JPH11294355A - Rolling piston type rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the efficiency of a compressor by suppressing the pulsation of the suction passage of a rolling piston type rotary compressor having a plurality of compression chambers by projecting/retreating a plurality of blades in one cylinder. SOLUTION: Length of communicating pipes 64, 65 from the intake opening of a compression chamber to a compressor outside intake piping system is set to approximately the same. Thereby, amplitude of pulsation produced in the communicating pipes 64, 65 is approximately equalized, pulsation in a confluent part of the communicating pipe 64 with the communicating pipe 65 is countervailed so as to reduce the pressure loss of the intake piping system, and the efficiency of this compressor can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a suction line system for a rotary compressor.

[0002]

2. Description of the Related Art The structure of a rolling piston type rotary compressor, which is widely used in compressors for air conditioners, is well known as represented by a vertical section shown in FIG. 4 and a horizontal section shown in FIG. ing.

[0003] In other words, the interior of the sealed container 101 is a motor 102 in a state where the discharge pressure acts, and the motor 102
And a compression unit 103 driven by the
A drive shaft 106 is connected to the electric motor 102 and supported by main bearings 108 and sub-bearings 109 arranged on both sides of the cylinder block 111.

[0004] Inside a cylinder block 111 having a cylinder 119, a roller 110 for covering a crank portion 107 eccentric from the main shaft of the drive shaft 106 is provided with a cylinder 110.
9 and is formed close to the inner wall of the diaper 9 to form a compression chamber 115.

The guide groove 112 of the cylinder block 111 has a blade 114 and the tip of the blade 114
10, a spring device 113 for urging the spring device 1 is provided.
The space for accommodating 13 communicates with the inside of the sealed container 101, and the compression chamber 115 is divided into a suction side and a compression side.

[0006] The blade 1 is mounted on the cylinder block 111.
Suction port 116 opening to cylinder 119 at the boundary of 14
And a discharge port 117 are provided.

[0007] The suction port 116 is connected to an accumulator 160 for storing the low-pressure side refrigerant.

However, such one compression chamber 1
The rotary compressor having the structure 15 has a problem that the compression torque fluctuation is large and the vibration is large and the compressor piping system is damaged. As shown in FIG.
A rolling piston type rotary compressor having two compression chambers therein is proposed.

In FIG. 1, a blade 221 and a spring device 222 are arranged in a guide groove 220 provided in a cylinder block 211 and communicating with a discharge chamber, and a blade 224 and a spring device 225 are arranged in a guide groove 223. Compression chamber 227
It has.

The compression chamber 226 has a suction port 228 and a discharge port 2
29 are open, and a suction port 230 and a discharge port 231 are open in the compression chamber 227.

In the compressor having such two blades, the working range of the compression torque per one rotation of the drive shaft 206 is divided into two, and the vibration of the compressor is smaller than that of the compressor shown in FIGS. Is also halved (JP-A-63-208688).

On the other hand, a compressor in a practical use state in which the above-described cylinder block 211 is provided with a suction port 228 and a suction port 230 is provided with a first accumulator 218 and a second accumulator 214 on the suction side as shown in FIG. The structure shown in FIG. 9 has been proposed to simplify the suction piping system (Japanese Patent Laid-Open No. 1-249977).

FIG. 1 shows that an accumulator 350 penetrates a side wall of a closed vessel 301 and a suction port 349 of one compression chamber.
And a suction port 349 communicates with a suction port of the other compression chamber via a communication pipe 363 in the sealed container 301. The communication pipe 363 bypasses the bearing boss of the main bearing 334 that supports the drive shaft 336.

[0014]

However, the above-described conventional configuration has the following problems.

That is, the compression principle of a compressor in which two blades are arranged in one cylinder block to form two compression chambers in a cylinder as described above is shown in FIGS.
-D.

That is, the hatched space in FIG. 7A shows the state of the maximum suction stroke volume of the compression chamber. Fig. 7-
The hatched space in b shows the compression chamber immediately before the suction port is closed in the state of the minimum suction stroke volume of the compression chamber, and is reduced from the state of the maximum suction stroke volume in FIG. 7A. This decrease in the suction stroke volume means that the suction gas flows back to the suction piping system through the suction port. The hatched space in FIG. 7C shows the state where the suction port is closed and the compression is substantially started. The hatched space in FIG. 7D indicates a state where the space is discharged from the compression chamber through the discharge port as a result of an increase in the compression chamber pressure.

Since the inflow and reverse flow of the suction gas in the suction / compression process occur, the magnitude of the pulsation generated in each suction path differs in the case of the split flow of the suction paths having unequal lengths as shown in FIG. As a result, there is a problem that the pulsation is not canceled at the merging portion of the suction path, pressure loss is induced in the suction path, compression efficiency is reduced, and vibration of the suction piping system is promoted.

The present invention has been made to solve such conventional problems, and has as its object to improve compression efficiency and reduce vibration of a suction piping system.

[0019]

In order to solve the above-mentioned problems, the present invention is to set the lengths of the communication pipes connected to the respective compression chambers to be substantially the same.

By setting the length, the pulsation is canceled at the junction of the communication pipes, and pressure loss in the suction pipe system is prevented.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The first aspect of the present invention is to set the length of each communication pipe from each suction port of each compression chamber to the suction pipe system outside the compressor to be substantially the same. According to this configuration, the magnitude of the pulsation generated in each communication pipe becomes substantially the same, the pulsation is canceled at the junction of the communication pipes, and pressure loss and pipe vibration of the suction pipe system can be suppressed.

According to a second aspect of the present invention, a muffler chamber that supports a drive shaft and is connected to a compressor external suction piping system is disposed outside the compressor on the side of a sub-bearing adjacent to a cylinder block. Each communication pipe is opened at the bottom. According to this configuration, mitigation of the pulsation generated in each communication pipe and cancellation of the pulsation are promoted, and pressure loss and vibration of the suction pipe system can be further suppressed.

According to a third aspect of the present invention, each communication pipe is disposed to penetrate the end wall of the sealed container and the auxiliary bearing in the axial direction, and each communication pipe is directly connected to a suction passage provided in the cylinder block. It is connected. And according to this configuration,
The length of each communication pipe can be shortened and the airtightness of the suction passage can be easily ensured.

According to a fourth aspect of the present invention, an accumulator for gas-liquid separation and storage is provided in a suction pipe system external to the compressor, and a muffler chamber is provided in a final end path at the bottom of the accumulator. . And according to this configuration,
The arrangement of the muffler room becomes easy.

[0025]

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

(Embodiment 1) FIG. 1 shows a vertical cross section of a rolling piston type rotary refrigerant compressor, in which an electric motor 2 is arranged in an upper part of an inside of a closed vessel 1 and a compression part 3 is arranged in a lower part. A discharge pipe 49 connected to the system is connected to the upper space of the electric motor 2. Compressed part 3 outside bottom of closed container 1
A muffler chamber 50 that communicates with the suction side is disposed, and a suction pipe 51 is connected to the muffler chamber 50.

The compression section 3 has a main bearing 8 and a sub-bearing 9 which are internally fixed to the closed casing 1 and are fixed with a cylinder block 11 interposed therebetween.

A drive shaft 6 connected to a rotor 5 of the electric motor 2 is supported by a main bearing 8 and a sub bearing 9, and a roller 10 is fitted on a crank portion 7 of the drive shaft 6.

The roller 10 has a double structure of an inner roller 10a and an outer roller 10b, and the outer peripheral surface of the inner roller 10a can be in sliding contact with the inner peripheral surface of the outer roller 10b. The axial dimension of the inner roller 10a is set smaller than the axial dimension of the outer roller 10b so that an oil film cannot be formed between the side surface of the inner roller 10a and the side surfaces of the main bearing 8 and the auxiliary bearing 9. The lubricating oil supplied to the inside of the outer roller 10b is supplied to the inner peripheral surface of the outer roller 10b.

As shown in FIG. 2, a blade 14 is fitted in a guide groove 12 provided in a cylinder block 11, and the tip of the blade 14 is
Is pressed against. A blade 24 is mounted in the guide groove 23 provided at the opposite side, and the tip of the blade 24 is pressed against the outer roller 10 b by the spring device 13.

A cylinder 1 provided with a cylinder block 11 having a suction port 28 and a suction port 30 opened to a compression chamber 26 and a compression chamber 27 partitioned by a blade 14 and a blade 24.
5 is open on the inner peripheral surface. The discharge port 29 and the discharge port 31 are provided at symmetrical positions on the mounting surface side of the main bearing 8 of the cylinder block 11.

The discharge valve device 61, the discharge valve device 62, and the discharge guide 63 are arranged on the main bearing 8 and form a part of the discharge refrigerant passage.

A communication pipe 64 communicating with the suction port 28 and a communication pipe 65 communicating with the suction port 30 pass through the auxiliary bearing 9 and the bottom of the closed casing 1 in the axial direction, and communicate with the muffler chamber 50. The connecting portion between the outer peripheral surfaces of the communication pipes 64 and 65 and the auxiliary bearing 9 is sealed with an o-ring.

The communication pipe 64 and the communication pipe 65 are fixed to the bottom of the sealed container 1 and the outer wall of the muffler chamber 50 by silver brazing.
The muffler chamber 50 is configured to be supported. The ends of the communication pipe 64 and the communication pipe 65 that have entered the muffler chamber 50 are disposed at the bottom of the muffler chamber 50 so as to face each other.

The upper space and the lower space of the motor room 70 in which the motor 2 is housed communicate with a cooling passage 71 provided outside the stator 4 of the motor 2.

The oil reservoir 35 communicates with the lower space of the motor room 70. The opening of the suction pipe 51 entering the muffler chamber 50 is located substantially at the center with respect to the opening positions of the communication pipe 64 and the communication pipe 65, and the opening direction is orthogonal to the opening direction of the communication pipe 64 and the communication pipe 65. doing.

The operation of the rolling piston type rotary refrigerant compressor configured as described above will be described.

Drive shaft 6 connected to rotor 5 of electric motor 6
Is rotated, the refrigerant gas is sucked and compressed in the compression chamber 26 and the compression chamber 27, respectively, by the compression principle of FIGS. 7A to 7D described above, and the discharge valve device 61 and the discharge valve device 6
2. It is discharged to the motor room 70 via an annular passage between the main bearing 8 and the discharge guide 63.

A part of the lubricating oil contained in the refrigerant gas is separated and returned to the oil reservoir 35, and the remaining lubricating oil is sent out of the compressor together with the refrigerant gas through the discharge pipe 49.

On the other hand, the refrigerant gas (including the lubricating oil) flowing into the muffler chamber 50 via the suction pipe 51 from the low-pressure side of the refrigeration cycle piping system passes through the communication pipe 64 and the communication pipe 65 and the compression chamber 26. And alternately flows into the suction side of the compression chamber 27.

A part of the lubricating oil mixed into the refrigerant gas is separated once after flowing into the muffler chamber 50.
The refrigerant gas is again mixed into the refrigerant gas sucked and discharged from the bottom of the communication pipe 64 to the communication pipe 64 and the communication pipe 65.

The suction refrigerant gas during the suction stroke in the compression chambers 26 and 27 flows through the communication pipes 64 and 65 of the same length according to the suction / compression principle described with reference to FIGS. 7A to 7D. Ingress and egress, resulting in pulsations of approximately the same amplitude and 180 degrees out of phase with each other.

However, since the lengths of the communication pipe 64 and the communication pipe 65 are short, the amplitude of the pulsation is small, and the communication pipes 64, 6
The pulsation in 5 is counteracted with the pulsation mitigation in muffler chamber 50.

The suction refrigerant gas flowing backward through the communication pipe 64 leading to the compression chamber 26 passes through the muffler chamber 50 to the compression chamber 27.
Is instantaneously sucked into the communication pipe 65 which is communicated during the suction stroke of.

For this reason, since the suction passage resistance due to the generation of pulsation in the communication pipes 64 and 65 is extremely small, when the refrigerant gas flows back through the communication pipes 64 and 65, the suction in the compression chambers 26 and 27 is performed. There is no boost during the journey.

Next, the flow of the lubricating oil and the operation of the roller 10 and the blades 14, 24 will be described.

The lubricating oil supplied to the inside of the inner roller 10a by a pump means (not shown) incorporated in the drive shaft 6 is supplied to the inner roller 10a by a differential pressure between the compression chambers 26 and 27 and centrifugal force. It is supplied to the inside of the outer roller 10b via the side surface 10a.

Also, the oil is supplied to the inner peripheral surface of the outer roller 10b through an oil hole (not shown) provided through the inner and outer peripheral surface of the inner roller 10a.

By supplying the lubricating oil, the inner roller 10
The sliding surface between the roller a and the outer roller 10b maintains a state in which an oil film can be formed.

The lubricating oil mixed into the refrigerant gas is supplied to the muffler chamber 5
The bottom of the communication pipe 6 has no liquid refrigerant or lubricating oil remaining at the bottom.
4. The water is sucked up by the communication pipe 65 and does not affect the pulsation mitigation or the canceling action in the muffler chamber 50.

As described above, according to the above embodiment, the communication pipes 64 and 65 from the suction ports of the compression chambers 26 and 27 to the suction pipe system outside the compressor are set to have substantially the same length, so that the communication is established. The amplitude of the pulsation generated in the pipes 64 and 65 becomes substantially the same, the pulsation is canceled at the junction of the communication pipes 64 and 65, and the pressure loss and the pipe vibration of the suction pipe system are suppressed to realize a high efficiency and low vibration compressor. realizable.

In the above embodiment, the muffler chamber 5 supporting the drive shaft 6 and connected to the compressor external suction piping system outside the compressor on the side of the auxiliary bearing 9 adjacent to the cylinder block 11.
0, and communication pipes 64, 65 are provided at the bottom of the muffler chamber 50.
Are respectively opened, mitigation of the pulsation generated in the communication pipes 64 and 65 and cancellation of the pulsation are promoted, and the pressure loss and the pipe vibration of the suction pipe system can be further suppressed.

In the above embodiment, the communication pipes 64 and 65 are disposed so as to pass through the end wall of the closed casing 1 and the auxiliary bearing 9 in the axial direction, and the communication pipes 64 and 65 are connected to the cylinder block 1.
By directly connecting to the suction passage provided in 1, the communication pipes 64 and 65 can be shortened in length and airtightness of the suction passage can be easily ensured, and the compressor efficiency can be improved.

(Embodiment 2) FIG. 3 shows a longitudinal section of a rolling piston type rotary refrigerant compressor, in which the muffler chamber 50 shown in FIG. 1 is eliminated, and an accumulator 50a which serves both for gas-liquid separation and storage of the refrigerant is connected. Tubes 64a, 65a
Connected to

The accumulator 50a comprises an upper gas-liquid separation chamber 50b and a lower muffler chamber 50c, and the gas-liquid separation chamber 50b passes through the muffler chamber 50c via a suction pipe 50d provided at the center thereof. An oil hole 50e is provided at the bottom of the suction pipe 50d.

The muffler chamber 50b has communication pipes 64a and 65a.
Is connected to the central part of the connection. Other configurations are the same as those in FIG.

In the above embodiment, the accumulator 50a for gas-liquid separation and storage is arranged in the suction pipe system external to the compressor, and the muffler chamber 50c is arranged in the final end passage at the bottom of the accumulator. The arrangement of 50c can be facilitated.

In the above embodiment, the refrigerant compressor has been described. However, the same operation and effect can be obtained with other gas compressors such as nitrogen, oxygen and helium.

[0059]

As is apparent from the above embodiment, the first aspect of the present invention is as follows.
According to the invention described in (1), an electric motor and a compression unit are arranged inside a closed container, and a cylinder having a cylindrical inner surface provided in a cylinder block of the compression unit, and a crankshaft portion of a drive shaft connected to the electric motor, and an inner surface of the cylinder And a plurality of compression chambers formed at a substantially equal interval to protrude and retract from the cylinder block into the cylinder so that the leading end thereof slides on the outer peripheral surface of the roller to form a compression chamber formed by the inner surface of the cylinder and the outer peripheral surface of the roller. In a rolling piston type rotary compressor having a blade and a suction port and a discharge port in each of the divided compression chambers,
The length of each communication pipe from each suction port of each compression chamber to the compressor external suction pipe system is set to be substantially the same. According to this configuration, the amplitude of pulsation generated in each communication pipe becomes almost the same. ,
Since the pulsation is canceled at the junction of the communication pipes, the pressure loss and the pipe vibration of the suction pipe system can be suppressed, and the compressor efficiency can be prevented from lowering and the vibration can be reduced.

According to a second aspect of the present invention, the compressor is provided at a position opposite to the electric motor to support the drive shaft, and is connected to a compressor external suction piping system outside the compressor on the side of the auxiliary bearing adjacent to the cylinder block. The muffler chamber is arranged, and each communication pipe is opened at the bottom of the muffler chamber. According to this configuration, the pulsation generated in each communication pipe can be alleviated and the pulsation can be canceled out. Pressure loss and pipe vibration can be further suppressed, a decrease in compressor efficiency can be prevented, and vibration can be further reduced.

According to a third aspect of the present invention, each communication pipe is disposed so as to penetrate the end wall of the sealed container and the auxiliary bearing in the axial direction, and each communication pipe is provided in a suction passage provided in a cylinder block. According to this configuration, the length of each communication pipe can be shortened and the airtightness of the suction passage can be easily ensured, so that the efficiency of the compressor can be improved.

According to a fourth aspect of the present invention, an accumulator for gas-liquid separation and storage is disposed in a suction pipe system external to the compressor, and a muffler chamber is disposed in a final end path at the bottom of the accumulator. According to this configuration, the arrangement of the muffler chamber can be simplified and the cost can be reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a rolling piston type rotary refrigerant compressor showing an embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along line AA in FIG.

FIG. 3 is a longitudinal sectional view of a rolling piston type rotary refrigerant compressor showing another embodiment of the present invention.

FIG. 4 is a longitudinal sectional view of a conventional rolling piston type rotary compressor.

FIG. 5 is a cross-sectional view of a compression section of the compressor.

FIG. 6 is a cross-sectional view of a compression section of another conventional rolling piston type rotary compressor.

FIGS. 7A to 7D are explanatory diagrams of a compression principle of the compressor.

FIG. 8 is a cross-sectional view of another conventional rolling piston type rotary compressor.

FIG. 9 is a partial cross-sectional view of a main part of another conventional rolling piston rotary compressor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Closed container 2 Electric motor 3 Compression part 6 Drive shaft 7 Crank part 10 Roller 11 Cylinder block 12, 23 Guide groove 14, 24 Blade 15 Cylinder 26, 27 Compression chamber 28, 30 Suction port 29, 31 Discharge port 50, 50a Muffler chamber 64, 64a, 65, 65a Communication pipe

Claims (4)

[Claims] An electric motor and a compression section are arranged inside a closed container, and a cylinder having a cylindrical inner surface provided in a cylinder block of the compression section, and a cylinder externally mounted on a crank section of a drive shaft connected to the electric motor. A roller that moves along the inner surface of the roller, and a compression chamber formed by the inner surface of the cylinder and the outer surface of the roller that protrudes and retracts into the cylinder from the cylinder block so that the tip slides on the outer surface of the roller. In a rolling piston type rotary compressor having a plurality of blades partitioned at approximately equal intervals, and a suction port and a discharge port in each of the divided compression chambers, a compressor external suction pipe system is provided from each of the suction ports of each of the compression chambers. Rolling piston type rotary compressor in which the length of each communication pipe up to is set to be approximately the same. 2. A muffler chamber which is provided at a position opposite to the electric motor to support a drive shaft and is connected to a compressor external suction piping system outside the compressor on the side of a sub-bearing adjacent to a cylinder block, 2. The rolling piston type rotary compressor according to claim 1, wherein each communication pipe is opened at a bottom of the muffler chamber. 3. The communication pipe according to claim 1, wherein each communication pipe is disposed so as to extend axially through an end wall of the sealed container and the auxiliary bearing, and each communication pipe is directly connected to a suction passage provided in a cylinder block. The rolling piston type rotary compressor as described in the above. 4. The rolling piston type rotary according to claim 1, wherein an accumulator for gas-liquid separation and storage is arranged in a suction pipe system external to the compressor, and a muffler chamber is arranged in a final end passage portion at a bottom inside the accumulator. Compressor.