WO2015129184A1 - 密閉型圧縮機および冷凍装置 - Google Patents
密閉型圧縮機および冷凍装置 Download PDFInfo
- Publication number
- WO2015129184A1 WO2015129184A1 PCT/JP2015/000651 JP2015000651W WO2015129184A1 WO 2015129184 A1 WO2015129184 A1 WO 2015129184A1 JP 2015000651 W JP2015000651 W JP 2015000651W WO 2015129184 A1 WO2015129184 A1 WO 2015129184A1
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- WIPO (PCT)
- Prior art keywords
- piston
- cylinder
- hermetic compressor
- shaft
- sliding surface
- Prior art date
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Classifications
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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
- 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
- F04B39/0094—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 crankshaft
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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
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
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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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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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
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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
- 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
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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
- 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
- F04B39/0022—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 piston rods
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
Definitions
- the present invention relates to a hermetic compressor for reducing sliding loss of a piston and a refrigeration apparatus equipped with the same.
- FIG. 8 is a longitudinal sectional view of a conventional hermetic compressor.
- FIG. 9 is a cross-sectional view of a main part around a piston in a compression stroke of a conventional hermetic compressor.
- FIG. 10 is a cross-sectional view of a main part around a piston in a suction stroke of a conventional hermetic compressor.
- an electric element 304 having a stator 302 and a rotor 303 and a compression element 305 driven by the electric element 304 are contained in an airtight container 301 of a conventional hermetic compressor. Contained.
- the shaft 310 has a main shaft portion 311 and an eccentric shaft portion 312 formed eccentrically at one end thereof.
- a rotor 303 is fixed to the main shaft portion 311.
- the cylinder block 314 has a substantially cylindrical cylinder 315 and a bearing portion 320.
- a piston 323 is reciprocally inserted in the cylinder 315, and a valve plate 350 is mounted on the end surface thereof.
- a compression chamber 316 is formed by the cylinder 315 and the piston 323.
- a piston pin 325 is attached to the piston 323 so as to be parallel to the eccentric shaft portion 312.
- the bearing portion 320 forms a cantilever bearing by pivotally supporting the main shaft portion 311 of the shaft 310.
- the connecting rod 326 includes a large hole end portion 328, a small hole end portion 329, and a rod portion 330.
- the large hole end 328 is fitted to the eccentric shaft portion 312.
- the small hole end portion 329 is connected to the piston 323 via the piston pin 325.
- the eccentric shaft 312 and the piston 323 are connected by the connecting rod 326 and the piston pin 325.
- the axis C indicates the axis of the piston 323, and the axis D indicates the axis of the cylinder 315.
- the piston 323 In the compression stroke of the reciprocating motion of the piston 323, the piston 323 is pushed toward the eccentric shaft portion 312 by a compressive load that compresses the refrigerant gas, so that the shaft 310 is inclined in the bearing portion 320. As the shaft 310 is inclined, the axis C of the piston 323 is also inclined. For this reason, the axis C of the piston 323 and the axis D of the cylinder 315 are formed so that the axis D of the cylinder 315 is inclined so as to coincide with each other during the compression stroke. Thereby, the twist of the piston 323 in the cylinder 315 is reduced in the compression stroke, the sliding loss can be reduced, and high efficiency can be achieved.
- the piston 323 is pulled toward the cylinder 315 by the suction load for sucking the refrigerant gas in the reciprocating suction stroke of the piston 323. Tilt to 315 side. Along with this, the axis C of the piston 323 is shifted from the axis D of the cylinder 315 formed by being tilted in advance.
- the axis C of the piston 323 is further inclined so that the tip of the piston 323 is pressed against the bottom surface side of the compression chamber 316. For this reason, there is a problem that the piston 323 is twisted and the input increases.
- the present invention solves such a conventional problem, and provides a highly efficient hermetic compressor that reduces the twist caused by the tilting of the piston during the intake stroke and prevents an increase in input. is there.
- the hermetic compressor of the present invention is a hermetic compressor in which an electric element and a compression element driven by the electric element are accommodated in an airtight container.
- the compression element includes a main shaft portion, a shaft having an eccentric shaft portion that moves integrally with the main shaft portion, and a bearing portion that forms a cantilever bearing by pivotally supporting the main shaft portion of the shaft.
- the compression element includes a cylinder that compresses gas, a piston that is reciprocally inserted into the cylinder, and a connecting rod that connects the eccentric shaft portion and the piston.
- the angle a1 formed by the first center line indicating the axis of the bearing portion and the second center line indicating the axis of the cylinder and the absolute value c1 of the angle of inclination of the shaft with respect to the bearing portion are expressed by the equation Satisfy (1).
- the outer peripheral surface of the piston has a gap with the inner peripheral surface of the cylinder and forms a sliding portion, an extension portion that is located behind the sealing portion and forms the sliding surface, and a sealing portion And a non-sliding portion that does not form a sliding surface.
- the hermetic compressor of the present invention can reduce local twisting in the intake stroke of the piston and prevent an increase in input, so that the efficiency can be improved.
- FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 2 is an enlarged cross-sectional view of a main part when a compression load acts during the compression stroke of the hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 3 is an enlarged cross-sectional view of a main part when a suction load acts during the suction stroke of the hermetic compressor according to the first embodiment of the present invention.
- FIG. 4 is a top sectional view of the cylinder / piston of the hermetic compressor according to the first embodiment of the present invention.
- FIG. 5 is a longitudinal sectional view of the cylinder / piston of the hermetic compressor according to the first embodiment of the present invention.
- FIG. 6 is a cross-sectional view of the main part showing the positional relationship between the bearing portion and the cylinder of the hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 7 is a schematic cross-sectional view of the refrigerator in the second embodiment of the present invention.
- FIG. 8 is a longitudinal sectional view of a conventional hermetic compressor.
- FIG. 9 is a cross-sectional view of a main part around a piston in a compression stroke of a conventional hermetic compressor.
- FIG. 10 is a cross-sectional view of a main part around a piston in a suction stroke of a conventional hermetic compressor.
- FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 2 is an enlarged cross-sectional view of a main part when a compression load is applied during the compression stroke of the hermetic compressor.
- FIG. 3 is an enlarged cross-sectional view of a main part when a suction load acts during the suction stroke of the hermetic compressor.
- FIG. 4 is a top sectional view of the cylinder / piston of the hermetic compressor.
- FIG. 5 is a longitudinal sectional view of a cylinder / piston of the hermetic compressor.
- FIG. 6 is a cross-sectional view of the main part showing the positional relationship between the bearing portion and the cylinder of the hermetic compressor.
- the hermetic container 101 accommodates an electric element 104 including a stator 102 and a rotor 103 and a compression element 105 driven by the electric element 104. Furthermore, lubricating oil 106 is stored at the bottom of the sealed container 101.
- the sealed container 101 is filled with a hydrocarbon-based R600a refrigerant 106, and a lubricating oil 102 of low-viscosity oil VG3 to VG10 is sealed at the bottom.
- the electric element 104 includes a rotor 103 and a stator 102, and is driven by an inverter (not shown) at a plurality of operation frequencies including at least an operation frequency equal to or higher than a power supply frequency.
- the maximum operating frequency for driving the electric element 104 is 80 Hz, and the electric element 104 is driven at an operating frequency of 17 Hz or more.
- the shaft 110 has a main shaft portion 111 and an eccentric shaft portion 112 formed eccentrically at one end of the main shaft portion 111 so as to move integrally with the main shaft portion 111.
- the rotor 103 is fixed to the main shaft portion 111.
- An oil supply passage 113 is provided inside and on the surface of the shaft 110. The lower portion of the oil supply passage 113 extends so as to be immersed in the lubricating oil 106 to a predetermined depth position of the lubricating oil 106.
- the cylinder block 114 includes a cylinder 115 (including a substantially cylindrical shape) and a bearing portion 120.
- the bearing portion 120 forms a cantilever bearing by pivotally supporting the main shaft portion 111 of the shaft 110.
- a piston 123 is reciprocally inserted in the cylinder 115.
- a valve plate 150 is attached to the end of the cylinder 115.
- a compression chamber 116 is formed by the cylinder 115 and the piston 123.
- the piston 123 is attached to the piston 123 so as to be parallel to the eccentric shaft portion 112. As shown in FIGS. 4 and 5, a seal portion 123 a and an extension portion 123 b are provided on the outer peripheral surface of the piston 123.
- the seal portion 123 a forms a sliding surface in a cylindrical shape so as to have a small clearance with respect to the inner peripheral surface of the cylinder 115.
- the extension part 123b has the same radius as the seal part 123a on both side surfaces behind the seal part 123a, and forms a sliding surface extended with a constant width in the axial direction of the piston 123.
- On the vertical upper and lower surfaces behind the seal portion 123a a non-sliding portion 123c that does not slide due to a larger clearance with respect to the inner peripheral surface of the cylinder 115 is provided.
- the connecting rod 126 includes a large hole end portion 128, a small hole end portion 129, and a rod portion 130.
- the large hole end portion 128 is fitted to the eccentric shaft portion 112.
- the small hole end portion 129 is connected to the piston 123 via the piston pin 125.
- the eccentric shaft portion 112 and the piston 123 are connected by the connecting rod 126 and the piston pin 125.
- the shaft 110, the connecting rod 126, the piston pin 125, and the piston 123 that constitute a part of the compression element 105 are the axis 144 of the main shaft portion 111 of the shaft 110 and the axis of the piston 123 that reciprocates.
- the center C is assembled at an angle ⁇ / 2 (rad). This is because the driving loss is smoothest during driving and the driving loss is reduced.
- the configuration of the present embodiment is also like that.
- the dimensions of the piston 123 in the present embodiment are a diameter of 26 mm and a total length of 23 mm, and the axial lengths of the seal portion 123a and the extension portion 123b are 8 mm and 15 mm, respectively.
- the radial clearance between the inner peripheral surface of the cylinder 115 and the seal portion 123a and the extension portion 123b which are sliding surfaces is 0.005 mm.
- the radial clearance between the inner peripheral surface of the cylinder 115 and the non-sliding portion 123c is 0.5 mm.
- a projection plane parallel to the first center line 141 indicating the axis of the bearing 120 and parallel to the second center line 142 indicating the axis of the cylinder 115 is considered.
- An angle formed by the first center line 141 and the second center line 142 is a1.
- the absolute value of the inclination angle of the shaft 110 with respect to the bearing portion 120 due to the diameter clearance between the bearing portion 120 and the main shaft portion 111 is defined as c1 (rad).
- the cylinder block 114 (cylinder 115) is configured such that a1 and c1 satisfy the formula (1).
- the piston 123 reciprocates in the cylinder 115.
- the reciprocating motion of the piston 123 causes the refrigerant gas to be sucked into the compression chamber 116 from a cooling system (not shown) having a refrigeration cycle.
- the refrigerant gas is compressed in the compression chamber 116 and then discharged to the cooling system again.
- a pumping action is applied to the lower end of the oil supply passage 113 by the rotation of the shaft 110.
- the lubricating oil 106 at the bottom of the sealed container 101 is pumped upward through the oil supply passage 113 and scatters horizontally in the entire circumferential direction in the sealed container 101.
- the scattered lubricating oil 106 is supplied to the piston pin 125, the piston 123, etc., and lubricates the piston pin 125, the piston 123, etc.
- a compression load when compressing a refrigerant gas is supported only on one side of the main shaft portion 111 of the shaft 110. Therefore, when a compressive load is applied during the compression stroke, the shaft 110 is inclined within the diameter clearance between the main shaft portion 111 and the bearing portion 120 as shown in FIG. Therefore, since the angle of the axis C of the piston 123 with respect to the axis 144 of the main shaft 111 is set to ⁇ / 2 (rad), the valve plate 150 side of the piston 123 is lifted above the horizontal line. Tilt.
- valve plate 150 side of the axis D of the cylinder 115 is formed in advance so as to be inclined upward from the horizontal line.
- an intersection of a first center line 141 indicating the axis of the bearing 120 and a second center line 142 indicating the axis of the cylinder 115 is defined as O.
- the absolute value of the angle of inclination of the shaft 110 with respect to the bearing portion 120 based on the diameter clearance between the bearing portion 120 and the main shaft portion 111 is defined as c1.
- the cylinder 115 is moved so that the angle a1 between the first center line 141 indicating the axis of the bearing portion 120 and the second center line 142 indicating the axis of the cylinder 115 satisfies the expression (1).
- the angle a1 represented by the expression (1) is set as the design value of the angle of the axis of the cylinder 115.
- the angle a1 is designed to approach an actual value using the absolute value c1 of the angle of inclination of the shaft 110 with respect to the bearing portion 120. Therefore, the twist between the piston 123 and the cylinder 115 can be more reliably reduced.
- the piston 123 of the hermetic compressor used for the same application as that of the present embodiment is formed with the entire axial length of the piston 123 as a seal portion 123a in order to ensure sealing performance and sliding reliability. Is done.
- the radial clearance of the seal portion 123a is the smallest among the constituent elements of the compression element 105, and is 0.005 mm in the present embodiment. Therefore, the maximum amount of radial inclination of the seal portion 123a during the suction stroke is greater than the radial clearance 0.005 mm of the seal portion 123a. For this reason, the E portion on the compression chamber 116 side of the piston 123 and the F portion on the eccentric shaft portion 112 side are twisted.
- the sliding portion of the piston 123 is composed of the seal portion 123a and the extension portions 123b on both side surfaces that support the side pressure.
- F part is non-sliding part 123c whose radius clearance is 0.5 mm, and is sufficiently larger than the radial clearance 0.005 mm of the seal part. For this reason, the piston 123 does not come into contact with the inner peripheral surface of the cylinder 115 at the F portion.
- the maximum radial amount L ⁇ Sin ( ⁇ ) of the seal portion 123a in the radial direction due to the shaft misalignment angle ⁇ is smaller than the radial clearance 0.005 mm because the length L of the seal portion 123a is small. .
- the inclination angle of the piston 123 is smaller during the suction stroke than during the compression stroke. Further, since the piston 123 and the cylinder 115 are smaller in the suction stroke than in the compression stroke, the twist between the piston 123 and the cylinder 115 in the suction stroke is effectively reduced.
- the sliding loss between the piston 123 and the cylinder 115 can be reduced and the efficiency can be increased during both the compression and suction strokes.
- the hermetic compressor according to the present embodiment is a hermetic compressor in which the electric element 104 and the compression element 105 driven by the electric element 104 are accommodated in the hermetic container 101.
- the compression element 105 includes a main shaft 111, a shaft 110 having an eccentric shaft 112 that moves integrally with the main shaft 111, and a bearing 120 that forms a cantilever bearing by supporting the main shaft 111 of the shaft 110.
- the compression element 105 includes a cylinder 115 that compresses gas, a piston 123 that is reciprocally inserted into the cylinder 115, and a connecting rod 126 that connects the eccentric shaft portion 112 and the piston 123.
- the absolute angle of the angle a1 formed by the first center line 141 indicating the axis of the bearing portion 120 and the second center line 142 indicating the axis of the cylinder 115 and the inclination angle of the shaft 110 with respect to the bearing portion 120 are absolute.
- the value c1 satisfies the formula (1).
- the outer peripheral surface of the piston 123 has a gap with the inner peripheral surface of the cylinder 115, and forms a sliding surface, a seal portion 123a, and an extension portion that is located behind the sealing portion 123a and forms a sliding surface.
- 123b and the non-sliding part 123c which is located behind the seal part 123a and does not form a sliding surface.
- the extension portion 123b has the same radius as the seal portion 123a, and forms a sliding surface that supports the side pressure. As a result, local twisting of the piston can be reduced, an increase in input can be prevented, and high efficiency can be achieved.
- the electric element 104 is driven at a plurality of rotation speeds by an inverter circuit.
- FIG. 7 is a schematic cross-sectional view of the refrigerator in the second embodiment of the present invention.
- a refrigerator will be described as an example of the refrigeration apparatus.
- the refrigerator in FIG. 7 is mounted with the hermetic compressor described in the first embodiment.
- the heat insulating box 180 includes an inner box 182, an outer box 184, and a heat insulating wall.
- the inner box 182 is formed by vacuum molding a resin body such as ABS (Acrylonitrile, Butadiene, Styrene).
- a metal material such as a pre-coated steel plate is used for the outer box 184.
- the heat insulating wall is formed by injecting a heat insulating body 186 to be foam-filled into a space formed by the inner box 182 and the outer box 184.
- the heat insulator 186 for example, rigid urethane foam, phenol foam, styrene foam, or the like is used.
- the foaming material use of hydrocarbon-based cyclopentane is better from the viewpoint of preventing global warming.
- the heat insulation box 180 is divided into a plurality of heat insulation sections, and the upper part is configured as a revolving door type and the lower part as a drawer type.
- the plurality of heat insulation compartments are, from above, a refrigerator compartment 188, a drawer type switching room 190 and an ice making room 192, a drawer type vegetable room 194, and a drawer type freezing room 196 provided side by side.
- Each heat insulation section is provided with a heat insulation door via a gasket. From the top, the refrigerating room rotary door 198, the switching room drawer door 200, the ice making room drawer door 202, the vegetable room drawer door 204, and the freezer compartment drawer door 206.
- the outer box 184 of the heat insulation box 180 is provided with a recess 208 having a recessed top surface.
- the refrigeration cycle includes a hermetic compressor 210, a condenser (not shown) provided on the side of the heat insulating box 180, a capillary 212 as a decompressor, a dryer (not shown) for removing moisture, and evaporation.
- the vessel 216 and the suction pipe 218 are connected in a ring shape.
- the hermetic compressor 210 is the hermetic compressor described in the first embodiment, and is elastically supported by the recess 208.
- the evaporator 216 is provided with a cooling fan 214 in the vicinity on the back of the vegetable compartment 194 and the freezer compartment 196.
- the temperature of the refrigerator compartment 188 is usually set at 1 to 5 ° C., with the lower limit being the temperature that does not freeze for refrigerated storage.
- the temperature of the switching chamber 190 can be changed by the user, and the setting can be changed within a predetermined temperature range from the freezer temperature range to the refrigeration and vegetable room temperature ranges.
- the ice making room 192 is an independent ice storage room.
- the ice making chamber 192 includes an automatic ice making device (not shown), and automatically creates and stores ice.
- the temperature of the ice making chamber 192 is a freezing temperature zone for storing ice, but may be set at a freezing temperature of ⁇ 18 ° C. to ⁇ 10 ° C., which is relatively higher than the freezing temperature zone for storing ice. Is possible.
- the temperature of the vegetable room 194 is often set to 2 ° C. to 7 ° C., which is the same as or slightly higher than that of the refrigerator room 188. It is possible to maintain the freshness of leafy vegetables for a long period of time as the temperature is lowered so as not to freeze.
- the temperature of the freezer compartment 196 is normally set at ⁇ 22 to ⁇ 18 ° C. for frozen storage. However, it may be set at a low temperature of, for example, ⁇ 30 to ⁇ 25 ° C. in order to improve the frozen storage state.
- Each room is separated by a heat insulating wall to efficiently maintain different temperature settings.
- it is possible to foam-fill the heat insulation box 180 integrally with the heat insulator 186.
- foam filling with the heat insulator 186, it is possible to achieve a heat insulation performance that is approximately twice that of using a heat insulating member such as polystyrene foam, and the storage volume can be increased by thinning the partition.
- the cooling operation is started and stopped by a signal from a temperature sensor (not shown) and a control board.
- the hermetic compressor 210 performs a predetermined compression operation according to the instruction of the cooling operation.
- the discharged high-temperature and high-pressure refrigerant gas dissipates heat in a condenser (not shown) to be condensed and liquefied, and is depressurized by the capillary 212 to become a low-temperature and low-pressure liquid refrigerant and reaches the evaporator 216.
- the cooling fan 214 By the operation of the cooling fan 214, heat is exchanged with the air in the refrigerator, the refrigerant gas in the evaporator 216 is evaporated, and the low-temperature cold air that has been heat-exchanged is distributed by a damper (not shown), etc.
- the chamber is cooled.
- the cylinder block 114 includes the first center line 141 indicating the axis of the bearing 120 and the cylinder 115.
- the bearing portion 120 and the cylinder 115 are arranged so that the second center line 142 indicating the axial center of the shaft intersects each other.
- the absolute value c1 of the angle between the angle a1 (rad) formed by the first center line 141 and the second center line 142 and the inclination of the shaft 110 with respect to the bearing portion 120 due to the diameter clearance between the bearing portion 120 and the main shaft portion 111 ( rad) satisfies the formula (1).
- the piston 123 has a cylindrical seal portion 123a that has a uniform gap with the inner peripheral surface of the cylinder 115 on the outer peripheral surface and forms a sliding surface. Furthermore, the piston 123 has an extension part 123b that is located behind the seal part 123a, has the same radius as the seal part 123a, and forms a sliding surface that supports the side pressure.
- the sliding area when the piston 123 tilts becomes small.
- the piston 123 has only an extension portion 123b that forms a sliding surface that supports the lateral pressure behind the cylindrical seal portion 123a that forms the sliding surface of the piston 123, and the sliding surface in the vertical vertical direction. It is because it does not have.
- the refrigerator of the present embodiment is a refrigeration apparatus that uses the hermetic compressor of the first embodiment for the refrigeration cycle. Thereby, the power consumption of a freezing apparatus can be reduced.
- the hermetic compressor according to the present invention can improve the efficiency by reducing the sliding loss of the piston, and is not limited to an electric refrigerator-freezer for home use, but also an air conditioner, a vending machine, and others. It can be applied to refrigeration equipment.
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Abstract
Description
これにより、吸入行程時に、シリンダの軸心とピストンの軸心との軸心ズレが大きくなった場合においても、ピストンの摺動面を形成するシール部の後方には、摺動面を形成する側面延長部が存在する。これにより、鉛直上下方向には摺動面となる部分を有していない。したがって、ピストン傾斜時の鉛直上下方向の局所的なこじりを軽減することができる。
図1は、本発明の実施の形態1における密閉型圧縮機の縦断面図である。図2は、同密閉型圧縮機の圧縮行程時に圧縮荷重が作用するときの要部拡大断面図である。図3は、同密閉型圧縮機の吸入行程時に吸引荷重が作用するときの要部拡大断面図である。図4は、同密閉型圧縮機のシリンダ・ピストンの上視断面図である。図5は、同密閉型圧縮機のシリンダ・ピストンの縦断面図である。図6は、同密閉型圧縮機の軸受部とシリンダとの位置関係を示す要部断面図である。
以上のように構成された密閉型圧縮機について、以下にその動作を説明する。電動要素104に通電されると、回転子103はシャフト110を回転させる。シャフト110の回転に伴う偏心軸部112の回転運動が、コンロッド126を介して、ピストン123に伝えられる。
図7は、本発明の実施の形態2における冷蔵庫の概略断面図である。ここでは、冷凍装置として冷蔵庫を例にして説明する。図7の冷蔵庫は、実施の形態1で説明した密閉型圧縮機を搭載したものである。
102 固定子
103 回転子
104 電動要素
105 圧縮要素
106 潤滑油
110 シャフト
111 主軸部
112 偏心軸部
113 給油通路
114 シリンダブロック
115 シリンダ
116 圧縮室
120 軸受部
123 ピストン
123a シール部
123b 延長部
123c 非摺動部
125 ピストンピン
126 コンロッド
128 大孔端部
129 小孔端部
130 ロッド部
141 第1の中心線
142 第2の中心線
144 軸心
150 バルブプレート
180 断熱箱体
182 内箱
184 外箱
186 断熱体
188 冷蔵室
190 切替室
192 製氷室
194 野菜室
196 冷凍室
198 冷蔵室回転扉
200 切替室引出し扉
202 製氷室引出し扉
204 野菜室引出し扉
206 冷凍室引出し扉
208 凹み部
210 密閉型圧縮機
212 キャピラリ
214 冷却ファン
216 蒸発器
218 吸入配管
Claims (4)
- 密閉容器内に、電動要素と、前記電動要素によって駆動される圧縮要素とが収容された密閉型圧縮機であって、
前記圧縮要素は、
主軸部、および、前記主軸部と一体運動する偏心軸部を有するシャフトと、
前記シャフトの前記主軸部を軸支することによって、片持ち軸受を形成する軸受部と、
気体を圧縮するシリンダと、
前記シリンダの内部に往復自在に挿設されたピストンと、
前記偏心軸部と前記ピストンとを連結するコンロッドとを備え、
前記軸受部の軸心を示す第1の中心線と、前記シリンダの軸心を示す第2の中心線とのなす角度a1と、
前記軸受部に対する前記シャフトの傾きの角度の絶対値c1とが、式(1)を満たし、
前記ピストンの外周面には、
前記シリンダの内周面と隙間を有し、摺動面を形成するシール部と、
前記シール部の後方に位置し、摺動面を形成する延長部と、
前記シール部の後方に位置し、摺動面を形成しない非摺動部と
を備える密閉型圧縮機。
a1=π/2+c1‥‥‥(1) - 前記延長部は、前記シール部と同じ半径を有し、側圧を支持する前記摺動面を形成する請求項1に記載の密閉型圧縮機。
- 前記電動要素は、インバータ回路により複数の回転数で駆動される請求項1または2に記載の密閉型圧縮機。
- 冷凍サイクルに請求項1から3のいずれかに記載の密閉型圧縮機を用いた冷凍装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016505029A JPWO2015129184A1 (ja) | 2014-02-25 | 2015-02-13 | 密閉型圧縮機および冷凍装置 |
DE112015000951.5T DE112015000951T5 (de) | 2014-02-25 | 2015-02-13 | Abgedichteter Kompressor und Kühlvorrichtung |
US15/113,272 US20170009758A1 (en) | 2014-02-25 | 2015-02-13 | Sealed compressor and refrigeration device |
CN201580010415.XA CN106062363A (zh) | 2014-02-25 | 2015-02-13 | 密闭型压缩机和制冷装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2014033746 | 2014-02-25 | ||
JP2014-033746 | 2014-02-25 |
Publications (1)
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WO2015129184A1 true WO2015129184A1 (ja) | 2015-09-03 |
Family
ID=54008522
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PCT/JP2015/000651 WO2015129184A1 (ja) | 2014-02-25 | 2015-02-13 | 密閉型圧縮機および冷凍装置 |
Country Status (5)
Country | Link |
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US (1) | US20170009758A1 (ja) |
JP (1) | JPWO2015129184A1 (ja) |
CN (1) | CN106062363A (ja) |
DE (1) | DE112015000951T5 (ja) |
WO (1) | WO2015129184A1 (ja) |
Families Citing this family (1)
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JP7142100B2 (ja) * | 2018-11-08 | 2022-09-26 | パナソニックホールディングス株式会社 | 冷媒圧縮機及びこれを用いた冷凍装置 |
Citations (6)
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JP2005264740A (ja) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | 密閉型圧縮機 |
JP2006022720A (ja) * | 2004-07-08 | 2006-01-26 | Matsushita Electric Ind Co Ltd | 圧縮機 |
JP2010180740A (ja) * | 2009-02-04 | 2010-08-19 | Panasonic Corp | 密閉型圧縮機および冷凍装置 |
JP2011508840A (ja) * | 2008-05-12 | 2011-03-17 | パナソニック株式会社 | 密閉型圧縮機およびそれを用いた冷凍冷蔵装置 |
US20120107148A1 (en) * | 2010-10-27 | 2012-05-03 | Samsung Electronics Co., Ltd. | Hermetic compressor |
JP2013044255A (ja) * | 2011-08-23 | 2013-03-04 | Hitachi Appliances Inc | 密閉型圧縮機及びこれを用いた冷蔵庫 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
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US2587246A (en) * | 1949-11-28 | 1952-02-26 | Tresco Inc | Hermetic refrigeration compressor |
US3419207A (en) * | 1966-09-13 | 1968-12-31 | Hintze Rudolf | Small hermetic compressor |
DK1456538T3 (da) * | 2001-12-17 | 2009-01-26 | Lg Electronics Inc | Kompressor med to ydeevner |
JP4760003B2 (ja) * | 2004-12-14 | 2011-08-31 | パナソニック株式会社 | 密閉型圧縮機 |
JP5753983B2 (ja) * | 2009-10-27 | 2015-07-22 | パナソニックIpマネジメント株式会社 | 密閉型圧縮機 |
-
2015
- 2015-02-13 WO PCT/JP2015/000651 patent/WO2015129184A1/ja active Application Filing
- 2015-02-13 JP JP2016505029A patent/JPWO2015129184A1/ja active Pending
- 2015-02-13 DE DE112015000951.5T patent/DE112015000951T5/de not_active Withdrawn
- 2015-02-13 CN CN201580010415.XA patent/CN106062363A/zh active Pending
- 2015-02-13 US US15/113,272 patent/US20170009758A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005264740A (ja) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | 密閉型圧縮機 |
JP2006022720A (ja) * | 2004-07-08 | 2006-01-26 | Matsushita Electric Ind Co Ltd | 圧縮機 |
JP2011508840A (ja) * | 2008-05-12 | 2011-03-17 | パナソニック株式会社 | 密閉型圧縮機およびそれを用いた冷凍冷蔵装置 |
JP2010180740A (ja) * | 2009-02-04 | 2010-08-19 | Panasonic Corp | 密閉型圧縮機および冷凍装置 |
US20120107148A1 (en) * | 2010-10-27 | 2012-05-03 | Samsung Electronics Co., Ltd. | Hermetic compressor |
JP2013044255A (ja) * | 2011-08-23 | 2013-03-04 | Hitachi Appliances Inc | 密閉型圧縮機及びこれを用いた冷蔵庫 |
Also Published As
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US20170009758A1 (en) | 2017-01-12 |
JPWO2015129184A1 (ja) | 2017-03-30 |
DE112015000951T5 (de) | 2016-11-03 |
CN106062363A (zh) | 2016-10-26 |
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