KR20150081785A - Compressor check valve - Google Patents

Compressor check valve Download PDF

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Publication number
KR20150081785A
KR20150081785A KR1020140001611A KR20140001611A KR20150081785A KR 20150081785 A KR20150081785 A KR 20150081785A KR 1020140001611 A KR1020140001611 A KR 1020140001611A KR 20140001611 A KR20140001611 A KR 20140001611A KR 20150081785 A KR20150081785 A KR 20150081785A
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South Korea
Prior art keywords
resonance
suction
valve
core
hole
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KR1020140001611A
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Korean (ko)
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KR102005745B1 (en
Inventor
송세영
신정식
윤영섭
정환명
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한라비스테온공조 주식회사
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F05B2260/962—Preventing, counteracting or reducing vibration or noise by means creating "anti-noise"
    • 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

The present invention relates to a check valve for a compressor capable of reducing a flow noise of a refrigerant (P) using resonance in a specific frequency by the Helmholtz resonance effect. The check valve for a compressor (200) comprises: a valve cap (210) having a suction hole (213); a valve case (230) coupled to one side of the valve cap (210); a core (250) enabling a suction slit (231) and the suction hole (213) to selectively be communicated; a spring (S) installed in an inner space (233) of the valve case (230); and a resonance unit (270) coupled to the other side of the valve cap (210) and having a communication hole (273).

Description

[0001] COMPRESSOR CHECK VALVE [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a check valve for a compressor, and more particularly, to a check valve for a compressor capable of reducing noise caused by vibration of a core using resonance at a specific frequency by Helmholtz resonance theory.

Generally, an air conditioner for cooling and heating is installed in an automobile. Such an air conditioner includes a compressor that compresses low-temperature low-pressure refrigerant introduced from an evaporator into a high-temperature high-pressure refrigerant and sends it to a condenser. A swash plate type compressor is used.

When the compressor is driven, the temperature of the evaporator is lowered. When the compressor is stopped, the temperature of the evaporator is increased.

In the swash plate type compressor, a swash plate having an inclination angle of a predetermined angle is provided on a rotating shaft provided in a compressor, and a piston in a cylinder bore connected to the swash plate reciprocates in conjunction with rotation of the rotating shaft to compress the refrigerant.

Such swash plate type compressors include a fixed capacity type and a variable capacity type. Generally, the discharge capacity of the variable displacement swash plate type compressor is achieved by controlling the inclination angle of the swash plate. When the cooling load is increased, the inclination angle of the swash plate is increased and when the cooling load is decreased, the inclination angle of the swash plate is controlled to be decreased.

FIG. 1 is a cross-sectional view of a configuration of a conventional variable displacement swash plate type compressor, and FIG. 2 is a schematic view of a conventional check valve 20.

2, the check valve 20 includes a valve case 23 having a bottom surface and a cylindrical outer circumferential surface, and a core 25 movably installed in the inner space of the valve case 23 .

A plurality of suction slits (29) are formed on the outer peripheral surface of the valve case (23). The refrigerant flowing into the valve case 23 is transmitted through the suction slit 29. [ The suction slits 29 are arranged at regular intervals and penetrate the valve case 23 in the longitudinal direction.

The core 25 is installed movably in the valve case 23 and is formed in a substantially cylindrical shape.

The core (25) is elastically supported by a spring (S) provided in the inner space, and receives the elastic force by the spring (S) toward the inlet side of the valve case (23).

When the compressor is operated, the check valve (20) opens the core (25), and the refrigerant moves from the outside of the compressor to the suction chamber through the suction port. If the compressor is not operated, the core 25 is closed to block the refrigerant from moving from the outside of the compressor to the suction chamber through the suction port.

However, the check valve of the conventional configuration as described above has a drawback in that the pressure difference between the core 25 itself and the core 25 and the valve case 23, and the pressure difference between the elastic force of the spring S and the refrigerant suction pressure, There is a problem that a resonance phenomenon occurs and a vibration noise due to vibration of the core 25 occurs.

Korean Patent Publication No. 2013-0027263 Korean public patent 2011-0062109

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and it is an object of the present invention to provide a check valve having a resonance part according to the Helmholtz resonance theory in a check valve to eliminate resonance phenomenon of a core at a specific frequency, .

In order to achieve the above object, according to a first aspect of the present invention, there is provided a check valve for a compressor, which is installed in a suction port to suck refrigerant into a suction chamber and selectively blocks the flow of the refrigerant, A valve case coupled to one side of the valve cap and having a plurality of suction slits penetrated therethrough; a core movably installed in an inner space of the valve case and selectively communicating the suction slit and the suction hole; And a resonance part installed in an inner space of the valve case to elastically support the core and a resonance part coupled to the other side of the valve cap and having a communication hole communicating the suction hole and the suction port .

The resonance unit may include a resonance chamber formed by a first support wall having a cylindrical shape extending to the outer periphery of the valve cap and a second support wall formed on the first support wall at a predetermined interval, And a resonance hole communicating the resonance chamber and the communication hole.

At this time, the resonance holes may be plural and be formed diagonally in the direction of the valve cap on the suction flow path side.

According to a second aspect of the present invention, there is provided a check valve for a compressor, which is installed in a suction port for sucking refrigerant into a suction chamber and selectively blocks the flow of the refrigerant, the valve cap comprising a suction hole, A valve case coupled to one side of the valve case and formed to penetrate a plurality of suction slits, a core movably installed in an inner space of the valve case and selectively communicating the suction slit and the suction hole, And a spring installed in the inner space to elastically support the core, wherein the valve cap includes a resonance part inside the wall.

In this case, the resonance unit may include a resonance chamber in a hollow space formed along the circumferential direction of the valve cap in the wall, and a resonance hole communicating the resonance chamber and the suction hole.

The present invention has a resonance part according to the Helmholtz resonance theory in a check valve to eliminate the resonance phenomenon of the core at a specific frequency caused by the weight of the core, the frictional force between the core and the valve case, and the pressure difference between the elastic force of the spring and the refrigerant suction pressure So that the vibration noise is remarkably reduced.

1 is a conceptual view showing a conventional variable displacement swash plate type compressor,
2 is a perspective view showing a conventional check valve,
3 is a conceptual view showing a variable displacement swash plate type compressor of the present invention,
4 is a perspective view showing a check valve according to an embodiment of the present invention separated from a compressor,
5 is a bottom view showing a check valve according to an embodiment of the present invention;
6 is a cross-sectional view of a check valve according to an embodiment of the present invention,
7 and 8 are operational states of a check valve according to an embodiment of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS The objectives, specific advantages and novel features of the present invention will become more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which: FIG. In the following description of the present invention, detailed description of known related arts will be omitted when it is determined that the gist of the present invention may be unnecessarily obscured by the present invention. Also, the thickness of the lines and the size of the components shown in the drawings may be exaggerated for clarity and convenience of explanation. In addition, terms used are terms defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be based on the entire contents of the present specification.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. FIG. 3 is a conceptual diagram of a compressor according to an embodiment of the present invention.

3, the compressor 100 according to an embodiment of the present invention includes a cylinder block 110 having a plurality of cylinder bores 111 and a crank chamber 110 coupled to the front of the cylinder block 110. [ And a rear housing 150 coupled to the rear of the cylinder block 110 to form a suction chamber 151 and a discharge chamber 153. The front housing 130 includes a front housing 130,

In the cylinder block 110, a plurality of cylinder bores 111 are radially formed at regular intervals. The cylinder bore 111 is a part for compressing the refrigerant P and the piston 114 is accommodated in the cylinder bore 111 so that the piston 114 reciprocates linearly and compresses the refrigerant P in the space therebetween . The cylinder bore 111 is formed in a cylindrical shape so as to pass through the cylinder block 110, and the piston 114 is formed into a cylindrical shape corresponding to the cylinder bore 111.

The front housing 130 is coupled to one side of the cylinder block 110, that is, the front side. The rear portion of the front housing 130 is recessed to engage with the cylinder block 110 to form a crank chamber 131 therein. A driving unit for reciprocating the piston 114 is installed in the crank chamber 131 formed between the cylinder block 110 and the front housing 130.

A rear housing 150 is installed on the opposite side of the cylinder block 110 on which the front housing 130 is installed. A suction chamber 151 for sucking refrigerant P is formed at the center of a surface of the rear housing facing the cylinder block 110. The suction chamber 151 serves to temporarily store the refrigerant P to be compressed into the cylinder bore 111.

A suction port 155 is formed in the rear housing 150 to transmit the refrigerant P to the suction chamber 151.

The suction port 155 is formed to penetrate the outside of the compressor 100 and the inside of the suction chamber 151.

A discharge chamber 153 through which the refrigerant P compressed by the cylinder bore 111 is discharged is formed in the rear housing 150. The discharge chamber 153 is formed at a portion radially outward of the rear housing 150 at a portion corresponding to the cylinder bore 111. The discharge chamber 153 serves to temporarily store refrigerant compressed and discharged from the cylinder bore 111.

A valve assembly 170 is provided between the cylinder block 110 and the rear housing 150 for interrupting the flow of the refrigerant P between the suction chamber 151 and the discharge chamber 153. The suction chamber 151 and the discharge chamber 153 are selectively communicated with the cylinder bores 111 due to a pressure difference with the cylinder bores 111 to move the refrigerant P. [

In order to adjust the inclination angle of the swash plate 126, a control valve 180 is installed on one side of the rear housing 150.

In the compressor 100 of this type, the check valve 190 is installed at one side of the suction port 155 on the suction flow path communicating the suction port 155 and the suction chamber 151.

The conventional check valve 20 has a resonance phenomenon at some frequencies due to the weight of the core 25, the frictional force between the core 25 and the valve case 23, and the pressure difference between the elastic force of the spring S and the refrigerant suction pressure And vibration noise due to the vibration of the core 25 is generated. (See Fig. 2)

4 and 5, the check valve 200 according to an embodiment of the present invention includes a valve cap 210, a valve case 230, a core 250, A spring S and a resonance unit 270.

The valve cap 210 is formed with a suction hole 213 through which the refrigerant P flowing from the suction port flows. The valve cap 210 is annular and the inner diameter of the valve cap 210 is preferably smaller than the diameter of the core 250 described later. This is to prevent the core 250 from being separated from the valve case 230. That is, the valve cap 210 functions as a stopper for regulating the movement of the core 250.

The valve case 230 is coupled to one side of the valve cap 210 and has a plurality of suction slits 231 through the outer circumferential surface thereof. The valve case 230 has a cylindrical shape and has an opening in the suction port direction and is connected to one side of the valve cap 210.

A plurality of suction slits 231 are formed in the outer circumferential surface of the valve case 230 along the longitudinal direction and the refrigerant P introduced from the suction port through the suction slit 231 is transmitted to the suction chamber.

The core 250 is movably installed in the inner space 233 of the valve case 230. The core 250 has a substantially cylindrical shape and is elastically supported by a spring S to be described later.

The core 250 reciprocates according to a pressure difference between the elastic force of the spring S and the suction pressure of the refrigerant P to selectively block the flow of the refrigerant P. [

At this time, a plurality of communication grooves 251 may be formed in the longitudinal direction on the outer circumferential surface of the core 250 at predetermined intervals, and the communication grooves 251 may be formed in the suction port and the suction port So that the refrigerant (P) flows into the suction chamber through the slit (231).

The spring S is installed in the inner space 233 of the valve case 230 to elastically support the core 250. Specifically, one side of the spring S supports the bottom surface of the core 250, so that the core 250 receives an elastic force in a direction blocking the suction port.

The other side of the spring (S) is fixed to the bottom surface of the valve case (230). At this time, a support boss 235 protruding from the bottom surface of the valve case 230 is inserted to prevent the spring S from flowing.

The resonance unit 270 has a communication hole 273 which is coupled to the other side (suction port direction) of the valve cap 210 and communicates with the suction hole 213 and the suction port. Specifically, the resonance unit 270 has a substantially cylindrical shape, and a communication hole 273 is formed through the resonance unit 270.

At this time, the cross-section of the communication hole 273 may be formed to correspond to the valve cap 210, and the resonance part 270 and the valve cap 210 may be integrally injection-molded.

The resonator 270 is a Helmholtz resonator according to the Helmholtz resonance theory. The Helmholtz resonator is widely used in recent years due to its inherent characteristic of effectively reducing noise at a specific frequency. The resonator 270 is configured to vary the resonance frequency over a wide frequency range .

Such a Helmholtz resonator has a structure with a short neck and a large volume connected to a conduit, that is, a resonance space, and its resonance frequency is calculated by the following equation.

Figure pat00001

Here, f is the resonance frequency of Helmholtz, C is the velocity of the fluid, S is the cross-sectional area of the neck communicating with the resonance space formed on the side of the flow path, L is the length of the neck, and V is the volume of the resonance space.

Since the resonant frequency of the Helmholtz resonator can be varied by the above three variables, the variable frequency bandwidth can be widened.

The present invention realizes the Helmholtz resonator principle as described above, thereby eliminating the resonance phenomenon of the core 250 at a specific frequency, thereby significantly reducing vibration noise.

The resonance unit 270 includes a resonance chamber 274 and a resonance hole 275. The resonance chamber 274 corresponds to the resonance space of the Helmholtz resonator, and the resonance hole 275 corresponds to the resonator cavity formed on the flow path side of the Helmholtz resonator to communicate the resonance space.

The volume of the resonance chamber 274 and the cross-sectional area of the resonance hole 275 are calculated inversely through the above equation according to the frequency at which the resonance phenomenon occurs.

The resonance chamber 274 includes a first support wall 274a having a cylindrical shape extending from the outer periphery of the valve cap 210 and a second support wall 274b formed inside the first support wall 274a at predetermined intervals And is formed by the second support wall 274b.

At this time, the resonance chamber 274 is a space having an annular cross section between the walls of the first and second support walls 274a and 274b, and may be a resonance chamber 274 integrally formed with the first support wall 274a, 274a and the second support wall 274b.

At this time, the ceiling of the resonance chamber 274 is sealed by the ceiling surface, and the bottom of the resonance chamber 274 is sealed by the upper surface of the valve cap 210.

The resonance hole 275 is formed to penetrate through the second support wall 274b with a small hole communicating the resonance chamber 274 and the communication hole 273.

At this time, the resonance hole 275 may be plural, and is formed diagonally in the direction of the valve cap 210 from the suction port side. This is to allow the refrigerant P to flow into the resonance chamber 274 when the refrigerant P is sucked into the check valve 200 through the suction port.

Hereinafter, the operation of the check valve 200 according to the present invention having the above-described configuration will be described with reference to FIG.

When a part of the refrigerant P flowing to the check valve 200 through the suction port flows into the resonance chamber 274 through the narrow neck of the resonance hole 275, The phase shift is generated and the resonance phenomenon is extinguished to reduce the vibration of the core 250.

7 is a schematic view of a check valve 200 according to another embodiment of the present invention.

The check valve 200 for a compressor according to the present embodiment includes a valve cap 210, a valve case 230, a core 250, and a spring S.

The check valve 200 for a compressor according to the present embodiment is the same as the previous embodiment except for the configuration of the valve cap 210, and the same constitution is replaced with the description of the previous embodiment.

The valve cap 210 includes a resonance part 270 inside the wall of the valve cap 210. Advantageously, the resonance unit 270 of the previous embodiment is different from the valve cap 210 in that it is coupled to the other side of the valve cap 210.

The resonance unit 270 includes a resonance chamber 274 and a resonance hole 275. The resonance unit 270 is disposed inside the wall of the valve cap 210 along the circumferential direction of the valve cap 210 And the resonance hole 275 is formed to penetrate the inner wall to communicate with the resonance chamber 274 and the suction hole 213. [

At this time, the ceiling of the resonance chamber 274 is sealed by the ceiling surface, and the bottom is sealed by the upper surface of the valve case 230.

Also, the resonance hole 275 may be formed diagonally in the direction of the valve case 230 from the suction port side, or may be formed in plural.

The resonance unit 270 is a Helmholtz resonator according to the Helmholtz resonance theory. The resonance unit 270 reduces the vibration noise by eliminating the resonance phenomenon of the core 250 at a specific frequency.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it will be understood by those of ordinary skill in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. It is to be understood that the invention may be variously modified and changed.

100: compressor 110: cylinder block 111: cylinder bore
114: piston 130: front housing 131: crank chamber
150: rear housing 151: suction chamber 153: discharge chamber
155: Suction port 170: Valve assembly 180: Control valve
200: check valve 210: valve cap 213: suction hole
230: valve case 231: suction slit 233: inner space
235: support boss 250: core 251: communicating groove
270: resonance part 273: communication hole 274: resonance chamber
274a: first support wall 274b: second support wall 275: resonance hole
P: Refrigerant S: Spring

Claims (5)

A check valve (200) for a compressor installed in a suction port for sucking refrigerant (P) into a suction chamber and selectively blocking the flow of the refrigerant (P)
A valve cap 210 in which a suction hole 213 is formed;
A valve case 230 coupled to one side of the valve cap 210 and having a plurality of suction slits 231 formed therethrough;
A core 250 which is movably installed in the inner space 233 of the valve case 230 and selectively communicates the suction slit 231 with the suction hole 213;
A spring (S) installed in the inner space (233) of the valve case (230) to elastically support the core (250); And
And a resonance part coupled to the other side of the valve cap and having a communication hole communicating the suction hole and the suction port.
The method according to claim 1,
The resonance unit 270 includes:
A first support wall 274a having a cylindrical shape extending to the outer periphery of the valve cap 210 and a second support wall 274b formed on the inner side at a predetermined distance from the first support wall 274a, A resonance chamber 274 formed by the resonator 274; And
And a resonance hole (275) communicating the resonance chamber (274) and the communication hole (273).
3. The method of claim 2,
Wherein the resonance holes (275) are formed in a plurality of diagonals in the direction of the valve cap (210) from the suction port side.
A check valve (200) for a compressor installed in a suction port for sucking refrigerant (P) into a suction chamber and selectively blocking the flow of the refrigerant (P)
A valve cap 210 in which a suction hole 213 is formed;
A valve case 230 coupled to one side of the valve cap 210 and having a plurality of suction slits 231 formed therethrough;
A core 250 which is movably installed in the inner space 233 of the valve case 230 and selectively communicates the suction slit 231 with the suction hole 213; And
And a spring (S) installed in the inner space (233) of the valve case (230) to elastically support the core (250)
Wherein the valve cap (210) comprises a resonance part (270) within the wall.
5. The method of claim 4,
The resonance unit 270 includes:
A resonance chamber (274) having a space formed in the wall along the circumferential direction of the valve cap (210); And
And a resonance hole (275) communicating the resonance chamber (274) and the suction hole (213).
KR1020140001611A 2014-01-07 2014-01-07 Compressor check valve KR102005745B1 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107642479A (en) * 2016-07-21 2018-01-30 翰昂汽车零部件有限公司 Internally-damped drawing-in type damping unit is carried for air conditioner compressor of vehicle
KR20190100054A (en) * 2018-02-19 2019-08-28 한온시스템 주식회사 Device for damping pressure pulsations for a compressor of a gaseous fluid

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Publication number Priority date Publication date Assignee Title
JP2000161216A (en) * 1998-11-27 2000-06-13 Sanden Corp Reciprocating compressor
JP2008223757A (en) * 2007-02-16 2008-09-25 Toyota Industries Corp Device for reducing pulsation in variable displacement compressor
US20110062109A1 (en) 2008-11-06 2011-03-17 Richard Lawrence Horstman Container with an Integrated Spout
US20130027263A1 (en) 2011-07-29 2013-01-31 Toshiba Tec Kabushiki Kaisha Antenna apparatus

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000161216A (en) * 1998-11-27 2000-06-13 Sanden Corp Reciprocating compressor
JP2008223757A (en) * 2007-02-16 2008-09-25 Toyota Industries Corp Device for reducing pulsation in variable displacement compressor
US20110062109A1 (en) 2008-11-06 2011-03-17 Richard Lawrence Horstman Container with an Integrated Spout
US20130027263A1 (en) 2011-07-29 2013-01-31 Toshiba Tec Kabushiki Kaisha Antenna apparatus

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107642479A (en) * 2016-07-21 2018-01-30 翰昂汽车零部件有限公司 Internally-damped drawing-in type damping unit is carried for air conditioner compressor of vehicle
CN107642479B (en) * 2016-07-21 2018-11-23 翰昂汽车零部件有限公司 Internally-damped drawing-in type damping unit is had for air conditioner compressor of vehicle
US10591074B2 (en) 2016-07-21 2020-03-17 Hanon Systems Suction dampening device with internal dampening for vehicle air conditioning compressor
KR20190100054A (en) * 2018-02-19 2019-08-28 한온시스템 주식회사 Device for damping pressure pulsations for a compressor of a gaseous fluid
US10935015B2 (en) 2018-02-19 2021-03-02 Hanon Systems Device for damping pressure pulsations for a compressor of a gaseous fluid

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