KR102485663B1 - Discharge check valve for compressor - Google Patents

Abstract

The present invention relates to a discharge check valve and a compressor including the same. To this end, the present invention relates to a discharge check valve capable of reducing weight and manufacturing cost by making a main component of the discharge check valve with plastic, which is an example of a non-metallic material, and the same. It is about a compressor that includes.

Description

Discharge check valve and compressor including the discharge check valve {Discharge check valve for compressor}

The present invention relates to a discharge check valve for a compressor, and more particularly, to a discharge check valve that is lightweight by improving problems caused by weight and vibration, and a compressor including the same.

In general, an air conditioning unit (A/C) for cooling and heating the interior of a vehicle is installed. As a component of a cooling system, such an air conditioner includes a compressor that compresses a low-temperature, low-pressure gaseous refrigerant introduced from an evaporator into a high-temperature, high-pressure gaseous refrigerant and sends it to a condenser.

Compressors include a reciprocating type compressing refrigerant by reciprocating motion of a piston and a rotary type compressing refrigerant by rotational motion according to a compression method. In the reciprocating type, there is a crank type that uses a crank to transmit to a plurality of pistons according to the transmission method of the drive source, and a swash plate type that transmits to a rotating shaft on which a swash plate is installed. The rotary type includes a vane rotary type using a rotating rotary shaft and a vane, and a scroll type using an orbiting scroll and a fixed scroll.

Among the above-described reciprocating compressors, the swash plate type compressor rotates the swash plate while the rotating shaft is rotated by the driving force of the engine, and compresses the refrigerant by allowing the piston to reciprocate according to the rotation of the swash plate.

In general, a variable displacement swash plate type compressor means a compressor configured such that the inclination angle of the swash plate can be changed according to the compression capacity of the swash plate in the swash plate type compressor.

The swash plate type compressor is driven according to the on/off of the air conditioner switch. When the compressor is driven, the temperature of the evaporator decreases, and when the compressor is stopped, the temperature of the evaporator rises. When the air conditioner switch is turned on, the swash plate compressor discharges high-pressure refrigerant to the condenser outside the compressor according to the relative motion of the piston, the rotating shaft and the swash plate.

1 is a cross-sectional view of a conventional variable displacement swash plate compressor, and a schematic configuration of the conventional variable displacement swash plate compressor will be described with reference to FIG. 1.

The cylinder block 10 forms part of the exterior and skeleton of the compressor 1, and a center bore 12 is formed through the center of the cylinder block.

A rotating shaft 40 is rotatably installed in the center bore 12, and a plurality of cylinder bores 11 are formed to radially penetrate the cylinder block 10 while surrounding the center bore 12. The cylinder bore 11 is installed so that the piston 13 can linearly reciprocate therein.

Preferably, the piston 13 is formed in a cylindrical shape, and the cylinder bore 11 is formed in a cylindrical space to correspond to the shape of the piston 13. Accordingly, the piston 13 compresses the refrigerant sucked through the suction chamber 31 while linearly reciprocating inside the cylinder bore 11 .

In the variable displacement swash plate type compressor, a front housing 20 is installed at one end of the cylinder block 10. The front housing 20 is recessed on the side facing the cylinder block 10, forming a crank chamber 21 inside with the cylinder block 10, and the crank chamber 21 is airtight with the outside. .

A pulley 60 is rotatably installed on one side of the front housing 20, and the pulley 60 serves to rotate the rotating shaft by receiving the driving force of the engine.

The rear housing 30 is installed so that the cylinder block 10 faces the front housing 20 at a facing position. A suction chamber 31 is formed in the rear housing 30 so as to communicate with the suction port 32 through the suction passage 33 on the inside by a circular partition wall formed therein.

The suction chamber 31 serves to deliver the refrigerant to be compressed into the cylinder bore 11 . In addition, a discharge chamber 34 is formed outside the rear housing 30 by a circular partition wall formed therein. The discharge chamber 34 serves to temporarily store the compressed refrigerant before discharging it to the outside of the compressor.

The rotating shaft 40 is rotatably installed through the center bore 12 and the crank chamber 21 of the front housing 20 . The rotating shaft 40 is rotated by driving force transmitted from an engine, and a rotor 41 is installed.

The rotor 41 passes through the center of the rotation shaft 40 and is installed in the crank chamber 21 to rotate integrally with the rotation shaft 40 . The rotor 41 is fixedly installed to the rotating shaft 40 in a substantially disk shape, and a hinge arm 42 is formed to protrude from one surface of the rotor 41 .

The swash plate 44 is installed to be connected to the rotating shaft 40 by the shoe 45, and the swash plate 44 is hinged with the rotor 41 to rotate together with the rotor 41. The swash plate 44 is installed to have a variable angle to the rotating shaft 40, and is installed at a position between a state orthogonal to the longitudinal direction of the rotating shaft 40 and a state inclined at a predetermined angle with respect to the rotating shaft 40 do.

In addition, a semi-reflexive spring 43, which is a coil spring, is installed on the rotating shaft 40 so as to surround the rotating shaft 40. The anti-reflection spring 43 exerts an elastic force between the rotor 41 and the swash plate 44. That is, the anti-reflection spring 43 functions to apply an elastic force in a direction in which the inclination angle of the swash plate 44 decreases and absorbs the force acting on the swash plate 44 when the operation of the compressor 1 is stopped. .

A valve assembly 50 is installed between the cylinder block 10 and the rear housing 30 to control the flow of refrigerant.

2, a discharge check valve (60 ) is installed by press-fitting.

The discharge check valve 60 is installed in the rear housing 30. In order to damp the discharge pulsation caused by the movement of the refrigerant, the body portion constituting the exterior is made of metal, which causes a problem of increasing manufacturing cost.

In addition, a problem in that the discharge check valve 60 is stuck after being forcibly press-fitted into the rear housing 60 is caused, and a countermeasure for this is required.

Korean Patent Publication No. 10-2003-0092167

The present invention has been made to solve the above problems, and provides a discharge check valve capable of promoting stable operation by minimizing vibration and noise due to discharge pulsation during operation of a variable swash plate type compressor and a compressor including the same. .

In order to achieve the above object, a discharge check valve according to an embodiment of the present invention and a compressor including the same include a front head (110); a cylinder block 150 coupled to a surface facing the front head 110; a rear head 120 coupled to a surface facing the cylinder block 150 and having a suction chamber 122 and a discharge chamber 124; And a discharge check valve 200 is provided in the passage 124a formed in the discharge chamber 123 to reduce pulsation caused by the discharge of the refrigerant into the discharge chamber 124 .

And, the discharge check valve 200 is provided with a hooking part 212 at one end so as to be held in the passage 124a formed in the discharge chamber 124, and an opening 216 in the circumferential direction for the movement of the refrigerant. Formed body portion 210; A core 300 movably inserted in the axial direction from the inside of the body 210; and an elastic member 400 inserted into the body 210 to elastically support one side of the core 300 and elastically support one side of the passage 124a by contacting the other side.

The body portion 210 is formed with an expansion portion 214 whose diameter is increased outwardly at the lower side in the axial direction.

The discharge check valve 200 is molded of resin, and an insertion groove 125 is formed in the passage 124a at a position facing the locking portion 212 .

The body part 210 is provided with an O-ring 50 for sealing in an axial direction.

A position fixing part 500 facing the body part 210 in the axial direction and protruding from the discharge passage 124a to be inserted into the inside of the elastic member 400 to fix the position of the elastic member 400 is provided

The position fixing part 500 extends to the inside of the body part 210 and is inserted into the inside of the elastic member 400 .

The position fixing part 500 is concavely formed on one surface of the passage 124a so that the elastic member 400 is accommodated in the position fixing part 500 .

The core 300 is configured such that one side of the core 300 is partially exposed from the body 210 to the outside of the extension 214 when it is moved toward the lower side of the body 210 .

According to an embodiment of the present invention, vibration and noise due to discharge pulsation can be minimized by stably inducing a damping operation according to the discharge pulsation phenomenon generated during operation of the variable swash plate type compressor.

Embodiments of the present invention can reduce the manufacturing cost by reducing the manufacturing cost and weight of the discharge check valve.

Embodiments of the present invention can maintain a fixed position of the elastic member provided in the discharge check valve at all times, so that stable damping can be maintained regardless of rapid changes in pulsating pressure.

1 is a cross-sectional view showing a conventional variable swash plate type compressor.
Figure 2 is a view showing a discharge check valve provided in Figure 1;
3 is a cross-sectional view showing a variable swash plate type compressor according to an embodiment of the present invention.
4 is a cross-sectional view of a discharge check valve according to an embodiment of the present invention.
5 is a front view of a discharge check valve according to an embodiment of the present invention.
Figure 6 is a cross-sectional view showing another embodiment of the core shown in Figure 4;
7 is a cross-sectional view of an operating state of a discharge check valve according to an embodiment of the present invention.
8 is a view showing a state in which an elastic member is supported in a position fixing unit according to another embodiment of the present invention.

Since the present invention can make various changes and have various embodiments, specific embodiments are illustrated in the drawings and described in detail. However, this is not intended to limit the present invention to specific embodiments, and should be understood to include all modifications, equivalents, and substitutes included in the spirit and scope of the present invention. The thickness of lines or the size of components shown in the accompanying drawings may be exaggerated for clarity and convenience of description.

In addition, terms to be described later are terms defined in consideration of functions in the present invention, which may vary according to the intention of a user or operator or a precedent. Therefore, definitions of these terms should be made based on the content throughout this specification.

Hereinafter, preferred embodiments according to the present invention will be described in detail with reference to the accompanying drawings. For reference, FIG. 3 is a cross-sectional view showing a variable swash plate compressor according to an embodiment of the present invention, FIG. 4 is a cross-sectional view of a discharge check valve according to an embodiment of the present invention, and FIG. 5 is an embodiment of the present invention. This is a front view of the discharge check valve by

3 to 6, the variable swash plate type compressor according to the present embodiment includes a front head 110 and a cylinder block 150 coupled to a surface facing the front head 110. ), and a rear head 120 coupled to a surface facing the cylinder block 150 and equipped with a suction chamber 122 and a discharge chamber 124 is provided.

A rotating shaft 2 is rotatably installed in the center bore, and a plurality of cylinder bores are formed to penetrate the cylinder block 150 radially while surrounding the center bore.

The cylinder bore is installed so that the piston 4 can linearly reciprocate therein, and the swash plate 3 is coupled to the rotation shaft 2.

The discharge check valve 200 is installed in the passage 124a to reduce the pulsation caused by the discharge of the refrigerant in the discharge chamber 124 and minimizes the discharge pulsation to reduce vibration or noise generated when the variable swash plate compressor operates. can be suppressed

The discharge check valve 200 is molded of resin, has a hooking part 212 at one end so as to be held in the passage 124a formed in the discharge chamber 124, and extends outward at the lower side in the axial direction. An expansion part 214 having an increased diameter is formed, and a body part 210 having an opening 216 formed in a circumferential direction for movement of the refrigerant is provided.

Since the body part 210 uses a resin rather than a steel material, processing and molding can be performed more easily than steel. In particular, since the weight of the body portion 210 is reduced compared to that of steel, weight reduction may be achieved.

Since the body part 210 is formed of a heat-resistant resin, it is not affected by the temperature change of the refrigerant and maintains a constant state at all times. The body portion 210 may be stable in terms of durability in that it does not expand or contract under various temperature conditions of the refrigerant and maintains a constant shape.

In particular, in this embodiment, since the body portion 210 is made of the above-described configuration, manufacturing costs can be reduced compared to metal materials.

The body portion 210 is movably inserted in the axial direction from the inside, and is inserted into the core 300 molded of resin and the inside of the body portion 210 to elastically support one side of the core 300, The other side is provided with an elastic member 400 elastically supported in contact with one surface of the passage 124a.

For example, the hooking portion 212 protrudes outward from an upper radial direction based on an axial direction of the body portion 210 . The locking part 212 is provided to prevent movement due to fixing the position of the body part 210 and pulsation of the refrigerant.

A refrigerant inlet hole 211 is formed in the center of the upper surface of the body part 210 for the movement of refrigerant in the axial direction, and after the refrigerant flows in through the refrigerant inlet hole 211, the passage 124a passes through the opening 216. ), it is possible to reduce the pulsation noise caused by the movement of the refrigerant.

In the body part 210 according to the present embodiment, an insertion groove 125 is formed in the passage 124a at a position facing the locking part 212 to fix the position. Since the insertion groove 125 is provided for fixing the body part 210 when a worker installs the discharge check valve 200, it can be easily inserted into the passage 124a.

The body part 210 according to this embodiment is provided with an O-ring 50 for sealing in the axial direction. The O-ring 50 allows the refrigerant to move only through the refrigerant inlet hole 211 so that the stable pulsation pressure according to the film movement of the refrigerant can be adjusted.

One or two or more O-rings 50 may be provided, and the number is not particularly limited.

The core 300 is located inside the body 210 and is moved in the axial direction by the refrigerant introduced through the refrigerant inlet hole 211 according to the pressure fluctuation of the refrigerant. When the pressure of the refrigerant is not applied, the core 300 blocks the open area of the opening 216 so that the refrigerant does not move.

When the core 300 is moved in the axial direction of the body 210 by the pressure of the refrigerant, it moves downward at 6 o'clock in the drawing while elastically compressing the elastic member 400 to be described later.

In this case, since the opening 216 is opened, the refrigerant is moved to the passage 124a, so that pulsation caused by the movement of the refrigerant can be minimized.

In the expansion part 214 according to the present embodiment, the elastic member 400 moves the core 300 from the rear of the core 300 (6 o'clock position in FIG. 4) to the front (12 o'clock position in FIG. 4) by increasing the area. ) is formed to increase the force of the ball.

The elastic member 400 is configured with an increased spring constant to support the core 300 or, as described above, the area of the extension part 214 is increased to increase the support capacity for the core 300. can be configured.

As described above, the elastic member 400 increases the cost of specification change when the spring constant is increased, and unexpected noise amplification may occur due to overlap with the driving frequency generated during operation of the variable swash plate type compressor. problems can arise.

In this embodiment, the spring constant of the elastic member 400 is reduced so that the above problems do not occur, but the spring constant is changed so that noise due to overlapping with the driving frequency generated during operation of the variable swash plate compressor is not amplified, and insufficient damping The force can stably maintain the support capacity for the core part 300 through an increase in the area of the expansion part 214 .

That is, since the force applied to the core part 300 is a force obtained by adding the elastic force of the elastic member 400 and the pressure applied to the expansion part 214 having an expanded diameter, the spring constant of the elastic member 400 It is possible to achieve stable operation of the discharge check valve 200 without increasing , and it is possible to prevent a phenomenon that coincides with the driving frequency of the variable swash plate type compressor.

In this embodiment, the position fixing part protrudes from the discharge passage 124a and is inserted into the inside of the elastic member 400 while facing the body part 210 in the axial direction for fixing the position of the elastic member 400. 500 is provided.

Since the position fixing part 500 is inserted into the elastic member 400 with a predetermined length, the elastic member 400 is fixed in position, and even when elastically deformed by the core 300, the body part ( 210) can be prevented from escaping to the outside.

The position fixing part 500 extends to a length shorter than the height of the extension part 214 when it extends to the inside of the body part 210 . When the core 300 is moved in the axial direction of the body part 210, the position fixing part 500 preferably does not come into direct contact with it.

Referring to FIG. 6 attached, the core 300 may also be of a type in which a groove 310 recessed inwards is formed on the lower surface based on the drawing so as to prevent direct contact with the position fixing part 500.

The groove part 310 may have a diameter similar to or the same as the radius of the elastic member 400, and when the core 300 moves downward toward the position fixing part 500, the lower surface of the core 300 It is possible to prevent a phenomenon in which the upper part of the position fixing part 500 is directly contacted.

Therefore, while the core 300 elastically compresses the elastic member 400 to damp the rapid pressure fluctuation of the refrigerant, noise or malfunction due to interference with the position fixing unit 500 is prevented and safe damping due to discharge pulsation can help

The elastic member 400 has a wire diameter of 0.45, a central diameter of 5.7, an outer diameter of 6.15, an inner diameter of 5.25, an effective number of turns of 9.5, a spring constant of 20.4 gf/mm, and a natural frequency of 115.58. characterized in that it is Hz.

The wire diameter, outer diameter, effective number of turns, and spring constant of the elastic member 400 are reduced compared to specifications used in the related art.

For example, the conventional elastic member has a wire diameter of 0.5, a center diameter of 5.7, an outer diameter of 6.2, an inner diameter of 5.2, an effective number of turns of 10.5, a spring constant of 28.1 gf/mm, and a natural frequency of 136.76. Hz is maintained.

In this way, when comparing the detailed specifications of the elastic member 400 according to the present embodiment and the conventional elastic member, it can be seen that the natural frequency of the elastic member 400 of the present invention is significantly different.

The natural frequency of the elastic member 400 is maintained as low as possible so as not to overlap with the frequency generated when the variable swash plate type compressor is operated and the frequency generated when the engine provided in the vehicle is operated Reduce unnecessary vibration noise It is advantageous for the stable operation of the core 300, and it is possible to prevent occurrence of vibration due to overlap with the drive frequency of the variable swash plate type compressor.

For this purpose, the present embodiment changes the detailed specifications so that the natural frequency of the elastic member 400 is kept lower than that of the conventional elastic member as described above, so that the driving frequency generated while the variable swash plate type compressor is operated and the engine provided in the vehicle It is possible to reduce the occurrence of vibration to a minimum by not overlapping with the frequency generated during operation.

Referring to the attached FIG. 7 , when the core 300 moves toward the lower side of the body part 210 at maximum, one side is partially exposed from the body part 210 to the outside of the extension part 214 .

The core 300 may have a different moving distance in the axial direction of the body part 210 due to the refrigerant according to pressure fluctuations of the refrigerant, but when the maximum pulsating pressure is applied to the core 300, the expansion part 214 A lower end portion may be partially exposed to the outside.

For example, when discharge pulsation occurs in a variable swash plate type compressor, the refrigerant moves along the arrow direction via the inside of the body 210, and the core 300 elastically compresses and deforms the elastic member 400 in the arrow direction. Since it is moved, it is possible to stably dampen sudden pressure fluctuations and minimize vibration and noise generated from the variable swash plate type compressor.

Therefore, the core 300 can stably operate with respect to various fluctuations of the refrigerant, and through this, vibration and noise due to discharge pulsation can be minimized.

8 is a view showing a state in which an elastic member is supported in a position fixing unit according to another embodiment of the present invention.

The position fixing part 500 according to this embodiment may be formed concave so that the lower side of the elastic member 400 is partially inserted into the position fixing part 500 for stable support of the elastic member 400. there is.

In this case, the elastic member 400 can be positioned in the concave position of the position fixing part 500, and the position deviation does not occur due to elastic deformation and the installed state is stably maintained.

As described above, the present invention has been described with reference to the embodiments shown in the drawings, but these are merely exemplary, and various modifications and other equivalent embodiments will be made by those skilled in the art in the field to which the technology belongs. You will understand that it is possible. Therefore, the true technical protection scope of the present invention should be determined by the claims below.

50 : O-ring
200: valve discharge check valve
210: body part
214: extension
300: core
400: elastic member
500: position fixing part

Claims (8)

Front head 110;
a cylinder block 150 coupled to a surface facing the front head 110;
a rear head 120 coupled to a surface facing the cylinder block 150 and having a suction chamber 122 and a discharge chamber 124;
A discharge check valve 200 is provided in the passage 124a formed in the discharge chamber 124 to reduce pulsation caused by the discharge of the refrigerant in the discharge chamber 124,
The discharge check valve 200 is provided with a hooking part 212 at one end so as to be held in the passage 124a formed in the discharge chamber 124, and an opening 216 formed in the circumferential direction for the movement of the refrigerant. body portion 210;
A core 300 movably inserted in the axial direction from the inside of the body 210; and
An elastic member 400 inserted into the body portion 210 to elastically support one side of the core 300 and elastically supported by the other side in contact with one surface of the passage 124a,
The body portion 210 is formed with an expansion portion 214 having an increased diameter outwardly at the lower side in the axial direction,
The force applied to the core 300 is a force obtained by adding the elastic force of the elastic member 400 and the pressure applied to the expansion part 214,
The body part 210 is a compressor including a discharge check valve extending from an upper side to a position spaced apart from a lower end at a predetermined interval with respect to the entire longitudinal direction of the passage 124a. delete According to claim 1,
The discharge check valve 200 is molded of resin,
A discharge check valve having an insertion groove 125 formed in the passage 124a at a position facing the locking portion 212 and a compressor including the same. According to claim 3,
A discharge check valve having an O-ring 50 for sealing in an axial direction in the body part 210 and a compressor including the same. According to claim 1,
A position fixing part 500 facing the body part 210 in the axial direction and protruding from the discharge passage 124a to be inserted into the inside of the elastic member 400 to fix the position of the elastic member 400 Discharge check valve provided with and a compressor including the same. According to claim 5,
The position fixing part 500 extends to the inside of the body part 210,
A discharge check valve inserted inside the elastic member 400 and a compressor including the same. According to claim 5,
The position fixing part 500 is concavely formed on one surface of the passage 124a, and the discharge check valve in which the elastic member 400 is accommodated in the position fixing part 500 and a compressor including the same.
According to claim 1,
The core 300 is a discharge check valve in which one side is partially exposed from the body part 210 to the outside of the expansion part 214 when it moves toward the lower side of the body part 210 at maximum, and a compressor including the same.

Images