KR102413930B1 - Discharge valve assembly and rotary compressor including thereof - Google Patents

Abstract

A discharge valve assembly and a rotary compressor including the same are provided. A rotary compressor according to an aspect of the present specification includes a cylinder; a roller disposed inside the cylinder; a plurality of bearings disposed on both sides of the cylinder to form a compression space, at least one of which has a discharge port communicating with the compression space; a discharge valve disposed on one surface of the bearing and configured to open and close the discharge port; a retainer disposed at one side of the discharge valve to support the discharge valve; and a reinforcing member disposed between the discharge valve and the discharge port.

Description

Discharging valve assembly and rotary compressor comprising same

The present specification relates to a discharge valve assembly and a rotary compressor including the same. More particularly, it relates to a discharge valve assembly capable of reducing the intensity of a shock wave generated by an excessive pressure difference generated when a compressed refrigerant is discharged, and reducing noise caused by the shock wave, and a rotary compressor including the same.

In general, a compressor refers to a device configured to compress a working fluid such as air or a refrigerant by receiving power from a power generating device such as a motor or a turbine. Specifically, the compressor is widely applied to the entire industry, home appliances, in particular, a vapor compression refrigeration cycle (hereinafter referred to as a 'refrigeration cycle').

Such a compressor may be classified into a reciprocating compressor, a rotary compressor, and a scroll compressor according to a method of compressing the refrigerant.

The rotary compressor may be classified into a rolling piston type and a hinged vane type depending on whether the rollers and the vanes are coupled. The rolling piston method is a method in which the vanes are detachably coupled from the rollers so that the vanes are in close contact with the rollers, and the hinged vane method is a method in which the vanes are hinged to the rollers. Patent Document 1 and Patent Document 2 each disclose a hinged vane method, and the hinge vane method can reduce axial leakage by stabilizing the behavior of the vane compared to the rolling piston method.

The rotary compressor discharges the refrigerant compressed in the compression process into the inner space of the casing through the outlet. In this case, a reed valve is applied to open and close the discharge port. However, when the discharge port is opened and closed using the reed valve, there is a problem in that when the compressed refrigerant hits the reed valve, noise is generated. In addition, there is a problem in that the reed valve is damaged by the shock wave generated when the compressed refrigerant is discharged.

Japanese Laid-Open Patent Publication No. 2010-168977 (2010.08.05) Korean Patent Publication No. 10-2016-0034071 (2016.03.29)

An object of the present specification is to provide a discharge valve assembly capable of reducing noise generated when a compressed refrigerant hits a discharge valve, and a rotary compressor including the same.

Another object of the present specification is to provide a discharge valve assembly capable of preventing damage to a discharge valve due to a shock wave generated when a compressed refrigerant is discharged, and a rotary compressor including the same.

A rotary compressor according to an aspect of the present specification for achieving the above object includes: a cylinder; a roller disposed inside the cylinder; a plurality of bearings disposed on both sides of the cylinder to form a compression space, at least one of which has a discharge port communicating with the compression space; a discharge valve disposed on one surface of the bearing and configured to open and close the discharge port; a retainer disposed at one side of the discharge valve to support the discharge valve; and a reinforcing member disposed between the discharge valve and the discharge port.

Through this, it is possible to reduce noise generated when the compressed refrigerant hits the discharge valve. In addition, it is possible to prevent damage to the discharge valve due to a shock wave generated when the compressed refrigerant is discharged.

Also, a longitudinal length of the reinforcing member may be shorter than a longitudinal length of the discharge valve.

In addition, one side of the discharge valve and one side of the retainer may be coupled to one surface of the bearing.

In addition, the bearing may include a first groove formed on one surface, and one side of the discharge valve and one side of the retainer may be coupled to a bottom surface of the first groove.

The bearing may include a first groove formed on one surface and a second groove formed in the first groove and communicated with the discharge port, and the reinforcing member may be disposed in the second groove.

In addition, the reinforcing member may be hinged to the second groove.

In addition, the bearing may include a third groove concave in a horizontal direction from the second groove, and the reinforcing member may include a hinge portion extending in a vertical direction in a longitudinal direction and hingedly coupled to the third groove. have.

Also, a cross-sectional area of the reinforcing member may be smaller than a cross-sectional area of the second groove.

Also, an area of the other side of the reinforcing member adjacent to the discharge port may be smaller than an area of the other side of the second groove adjacent to the discharge port.

In addition, the bearing may include a seating part disposed between the first groove and the second groove, and one side of the discharge valve and one side of the retainer may be coupled to an upper surface of the seating part.

Also, a height of the seating portion may be higher than a height of the reinforcing member.

In addition, the seating part may include an extension part extending upward and on which a bottom surface of the discharge valve is disposed.

In addition, the reinforcing member may include a spacer formed concave on the lower surface and spaced apart from the bottom surface of the second groove.

In addition, the reinforcing member may include a protrusion extending downward and disposed at the discharge port.

Also, a radius of the protrusion may be smaller than a radius of the outlet.

Also, at least a portion of the protrusion may have a smaller radius as it goes down.

In addition, the bearing may include a second groove formed on one surface, one side of the discharge valve and one side of the retainer may be coupled to one surface of the bearing, and the reinforcing member may be disposed in the second groove.

In addition, the reinforcing member may be hinged to the second groove.

In addition, the other side of the discharge valve, the other side of the retainer, and the other side of the reinforcing member may overlap the discharge port in an axial direction.

A discharge valve assembly according to an aspect of the present specification for achieving the above object includes a cylinder, a roller disposed in the cylinder, and a plurality of bearings disposed on both sides of the cylinder to form a compression space A discharge valve assembly used in a rotary compressor, comprising: a discharge valve formed in at least one of the plurality of bearings to open and close a discharge port communicating with the compression space; a retainer disposed at one side of the discharge valve to support the discharge valve; and a reinforcing member disposed between the discharge valve and the discharge port.

Through this, it is possible to reduce noise generated when the compressed refrigerant hits the discharge valve. In addition, it is possible to prevent damage to the discharge valve due to a shock wave generated when the compressed refrigerant is discharged.

Through the present specification, it is possible to provide a discharge valve assembly capable of reducing noise generated when the compressed refrigerant hits the discharge valve, and a rotary compressor including the same.

Further, through the present specification, it is possible to provide a discharge valve assembly capable of preventing damage to the discharge valve due to a shock wave generated when the compressed refrigerant is discharged, and a rotary compressor including the same.

1 is a longitudinal cross-sectional view of a rotary compressor according to an embodiment of the present specification.
2 is a lateral cross-sectional view of a compression unit of a rotary compressor according to an embodiment of the present specification.
3 to 8 are views illustrating a change in the position of the vane roller with respect to the rotation angle of the rotation shaft in the rotary compressor according to an embodiment of the present specification.
9 is a perspective view illustrating a part of a main bearing and a part of a discharge valve assembly of a rotary compressor according to an embodiment of the present specification.
10 is a perspective view of a main bearing of a rotary compressor according to an embodiment of the present specification.
11 and 12 are perspective views of a reinforcing member according to an embodiment of the present specification.
13 is a cross-sectional view of a main bearing and a discharge valve assembly of a rotary compressor according to an embodiment of the present specification.
14 and 15 are perspective views of a reinforcing member according to an embodiment of the present specification.
16 is a graph illustrating a noise peak component in a discharge valve assembly of a rotary compressor according to the related art.
17 is a graph illustrating a damping value of a discharge valve assembly of a rotary compressor according to the prior art and an embodiment of the present specification.

Hereinafter, the embodiments disclosed in the present specification (discloser) will be described in detail with reference to the accompanying drawings, but the same or similar components are assigned the same reference numbers regardless of reference numerals, and redundant description thereof will be omitted.

In the description of the embodiments disclosed in this specification, when a component is referred to as being “connected” or “connected” to another component, it may be directly connected or connected to the other component, but It should be understood that other components may exist in between.

In addition, in describing the embodiments disclosed in the present specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in the present specification, the detailed description thereof will be omitted. In addition, the accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical idea disclosed in this specification is not limited by the accompanying drawings, and all changes included in the spirit and scope of the present specification , should be understood to include equivalents or substitutes.

On the other hand, the terms of the specification (discloser) can be replaced with terms such as document, specification, description.

1 is a longitudinal cross-sectional view of a rotary compressor according to an embodiment of the present specification. 2 is a lateral cross-sectional view of a compression unit of a rotary compressor according to an embodiment of the present specification.

1 and 2, the rotary compressor according to an embodiment of the present specification includes a casing 10, an electric part 20 disposed in the inner space 11 of the casing 10, and the electric part. The rotating shaft 30 and the compression unit 100 mechanically connected to the rotating shaft 30 may be included, but an additional configuration is not excluded.

In an embodiment of the present specification, the axial direction may mean an up-down direction with reference to FIG. 1 , and the radial direction may mean a left-right direction based on FIG. 1 .

The electric part 20 may include a stator 21 press-fitted to the inner circumferential surface of the casing 10 and fixed, and a rotor 22 rotatably inserted into the stator 21 . The rotation shaft 30 may be press-fitted to the rotor 22 . The rotation shaft 30 may have an eccentric part 35 eccentric with respect to the shaft part 31 . The roller 141 of the vane roller 140 may be slidably coupled to the eccentric part 35 .

The compression unit 100 may include a main bearing 110 , a sub bearing 120 , a cylinder 130 , and a vane roller 140 . The main bearing 110 and the sub bearing 120 may be disposed on both sides in the axial direction with the cylinder 130 interposed therebetween. A compression space V may be formed between the main bearing 110 , the sub bearing 120 , and the cylinder 130 . The main bearing 110 and the sub bearing 120 may radially support the rotation shaft 30 penetrating the cylinder 130 . The vane roller 140 may be coupled to the eccentric portion 35 of the rotation shaft 30 . The vane roller 140 may rotate in the cylinder 130 to compress the refrigerant.

The main bearing 110 may include a main flange portion 111 formed in a disk shape and a sidewall portion 111a formed in an edge region of the main flange portion 111 . The side wall portion 111a may be shrink-fitted or welded to the inner circumferential surface of the casing 10 . A main bearing part 112 may protrude upwardly in the central region of the main flange part 111 . A main bearing hole 112a may be formed through the main bearing part 112 so that the rotation shaft 30 is inserted and supported.

The main bearing unit 112 may include a discharge port 114 communicating with the compression space (V). The discharge port 114 may discharge the refrigerant compressed in the compression space V to the inner space 11 of the casing 10 . In one embodiment of the present specification, the discharge port 114 is described as an example formed in the main bearing 110 , but is not limited thereto, and the discharge port 114 may be formed in the sub bearing 120 , and the main bearing 110 . ) and the sub-bearing 120 may be formed in both.

The sub bearing 120 may include a sub flange portion 121 formed in a disk shape. The sub flange part 120 may be coupled to the main bearing 110 . For example, the sub flange part 120 may be bolted to the main bearing 110 together with the cylinder 130 . Alternatively, when the cylinder 130 is fixed to the casing 10 , the main bearing 110 may be respectively bolted to the sub bearing 120 and the cylinder 130 , and the sub bearing 120 is the casing 10 . When fixed to the cylinder 130 and the main bearing 110 may be bolted to the sub bearing 120 .

In the central region of the sub flange part 121 , the sub bearing part 122 may protrude downward. In the sub bearing part 122 , a sub bearing hole 122a may be formed on the same axis as the main bearing hole 112a. The sub-axle hole 122a may support a lower region of the rotation shaft 30 .

The inner circumferential surface of the cylinder 130 may be formed in an annular shape having the same inner diameter. The inner diameter of the cylinder 130 may be formed larger than the outer diameter of the roller 141 . A compression space V may be formed between the inner peripheral surface of the cylinder 130 and the outer peripheral surface of the roller 141 . The inner peripheral surface of the cylinder 130 forms the outer wall surface of the compression space (V), the outer peripheral surface of the roller 141 forms the inner wall surface of the compression space (V), the vane 145 is the side of the compression space (V) wall can be formed. As the roller 141 rotates, the outer wall surface of the compression space V forms a fixed wall, while the inner wall surface and the side wall surface of the compression space V form a variable wall whose position is variable. .

The cylinder 130 may include a suction port 131 . A vane slot 132 may be formed at one side in the circumferential direction of the suction port 131 . A discharge guide groove 133 may be formed on the opposite side of the suction port 131 with the vane slot 132 interposed therebetween.

The suction port 131 may be formed in a circular cross-sectional shape. The suction port 131 may pass through between the outer circumferential surface and the inner circumferential surface of the cylinder 130 . The suction port 131 may be connected to the suction pipe 12 passing through the casing 10 . The refrigerant may be sucked into the compression space V of the cylinder 130 through the suction pipe 12 and the suction port 131 .

The vane slot 132 may be formed in a rectangular parallelepiped cross-sectional shape. The vane slot 132 may be elongated in a radial direction from the inner circumferential surface to the outer circumferential surface of the cylinder 130 . An inner peripheral side of the vane slot 132 may be opened. The outer circumferential side of the vane slot 132 may be blocked or opened to be blocked by the inner circumferential surface of the casing 10 may be formed.

In the vane slot 132 , the vane 145 of the vane roller 140 may be slidably inserted. The width and thickness of the vane slot 132 may correspond to the width and thickness of the vane 145 . Both sides of the vane 145 are supported by both inner wall surfaces of the vane slot 132 and can slide radially.

The discharge guide groove 133 may be formed at an inner edge of the cylinder 130 . The discharge guide groove 133 may be formed in a hemispherical cross-sectional shape. The discharge guide groove 133 may be formed in a chamfer shape. The discharge guide groove 133 may guide the refrigerant compressed in the compression space V of the cylinder 130 to the discharge port 144 of the main bearing 110 . The discharge guide groove 133 may overlap the discharge port 133 in the axial direction to communicate with the discharge port 133 . The discharge guide groove 133 may be excluded and implemented to prevent generation of a dead body, or may be formed in a minimum size.

The vane roller 140 may include a roller 141 and a vane 145 . The roller 141 and the vane 145 may be integrally formed, or may be separately formed and coupled to move relative to each other. In one embodiment of the present specification, the roller 141 and the vane 145 are rotatably coupled as an example.

The roller 141 may be formed in a cylindrical shape. The roller 141 may be disposed in the cylinder 130 . The axial height of the roller 141 may correspond to the height of the inner peripheral surface of the cylinder 130 . In order for the roller 141 to slide with respect to the main bearing 110 and the sub bearing 120 , the axial height of the roller 141 may be formed to be slightly smaller than the height of the inner circumferential surface of the cylinder 130 .

The height of the inner peripheral surface and the height of the outer peripheral surface of the roller 141 may be formed to be substantially the same. Both axial end surfaces connecting the inner peripheral surface and the outer peripheral surface of the roller 141 may form a first sealing surface 141a and a second sealing surface 141b. The first sealing surface 141a and the second sealing surface 141b may form a right angle with respect to the inner peripheral surface or the outer peripheral surface of the roller 141, respectively. The edge between the inner peripheral surface of the roller 141 and the first and second sealing surfaces 141a and 141b, or the edge between the outer peripheral surface of the roller 141 and the first and second sealing surfaces 141a, 141b is formed at a right angle. It may be, or it may be formed in an inclined or curved surface.

The roller 141 may be rotatably coupled to the eccentric portion 35 of the rotation shaft 30 . The roller 141 may be rotatably inserted into the eccentric portion 35 of the rotation shaft 30 . The vane 145 may be slidably coupled to the vane slot 132 of the cylinder 130 . The vane 145 may be hinged to the outer circumferential surface of the roller 141 . Accordingly, when the rotation shaft 30 rotates, the roller 141 rotates inside the cylinder 130 by the eccentric part 35 , and the vane 145 is coupled to the roller 141 . Can reciprocate.

A hinge groove 1411 into which the hinge protrusion 1452 of the vane 145 is inserted may be formed on the outer peripheral surface of the roller 141 . The hinge protrusion 1452 of the vane 145 may be rotatably coupled to the hinge groove 1411 . The outer peripheral surface of the hinge groove 1411 may be formed in an open arc shape.

The inner diameter of the hinge groove 1411 may be larger than the outer diameter of the hinge protrusion 1452 . The inner diameter of the hinge groove 1411 may be formed to a size sufficient to slide without falling out while the hinge protrusion 1452 is inserted.

The vane 145 may include a sliding part 1451 , a hinge protrusion 1452 , and an interference avoiding part 1453 .

The sliding part 1451 may be formed in a flat plate shape. The sliding part 1451 may have a preset length and thickness. For example, the sliding part 1451 may be formed in a hexahedral shape of a longitudinal direction as a whole. The sliding portion 1451 may be formed to have a length such that the vane 145 remains in the vane slot 132 even when the roller 141 is completely moved to the opposite side of the vane slot 132 .

The hinge protrusion 1452 may be formed to extend to the front end of the sliding part 1451 facing the roller 141 . The hinge protrusion 1452 may be rotated by being inserted into the hinge groove 1411 . The hinge protrusion 1452 may be inserted into the hinge groove 1411 to have a rotatable cross-sectional area. The hinge protrusion 1452 may be semi-circular to correspond to the hinge groove 1411 , but may be formed in a circular cross-sectional shape except for a connecting portion.

The interference avoiding part 1453 may prevent the sliding part 1451 from interfering with the axial edge of the hinge groove 1411 when the vane 145 rotates with respect to the roller 141 . The interference avoiding part 1453 may be formed between the sliding part 1451 and the hinge protrusion 1452 . The interference avoiding part 1453 may be formed to be depressed in a direction in which an area between the sliding part 1451 and the hinge protrusion 1452 decreases.

The interference avoiding unit 1453 may be formed symmetrically with respect to the longitudinal center line of the sliding unit 1451 . The interference avoiding part 1453 may be formed in a cross-sectional shape of a recessed wedge or a curved cross-sectional shape. The interference avoiding unit 1453 may be spaced apart from the inner wall surface of the vane slot 132 by a predetermined distance while being inserted into the vane slot 132 , and may form a refrigerant residual space with the outer peripheral surface of the roller 141 .

The discharge valve 150 may be disposed on the main bearing 110 . The discharge valve 150 may open and close the discharge port 114 . The discharge valve 150 may include a lead valve. The discharge valve 150 opens the discharge port 114 when the refrigerant compressed in the compression space V is discharged, and seals the discharge port 114 in other cases to prevent refrigerant leakage from the compression space V. have. In the exemplary embodiment of the present specification, the discharge valve 150 is installed on the main bearing 110 as an example, but is not limited thereto and is installed on the sub bearing 120 , or the main bearing 110 and the sub bearing 120 . It can be installed on all of them.

The muffler 160 may be disposed on the main bearing 110 . The muffler 160 may be coupled to the main bearing 160 by bolting. A space may be formed between the inner surface of the muffler 160 and the upper surface of the main bearing 110 . Through this, it is possible to reduce resonance noise generated when the compressed refrigerant discharged from the discharge port 114 is discharged to the inner space 11 .

The rotary compressor may be operated as follows.

When power is applied to the electric part 20 , the rotor 22 of the electric part 20 may rotate to rotate the rotating shaft 30 . In this case, while the roller 141 of the vane roller 140 coupled to the eccentric portion 35 of the rotation shaft 30 rotates, the refrigerant may be sucked into the compression space V of the cylinder 130 .

This refrigerant is compressed by the rollers 141 and the vanes 145 of the vane roller 140, and the compressed refrigerant opens the discharge valve 150 provided in the main bearing 110, and through the discharge port 114, the muffler ( It may be discharged into the inner space 11 of the casing 10 through the 160 .

3 to 8 are views illustrating a change in the position of the vane roller with respect to the rotation angle of the rotation shaft in the rotary compressor according to an embodiment of the present specification.

The positions of the rollers 141 and the vanes 145 may be changed as follows according to the rotation angle of the rotation shaft 30 .

Referring to FIG. 3 , the axial center (O) of the rotating shaft 30 and the axial center (O`) of the hinge groove 1411 at a position where the eccentric part 35 of the rotating shaft 30 faces the vane slot 132 . An imaginary line passing through is a reference, and it can be assumed that the position of this imaginary line is 0°. In this case, the axial center O of the rotating shaft 30 may be the same as the axial center of the cylinder 130 . The hinge groove 1411 of the roller 141 is adjacent to the inner circumferential surface of the cylinder 130 so that the vane 145 may be introduced into the vane slot 132 .

4 shows a state in which the rotating shaft rotates by 60°, and FIG. 5 shows a state in which the rotating shaft rotates by 120°. The hinge groove 1411 of the roller 141 may be spaced apart from the inner circumferential surface of the cylinder 130 . A portion of the vane 145 may be withdrawn from the vane slot 132 . The refrigerant may be introduced into the subsequent compression chamber V2 through the suction port 131 , and the subsequent compression chamber V2 may form a suction chamber. The preceding compression chamber V1 may compress the refrigerant filled in the preceding compression chamber V1 by forming a compression chamber.

6 shows a state in which the rotating shaft rotates by 180°. The hinge groove 1411 of the roller 141 may be maximally spaced apart from the inner circumferential surface of the cylinder 130 . The vane 145 may be withdrawn from the vane slot 132 to the maximum. The preceding compression chamber V1 may be in a state in which the compression stroke has been significantly advanced. The refrigerant accommodated in the preceding compression chamber V1 may be in a state close to the discharge pressure.

7 shows a state in which the rotating shaft rotates by 240°. The hinge groove 1411 of the roller 145 may move toward the inner circumferential surface of the cylinder 130 again. A part of the vane 145 may be introduced into the vane slot 132 . The refrigerant accommodated in the preceding compression chamber V1 may have already reached the discharge pressure to start discharging, or may be in a state where the discharging start time has been reached.

8 shows a state in which the rotating shaft rotates by 300°. The refrigerant in the preceding compression chamber V1 may be almost completely discharged. The hinge groove 1411 of the roller 141 may be adjacent to the inner circumferential surface of the cylinder 130 . The vane 145 may be in a state substantially retracted into the vane slot 132 .

9 is a perspective view illustrating a part of a main bearing and a part of a discharge valve assembly of a rotary compressor according to an exemplary embodiment of the present specification. 10 is a perspective view of a main bearing of a rotary compressor according to an embodiment of the present specification. 11 and 12 are perspective views of a reinforcing member according to an embodiment of the present specification. 13 is a cross-sectional view of a main bearing and a discharge valve assembly of a rotary compressor according to an embodiment of the present specification. 14 and 15 are perspective views of a reinforcing member according to an embodiment of the present specification. 16 is a graph illustrating a noise peak component in a discharge valve assembly of a rotary compressor according to the related art. 17 is a graph illustrating a damping value of a discharge valve assembly of a rotary compressor according to the prior art and an embodiment of the present specification.

9 to 15 , the rotary compressor according to an embodiment of the present specification may include a discharge valve assembly.

The discharge valve assembly may be disposed on the main bearing 110 . The discharge valve assembly may be disposed on the main flange portion 111 of the main bearing 110 . The discharge valve assembly may be disposed in the first groove 115 and/or the second groove 116 of the main flange portion 111 of the main bearing 110 . The discharge valve assembly may open and close the discharge port 114 . The discharge valve assembly may be coupled to the main bearing 110 through the coupling member 152 . One side of the discharge valve assembly is fixed on the main bearing 110 by the coupling member 152, and the other side of the discharge valve assembly can open and close the discharge port 114 by the pressure of the refrigerant compressed in the compression space (V). have. The discharge valve assembly may include a discharge valve 150 , a retainer 151 , and a reinforcing member 200 .

In one embodiment of the present specification, the discharge valve assembly has been described as being disposed on the main bearing 110 as an example, but it may be installed on the sub bearing 120 depending on the position of the discharge port 114, the main bearing 110 and It may be installed on all of the sub bearings 120 .

The discharge valve assembly may include a discharge valve 150 . The discharge valve 150 may be disposed on the main bearing 110 . The discharge valve 150 may be disposed on the main flange part 111 of the main bearing 110 . The discharge valve 150 may be disposed in the first groove 115 of the main flange part 111 of the main bearing 110 . The discharge valve 150 may be coupled to the main bearing 110 . The discharge valve 150 may be coupled to the first groove 115 of the main flange portion 111 of the main bearing 110 . The discharge valve 150 may be coupled to the bottom surface of the first groove 115 . The discharge valve 150 may be coupled to the main bearing 110 through the coupling member 152 . For example, one side of the discharge valve 150 may be bolted to the first groove 115 of the main bearing 110 by the coupling member 152 . In this case, the first hole 1501 formed at one side of the discharge valve 150 may be penetrated by the coupling member 152 . One side of the discharge valve 150 is fixed on the main bearing 110 by the coupling member 152 , and the other side of the discharge valve 150 is a discharge port 114 by the pressure of the refrigerant compressed in the compression space (V). can be opened and closed.

In an embodiment of the present invention, the first groove 115 has been described as being formed on one surface of the main bearing 110 as an example, but may be formed on one surface of the sub bearing 120 , or one surface of the main bearing 110 . It may be formed on one surface of the sub-bearing 120 and the sub-bearing 120 .

The discharge valve 150 may be formed in a plate shape. The discharge valve 150 may be formed of a metal material. The discharge valve 150 may have elasticity. For example, the discharge valve 150 may be a lead valve. When the discharge start time is reached, the other side of the discharge valve 150 may move upward by the discharge pressure. In this case, the other side of the discharge valve 150 may be separated from the main bearing 110 to open the discharge port 114 to discharge the compressed refrigerant.

The discharge valve assembly may include a retainer 151 . The retainer 151 may be disposed on the main bearing 110 . The retainer 151 may be disposed on the main flange portion 111 of the main bearing 110 . The retainer 151 may be disposed in the first groove 115 of the main flange portion 111 of the main bearing 110 . The retainer 151 may be coupled to the bottom surface of the first groove 115 . The retainer 151 may be coupled to the main bearing 110 through a coupling member 152 . For example, one side of the retainer 151 may be bolted to the main bearing 110 by the coupling member 152 . In this case, the second hole 151 formed on one side of the retainer 151 may be penetrated by the coupling member 152 .

The retainer 151 may be disposed on one side of the discharge valve 150 . For example, the retainer 151 may be disposed above the discharge valve 150 . The retainer 151 may support the discharge valve 150 . When it is not the discharge start time, the other side of the retainer 151 may be spaced apart from the other side of the discharge valve 150 in an axial or vertical direction. One side of the retainer 151 is fixed on the main bearing 110 by the coupling member 152 , and the other side of the retainer 151 supports the other side of the discharge valve 150 when the discharge valve 150 moves upward. can do.

In one embodiment of the present specification, one side of the discharge valve 150 and one side of the retainer 151 are bolted to the main bearing 110 by one coupling member 152 as an example, but each separate coupling It is not excluded that it is fixed on the main bearing 110 by a member.

The discharge valve assembly may include a reinforcing member 200 . The reinforcing member 200 may be disposed on the main bearing 110 . The reinforcing member 200 may be disposed on the main flange portion 111 of the main bearing 110 . The reinforcing member 200 may be disposed in the first groove 115 of the main flange portion 111 of the main bearing 110 . The reinforcing member 200 may be formed in the first groove 115 of the main flange portion 111 of the main bearing 110 and disposed in the second groove 116 communicating with the outlet 114 . For example, the reinforcing member 200 may be hinged to the second groove 116 . Through this, at the discharge start time, one side of the reinforcing member 200 is disposed in the second groove 116, and the other side of the reinforcing member 200 rotates upward to move the discharge valve 150 upward. .

The reinforcing member 200 may be disposed between the discharge valve 150 and the discharge port 114 . The reinforcing member 200 may be disposed below the discharge valve 150 . At least a portion of the reinforcing member 200 may be disposed on the outlet 114 . When it is not the discharge start time, the other side of the reinforcing member 200 may be adjacent to or in contact with the other side of the discharge valve 150 , but the other side of the reinforcing member 200 is axial or vertical with the other side of the discharge valve 150 . It does not exclude that they are spaced apart in the direction.

The lengthwise length of the reinforcing member 200 may be shorter than the lengthwise length of the discharge valve 150 . One side of the reinforcing member 200 may overlap the discharge valve 150 and the retainer 151 in the axial direction. One side of the reinforcing member 200 may overlap the central region of the discharge valve 150 and the central region of the retainer 151 in the axial direction. The other side of the reinforcing member 200 may overlap the discharge port 150 . The other side of the reinforcing member 200 may overlap the other side of the discharge valve 150 and the other side of the retainer 151 in the axial direction. That is, by adding the reinforcing member 200 of a small size, it is possible to prevent the cost of the product from being excessively increased.

A cross-sectional area of the reinforcing member 200 may be smaller than a cross-sectional area of the second groove 116 . Specifically, the area of the other side of the reinforcing member 200 adjacent to the outlet 114 may be smaller than the area of the other side of the second groove 116 adjacent to the outlet 114 . Through this, it is possible to prevent the reinforcing member 200 from being caught in the second groove 116 . In addition, when the reinforcing member 200 rotates to expose the second groove 116 , the compressed refrigerant may smoothly escape through the outlet 114 .

The height of the reinforcing member 200 may be smaller than the height of the seating portion 117 of the main bearing 110 disposed between the first groove 115 and the second groove 116 . In this case, one side of the discharge valve 150 and one side of the retainer 151 may be coupled to the upper surface of the seating part 117 , and the upper surface of the reinforcing member 200 may be adjacent to or spaced apart from the lower surface of the discharge valve 150 . can be Through this, it is possible to prevent damage to the product due to excessive friction between the reinforcing member 200 and the discharge valve 150 . In addition, when the other side of the reinforcing member 200 rotates, only the other side area of the reinforcing member 200 can contact the other side area of the discharge valve 150 , so that the discharge valve 150 is supported by the retainer 151 . structure can be maintained. To this end, an extension portion 1171 extending upwardly and disposed on the bottom surface of the discharge valve 150 may be formed on the upper surface of the seating portion 117 .

In one embodiment of the present specification, since the seating portion 117 is formed on the main bearing 110 , the discharge valve 150 and the retainer 151 are attached to the main bearing 110 without increasing the discharge body volume compared to the existing one. Bonding rigidity can be increased.

The reinforcing member 200 may be formed of the same material as the discharge valve 150 . For example, when the discharge valve 150 is formed of metal, the reinforcing member 200 may also be formed of metal. The reinforcing member 200 may be formed of a material having elasticity. Alternatively, the buoyancy member 200 may be formed of a rigid body.

The reinforcing member 200 may include a main body 220 , a hinge part 210 , and a protrusion part 230 .

The body 220 may extend in the longitudinal direction. One side of the body 220 may be connected to the hinge part 210 . The cross-section of the other side of the body 220 may be formed in an arc shape. The other side of the body 220 may overlap the outlet 114 in the axial direction. In the case of the discharge start time, the other side of the main body 200 may move upward to move the discharge valve 150 upward. That is, by preventing the discharge valve 150 from being directly exposed to the discharge pressure, noise generated when the compressed refrigerant hits the discharge valve can be reduced. In addition, it is possible to prevent damage to the discharge valve 150 and the retainer 151 due to a shock wave generated when the compressed refrigerant is discharged.

The other side of the main body 220 may be formed smaller than the area of the second groove 116 that is in communication with or adjacent to the outlet 114 . The area of the other side of the main body 220 may be formed to be smaller than the area of the other side of the second groove 116 communicating with or adjacent to the outlet 114 . Through this, it is possible to prevent the reinforcing member 200 from being caught in the second groove 116 . In addition, when the reinforcing member 200 rotates to expose the second groove 116 , the compressed refrigerant may smoothly escape through the outlet 114 .

The reinforcing member 200 is concavely formed on the lower surface of the main body 220 and may include a spacer 222 spaced apart from the bottom surface of the second groove 116 . The spacer 222 may be formed in a 'groove' shape. Through this, when the oil is discharged through the discharge port 114, the spacer 222 can serve to confine the oil, thereby minimizing the stickiness caused by the oil, thereby reducing energy loss.

In an embodiment of the present invention, the cross-section of the spacer 222 is described as an example that is formed in a rectangular shape, but is not limited thereto, and the shape of the cross-section of the spacer 222 may be variously changed.

The hinge part 210 may be formed on one side of the body 220 . The hinge part 210 may extend in a direction perpendicular to the longitudinal direction of the reinforcing member 200 . The hinge part 210 may be formed in a cylindrical shape. The hinge part 210 may be hinge-coupled to the second groove 116 . Specifically, the hinge part 210 may be hinge-coupled to the third groove 119 concave in the direction perpendicular to the axial direction or the horizontal direction in the second groove 116 .

13 and 14 , the protrusion 230 may extend below the reinforcing member 200 . The protrusion 230 may extend downward from the lower surface of the body 220 . When it is not the discharge start time, the protrusion 230 may be disposed at the discharge port 114 . Through this, since the discharged dead volume can be reduced, the loss generated while the compressed refrigerant is discharged can be minimized.

The radius of the protrusion 230 may be smaller than the radius of the outlet 114 . Through this, when the reinforcing member 200 rotates, it is possible to prevent the protrusion 230 from contacting the discharge port 114 .

Referring to FIG. 15 , at least a portion 240 of the protrusion 230 may have a smaller radius as it goes down. Through this, when the reinforcing member 200 rotates, it is possible to prevent the protrusion 230 from coming into contact with the discharge port 114 . Alternatively, the radius or cross-sectional area may decrease as only at least a portion of the other side area (the right area with reference to FIG. 13 ) of the protrusion 230 facing the discharge port 114 goes down.

In one embodiment of the present specification, the second groove 116 is formed in the first groove 115 , and the discharge valve 150 and the retainer 151 are coupled to the bottom surface of the first groove 115 , and the second groove 116 is formed. Although it has been described as an example that the reinforcing member 200 is disposed in the second groove 116 , it may be implemented without the first groove 115 . For example, the second groove 116 is formed on one surface of the main bearing 110 , the discharge valve 150 and the retainer 151 are coupled to one surface of the main bearing 110 , and the second groove 116 . A reinforcing member 200 may be disposed on the .

Referring to FIG. 16 , it can be seen that noise becomes a peak value in the primary vibration mode and the secondary vibration mode of the retainer 151 in the prior art. In one embodiment of the present specification, the shock applied to the discharge valve 150 is alleviated through the reinforcing member 200, and through this, the shock applied to the retainer 151 by the discharge valve 150 can be alleviated, so the retainer ( 151), noise in both the primary and secondary vibration modes can be reduced.

Also, referring to FIG. 17 , the vibration damping effect on the discharge valve 150 and the retainer 151 is increased due to the reinforcing member 200 of the discharge valve assembly of the rotary compressor according to the exemplary embodiment of the present specification compared to the prior art. it can be seen that

Any or other embodiments of the present specification described above are not mutually exclusive or distinct. Any of the above-described embodiments or other embodiments of the present specification may be combined or combined with each configuration or function.

For example, it means that configuration A described in a specific embodiment and/or drawings may be combined with configuration B described in other embodiments and/or drawings. That is, even if the coupling between the components is not directly described, it means that the coupling is possible except for the case where it is described that the coupling is impossible.

The above detailed description should not be construed as restrictive in all respects and should be considered as exemplary. The scope of this specification should be determined by a reasonable interpretation of the appended claims, and all modifications within the scope of equivalents of this specification are included in the scope of this specification.

10: casing 11: interior space
12: suction pipe 13: discharge pipe
20: electric part 21: stator
22: rotor 30: rotation shaft
31: shaft 35: eccentric
100: compression unit 110: main bearing
111: main flange portion 111a: side wall portion
112: main bearing part 112a: main shaft hole
114: discharge port 115: first groove
116: second groove 117: seating portion
120: sub bearing 121: sub flange portion
122: sub bearing part 122a: sub shaft hole
130: cylinder 131: intake port
132: vane slot 133: discharge guide groove
140: vane roller 141: roller
141a: first sealing surface 141b: second sealing surface
1411: hinge groove 145: vane
1451: sliding portion 1452: hinge protrusion
1453: interference avoidance unit 150: discharge valve
151: retainer 152: coupling member
160: muffler 200: reinforcing member

Claims (20)

cylinder;
a roller disposed inside the cylinder;
a plurality of bearings disposed on both sides of the cylinder to form a compression space, at least one of which has a discharge port communicating with the compression space;
a discharge valve disposed on one surface of the bearing and configured to open and close the discharge port;
a retainer disposed at one side of the discharge valve to support the discharge valve; and
a reinforcing member disposed between the discharge valve and the discharge port;
The bearing includes a first groove formed on one surface, and a second groove formed in the first groove and communicating with the outlet,
The reinforcing member is disposed in the second groove. The method of claim 1,
A longitudinal length of the reinforcing member is shorter than a longitudinal length of the discharge valve. The method of claim 1,
One side of the discharge valve and one side of the retainer are coupled to one surface of the bearing. The method of claim 1,
One side of the discharge valve and one side of the retainer are coupled to a bottom surface of the first groove. delete The method of claim 1,
The reinforcing member is hinge-coupled to the second groove. 7. The method of claim 6,
The bearing includes a third groove concave in the horizontal direction from the second groove,
The reinforcing member extends in a direction perpendicular to the longitudinal direction, and the rotary compressor includes a hinge portion hinged to the third groove. The method of claim 1,
A cross-sectional area of the reinforcing member is smaller than a cross-sectional area of the second groove. 9. The method of claim 8,
An area of the other side of the reinforcing member adjacent to the discharge port is smaller than an area of the other side of the second groove adjacent to the discharge port. The method of claim 1,
The bearing includes a seating portion disposed between the first groove and the second groove,
A rotary compressor in which one side of the discharge valve and one side of the retainer are coupled to an upper surface of the seating part. 11. The method of claim 10,
The height of the seating portion is a rotary compressor that is formed to be higher than the height of the reinforcing member. 11. The method of claim 10,
and an extension part extending upwardly from the seating part and on which a bottom surface of the discharge valve is disposed. The method of claim 1,
The reinforcing member is formed to be concave on a lower surface and includes a spaced portion spaced apart from the bottom surface of the second groove. The method of claim 1,
and the reinforcing member extends downward and includes a protrusion disposed at the discharge port. 15. The method of claim 14,
A radius of the protrusion is formed smaller than a radius of the discharge port. 15. The method of claim 14,
A rotary compressor in which at least a portion of the protrusion has a smaller radius as it goes down. cylinder;
a roller disposed inside the cylinder;
a plurality of bearings disposed on both sides of the cylinder to form a compression space, at least one of which has a discharge port communicating with the compression space;
a discharge valve disposed on one surface of the bearing and configured to open and close the discharge port;
a retainer disposed at one side of the discharge valve to support the discharge valve; and
a reinforcing member disposed between the discharge valve and the discharge port;
The bearing includes a second groove formed on one surface,
One side of the discharge valve and one side of the retainer are coupled to one surface of the bearing,
The reinforcing member is disposed in the second groove. 18. The method of claim 17,
The reinforcing member is hinge-coupled to the second groove. The method of claim 1,
The other side of the discharge valve, the other side of the retainer, and the other side of the reinforcing member overlap the discharge port in an axial direction. A discharge valve assembly used in a rotary compressor comprising a cylinder, a roller disposed in the cylinder, and a plurality of bearings disposed on both sides of the cylinder to form a compression space,
a discharge valve formed in at least one of the plurality of bearings and opening and closing a discharge port communicating with the compression space;
a retainer disposed at one side of the discharge valve to support the discharge valve; and
a reinforcing member disposed between the discharge valve and the discharge port;
At least one of the plurality of bearings includes a first groove formed on one surface and a second groove formed in the first groove and communicated with the outlet,
The reinforcing member is disposed in the second groove.

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