KR20130109509A - Rotary piston type compressor - Google Patents

Rotary piston type compressor Download PDF

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Publication number
KR20130109509A
KR20130109509A KR1020120031270A KR20120031270A KR20130109509A KR 20130109509 A KR20130109509 A KR 20130109509A KR 1020120031270 A KR1020120031270 A KR 1020120031270A KR 20120031270 A KR20120031270 A KR 20120031270A KR 20130109509 A KR20130109509 A KR 20130109509A
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KR
South Korea
Prior art keywords
cylinder
piston
refrigerant
groove
rotary piston
Prior art date
Application number
KR1020120031270A
Other languages
Korean (ko)
Inventor
이건호
권윤기
김학수
Original Assignee
학교법인 두원학원
주식회사 두원전자
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 학교법인 두원학원, 주식회사 두원전자 filed Critical 학교법인 두원학원
Priority to KR1020120031270A priority Critical patent/KR20130109509A/en
Publication of KR20130109509A publication Critical patent/KR20130109509A/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary piston compressor, and to a rotary piston compressor capable of inducing a smooth suction and discharge of refrigerant through a suction and compression stroke while linearly moving a piston along an inner wall of a cylinder bore.
In order to achieve the above object, the present invention provides a cylinder block, a front housing and a rear housing that are hermetically coupled to the front and rear of the cylinder block, respectively, a working cylinder rotatably received in the cylinder block, and A fixed cylinder corresponding to the working cylinder and fixed in the cylinder block and a curved guide groove in the circumferential direction are continuously formed on the outer periphery, and a rotation preventing groove is formed in the longitudinal direction, and the cylinder bore of the working cylinder and the fixed cylinder is formed. It characterized in that it comprises a piston which is accommodated in the reciprocating movement and a power transmission device for supplying rotational power to the working cylinder.

Description

ROTARY PISTON TYPE COMPRESSOR}

The present invention relates to a compressor, and more particularly to a rotary piston compressor for compressing a fluid in a cylinder by the reciprocating motion of the piston.

In general, an air conditioner includes a compressor for compressing a refrigerant gas at a high temperature and a high pressure to perform a cooling cycle, a condenser for gradually condensing the high temperature and high pressure refrigerant gas from the compressor into a liquid phase through heat discharge, from the condenser An expansion valve for lowering the pressure of the liquid refrigerant to form a mixed refrigerant consisting of low temperature gas and liquid, and an evaporator for evaporating the mixed refrigerant to absorb ambient heat and sending the evaporated refrigerant back to the compressor. .

In particular, the compressor serves to compress the low pressure refrigerant gas of the evaporator to a high pressure to deliver to the condenser.

In a typical rotary piston compressor according to the prior art, a disk-shaped swash plate is installed in a state in which the inclination angle is variable or fixed to a drive shaft to which the engine is transmitted, corresponding to rotation of the drive shaft, and the circumference of the swash plate is rotated by the rotation of the swash plate. Accordingly, a plurality of pistons installed via a shoe is configured to suck, compress and discharge the refrigerant gas by linearly reciprocating the inside of the plurality of cylinder bores formed in the cylinder block.

In addition, in the process of inhaling, compressing and discharging the refrigerant gas, a valve plate for intermitting the suction and discharge of the refrigerant gas is provided between the housing and the cylinder block.

In addition, it is divided into a front cylinder block and a rear cylinder block, the front and rear cylinder block is formed with a muffler for pulsation and noise reduction of the discharge refrigerant.

By the way, the conventional rotary piston compressor is discharged to the muffler through the discharge chamber of the front and rear housings, respectively compressed in the cylinder bore of the front and rear cylinder block during the compression stroke, the discharged to face each other Since the front refrigerant and the rear refrigerant collide with the muffler to generate a pulsation, there is a problem in that noise and vibration of the compressor occur.

In addition, there is a problem that the operation efficiency of the compressor is lowered due to the vibration generated through the pulsation phenomenon.

Accordingly, the present invention has been made to solve the above problems, an object of the present invention is to induce a smooth suction and discharge of the refrigerant through the suction and compression stroke while the piston is linearly moved along the cylinder bore. have.

Rotary piston compressor according to the present invention to achieve the above object, the cylinder block; A front housing and a rear housing which are hermetically coupled to the front and rear of the cylinder block, respectively; An operating cylinder rotatably received in said cylinder block; A fixed cylinder corresponding to the working cylinder and fixed in a cylinder block; A piston which is continuously formed in the circumferential direction of the curved guide groove in the circumferential direction and is formed with a rotation preventing groove in the longitudinal direction and is reciprocally accommodated in the cylinder bore of the working cylinder and the fixed cylinder; And, characterized in that it comprises a power transmission device for supplying rotational power to the working cylinder.

The front housing is characterized in that the oil separator is formed to separate the oil contained in the introduced refrigerant to discharge only the pure refrigerant.

 The lower portion of the cylinder bore of the working cylinder, the chamber is formed so that the compressed refrigerant introduced through the clearance of the working cylinder and the piston acts as a back pressure of the piston.

The guide groove of the piston is characterized in that consisting of a sinusoidal curve.

The working cylinder is provided with a fixing pin which protrudes toward the inner direction and is inserted into the guide groove and is in contact with the surface, and the fixing cylinder is formed protruding toward the inner direction and is inserted into the anti-rotation groove for surface protection. It is characterized in that the pin is provided.

According to the rotary piston compressor according to the present invention having the configuration described above, the pulsation phenomenon due to the collision of the refrigerant generated in the muffler according to the prior art because the rotary motion of the drive motor is converted into a linear reciprocating motion of the working cylinder and the piston In addition to preventing it, there is an effect that can improve the durability performance and compression efficiency of the compressor.

It consists of a rotary piston type operating configuration, which has the effect of improving the simplicity and light weight of the parts.

In particular, it is possible to prevent the loss of compression during the compression stroke of the piston by placing a conical chamber in the working cylinder to which the piston reciprocates.

In addition, since the refrigerant is sucked through the rotational movement of the working cylinder, the configuration of the suction valve can be deleted, thereby reducing the number of parts and the cost of the parts.

Compressor efficiency can be improved by separating oil from refrigerant introduced into the front housing.

1 is an exploded perspective view showing a rotary piston compressor according to the present invention.
2 is a perspective view showing a suction stroke of a rotary piston compressor according to the present invention.
3 is a perspective view showing a compression stroke of a rotary piston compressor according to the present invention.
4 is a sectional perspective view showing an oil separator and a valve plate of the rotary piston compressor according to the present invention.
5 is a front sectional view showing an oil separator of a rotary piston compressor according to the present invention.
6 is a cutaway perspective view illustrating an oil discharge passage of an oil separator of a rotary piston compressor according to the present invention.
7 is a sectional view showing a suction stroke of the rotary piston compressor according to the present invention.
8 is a sectional view showing a compression stroke of a rotary piston compressor according to the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings of FIGS. 1 to 8.

1 and 3, the front and rear housings 20 and 30 are coupled to each other so as to be hermetically coupled to the cylinder block 10 and the front and rear of the cylinder block 10, respectively. And a working cylinder 40 rotatably received in the cylinder block 10, a fixed cylinder 50 corresponding to the working cylinder 40 and fixed in the cylinder block 10, and the working cylinder 40. And a piston 60 accommodated reciprocally in the cylinder bores 41 and 51 of the fixed cylinder 50.

Specifically, the rear housing 30 is formed with a suction passage 31 through which the refrigerant flows through the suction stroke of the piston 60, the power transmission device 70 for supplying rotational power to the working cylinder (40). ) Is mounted.

In the front housing 20, the oil separator 80 and the discharge passage 21 through which the refrigerant is discharged through the compression stroke of the piston 60 so as to separate the oil contained in the introduced refrigerant to discharge only the pure refrigerant. ) Is formed.

The working cylinder 40 is rotated about its inner center in the cylinder block 10 by the power transmission device 70.

At this time, the power transmission device 70 is composed of a drive motor 71 for supplying rotational power to the working cylinder 40, and a motor shaft 72 is connected to the drive motor 71 to exert a rotational force However, the present invention is not limited thereto, and various devices capable of supplying rotational power to the operating cylinder 40 may be adopted.

In addition, a stepped portion 42 is formed on the upper side of the working cylinder 40 to communicate with the suction port 52 to be described later.

In addition, a conical chamber 43 is provided below the cylinder bore 41 of the working cylinder 40.

At this time, the compressed refrigerant in the working cylinder 40 during the compression stroke of the piston 60 is moved to the inner lower portion of the working cylinder 40 through the clearance of the working cylinder 40 and the piston 60. In this case, the compressed refrigerant is introduced into the conical chamber 43 to act as a back pressure of the piston 60 to prevent the loss of the compressive force of the piston 60.

The fixed cylinder 50 flows into the cylinder bores 41 and 51 with the refrigerant flowing through the suction passage 31 of the rear housing 30 coinciding with the step 42 of the working cylinder 40. A suction port 52 is formed.

Of course, the suction passage is formed in the front and rear housings 20 and 30 and the cylinder block 10 of the compressor, through the suction passage 31 of the rear housing 30 during the suction stroke of the piston 60. Naturally, the refrigerant flows into the cylinder bore 41 and 51 of the working cylinder 40 and the fixed cylinder 50.

The piston 60 is accommodated reciprocally in the cylinder bores 41 and 51 of the working cylinder 40 and the fixed cylinder 50, and the guide groove 61 of the curve in the circumferential direction on the outer periphery is continuous Is formed.

The working cylinder 40 is provided with a fixing pin 44 which protrudes toward the inner direction and is inserted into the guide groove 61 to be in surface contact.

The position of the fixing pin 44 is located on the path of the guide groove 61, and is preferably fixed to the middle position of the highest point and the lowest point of the guide groove 61.

At this time, the guide groove 61 formed in the piston 60 is formed in the form of a sine curve having a period of 2πR / 2 when the radius of the piston 60 is R, the amplitude of A, The stroke distance is 2A while the piston 60 rotates one cycle.

 That is, the piston 60 is reciprocated twice while the working cylinder 40 is rotated once.

In addition, one side of the piston 60 is formed with a rotation preventing groove 62 in the longitudinal direction, the fixed cylinder 50 is formed to protrude toward the inner direction is inserted into the rotation preventing groove 62 The anti-rotation pin 53 for surface contact is provided.

Thus, the actuating cylinder 40 is rotated by the power train 70, while the piston 60 does not rotate with the actuating cylinder 40 but is merely the length of the cylinder bores 41, 51. Only move in the direction.

On the other hand, since a small amount of oil is mixed in the refrigerant acting in the compressor, it is necessary to separate it and discharge only pure refrigerant. This is because the presence of oil in the refrigeration cycle increases flow resistance, disrupts heat transfer, and lowers overall system efficiency.

Therefore, as shown in FIG. 4, the oil separator 80 is formed inside the front housing 20 with the fixed cylinder 50 and the valve plate 90 positioned in front of the fixed cylinder therebetween. have.

The oil separator 80 is configured to use the centrifugal force of the refrigerant, and as shown in FIG. 5, a first groove portion 82 having a refrigerant outlet passage 81 formed therein in the axial direction of the piston 60, and A cylinder wall 84 is formed between the second grooves 83 formed along the circumference of the first groove 82 and formed between the inner walls of the front housing 20, and the side surface of the cylinder wall 84. The coolant inflow groove 85 is formed therein, and an oil outflow passage 86 communicating with the compressor from the first groove portion 82 is formed.

Accordingly, the refrigerant introduced into the second groove 83 through the valve plate flows into the first groove 82 through the refrigerant inflow groove 85 of the cylinder wall 84.

At this time, the coolant inlet groove 85, as shown in Figure 5, when viewed in the axial direction of the piston 60, it is preferably formed inclined along the moving direction of the coolant.

This allows the refrigerant to naturally flow along the tangential direction of the circumference from the second groove portion 83 to the first groove portion 82, thereby giving a great centrifugal force to the refrigerant.

In addition, the inlet of the refrigerant inlet groove 85 is formed in a curved shape to allow a smoother inflow.

In addition, the center of the first groove 82 is preferably formed to be somewhat eccentric with respect to the center of the coolant outlet passage 81 to maximize the oil separation effect by varying the width of the coolant passage.

Hereinafter, the operation of the rotary piston compressor according to the present invention configured as described above is as follows.

First, the working cylinder 40 is rotated by the rotational power to the drive motor 71 which is the power transmission device 70.

When the working cylinder 40 rotates by the power transmission device 70, the cylinder bore of the working cylinder 40 and the fixed cylinder 50 while the piston 60 is sinusoidal by the fixing pin 44 A reciprocating motion is performed in the longitudinal direction of (41, 51).

At this time, when the piston 60 is located at the bottom dead center with respect to the working cylinder 40, that is, when the piston 60 is the suction stroke, as shown in FIG. ) And the inlet 52 of the fixed cylinder 50 coincide with each other so that the refrigerant flows into the cylinder bores 41 and 51.

In contrast, when the piston 60 is located at the top dead center with respect to the working cylinder 40, that is, when the piston 60 is in the compression stroke, as shown in FIG. The suction port 52 does not coincide, and the inside of the cylinder bores 41 and 51 is sealed so that the refrigerant is compressed by the piston 60.

At this time, the compressed refrigerant stored in the chamber 43 of the working cylinder 40 acts as a back pressure of the piston 60 to prevent the loss of the compressive force of the piston 60.

After that, when the refrigerant is compressed by the piston 60 to reach a predetermined pressure, the refrigerant compressed by the compression stroke of the piston 60 passes through the valve plate to form the second groove 83 of the oil separator 80. Flows into.

Subsequently, the refrigerant flows into the first groove 82 from the second groove 83 through the refrigerant inflow groove 85 formed in the cylinder wall 84, and the centrifugal force acts on the refrigerant.

At this time, the oil having a high density is supplied to the portion requiring lubrication through the oil outlet passage 86 formed on the sidewall of the first groove 82, and the refrigerant is cooled through the refrigerant outlet passage 81 and the discharge passage 21. Will join the cycle.

Therefore, the action of sucking the refrigerant from the suction passage 31 and compressing it by the piston 60, discharging the compressed refrigerant to the outside through the discharge passage 21, and sending the refrigerant to the next cooling cycle is repeated.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, Various modifications to the embodiments are also within the scope of the claims of the present invention.

10 cylinder block 20 front housing
21: discharge passage 30: rear housing
31: suction passage 40: working cylinder
41: cylinder bore 42: stepped portion
43: chamber 44: fixed pin
50: fixed cylinder 51: cylinder bore
52: suction port 53: anti-rotation pin
60: piston 61: guide groove
62: groove for preventing rotation 70: power transmission device
71: refrigerant outlet passage 72: motor shaft
80: oil separator 81: refrigerant flow passage
82: first groove 83: second groove
84: cylinder wall 85: refrigerant inlet groove
86: oil outflow passage 90: valve plate

Claims (13)

Cylinder block;
A front housing and a rear housing which are hermetically coupled to the front and rear of the cylinder block, respectively;
An operating cylinder rotatably received in said cylinder block;
A fixed cylinder corresponding to the working cylinder and fixed in a cylinder block;
A piston which is continuously formed in the circumferential direction of the curved guide groove in the circumferential direction and is formed with a rotation preventing groove in the longitudinal direction, the piston being reciprocally received in the cylinder bore of the working cylinder and the fixed cylinder; And
Rotary piston type compressor comprising a power transmission device for supplying rotational power to the working cylinder.
The method of claim 1,
The front piston rotary compressor, characterized in that the oil separator is formed to separate the oil contained in the introduced refrigerant to discharge only the pure refrigerant.
The method of claim 1,
The front housing is formed with a discharge passage for discharging the refrigerant,
And a suction passage through which the refrigerant flows is formed in the rear housing.
The method of claim 1,
The fixed cylinder is formed with a suction port,
The actuating cylinder is a rotary piston-type compressor, characterized in that the stepped portion is formed in communication with the upper inlet selectively in communication with the inlet.
The method of claim 1,
The lower portion of the cylinder bore of the working cylinder, the rotary piston compressor characterized in that the chamber is formed so that the compressed refrigerant introduced through the clearance between the working cylinder and the piston acts as a back pressure of the piston.
The method of claim 5,
The chamber is a rotary piston compressor, characterized in that the conical shape.
The method of claim 1,
Rotary piston type compressor, characterized in that the guide groove of the piston made of a sinusoidal curve.
The method of claim 7, wherein
The working cylinder is provided with a fixing pin which protrudes toward the inner direction and is inserted into the guide groove and in contact with the surface,
The fixed cylinder is a rotary piston type compressor, characterized in that the protruding toward the inner direction is inserted into the anti-rotation groove is provided with a anti-rotation pin for surface contact.
9. The method of claim 8,
The fixing pin is located on the path of the guide groove, the rotary piston compressor, characterized in that fixed to the middle position of the highest point and the lowest point of the guide groove.
The method of claim 7, wherein
And the guide groove is formed such that the piston reciprocates twice while the working cylinder is rotated once.
3. The method of claim 2,
The oil separator may include a cylinder wall formed between a first groove formed with a coolant outlet passage in an axial direction of the piston, and a second groove formed along a circumference of the first groove and formed between an inner wall of the front housing;
A refrigerant inlet groove formed to penetrate the side surface of the cylinder wall;
A rotary piston compressor comprising an oil outflow passage formed in communication with the compressor from the first groove.
12. The method of claim 11,
When the refrigerant inlet groove is viewed in the axial direction of the piston, the rotary piston-type compressor, characterized in that the inclination is formed along the direction of movement of the refrigerant, the inlet is curved.
12. The method of claim 11,
The center of the first groove portion is a rotary piston-type compressor characterized in that the eccentric with respect to the center of the refrigerant outflow passage so as to maximize the oil separation effect by varying the width of the refrigerant passage.













KR1020120031270A 2012-03-27 2012-03-27 Rotary piston type compressor KR20130109509A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020120031270A KR20130109509A (en) 2012-03-27 2012-03-27 Rotary piston type compressor

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Application Number Priority Date Filing Date Title
KR1020120031270A KR20130109509A (en) 2012-03-27 2012-03-27 Rotary piston type compressor

Publications (1)

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KR20130109509A true KR20130109509A (en) 2013-10-08

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107355368A (en) * 2017-07-21 2017-11-17 无锡鑫华控阀业有限公司 Oil mist separator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107355368A (en) * 2017-07-21 2017-11-17 无锡鑫华控阀业有限公司 Oil mist separator

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