WO2023182580A1 - Compresseur alternatif - Google Patents

Compresseur alternatif Download PDF

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Publication number
WO2023182580A1
WO2023182580A1 PCT/KR2022/010923 KR2022010923W WO2023182580A1 WO 2023182580 A1 WO2023182580 A1 WO 2023182580A1 KR 2022010923 W KR2022010923 W KR 2022010923W WO 2023182580 A1 WO2023182580 A1 WO 2023182580A1
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WO
WIPO (PCT)
Prior art keywords
discharge
valve
stopper
discharge hole
valve assembly
Prior art date
Application number
PCT/KR2022/010923
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English (en)
Korean (ko)
Inventor
김영환
이종목
김상민
Original Assignee
엘지전자 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Publication of WO2023182580A1 publication Critical patent/WO2023182580A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • 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.
  • 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.
  • a power generating device such as a motor or turbine
  • compressors are widely applied throughout industry and home appliances, especially vapor compression refrigeration cycles (hereinafter referred to as 'refrigeration cycles').
  • 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
  • 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.
  • 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.
  • the connected Recipro compressor is referred to as a 'Recipro compressor'.
  • the Recipro compressor is used to compress refrigerant in refrigerators.
  • the power consumption regulations for refrigerators have recently been strengthened, the demand for low cooling power and high efficiency has increased.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • the position where the head part and the stopper contact during the discharge stroke may overlap with the discharge hole.
  • 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.
  • the head portion may make one point contact or one line contact with the stopper.
  • 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.
  • the stopper may entirely overlap the discharge hole.
  • 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.
  • 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.
  • 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. .
  • the angle between the chamfer and an imaginary line extending the surface of the stopper facing the discharge hole may be 2° or more.
  • 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.
  • the main discharge valve 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a compressor can be provided with a recipe that can better bend the main discharge valve by increasing the discharge pressure.
  • FIG. 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.
  • FIGS 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.
  • FIGS 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.
  • FIG. 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.
  • the reciprocal compressor 100 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • the stopper 1246 may entirely overlap the discharge hole 1264.
  • the position where the head portion 1282c and the stopper 1246 contact may overlap with the discharge hole 1264.
  • positions where the head portion 1282c and the stopper 1246 contact may overlap in the vertical or vertical direction.
  • 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.
  • 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.
  • 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.
  • the first direction may be interpreted to mean the horizontal direction or the left and right direction with respect to FIG. 8.
  • the cooling power of the compressor 100 can be improved compared to the stress applied to the bent area of the head portion 1282c.
  • 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.
  • 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.
  • 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.
  • the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c.
  • 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.
  • 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.
  • the area where the main discharge valve 128 and the stopper 1246 meet is minimized to enable smooth bending of the head portion 1282c.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the head portion 1282c and the stopper 1246 may contact one line L2.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the head portion 1282c and the stopper 1246 may contact one line L3.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIGS 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.
  • 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.
  • 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.
  • the discharge hole 1264 may be formed in an oval shape or a peanut shape.
  • one area 1264a of the cross section of the discharge hole 1264 may be formed to be inclined.
  • the other area 1264b of the cross section of the discharge hole 1264 may be formed to be convex inward.
  • 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.
  • configuration A described in a particular embodiment and/or drawing may be combined with configuration B described in other embodiments and/or drawings.
  • configuration A described in a particular embodiment and/or drawing may be combined with configuration B described in other embodiments and/or drawings.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

Est fourni un compresseur alternatif. Le compresseur alternatif selon un aspect de la présente invention comprend : un boîtier; un moteur d'entraînement disposé dans le boîtier; un arbre rotatif relié au moteur d'entraînement; un cylindre disposé dans le boîtier et formant un espace de compression; un piston réalisant un mouvement de va-et-vient linéaire dans le cylindre en fonction de la rotation de l'arbre rotatif; un ensemble soupape comportant un trou d'évacuation et accouplé à l'extrémité avant du cylindre; un couvercle d'évacuation accouplé à l'extérieur de l'ensemble soupape; et un couvercle d'évacuation principal disposé entre le couvercle d'évacuation et l'ensemble soupape et ouvrant et fermant le trou d'évacuation. La soupape d'évacuation principale comporte une première extrémité fixe qui est fixée à l'ensemble soupape et une partie tête qui s'étend à partir de la première extrémité fixe et ouvre et ferme le trou d'évacuation. Le couvercle d'évacuation comporte un bouchon s'étendant à partir de la surface interne en direction du trou d'évacuation, et la position au niveau de laquelle la partie tête et le bouchon entrent en contact l'un avec l'autre pendant un cycle d'évacuation peut chevaucher le trou d'évacuation.
PCT/KR2022/010923 2022-03-21 2022-07-26 Compresseur alternatif WO2023182580A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020220034588A KR20230137013A (ko) 2022-03-21 2022-03-21 레시프로 압축기
KR10-2022-0034588 2022-03-21

Publications (1)

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WO2023182580A1 true WO2023182580A1 (fr) 2023-09-28

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PCT/KR2022/010923 WO2023182580A1 (fr) 2022-03-21 2022-07-26 Compresseur alternatif

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KR (1) KR20230137013A (fr)
WO (1) WO2023182580A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5213488A (en) * 1990-01-09 1993-05-25 Sanden Corporation Valved discharge mechanism of a refrigerant compressor
KR0165600B1 (ko) * 1995-09-05 1999-03-20 구자홍 밀폐형 압축기의 소음저감장치
KR100273739B1 (ko) * 1997-08-27 2000-12-15 배길성 밀폐형 압축기의 밸브 장치
KR20070093765A (ko) * 2006-03-15 2007-09-19 엘지전자 주식회사 밀폐형 압축기의 헤드커버 및 이를 사용한 밸브 어셈블리
KR20200017808A (ko) * 2018-08-09 2020-02-19 주식회사 대우컴프레셔 밀폐형 압축기용 밸브 장치 및 그 밸브 스톱퍼

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101484324B1 (ko) 2009-04-09 2015-01-20 엘지전자 주식회사 리니어 압축기 및 이에 적용된 피스톤

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5213488A (en) * 1990-01-09 1993-05-25 Sanden Corporation Valved discharge mechanism of a refrigerant compressor
KR0165600B1 (ko) * 1995-09-05 1999-03-20 구자홍 밀폐형 압축기의 소음저감장치
KR100273739B1 (ko) * 1997-08-27 2000-12-15 배길성 밀폐형 압축기의 밸브 장치
KR20070093765A (ko) * 2006-03-15 2007-09-19 엘지전자 주식회사 밀폐형 압축기의 헤드커버 및 이를 사용한 밸브 어셈블리
KR20200017808A (ko) * 2018-08-09 2020-02-19 주식회사 대우컴프레셔 밀폐형 압축기용 밸브 장치 및 그 밸브 스톱퍼

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