WO2023182580A1

WO2023182580A1 - Reciprocating compressor

Info

Publication number: WO2023182580A1
Application number: PCT/KR2022/010923
Authority: WO
Inventors: 김영환; 이종목; 김상민
Original assignee: 엘지전자 주식회사
Priority date: 2022-03-21
Filing date: 2022-07-26
Publication date: 2023-09-28
Also published as: KR20230137013A

Abstract

Provided is a reciprocating compressor. The reciprocating compressor according to an aspect of the present invention comprises: a case; a driving motor disposed in the case; a rotary shaft connected to the driving motor; a cylinder disposed in the case and forming a compression space; a piston linearly reciprocating in the cylinder according to the rotation of the rotary shaft; a valve assembly including a discharge hole and coupled to the front end of the cylinder; a discharge cover coupled to the outside of the valve assembly; and a main discharge cover disposed between the discharge cover and the valve assembly and opening and closing the discharge hole. The main discharge valve includes a first fixed end that is fixed to the valve assembly and a head part that extends from the first fixed end and opens and closes the discharge hole. The discharge cover includes a stopper extending from the inner surface toward the discharge hole, and the position at which the head part and the stopper come into contact with each other during a discharge cycle may overlap the discharge hole.

Description

Recipro Compressor

This specification relates to a reciprocating compressor. More specifically, it relates to a reciprocating compressor that compresses refrigerant by the linear reciprocating motion of a piston.

In general, a compressor refers to a device that receives power from a power generating device such as a motor or turbine and compresses a working fluid such as air or refrigerant. Specifically, compressors are widely applied throughout industry and home appliances, especially vapor compression refrigeration cycles (hereinafter referred to as 'refrigeration cycles').

These compressors can be classified into reciprocating compressors, rotary compressors, and scroll compressors depending on the method of compressing the refrigerant.

The reciprocating compressor compresses the fluid by forming a compression space between the piston and the cylinder and the piston moves in a straight line, the rotary compressor compresses the fluid by a roller rotating eccentrically inside the cylinder, and the scroll compressor uses a spiral compressor. This is a method in which a pair of scrolls are engaged and rotated to compress the fluid.

Recipro compressors can be divided into vibration type and connected type depending on the driving method of the piston. The vibrating type reciprocating compressor compresses the refrigerant while the piston is connected to the mover of the drive motor and vibrates in a reciprocating motion in the cylinder. In the connected type reciprocating compressor, a connecting rod is coupled to the rotating shaft of the driving motor and the connecting rod This is a method in which the piston is combined to convert the rotational force of the drive motor into the linear motion of the piston.

This specification relates to a connected Recipro compressor. Hereinafter, the connected Recipro compressor is referred to as a 'Recipro compressor'.

The Recipro compressor is used to compress refrigerant in refrigerators. As the power consumption regulations for refrigerators have recently been strengthened, the demand for low cooling power and high efficiency has increased. In order to achieve low cooling power and high efficiency, efficiency in the main operating section of the refrigerator has been improved. This is needed.

The discharge valve of the reciprocating compressor must be opened quickly in the discharge stroke to reduce excessive pressure in the cylinder, and must be closed quickly in the suction stroke to prevent the discharged refrigerant from flowing back to minimize cooling power loss.

However, the discharge valve of the conventional reciprocating compressor is a plate-type reed valve, which has the problem of being difficult to open quickly in the discharge stroke and close quickly in the suction stroke.

The problem that the present specification seeks to solve is to provide a reciprocating compressor that quickly opens in the discharge stroke to reduce excessive pressure in the cylinder and quickly closes in the suction stroke to prevent the discharged refrigerant from flowing back.

In addition, the problem that this specification aims to solve is to provide a compressor with a recipe that can enable smooth bending of the head portion by minimizing the area where the main discharge valve and the stopper meet.

In addition, the problem that the present specification aims to solve is to provide a reciprocating compressor that can improve cooling power compared to the stress applied to the bending area of the head portion.

In addition, the problem to be solved by this specification is to provide a reciprocating compressor that can facilitate the flow of discharged refrigerant discharged to the outside.

In addition, the problem that this specification seeks to solve is to provide a reciprocating compressor that can improve the closing response of the main discharge valve in the suction stroke.

In addition, the problem that this specification aims to solve is a Recipro compressor that can improve the responsiveness of the main discharge valve by allowing the main discharge valve to bend better even under weak force while maintaining the overall rigidity of the main discharge valve and sub-discharge valve. is to provide.

In addition, the problem that this specification aims to solve is to provide a compressor with a recipe that can secure the overall rigidity of the main discharge valve and sub discharge valve.

In addition, the problem that the present specification seeks to solve is to provide a compressor with a recipe that can better bend the main discharge valve by increasing the discharge pressure.

In addition, the problem that the present specification aims to solve is to provide a reciprocating compressor that can disperse the stress that occurs when the main discharge valve contacts the stopper.

In addition, the problem that this specification aims to solve is to reduce the impact force that occurs when the main discharge valve and the stopper contact, and to provide a compressor with a recipe that can prevent the end of the main discharge valve from secondary contact with the stopper. It is done.

A reciprocal compressor according to an aspect of the present specification for achieving the above problem includes a case, a drive motor disposed within the case, a rotation shaft connected to the drive motor, and a compression space disposed within the case. A cylinder forming a cylinder, a piston that reciprocates linearly within the cylinder as the rotation shaft rotates, a valve assembly including a discharge hole and coupled to the tip of the cylinder, and a discharge cover coupled to the outside of the valve assembly. , disposed between the discharge cover and the valve assembly, and comprising a main discharge valve that opens and closes the discharge hole, the main discharge valve having a first fixed end fixed to the valve assembly, and extending from the first fixed end. It may include a head portion that opens and closes the discharge hole, and the discharge cover may include a stopper extending from an inner surface toward the discharge hole.

In this case, the position where the head part and the stopper contact during the discharge stroke may overlap with the discharge hole.

Through this, the area between the contact area of the head of the main discharge valve and the stopper and the end of the head is bent by the discharge pressure, so it opens quickly in the discharge stroke to reduce excessive pressure in the cylinder, and closes quickly in the suction stroke to discharge. It can prevent refrigerant from flowing back.

Additionally, the head portion may make one point contact or one line contact with the stopper. Specifically, the area where the head and the stopper meet may form one point or one line. Through this, the area where the main discharge valve and the stopper meet can be minimized to enable smooth bending of the head portion.

Additionally, the stopper may entirely overlap the discharge hole.

In addition, the distance in the first direction in the longitudinal direction of the main discharge valve between the position where the head part and the stopper contact and the first fixed end and the furthest position among the discharge holes is 0.2 to 0.8 times the diameter of the discharge hole. It may be below. Through this, the cooling power of the reciprocating compressor can be improved compared to the stress applied to the bending area of the head portion.

In addition, the discharge cover includes a discharge passage that communicates the internal discharge space and the outside, and the area between the ends of the head portion at the position where the head portion and the stopper contact during the discharge stroke is bent toward the discharge passage. You can. Through this, the flow of the discharged refrigerant discharged to the outside can be smoothened.

In addition, the stopper includes a chamfer formed on a surface facing the discharge hole, and the area between the position where the head portion and the stopper contact during the discharge stroke and the end of the head portion may not be in contact with the chamfer. . In this case, the angle between the chamfer and an imaginary line extending the surface of the stopper facing the discharge hole may be 2° or more. In addition, during the discharge stroke, the head portion and the stopper may make one line contact. Through this, the closing responsiveness of the main discharge valve in the intake stroke can be improved.

Additionally, it may include a sub-discharge valve disposed between the discharge cover and the main discharge valve, and the sub-discharge valve may not overlap the stopper. Additionally, the sub discharge valve may not overlap the discharge hole. In this case, the sum of the thicknesses of the sub discharge valve and the main discharge valve may correspond to the thickness when there is only one discharge valve. Through this, while maintaining the overall rigidity of the main discharge valve and sub-discharge valve, the main discharge valve can bend better even under weak force, improving the responsiveness of the main discharge valve.

Additionally, the sub discharge valve includes a second fixed end fixed to the valve assembly, and the second fixed end may overlap the first fixed end. Through this, the overall rigidity of the main discharge valve and sub discharge valve can be secured.

Additionally, the discharge hole may have a length in a first direction, which is the longitudinal direction of the main discharge valve, greater than a length in a second direction perpendicular to the first direction. Through this, the width of the discharge hole is narrowed compared to a circular shape with the same effective area, so the main discharge valve can be better bent by increasing the discharge pressure.

Additionally, at least a portion of the cross section of the surface of the stopper facing the discharge hole may be curved. Through this, it is possible to distribute the stress that occurs when the main discharge valve contacts the stopper.

Additionally, the radius of curvature of the curve may increase as the distance from the first fixed end increases. Through this, the impact force can be lowered because the height at which the main discharge valve and the stopper collide is closer to the discharge hole, and the end of the main discharge valve can be prevented from secondary contact with the stopper.

Through this specification, it is possible to provide a compressor with a recipe that opens quickly in the discharge stroke to reduce excessive pressure in the cylinder and quickly closes in the suction stroke to prevent the discharged refrigerant from flowing back.

In addition, through this specification, it is possible to provide a compressor with a recipe that can enable smooth bending of the head portion by minimizing the area where the main discharge valve and the stopper meet.

In addition, through this specification, a compressor with a recipe that can improve cooling power compared to the stress applied to the bending area of the head can be provided.

In addition, through this specification, it is possible to provide a compressor with a recipe that can smooth the flow of discharged refrigerant discharged to the outside.

In addition, through this specification, it is possible to provide a compressor with a recipe that can improve the closing response of the main discharge valve in the suction stroke.

In addition, through this specification, a compressor can be provided with a recipe that improves the responsiveness of the main discharge valve by allowing the main discharge valve to bend better even under weak force while maintaining the overall rigidity of the main discharge valve and sub-discharge valve. .

In addition, through this specification, it is possible to provide a compressor with a recipe that can secure the overall rigidity of the main discharge valve and sub discharge valve.

In addition, through this specification, a compressor can be provided with a recipe that can better bend the main discharge valve by increasing the discharge pressure.

In addition, through this specification, it is possible to provide a compressor with a recipe that can distribute stress that occurs when the main discharge valve contacts the stopper.

In addition, through the present specification, it is possible to provide a compressor with a recipe that can reduce the impact force that occurs when the main discharge valve and the stopper contact and prevent the end of the main discharge valve from secondary contact with the stopper.

1 is a cross-sectional view of a reciprocal compressor according to an embodiment of the present specification.

Figure 2 is an enlarged view of one area of Figure 1.

Figure 3 is a perspective view of a discharge cover, a valve assembly, a main discharge valve, an intake valve, and a gasket of a Recipro compressor according to an embodiment of the present specification.

Figure 4 is an exploded perspective view of the discharge cover, valve assembly, main discharge valve, suction valve, and gasket of the Recipro compressor according to an embodiment of the present specification.

Figure 5 is a projection view of the discharge cover, main discharge valve, and discharge gasket of the Recipro compressor according to an embodiment of the present specification.

Figures 6 and 7 are cross-sectional views of the discharge cover, main discharge valve, and discharge gasket of the Recipro compressor according to an embodiment of the present specification.

Figure 8 is an enlarged view of a partial area of Figure 7.

Figure 9 is a graph showing the change in cooling force/stress according to L/D1 of the Recipro compressor according to an embodiment of the present specification.

10 to 14 are schematic diagrams showing various modifications of the stopper and head portion of the reciprocating compressor according to embodiments of the present specification.

Figure 15 is an exploded perspective view of the discharge cover, valve assembly, main discharge valve, sub discharge valve, suction valve, and gasket of the Recipro compressor according to an embodiment of the present specification.

Figure 16 is a front view of a portion of the discharge cover, discharge gasket, sub discharge valve, and main discharge valve of the Recipro compressor according to an embodiment of the present specification.

Figure 17 is a schematic diagram of a stopper, a head portion, and a sub-discharge valve of a reciprocal compressor according to an embodiment of the present specification.

Figures 18 and 19 are diagrams showing modifications of the discharge hole and main discharge valve of the reciprocating compressor according to an embodiment of the present specification.

Hereinafter, embodiments disclosed in the present specification (discloser) will be described in detail with reference to the attached drawings. However, identical or similar components will be assigned the same reference numbers regardless of reference numerals, and duplicate descriptions thereof will be omitted.

In describing the embodiments disclosed herein, 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. It should be understood that other components may exist in the middle.

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

Meanwhile, the term ‘discloser’ can be replaced with terms such as document, specification, description, etc.

1 is a cross-sectional view of a reciprocal compressor according to an embodiment of the present specification. Figure 2 is an enlarged view of one area of Figure 1. Figure 3 is a perspective view of a discharge cover, a valve assembly, a main discharge valve, an intake valve, and a gasket of a Recipro compressor according to an embodiment of the present specification. Figure 4 is an exploded perspective view of the discharge cover, valve assembly, main discharge valve, suction valve, and gasket of the Recipro compressor according to an embodiment of the present specification. Figure 5 is a projection view of the discharge cover, main discharge valve, and discharge gasket of the Recipro compressor according to an embodiment of the present specification.

1 to 5, the reciprocal compressor 100 according to an embodiment of the present specification includes a case 110, a compression mechanism 120, a drive motor 140, a rotation shaft 130, It may include a valve assembly 126, an intake valve 127, an intake muffler 125, a main discharge valve 128, a discharge cover 124, and

gaskets

1292 and 1296. It may be implemented excluding some configurations, and additional configurations are not excluded.

The case 110 may form the exterior of the compressor 100 as a recipe. Inside the case 110, there is a compression mechanism unit 120, a drive motor 140, a rotating shaft 130, a valve assembly 126, an intake valve 127, an intake muffler 125, and a main discharge valve. (128), discharge cover 124, and

gaskets

1292 and 1296 may be disposed. Inside the case 110, a compression mechanism 120 for compressing the sucked refrigerant is disposed in the upper area, and a rotation shaft 130 and a drive motor 140 connected to the compression mechanism 120 are located on the lower side of the compression mechanism 120. ) can be placed.

The drive motor 140 may be disposed inside the case 110. The drive motor 140 may be fixed inside the case 110. The drive motor 140 may generate rotational force. The drive motor 140 may transmit rotational force to the compression mechanism 120 to compress the refrigerant. The driving motor 140 may be connected to the rotation shaft 130. As the rotation shaft 130 rotates by driving the drive motor 140, the refrigerant can be compressed within the compression mechanism unit 120.

The driving motor 140 may include

rotors

141 and 142, a stator 143, and a coil 144 wound around the stator 143. The stator 143 may be formed by stacking a plurality of core plates. A first rotor 141 may be rotatably disposed inside the stator 143, and a second rotor 142 may be rotatably disposed outside the stator 143. The first rotor 141 may be coupled to the rotation shaft 130 through a bearing 150. The second rotor 142 may be coupled to the rotation shaft 130 through the rotor plate 145. When power is applied to the coil 144, the

rotors

141 and 142 may rotate the rotation shaft 130 by interacting with the stator 143.

The first rotor 141 and the second rotor 142 can be selectively driven. Through this, efficient driving is possible and power consumption can be reduced by adjusting the drive according to the driving section.

An air gap may be formed between the stator 143 and the first rotor 141, and an air gap may be formed between the stator 143 and the second rotor 142. The rotor plate 145 has through holes formed at positions corresponding to the gap formed between the stator 143 and the first rotor 141 and the gap formed between the stator 143 and the second rotor 142. It may include (145a). An air gap is formed between the stator 143 and the first rotor 141 by inserting a gap liner (not shown) through the through hole 145a, and an air gap is formed between the stator 143 and the second rotor 142. It is possible to have this constant radial gap.

The drive motor 140 may be fixed to the cylinder 123 by a fixed fastening member 160. The stator 143 of the driving motor 140 may be fixed to the cylinder 123 by a fixed fastening member 160. The fixed fastening member 160 may extend in the vertical direction. The fixed fastening member 160 may be inserted and coupled to the protrusion 147 disposed on the upper part of the stator 143. The stator 143 and the protrusion 147 may be formed of different materials. In this case, an insulator 146 may be formed on the upper surface of the stator 143 to insulate the stator 143.

The compression mechanism unit 120 may compress the refrigerant by receiving rotational force from the drive motor 140. The compression mechanism unit 120 can compress and discharge the sucked refrigerant. The compression mechanism unit 120 includes a cylinder 123, a connecting rod 121, a piston 122, a valve assembly 126, an intake valve 127, an intake muffler 125, and a main discharge valve ( 128),

gaskets

1292 and 1296, and a discharge cover 124.

The cylinder 123 forms a compressed space V1 and can be fixed inside the case 110. The refrigerant sucked into the compression space V1 may be compressed by the reciprocating motion of the piston 122 and then discharged to the outside.

The connecting rod 121 may be rotatably connected to the rotation shaft 130. The connecting rod 121 may be connected to the piston 122. Rotation by the drive motor 140 can be converted into linear reciprocating motion.

The piston 122 may be rotatably connected to the connecting rod 121. The piston 122 may reciprocate linearly within the cylinder 123. The piston 122 may compress the refrigerant in the compression space (V1).

Valve assembly 126 may be coupled to cylinder 123. The valve assembly 126 may be coupled to the tip of the cylinder 123. The valve assembly 126 may include a suction hole 1262 and a discharge hole 1264. In one embodiment of the present specification, the valve assembly 126 is described as being formed in a plate shape, but is not limited thereto. The suction hole 1262 of the valve assembly 126 communicates with the suction muffler 125 to suction refrigerant. The discharge hole 1264 of the valve assembly 126 communicates with the discharge cover 124 to discharge compressed refrigerant.

Intake valve 127 may be coupled to valve assembly 126. The intake valve 127 may be coupled to one side of the valve assembly 126. Intake valve 127 may be disposed inside the valve assembly 126. For example, intake valve 127 may be disposed between valve assembly 126 and cylinder 123. The suction valve 127 may open and close the suction hole 1262 of the valve assembly 126. The suction valve 127 may include a fixed end coupled to the valve assembly 126 and a free end 1272 extending from the fixed end to open and close the suction hole 1262. For example, the fixed end of the suction valve 127 may be fixedly coupled to the valve assembly 126, and the free end 1272 may be shaped to extend from the fixed end and cover the suction hole 1262.

The free end 1272 of the suction valve 127 may be spaced apart from the valve assembly 126 during the suction stroke to communicate with the suction hole 1262 and the compression space V1. Specifically, in the case of an intake stroke in which the piston 122 moves away from the valve assembly 126, the pressure in the compression space V1 is lowered, so the free end 1272 of the intake valve 127 is spaced away from the valve assembly 126. , through which fluid can be sucked into the compressed space (V1).

The free end 1272 of the suction valve 127 may be close to or in contact with the valve assembly 126 during the compression stroke and discharge stroke, so that the suction hole 1262 and the compression space V1 are not in communication. Specifically, in the case of the compression stroke and discharge stroke in which the piston 122 approaches the valve assembly 126, the pressure in the compression space V1 increases, so that the free end 1272 of the intake valve 127 is connected to the valve assembly 126. ) can get close to or come into contact with.

The intake valve 127 may include a first through hole 1274. The first through hole 1274 may overlap the discharge hole 1264 and/or the head portion 1282c of the main discharge valve 128. Through this, space efficiency can be improved.

The main discharge valve 128 may be coupled to the valve assembly 126. The main discharge valve 128 may be coupled to one side of the valve assembly 126. The main discharge valve 128 may be disposed outside the valve assembly 126. For example, the main discharge valve 128 may be disposed between the valve assembly 126 and the discharge cover 124. The main discharge valve 128 may open and close the discharge hole 1264 of the valve assembly 126.

The main discharge valve 128 may include a second through hole 1284. The second through hole 1284 may overlap the suction hole 1262 and/or the free end 1272 of the suction valve 127. Through this, space efficiency can be improved.

The main discharge valve 128 may include a discharge valve area 1282. The discharge valve area 1282 may include a first fixed end 1282a and a head portion 1282c extending from the first fixed end 1281a to open and close the discharge hole 1264. For example, the first fixed end 1282a may be fixedly coupled to the valve assembly 126, and the head portion 1282c may be shaped to extend from the first fixed end 1282a and cover the discharge hole 1264. there is.

Gaskets

1292 and 1296 may be disposed between the discharge cover 124 and the cylinder 123. The

gaskets

1292 and 1296 may be formed as a whole in a plate shape with an opening formed in the central area.

Gaskets

1292 and 1296 may include a discharge gasket 1292 and an intake gasket 1296.

The discharge gasket 1292 may be disposed between the discharge cover 124 and the discharge valve 128. The discharge gasket 1292 has a first opening 1295 that overlaps the second through hole 1284 and the suction hole 1262 of the main discharge valve 128, and a first through hole 1274 of the suction valve 127. and a second opening 1294 that overlaps the discharge hole 1264. The discharge gasket 1292 may include a protrusion hole 1293 inserted into the protrusion 1244 of the discharge cover 124.

The intake gasket 1296 may be disposed between the intake valve 127 and the cylinder 123. The suction gasket 1296 may be formed overall into a circular band shape. The intake gasket 1296 may include a third opening formed in a central area.

Intake muffler 125 may be coupled to valve assembly 126. The intake muffler 125 may be coupled to the other side of the valve assembly 126. The intake muffler 125 may be coupled to the outside of the valve assembly 126. The suction muffler 125 may communicate with the suction hole 1262 of the suction muffler 125. The suction muffler 125 may be combined with the discharge cover 124. The suction muffler 125 may be fitted with the discharge cover 124.

Discharge cover 124 may be coupled to valve assembly 126. The discharge cover 124 may be coupled to the other side of the valve assembly 126. The discharge cover 124 may communicate with the discharge hole 1264 of the valve assembly 126. The discharge cover 124 may form a discharge space V2. The refrigerant compressed by the piston 122 flows into the discharge space V2 through the discharge hole 1264, and the refrigerant flowing into the discharge space V2 may be discharged to the outside.

The discharge cover 124 may include at least one extension area 1242 extending to an outer area in the radial direction and a protrusion 1244 protruding toward the cylinder 123 in the extension area. The protrusion hole 1293 of the discharge gasket 1292 may be inserted into the protrusion 1244. The protrusion 1244 may be inserted into a protrusion groove (not shown) of the cylinder 123. Through this, the discharge cover 124 can be coupled to the cylinder 123.

The rotation axis 130 may extend in the vertical direction. The rotation axis 130 may extend in the vertical direction. The rotation axis 130 may be placed inside the case 110. The rotation shaft 130 may be connected to the driving motor 140. The rotation shaft 130 may be connected to the compression mechanism 120. The rotation shaft 130 may be rotated by the drive motor 140 to transmit rotational force for compressing the refrigerant to the compression mechanism unit 120.

When the rotating shaft 130 rotates, the oil feeder 131 installed at the bottom of the rotating shaft 130 pumps the oil stored in the case 110, and some of the oil flows through the oil passage 132 of the rotating shaft 130. It is supplied to the bearing surface as it is absorbed, and some of the oil may scatter from the top of the rotating shaft 130 and be supplied between the cylinder 123 and the piston 122.

Bearing 150 may be coupled to the rotating shaft 130. Bearing 150 may be a one-way bearing. The bearing 150 may be disposed on the outer peripheral surface of the rotating shaft 130. The bearing 150 may be disposed between the rotation shaft 130 and the first rotor 141. The bearing 150 can transmit only the rotational force generated by rotation of the first rotor 141 in one direction to the rotation shaft 130. For example, the first rotor 141 may rotate clockwise or counterclockwise by interaction with the stator 143, and the bearing 150 applies rotational force to the rotary shaft 130 only for clockwise (forward) rotation. ), and for counterclockwise (reverse) rotation, the rotational force may not be transmitted to the rotation shaft 130. Through this, two driving modes can be implemented by rotating both the first rotor 141 and the second rotor 142 in the forward direction, or by transmitting rotational force to the rotation shaft 130 while rotating only the second rotor 142 in the reverse direction. You can.

Figures 6 and 7 are cross-sectional views of the discharge cover, main discharge valve, and discharge gasket of the Recipro compressor according to an embodiment of the present specification. Figure 8 is an enlarged view of a partial area of Figure 7.

Referring to FIGS. 6 to 8 , the discharge cover 124 may include a stopper 1246 extending from the inner surface toward the discharge hole 1264. The stopper 1246 may be entirely formed in the shape of a circular pillar or a square pillar. In this case, it is easy to manufacture the stopper 1246. In contrast, the overall shape of the stopper 1246 may vary depending on the product.

Referring to FIG. 6, in the suction stroke, the piston 122 moves away from the valve assembly 126, and the pressure in the compression space V1 is lowered so that the discharge valve area 1282 of the main discharge valve 128 discharges. It covers the hole (1264). In this case, the pressure in the compression space (V1) is lowered, so the free end 1272 of the intake valve 127 is moved away from the valve assembly 126, and the inside of the intake muffler 125 and the compression space ( V1) becomes connected.

Referring to FIGS. 7 and 8, in the discharge stroke, the piston 122 moves adjacent to the valve assembly 126, and the pressure in the compression space V1 increases, thereby increasing the discharge valve area 1282 of the main discharge valve 128. ) is spaced apart from the valve assembly 126. In this case, the discharge hole 1264 communicates with the discharge space V2, and the compressed refrigerant passes through the discharge hole 1264 and flows into the discharge space V2.

In addition, since the pressure of the compression space (V1) increases in the discharge stroke, the free end 1272 of the suction valve 127 blocks the suction hole 1262 to prevent the compressed refrigerant from leaking through the suction hole 1262. You can.

The stopper 1246 may entirely overlap the discharge hole 1264. During the discharge stroke, the position where the head portion 1282c and the stopper 1246 contact may overlap with the discharge hole 1264. For example, based on FIGS. 7 and 8 , positions where the head portion 1282c and the stopper 1246 contact may overlap in the vertical or vertical direction. Through this, the area between the contact area (P) of the head part 1282c of the main discharge valve 128 and the stopper 1246 and the end 1282b of the head part 1282c is bent by the discharge pressure, so that the discharge stroke The discharge valve area 1282 is quickly opened to reduce excessive pressure in the cylinder 123, and the discharge valve area 1282 is quickly closed during the suction stroke to prevent the discharged refrigerant from flowing back.

The discharge cover 124 may include a discharge passage communicating the internal discharge space V2 with the outside. The area between the end 1282b of the head 1282c at the position P where the head 1282c and the stopper 1246 contact during the discharge stroke may be bent toward the discharge passage. Through this, the discharge refrigerant passing through the discharge hole 1264 and flowing into the discharge space V2 can be allowed to flow smoothly to the outside.

8 and 9, the position (P) where the head portion 1282c of the main discharge valve 128 and the stopper 1246 contact, the first fixed end 1282a of the discharge hole 1264, and The distance L in the first direction in the longitudinal direction of the main discharge valve 128 between the farthest positions may be 0.2 times or more and 0.8 times or less the diameter D1 of the discharge hole 1264. Here, the first direction may be interpreted to mean the horizontal direction or the left and right direction with respect to FIG. 8.

The distance (L) between the position (P) where the head portion (1282c) of the main discharge valve 128 and the stopper (1246) contacts the first fixed end (1282a) and the furthest position among the discharge holes (1264) If the diameter D1 of the discharge hole 1264 is smaller than 0.2 times, the amount of compressed refrigerant passing through the discharge hole 1264 and flowing into the discharge space V2 is small, thereby reducing the cooling power of the compressor 100. It decreases.

In addition, the distance between the position (P) where the head portion 1282c of the main discharge valve 128 and the stopper 1246 contacts the first fixed end 1282a and the furthest position among the discharge holes 1264 ( When L) is greater than 0.8 times the diameter D1 of the discharge hole 1264, the stress applied to the bending area of the head portion 1282c is excessively increased compared to the increase in cooling power of the reciprocating compressor 100. do.

That is, the distance between the position (P) where the head portion 1282c of the main discharge valve 128 and the stopper 1246 contacts and the first fixed end 1282a and the furthest position among the discharge holes 1264 ( When L) is 0.2 to 0.8 times the diameter D1 of the discharge hole 1264, the cooling power of the compressor 100 can be improved compared to the stress applied to the bent area of the head portion 1282c. .

Referring to FIG. 10, the stopper 1246 is formed in a circular pillar shape, and the stopper 1246 may entirely overlap the head portion 1282c of the discharge valve area 1282. In this case, the position P where the head portion 1282c of the main discharge valve 128 and the stopper 1246 contact may form one point. That is, the head portion 1282c of the main discharge valve 128 may make one point contact with the stopper 1246. Through this, the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c.

Referring to FIG. 11, the stopper 1246 is formed in the shape of a square pillar, and the stopper 1246 may entirely overlap the head portion 1282c of the discharge valve area 1282. In this case, the position P where the head portion 1282c of the main discharge valve 128 and the stopper 1246 contact may form one line L1. That is, the head portion 1282c of the main discharge valve 128 may make one line contact with the stopper 1246. Through this, the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c.

Referring to FIG. 12, the stopper 1246 is formed in a circular pillar shape, and the stopper 1246 may entirely overlap the head portion 1282c of the discharge valve area 1282. In this case, the stopper 1246 may include a chamfer 1247 formed on the surface facing the discharge hole 1264. The chamfer 1247 may be formed simultaneously on the surface of the stopper 1246 that faces the discharge passage of the discharge cover 124.

In this case, the angle a1 between the chamfer 1247 and an imaginary line extending the surface of the stopper 1246 facing the discharge hole 1264 may have a predetermined angle. Through this, the area between the position (L2) where the head part 1282c and the stopper 1246 contact in the discharge stroke and the end 1282b of the head part 1282c does not contact the chamfer 1247, thereby allowing the main discharge in the suction stroke. The closing responsiveness of the valve 128 can be improved. Preferably, when the angle a1 between the virtual line extending the surface facing the discharge hole 1264 of the stopper 1246 and the chamfer 1247 is 2° or more, the head portion 1282c in the reciprocal compressor 100 ) and the area between the position L2 where the stopper 1246 contacts and the end 1282b of the head portion 1282c may not be in contact with the chamfer 1247.

In addition, during the discharge stroke, the head portion 1282c and the stopper 1246 may contact one line L2. Through this, the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c, while the position (L2) where the head portion 1282c and the stopper 1246 contact is Since the area between and the end 1282b of the head portion 1282c does not contact the chamfer 1247, the closing responsiveness of the main discharge valve 128 in the suction stroke can be improved.

Referring to FIG. 13, the stopper 1246 is formed in the shape of a square pillar, and the stopper 1246 may entirely overlap the head portion 1282c of the discharge valve area 1282. In this case, the stopper 1246 may include a chamfer 1247 formed on the surface facing the discharge hole 1264. The chamfer 1247 may be formed simultaneously on the surface of the stopper 1246 that faces the discharge passage of the discharge cover 124.

In this case, the angle a1 between the chamfer 1247 and an imaginary line extending the surface of the stopper 1246 facing the discharge hole 1264 may have a predetermined angle. During the discharge stroke, the area between the position L3 where the head part 1282c and the stopper 1246 contact and the end 1282b of the head part 1282c may not be in contact with the chamfer 1247.

In addition, during the discharge stroke, the head portion 1282c and the stopper 1246 may contact one line L3. Through this, the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c, while the position (L3) where the head portion 1282c and the stopper 1246 contact is Since the area between and the end 1282b of the head portion 1282c does not contact the chamfer 1247, the closing responsiveness of the main discharge valve 128 in the suction stroke can be improved.

Referring to FIG. 14, at least a portion of the cross section of the surface of the stopper 1246 facing the discharge hole 1264 may be formed as a curve 1248. Through this, the stress that occurs when the main discharge valve 128 contacts the stopper 1246 can be distributed.

Additionally, the stopper 1246 may include a chamfer 1247 formed in an area far from the first fixed end 1282a. Instead of forming the chamfer 1247, the curve 1248 may be formed so that the radius of curvature increases as the distance from the first fixed end 1282a increases. Through this, the height of the point (P2) where the main discharge valve 128 and the stopper 1246 collide is closer to the discharge hole 1264, thereby lowering the impact force generated between the main discharge valve 128 and the stopper 1246. It is possible to prevent the end 1282b of the main discharge valve 128 from secondary contact with the stopper 1246.

Figure 15 is an exploded perspective view of the discharge cover, valve assembly, main discharge valve, sub discharge valve, suction valve, and gasket of the Recipro compressor according to an embodiment of the present specification. Figure 16 is a front view of a portion of the discharge cover, discharge gasket, sub discharge valve, and main discharge valve of the Recipro compressor according to an embodiment of the present specification. Figure 17 is a schematic diagram of a stopper, a head portion, and a sub-discharge valve of a reciprocal compressor according to an embodiment of the present specification.

Referring to FIGS. 15 to 17 , the reciprocal compressor 100 may further include a sub discharge valve 200. The sub discharge valve 200 may be disposed between the discharge cover 124 and the main discharge valve 128. Specifically, the sub discharge valve 200 may be disposed between the discharge gasket 1292 and the main discharge valve 128.

The sub discharge valve 200 may not overlap the stopper 1246. The sub discharge valve 200 may not overlap the discharge hole 1264. In this case, the sum of the thicknesses of the sub discharge valve 200 and the main discharge valve 128 may correspond to the thickness of the main discharge valve 128 when there is only the main discharge valve 128 without the sub discharge valve 200. there is. Through this, while maintaining the overall rigidity of the main discharge valve 128 and the sub discharge valve 200 the same as before, the main discharge valve 128 bends better even under weak force, improving the responsiveness of the main discharge valve 128. can be improved.

The sub discharge valve 200 may include a second fixed end fixed to the valve assembly 126. The second fixed end of the sub discharge valve 200 may overlap the first fixed end 1282a of the main discharge valve 128. Through this, the overall rigidity of the main discharge valve 128 and the sub discharge valve 200 can be maintained the same as before.

The sub discharge valve 200 may include a rigid body 202 extending from the second fixed end. Rigid body 202 may entirely overlap discharge valve area 1282. The rigid body 202 may not overlap the discharge hole 1264. The rigid body 202 may not overlap the stopper 1246. The width of the rigid body 202 may be equal to or smaller than the width of the discharge valve area 1282.

Referring to FIGS. 18 and 19 , the length of the discharge hole 1264 in the first direction, which is the longitudinal direction of the main discharge valve 128, may be formed to be larger than the length of the discharge hole 1264 in the second direction perpendicular to the first direction. For example, the first direction may be interpreted as a left-right direction or a horizontal direction based on FIGS. 18 and 19, and the second direction may be interpreted as a vertical direction or a vertical direction based on FIG. 18. For example, the discharge hole 1264 may be formed in an oval shape or a peanut shape. As shown in FIG. 19 , one area 1264a of the cross section of the discharge hole 1264 may be formed to be inclined. Additionally, the other area 1264b of the cross section of the discharge hole 1264 may be formed to be convex inward. In this case, the width of the discharge valve area 1282 of the main discharge valve 128 may also be formed to be narrower than before. Through this, the width of the discharge hole 1264 is narrowed compared to the circular shape having the same effective area, so that the discharge pressure of the discharge refrigerant can be increased to better bend the discharge valve area 1282 of the main discharge valve 128.

Any or other embodiments of the present disclosure described above are not exclusive or distinct from each other. Certain embodiments or other embodiments of the present specification described above may have their respective configurations or functions used in combination or combined.

For example, this means that configuration A described in a particular embodiment and/or drawing may be combined with configuration B described in other embodiments and/or drawings. In other words, even if the combination between components is not directly explained, it means that combination is possible, except in cases where it is explained that combination is impossible.

The above detailed description should not be construed as restrictive in any respect and should be considered illustrative. The scope of this specification should be determined by reasonable interpretation of the appended claims, and all changes within the equivalent scope of this specification are included in the scope of this specification.

Claims

case;

a drive motor disposed inside the case;

a rotating shaft connected to the driving motor;

a cylinder disposed inside the case and forming a compressed space;

A piston that reciprocates linearly within the cylinder as the rotation shaft rotates;

a valve assembly including a discharge hole and coupled to the tip of the cylinder;

a discharge cover coupled to the outside of the valve assembly; and

A main discharge valve disposed between the discharge cover and the valve assembly and opening and closing the discharge hole,

The main discharge valve includes a first fixed end fixed to the valve assembly, and a head portion extending from the first fixed end to open and close the discharge hole,

The discharge cover includes a stopper extending from an inner surface toward the discharge hole,

The compressor where the position where the head part and the stopper contact during the discharge stroke overlaps the discharge hole.
According to claim 1,

The head portion is a reciprocating compressor in which one point contact or one line contact is made with the stopper.
According to claim 1,

The distance in the first direction in the longitudinal direction of the main discharge valve between the position where the head part and the stopper contact and the first fixed end and the furthest position among the discharge holes is 0.2 to 0.8 times the diameter of the discharge hole. Pro Compressor.
According to claim 1,

The stopper is a reciprocating compressor that entirely overlaps the discharge hole.
According to claim 1,

The discharge cover includes a discharge passage communicating the interior discharge space with the exterior,

A reciprocating compressor in which an area between the ends of the head portion at a position where the head portion and the stopper contact during the discharge stroke is bent toward the discharge passage.
According to claim 5,

The stopper includes a chamfer formed on a surface facing the discharge hole,

A reciprocating compressor in which an area between a position where the head part and the stopper contact in the discharge stroke and an end of the head part does not contact the chamfer.
According to claim 6,

A reciprocal compressor wherein the angle between the chamfer and an imaginary line extending a surface of the stopper facing the discharge hole is 2° or more.
According to claim 6,

A reciprocating compressor in which the head part and the stopper make one line contact during the discharge stroke.
According to claim 1,

It includes a sub-discharge valve disposed between the discharge cover and the main discharge valve,

The sub-discharge valve is a reciprocating compressor that does not overlap the stopper.
According to clause 9,

The sub-discharge valve is a reciprocating compressor that does not overlap the discharge hole.
According to clause 9,

The sub-discharge valve includes a second fixed end fixed to the valve assembly,

The second fixed stage is a reciprocating compressor that overlaps the first fixed stage.
According to claim 1,

The discharge hole is a reciprocating compressor in which a length in a first direction, which is the longitudinal direction of the main discharge valve, is formed to be larger than a length in a second direction perpendicular to the first direction.
According to claim 1,

A reciprocating compressor wherein at least a portion of a cross section of the surface of the stopper facing the discharge hole is curved.
According to claim 13,

The curve is a recipe compressor in which the radius of curvature increases as the distance from the first fixed end increases.
According to claim 1,

The stopper is a reciprocating compressor formed in the shape of a circular pillar or a square pillar.
case;

a drive motor disposed inside the case;

a rotating shaft connected to the driving motor;

a cylinder disposed inside the case and forming a compressed space;

A piston that reciprocates linearly within the cylinder as the rotation shaft rotates;

a valve assembly including a discharge hole and coupled to the tip of the cylinder;

a discharge cover coupled to the outside of the valve assembly;

a main discharge valve disposed between the discharge cover and the valve assembly and opening and closing the discharge hole; and

It includes a sub-discharge valve disposed between the discharge cover and the main discharge valve,

The main discharge valve includes a first fixed end fixed to the valve assembly, and a head portion extending from the first fixed end to open and close the discharge hole,

The discharge cover includes a stopper extending from an inner side toward the discharge hole,

The sub-discharge valve is a reciprocating compressor that does not overlap the stopper.
According to claim 16,

The sub-discharge valve includes a second fixed end fixed to the valve assembly,

The second fixed stage is a reciprocating compressor that overlaps the first fixed stage.
According to claim 16,

A reciprocating compressor in which the width of the sub discharge valve is narrower than the width of the main discharge valve.
case;

a drive motor disposed inside the case;

a rotating shaft connected to the driving motor;

a cylinder disposed inside the case and forming a compressed space;

A piston that reciprocates linearly within the cylinder as the rotation shaft rotates;

a valve assembly including a discharge hole and coupled to the tip of the cylinder;

a discharge cover coupled to the outside of the valve assembly; and

A main discharge valve disposed between the discharge cover and the valve assembly and opening and closing the discharge hole,

The main discharge valve includes a first fixed end fixed to the valve assembly, and a head portion extending from the first fixed end to open and close the discharge hole,

The discharge cover includes a stopper extending from an inner surface toward the discharge hole,

A reciprocating compressor wherein at least a portion of a cross section of the surface of the stopper facing the discharge hole is curved.
According to claim 19,

The curve is a recipe compressor in which the radius of curvature increases as the distance from the first fixed end increases.