of the cylinder block and the front head.

Since the gasket is used as the oil separating member, the diaphragm can be formed simultaneously in the gasket punching step.

According to a fourth aspect of the present invention, there is provided a refrigerant compressor.
Or the refrigerant compressor according to 2, wherein the throttle is formed in the front head.

Since the orifice is formed in the front head, oil can be supplied into the crank chamber from the vicinity of the thrust bearing and the radial bearing.

[0025]

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

FIG. 1 is a longitudinal sectional view of a wobble plate compressor according to a first embodiment of the present invention, FIG. 2 is a partially enlarged view of FIG.
3A is a plan view of the baffle plate, FIG. 3B is a cross-sectional view of the baffle plate, and FIG. 4 is a plan view of the gasket.

Cylinder block 1 of this wobble plate compressor
One end face of the rear head 3
However, the front heads 4 are fixed to the other end surfaces via gaskets 80, respectively.

The rear head 3, the cylinder block 1 and the front head 4
And are integrally connected by a not-shown through bolt.

The cylinder block 1 has five cylinder bores 6 at regular intervals in the circumferential direction around the shaft 5.
Are arranged. A piston 7 is slidably accommodated in each of the cylinder bores 6.

A high-pressure chamber (second high-pressure chamber) 22 is provided on the outer peripheral surface of the cylinder block 1. A concave portion 1 a is provided on the outer peripheral surface of the cylinder block 1.
baffle plate (oil separating member) 50
The cover (lid member) 60 is fixed via the cover.

The high-pressure chamber 22 is formed by the cover 60 and the recess 1a of the cylinder block 1. The high-pressure chamber 22 discharges the refrigerant gas through a discharge port 23 to a condenser (not shown) mounted on the front of the radiator.

The baffle plate 50 also serves as a gasket, and is formed of a cold-rolled steel plate having the same outer shape as the open end 1b of the recess 1a. Baffle plate 50
A convex portion 51 is formed by embossing at a portion facing the opening end 1b of the concave portion 1a, and a plurality of holes 52 serving as refrigerant gas passages are formed over the entire surface at a portion facing the opening of the concave portion 1a. (See FIG. 3).

The baffle plate 50 is integrally fixed to the opening end 1b of the concave portion 1a together with the cover 60 by bolts (not shown) passing through the two bolt holes 53, and the inside of the high-pressure chamber 22 is lowered to the lower high-pressure chamber 22A. And an upper high-pressure chamber 22B.

The passage 31 of the recess 1 a on the rear head 3 side communicates with a passage 34 formed in the rear head 3 via a piping connector 70. O-rings 71 and 72 are provided between the pipe connector 70 and the cylinder block 1 and between the pipe connector 70 and the rear head 3, and between the pipe connector 70 and the cylinder block 1 and between the pipe connector 70 and the rear head 3. The seal between them has been made.

A discharge chamber (first high-pressure chamber) 12 and a suction chamber 13 located around the discharge chamber 12 are formed in the rear head 3. The discharge chamber 12 and the passage 34 communicate with each other via an oblique hole 35 formed so as not to cut the suction chamber 13.

The valve plate 2 has a discharge port 16 formed inside the cylinder bore 6 for communicating the compression chamber 91 with the discharge chamber 12, and a suction port 15 communicating the compression chamber 91 with the suction chamber 13. Each is provided only for the number of cylinders.

The discharge port 16 is opened and closed by a discharge valve 17. The discharge valve 17 is fixed to a rear head side end surface of the valve plate 2 by a rivet 19 together with a valve retainer 18.

The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is provided on the front end face of the valve plate 2 together with the discharge valve 17 and the valve holder 18 in the rivet 1.
9.

In the vicinity of the rivet 19, a guide hole 27 is provided for communicating the discharge chamber 12 and the bearing receiving hole 25 of the cylinder block 1 through the orifice 26.

The high-pressure refrigerant gas in the discharge chamber 12
It is supplied to the bearing housing hole 25 of the cylinder block 1 through the 7 and the orifice 26, and is supplied from the bearing housing hole 25 to the crank chamber 8 through the bearing housing hole 28.

On the other hand, a lower portion of the recess 1a on the front head 4 side communicates with the crank chamber 8 of the front head 4 via a communication passage 32 formed by a gasket 80 and having a passage 32A and a passage 32B.

The gasket 80 seals between the cylinder block 1 and the front head 4 to prevent leakage of gas and oil in the crank chamber 8.

The gasket 80 is formed by stamping a cold-rolled steel plate and forming a substantially annular shape as shown in FIG. Annular part 81
Are formed with bolt holes 82 and small holes 83. The small hole 83 is arranged in the middle of the communication passage 32 and functions as an orifice (throttle) between the high-pressure chamber 22 and the crank chamber 8 having different pressures.

The thrust flange 4 is provided in the crank chamber 8.
1, the drive hub 42 and the swing plate 10 are housed.

The thrust flange 41 is fixed to the shaft 5 and rotatably abuts on the inner wall surface of the front head 4 via a thrust bearing 43.

The drive hub 42 is rotatably mounted on the shaft 5 via the hinge ball 9.
It is connected to the thrust flange 41 via a link mechanism 49.

The oscillating plate 10 is mounted on the drive hub 42 via a thrust bearing 45 and a radial bearing 48.

The oscillating plate 10 is connected to the piston 7 via a connecting rod 11, and the oscillating plate 10 causes the piston 7 to reciprocate in the cylinder bore 6.
The tilt angle of the swing plate 10 changes according to the pressure in the crank chamber 8.

Next, the operation of the wobble plate compressor will be described.

When the rotational power of the engine (not shown) is transmitted to the shaft 5, the shaft 5
The rotation plate 10 rotates together with the drive hub 42, and the rotation causes the rocking plate 10 to rock, and the rocking causes the piston 7 to reciprocate in the cylinder bore 6.
The internal volume changes, and the suction, compression, and discharge of the refrigerant gas are sequentially performed according to the change in the volume, and a high-pressure refrigerant gas having a capacity corresponding to the inclination angle of the swinging plate 10 is discharged.

When the discharge valve 17 is opened, the refrigerant gas discharged into the discharge chamber 12 through the discharge port 16 flows into the lower high-pressure chamber 22A through the oblique hole 35, the passage 34 and the passage 31. At this time, the amount flowing into the lower high-pressure chamber 22A is reduced by the oblique hole 35, the passage 34, and the passage 31.

The refrigerant gas further flows into the upper high-pressure chamber 22B via the baffle plate 50.
The number of holes 52 that flow into the upper high-pressure chamber 22B is reduced. Therefore, the lower high pressure chamber 22A and the upper high pressure chamber 2
Pulsation is greatly reduced in combination with 2B.

At this time, a part of the refrigerant gas collides with the baffle plate 50 and is decelerated. Therefore, the oil 90 is separated from the refrigerant gas due to the difference in specific gravity as shown in FIG.

Further, the refrigerant gas passing through the hole 52 is decelerated by the collision with the wall surface 60a of the cover 60, and the oil is separated from the refrigerant gas. This oil also falls through the hole 52 and accumulates in the lower part of the high-pressure chamber 22.

At this time, the pressure in the crank chamber 8 is
2, the oil 90 accumulated in the lower part of the high-pressure chamber 22 flows out to the crank chamber 8 through the small hole 83 and the communication passage 32 due to the pressure difference between the two chambers, and the thrust bearing 45
And radial bearings 48 and the like.

According to the first embodiment, the oil 90 separated from the refrigerant gas by the baffle plate 50 and accumulated in the lower part of the high-pressure chamber 22 is returned to the crank chamber 8 through the small hole 83 and the communication passage 32. The amount of oil supplied to the crank chamber 8 increases, and the thrust bearing 45 and the radial bearing 4
8 can sufficiently supply the oil 90, and even when used under high-speed and low-load conditions, seizure does not occur on the thrust bearing 45 and the radial bearing 48. Further, another high-pressure chamber is formed in the high-pressure chamber by the baffle plate 50, so that pulsation is further reduced. Further, the baffle plate 50 also serving as a gasket is used, and the high pressure chamber 22 is sealed by the convex portion 51, so that the O-ring 153 for sealing is unnecessary as in the conventional case, and the O-ring 153 is further reduced.
The step of forming a groove for fitting the ring 153 becomes unnecessary.

FIG. 5 is a partially enlarged view of a wobble plate type compressor according to a modification of the first embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. .

In this modification, the passage 132A itself is formed as a fine hole so as to function as an orifice. Since the small hole 183 of the gasket 180 does not need to function as an orifice, its inside diameter is made larger than the inside diameter of the passage 132A.

According to this modification, the same effects as in the first embodiment can be exhibited.

FIG. 6 is a partially enlarged view of a wobble plate compressor according to another modification of the first embodiment of the present invention.

In this modification, the passage 132B is constituted by the oblique hole 84 functioning as an orifice and the port 85 communicating with the small hole 183 of the gasket 180.

According to this modification, the same effects as those of the first embodiment can be obtained, and the first inclination angle of the oblique hole 84 formed in the crank chamber 8 can be changed.
Ball bearing 48 and thrust bearing 4
It is also possible to drain the oil to 8 towards 5,
The clearing lubrication effect can be further improved.

FIG. 7 is a partially enlarged view of an oscillating plate compressor according to a second embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

In the second embodiment, as shown in FIG. 7, a passage 32C communicating with the passage 32A through the hole 283 of the gasket 80 is formed on the outer peripheral surface of the front head 204 in the same direction as the shaft (not shown). A slant hole (throttle) 86 is formed in the front head 4 at the front end of the passage 32 </ b> C and functions as an orifice for supplying oil 90 to the crank chamber 8.

The oblique hole 86 is provided in the thrust bearing 45 (see FIG. 1).
And in the vicinity of the radial bearing 48 and offset from the center of the shaft in the rotation direction of the shaft 5.
With this configuration, the drive hub 42
It becomes easy to join the oil to the flow generated by the rotation, and lubrication is promoted.

With the above configuration, the discharge chamber 12
The refrigerant gas discharged to the discharge chamber 12 is decelerated by hitting the wall surface of the discharge chamber 12, and flows into the high-pressure chamber 22 after a part of the oil in the refrigerant gas is separated. After the oil 90 is separated in the high-pressure chamber 22, the refrigerant gas is discharged from a discharge port 23 to a condenser (not shown).

The separated oil 90 is supplied to the crank chamber 8 through the communication path including the passage 32A and the passage 32C and the oblique hole 85.

According to the second embodiment, the same effects as in the first embodiment can be exhibited.

Further, according to the oscillating plate compressor of the second embodiment, the oil 90 separated in the high pressure chamber 22 is provided with the oblique hole 8 formed near the thrust bearing 45 and the radial bearing 48.
5 and can be supplied to the crank chamber 8 under high-speed and low-load conditions, and can be used for cooling the thrust bearings 45, 46, etc. and the radial bearings 47, 48, etc. Lubrication can be sufficiently performed, and seizure can be reliably prevented.

In particular, under high-speed and low-load conditions, the thrust bearing 45 receives only a large load, and is more effective than the first embodiment in preventing seizure.

In each of the above embodiments, a plurality of holes 52 that serve as refrigerant gas passages are formed in the baffle plate 50 over the entire surface. However, the present invention is not limited to this configuration.
It is sufficient that at least one hole is formed.

In each of the above embodiments, the case where the present invention is applied to a wobble plate compressor as a refrigerant compressor has been described. However, the present invention can be applied to other types of refrigerant compressors.

[0073]

As described above, according to the refrigerant compressor of the first aspect of the present invention, oil is separated in the second high-pressure chamber, and this oil is returned to the crank chamber through the communication passage.
The amount of oil supplied to the crankcase increases, and sufficient oil is supplied to the thrust bearings and radial bearings.As a result, even under high-speed and low-load conditions where the circulation flow rate of the refrigerant gas decreases, the thrust bearings and radial Oil is sufficiently supplied to the bearing, and the reliability of the refrigerant compressor is improved.

According to the refrigerant compressor of the second aspect of the present invention, the amount of the refrigerant gas is reduced by the hole of the plate mounted between the opening end of the concave portion and the lid member, so that the pulsation is further reduced. Further, the velocity of the refrigerant gas is reduced by the collision with the plate, and the oil is separated from the refrigerant gas by the difference in specific gravity.

According to the refrigerant compressor of the third aspect of the present invention, since the gasket is used as the oil separating member, the diaphragm can be simultaneously formed in the gasket punching step, and the conventional machining is not required. Therefore, the manufacturing cost can be reduced.

According to the refrigerant compressor of the fourth aspect of the present invention, since the orifice is formed in the front head, oil can be supplied into the crank chamber from the vicinity of the thrust bearing and the radial bearing, and seizure can be reliably achieved. Can be prevented.

[Brief description of the drawings]

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

FIG. 2 is a partially enlarged view of FIG. 1;

FIG. 3A is a plan view of a baffle plate, and FIG.
(B) is a cross-sectional view of the baffle plate.

FIG. 4 is a plan view of a gasket.

FIG. 5 is a partially enlarged view of a wobble plate compressor according to a modification of the first embodiment of the present invention.

FIG. 6 is a partially enlarged view of a wobble plate compressor according to another modification of the first embodiment of the present invention.

FIG. 7 is a partially enlarged view of a wobble plate compressor according to a second embodiment of the present invention.

FIG. 8 is a longitudinal sectional view showing a conventional rocking plate compressor.

[Description of Signs] 1 Cylinder block 1a recess 2 Valve plate 3 Rear head 4 Front head 8 Crank chamber 12 Discharge chamber (first high pressure chamber) 22 High pressure chamber (second high pressure chamber) 23 Discharge port 32 Communication passage 50 Baffle plate (Oil separation member) 52 hole 60 cover (lid member) 83 small hole (throttle)

Claims (4)

[Claims] A rear head provided on one end surface of the cylinder block via a valve plate; a front head provided on the other end surface of the cylinder block; A first high-pressure chamber into which the pressure is fed; a crank chamber formed in the front head; a second high-pressure chamber formed in the cylinder block and communicating with the first high-pressure chamber; A refrigerant compressor having a discharge port for sending refrigerant gas from the chamber to the outside, comprising: an oil separating member for separating oil from the refrigerant gas flowing into the second high-pressure chamber; A communication path for supplying the oil separated in the high-pressure chamber to the crank chamber. 2. The second high-pressure chamber is formed by a concave portion provided on an outer peripheral surface of the cylinder block, and a lid member fixed to an opening end of the concave portion, and the oil separating member is formed by the concave portion. 2. The refrigerant compressor according to claim 1, wherein the plate is a plate having a hole mounted between the open end of the cover and the lid member. 3. The refrigerant compressor according to claim 1, wherein the throttle is formed on a gasket mounted between the other end surface of the cylinder block and the front head. 4. The refrigerant compressor according to claim 1, wherein the throttle is formed in the front head.