JP2015025364A - Hermetic compressor and refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic compressor and a refrigerator using the same, capable of improving efficiency and reliability.SOLUTION: A hermetic compressor includes a connecting rod 144 connecting a piston to an eccentric shaft part of a shaft, an opening portion of an oil supply hole 160 communicating a large end hole 158 and a small end hole 156 of this connecting rod 144 with each other is formed close to an opposite side to a bearing with respect to a center of a vertical width of the large end hole 158. With this configuration, if a heavy load acts on a slide portion between the connecting rod and the eccentric shaft part in a compression stroke, an oil film thickness is small, and a high oil film pressure is generated, it is possible to prevent reduction of the oil film pressure because the opening portion of the oil supply hole 160 is not present at the center of the slide portion. It is thereby possible to prevent occurrence of solid contact, reduce slide loss, and prevent generation of friction on a slide surface.

Description

  The present invention relates to a hermetic compressor and a refrigeration apparatus such as a refrigerator using the same.

  In recent years, demand for protection of the global environment has accelerated the trend toward energy saving in household refrigerators and the like.

  Under such circumstances, a hermetic compressor conventionally used in this type of refrigerator or the like is provided with a gas vent groove in the shaft so that the refrigerant gas is not filled in the oil supply passage of the shaft and lubricated. There is one in which the occurrence of defects is prevented to improve efficiency (see, for example, Patent Document 1).

  The prior art hermetic compressor will be described below with reference to the drawings.

  In the following description, the upper and lower relationships are based on a state in which the hermetic compressor is installed in a normal posture.

  FIG. 9 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, and FIG. 10 is a stroke diagram showing a relationship between an oil supply hole in the connecting rod and an oil reservoir on the surface of the eccentric shaft portion.

  9 and 10, the lubricating oil 4 is stored at the bottom of the sealed container 2, and the compressor body 6 is elastically supported by the suspension container 8 with respect to the sealed container 2.

  The compressor body 6 includes an electric element 10 including a stator 14 and a rotor 16, and a compression element 12 disposed below the electric element 10.

  The shaft 18 of the compression element 12 includes a main shaft portion 20 and an eccentric shaft portion 22 extending to the lower side of the main shaft portion 20, and the main shaft portion 20 rotates on a main bearing 26 attached to the cylinder block 24. While being freely supported, a rotor 16 is fitted. The lower end of the shaft 18 opens in the lubricating oil 4 at the bottom of the sealed container 2, and an oil supply mechanism 30 that extends upward is provided inside the shaft 18.

  The cylinder block 24 includes a cylinder 34 that is a cylindrical hole, and a piston 36 is reciprocally inserted into the cylinder 34.

  Further, as shown in FIG. 10, the connecting rod 44 is eccentric by inserting a small end hole 56 and a large end hole 58 provided at both ends into the piston pin 42 attached to the piston 36 and the eccentric shaft portion 22, respectively. The shaft portion 22 and the piston 36 are connected.

  The connecting rod 44 is provided with an oil supply hole 60 that allows the small end hole 56 and the large end hole 58 to communicate with each other, and an oil reservoir 62 that communicates with the oil supply mechanism 30 and a vertical recess 64 are provided on the surface of the eccentric shaft portion 22. ing.

  The operation of the conventional hermetic compressor configured as described above will be described below.

  When the electric element 10 is energized, the shaft 18 also rotates as the rotor 16 rotates, and the compression element 12 performs a predetermined compression operation.

  The lubricating oil 4 is supplied to each part of the compression element 12 by the action of the oil supply mechanism 30 accompanying the rotation of the shaft 18, and the lubricating oil 4 is supplied to the oil reservoir 62.

  The oil reservoir 62 and the oil supply hole 60 communicate from the top dead center indicated by J in FIG. 10 to the bottom dead center indicated by H, and the lubricating oil 4 is supplied to the piston pin 42 and the like through the oil supply hole 60. Is done.

  In addition, since the refrigerant gas mixed in the lubricating oil 4 and staying in the oil reservoir 62 is discharged from the vertical recess 64 to the space in the sealed container 2, the oil supply of the piston pin 42 via the oil supply hole 60 is obstructed. It will not be done.

Japanese Utility Model Publication No. 47-16836

  However, in the conventional configuration described in Patent Document 1, the center of the sliding surface of the large end hole 58 of the connecting rod 44 that slides with the eccentric shaft portion 22 at the top dead center at which the pressure acting on the piston 36 is maximized. In addition, since the opening portion of the oil supply hole 60 is formed, the oil film pressure decreases around the opening portion, the oil film becomes thin, the oil film breaks, the sliding loss increases due to solid contact, and wear occurs. It had the subject of becoming easy to do.

  The present invention solves the above-described conventional problems, and prevents a decrease in oil film pressure between the connecting rod and the eccentric shaft portion, suppresses the occurrence of wear, and a highly efficient and reliable hermetic compressor and the same An object of the present invention is to provide a refrigeration apparatus using the above.

  In order to solve the above-described conventional problems, the hermetic compressor according to the present invention is configured such that the opening of the oil supply hole that communicates the large end hole and the small end hole of the connecting rod is located on the side opposite the bearing from the center of the vertical width of the large end hole The configuration is as follows.

  As a result, when a large load is applied to the sliding portion of the connecting rod and the eccentric shaft portion in the compression stroke, the oil film thickness is thin, and a high oil film pressure is generated, there is no opening of the oil supply hole at the center of the sliding portion. It is possible to prevent the oil film pressure from decreasing, thereby preventing the occurrence of solid contact, reducing the sliding loss, and preventing the sliding surface from being worn.

  The hermetic compressor of the present invention can prevent the occurrence of solid contact by reducing the oil film pressure generated at the sliding portion of the connecting rod and the eccentric shaft portion, and can reduce the sliding loss. In addition to improving the efficiency of the hermetic compressor, by preventing the occurrence of solid contact, the wear of the sliding surface can be prevented and the reliability can be improved. Further, a refrigeration apparatus such as a refrigerator using the hermetic compressor can reduce power consumption by improving the efficiency of the hermetic compressor.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. (A) Top view of connecting rod in the same embodiment, (b) Cross-sectional view of the connecting rod The conceptual diagram which shows the inclination of the shaft in the embodiment (A) The conceptual diagram which shows the generation | occurrence | production state of the oil film pressure in the embodiment, (b) The conceptual diagram which shows the generation | occurrence | production state of the oil film pressure in a comparative product The characteristic figure which shows the pressure change of the compression chamber in the same embodiment (H)-(K) Stroke diagram showing positional relationship between oil supply hole and oil reservoir in the same embodiment The conceptual diagram which shows the generation | occurrence | production state of the oil film pressure in the same embodiment Schematic sectional view of a refrigerator as a refrigeration apparatus in Embodiment 2 of the present invention Vertical section of a conventional hermetic compressor Process diagram showing the positional relationship between conventional oil supply holes and oil reservoirs

  A hermetic compressor according to a first aspect of the present invention stores lubricating oil in a hermetic container, and houses an electric element including a stator and a rotor, and a compression element disposed above the electric element, The compression element includes a shaft including a main shaft portion to which the rotor is fixed, an eccentric shaft portion, and an oil supply mechanism, a cylinder block including a main bearing and a cylinder that support the main shaft portion of the shaft, and A piston inserted into the cylinder so as to be capable of reciprocating; and a connecting rod that connects the piston pin and the eccentric shaft portion; the connecting rod having a small end hole provided at one end thereof; And the large end hole provided at the other end is fitted to the eccentric shaft portion of the shaft to connect the piston and the eccentric shaft portion, and the connecting rod is connected to the large end hole and the small shaft portion. Connect end holes It has an oil supply hole, the opening of the oil supply hole, in which the formed counter-bearing side of the center of the vertical width of the larger end hole.

  As a result, when a large load is applied to the sliding portion of the connecting rod and the eccentric shaft portion in the compression stroke, the oil film thickness is thin, and a high oil film pressure is generated, there is no opening of the oil supply hole at the center of the sliding portion. It is possible to prevent the oil film pressure from decreasing, thereby preventing the occurrence of solid contact, reducing the sliding loss, and preventing the sliding surface from being worn. As a result, the efficiency of the hermetic compressor can be improved, and the occurrence of solid contact can be prevented, so that the sliding surface can be prevented from being worn and the reliability can be improved.

  In the second invention, in particular, the opening to the large end hole and the small end hole of the oil supply hole of the hermetic compressor of the first invention is arranged such that the center lines of the large end hole and the small end hole are center lines. It arrange | positions in the position which does not exist on the said plane with respect to the plane to include.

  This prevents the oil film pressure from decreasing because the opening is located near the top dead center where the load on the sliding portion between the connecting rod and the eccentric shaft is the largest, and near the centerline where the piston load is the largest. In addition, since the oil film thickness increases, it is possible to reduce sliding loss and improve efficiency, and to prevent wear and improve reliability.

  In a third aspect of the invention, in particular, in the hermetic compressor according to the second aspect of the invention, a plane including a center line of the large end hole and the small end hole intersects the oil supply hole and the large end of the oil supply hole. The opening to the hole is arranged with an angle in the rotation direction of the shaft from the plane.

  As a result, in the vicinity of the top dead center where the load of the sliding portion between the connecting rod and the eccentric shaft portion becomes the largest, the opening to the large end hole of the communication hole is drawn into the sliding portion, and the oil film thickness is reduced. Since it is arranged downstream from the minimum position, the oil film pressure can be more reliably prevented from decreasing, and a higher oil film pressure can be generated, reducing sliding loss and increasing reliability. Can be improved.

  In a fourth aspect of the invention, in particular, in the hermetic compressor according to any one of the first to third aspects, the viscosity grade of the lubricating oil is VG8 or less.

As a result, even when the viscosity of the lubricating oil is low, the generation of the oil film pressure is not hindered by the oil supply holes, so the sliding loss can be reduced by reducing the viscosity, the efficiency can be improved, and the wear prevention can be achieved. The effect of improving reliability is remarkable.

  A fifth invention is a refrigeration apparatus using the hermetic compressor according to any one of the first to fourth inventions.

  Thereby, since the efficiency of the hermetic compressor is high, the power consumption of the refrigeration apparatus can be reduced, and the reliability of the refrigeration apparatus can be improved by using the highly reliable hermetic compressor. it can.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a hermetic compressor according to a first embodiment of the present invention. 2A is a top view of the connecting rod in the embodiment, FIG. 2B is a cross-sectional view, and FIG. 3 is a conceptual diagram showing the inclination of the shaft in the embodiment.

  FIG. 4A is a conceptual diagram showing a generation state of the oil film pressure in the embodiment, and FIG. 4B is a conceptual diagram showing a generation state of the oil film pressure in the comparative product. FIG. 5 is a characteristic diagram showing the pressure change in the compression chamber in the embodiment, and FIGS. 6H to 6K are stroke diagrams showing the positional relationship between the communication path and the oil reservoir in the embodiment, FIG. These are the conceptual diagrams which show the generation | occurrence | production state of the oil film pressure in the same embodiment.

  1 to FIG. 7, the lubricating oil 104 is stored in the bottom of the sealed container 102, and the compressor main body 106 is internally suspended in the sealed container 102 by a suspension spring 108. The sealed container 102 is filled with R600a (isobutane), which is a refrigerant gas having a low warming potential. In addition, the lubricating oil 104 has a viscosity grade of VG8 or less, preferably VG5, and a low viscosity so as to reduce power consumption by increasing the efficiency of the hermetic compressor.

  The compressor body 106 includes an electric element 110 and a compression element 112 driven by the electric element 110, and a power supply terminal 113 for supplying power to the electric element 110 is attached to the sealed container 102.

  First, the electric element 110 will be described.

  The electric element 110 includes a stator 114 in which a winding (not shown) is directly wound around a plurality of magnetic pole teeth of an iron core in which steel plates are laminated via an insulating material, and a permanent magnet disposed on the inner diameter side of the stator 114. This is a salient pole concentrated winding DC brushless motor including a rotor 116 (not shown). The windings of the stator 114 are connected to an inverter circuit (not shown) outside the hermetic compressor via a power supply terminal 113 by a conductive wire, and the electric element 110 is driven at a plurality of rotational speeds.

  Next, the compression element 112 will be described.

  The compression element 112 is disposed above the electric element 110.

  The shaft 118 constituting the compression element 112 is arranged in the vertical direction, and includes a main shaft portion 120 and an eccentric shaft portion 122 extending from the upper end of the main shaft portion 120 and parallel to the main shaft portion 120. Further, the rotor 116 is fixed to the main shaft portion 120 by a method such as shrink fitting.

  The cylinder block 124 includes a main bearing 126 having a cylindrical inner surface, and the shaft 118 is supported by the main shaft portion 120 being inserted into the main bearing 126 in a rotatable state. The compression element 112 has a configuration of a cantilever bearing that supports the load acting on the eccentric shaft portion 122 by the main shaft portion 120 and the main bearing 126 arranged below the eccentric shaft portion 122.

  The cylinder block 124 includes a cylinder 134 that is a cylindrical hole, and a piston 136 is reciprocally inserted into the cylinder 134.

  A valve plate 146 is attached to the end surface of the cylinder 134 and forms a compression chamber 148 together with the cylinder 134 and the piston 136. Further, the cylinder head 150 is fixed so as to cover the valve plate 146 and cover it. The suction muffler 152 is molded from a resin such as PBT, forms a silencing space inside, and is attached to the cylinder head 150.

  The shaft 118 has a lower end of the main shaft portion 120 immersed in the lubricating oil 104 stored in the inner bottom portion of the hermetic container 102, and includes a spiral groove 128 on the outer surface of the main shaft portion 120, and extends from the lower end to the upper end of the shaft 118. An oil supply mechanism 130 is provided. An oil sump 162 communicating with the oil supply mechanism 130 is provided on the surface of the eccentric shaft portion 122.

  Next, the connecting rod 144 will be described.

  As shown in FIG. 2, the connecting rod 144 is provided with a small end hole 156 at one end and a large end hole 158 at the other end, and the small end hole 156 and the large end hole 158 are respectively attached to the piston 136. The eccentric shaft portion 122 and the piston 136 are connected by being inserted into the pin 142 and the eccentric shaft portion 122.

  The connecting rod 144 is provided with an oil supply hole 160 extending from the opening 165 on the outer surface near the small end hole 156 to the opening 166 provided on the inner surface of the large end hole 158. An opening 168 is provided on the inner surface.

  The opening 166 of the oil supply hole 160 to the large end hole 158 is disposed at a position not on the plane AA including the center line of the small end hole 156 and the large end hole 158, and further, the plane AA. Accordingly, the shaft 118 is arranged at a position where the angle is shifted in the rotation direction of the shaft 118, that is, in the clockwise direction.

  Further, the opening 166 is disposed on the side opposite to the bearing, that is, above the BB surface that is the center of the vertical width of the large end hole 158.

  The oil supply hole 160 is arranged so as to intersect the plane AA, and the opening 168 on the inner surface of the small end hole 156 is opposite to the opening 166 on the inner surface of the large end hole 158 and the plane AA. Located on the side. A longitudinal groove 170 is provided in the opening 168 in the axial direction of the small end hole 156.

  The operation and action of the hermetic compressor configured as described above will be described below.

  When the electric element 110 is energized from the power supply terminal 113, the rotor 116 rotates together with the shaft 118 by the magnetic field generated in the stator 114. As the main shaft 120 rotates, the eccentric shaft 122 rotates eccentrically and is converted by the connecting rod 144 to reciprocate the piston 136 in the cylinder 134. Then, when the volume of the compression chamber 148 is changed, the refrigerant gas in the sealed container 102 is sucked into the compression chamber 148 and compressed.

  Next, the effect of shifting the oil supply hole 160 upward will be described.

  When performing the compression operation, as shown in FIG. 3, a compression load acts on the eccentric shaft portion 122 of the shaft 118 through the piston 136 and the connecting rod 144 due to the pressure P of the refrigerant gas in the compression chamber 148. A compressive load acts on the eccentric shaft portion 122 above the main shaft portion 120 and the main bearing 126 to generate a moment, and the main shaft portion 120 is inclined within the clearance with the main bearing 126.

  As a result, the gap in the axial direction between the large end hole 158 of the connecting rod 144 and the eccentric shaft 122 is narrower in the lower D than in the upper C. Since the large end hole 158 and the eccentric shaft portion 122 have a relative rotational speed, an oil film pressure is generated due to a wedge effect due to the lubricating oil 104 being drawn into a portion where the gap is narrow. The smaller it becomes, the bigger it becomes.

  Accordingly, the oil film pressure generated on the sliding surface of the connecting rod 144 is greatly generated below the oil supply hole 160 as shown in FIG. 4 (a) this product, and (b) the oil supply hole shown in the comparative product. Compared to the case where 160 is at the center, the oil film pressure generated on the entire sliding surface is increased.

  As described above, the oil film pressure can be increased under the condition that the compression load is high and the shaft 118 is inclined by arranging the opening 166 to the large end hole 158 of the oil supply hole 160 on the upper side, that is, on the opposite bearing side. Since the occurrence of solid contact due to oil film rupture can be prevented, sliding loss is reduced, and the efficiency of the hermetic compressor can be improved. Further, since the occurrence of wear can be prevented, the reliability is improved.

  Next, the effect that the oil supply hole 160 is angled in the rotation direction of the shaft 118 with respect to the center line of the connecting rod 144 will be described.

  FIG. 5 is a characteristic diagram showing the behavior of pressure in the compression chamber 148 as the shaft 118 rotates. The compression of the refrigerant gas starts from around I (crank angle 270 °), the pressure in the compression chamber 148 increases, and the pressure decreases after J (360 °) at the top dead center.

  As shown in FIG. 6, at the top dead center J, the opening 166 to the large end hole 158 of the oil supply hole 160 is shifted to the right from the center line of the piston 136. At this stage, the oil of the eccentric shaft 122 The reservoir 162 and the oil supply hole 160 are not in communication. Then, after passing through the top dead center J, the oil sump 162 and the oil supply hole 160 communicate with each other and the lubricating oil 104 flows through the oil supply hole 160 in the section between K and H at the bottom dead center. The lubricating oil 104 that has flowed through the oil supply hole 160 is supplied to the entire surface of the piston pin 142 from the opening 168 to the small end hole 156 via the vertical groove 170 and lubricates the surface of the piston pin 142. Further, the excess lubricating oil 104 further flows through the oil supply hole 160 and is discharged from the opening 165 to the outside.

  At the top dead center J where the compressive load is maximum, the openings 166 and 168 of the oil supply hole 160 are all separated from the load center near the center line of the piston 136. Since the openings 166 and 168 are not located at the center of the sliding portion, the oil film pressure does not decrease and the oil film thickness can be increased, so that sliding loss is reduced, efficiency is improved, and wear is prevented and reliable. Can be improved.

  Further, as shown in FIG. 7, in the large end hole 158 of the connecting rod 144, the eccentric shaft portion 122 rotates with respect to the connecting rod 144, so that the lubricating oil 104 is drawn into a portion where the gap is narrow, thereby causing an oil film pressure. The wedge effect is generated.

At the position J where the compression load is maximum, the opening 166 to the large end hole 158 of the oil supply hole 160 is at a position shifted from the vicinity of the central axis of the piston 136, and the lubricating oil 10
Since the oil film pressure on the downstream side of the load center with respect to the inflow direction 4 is disposed at a position where the oil film pressure is low, the adverse effect on the generation of the oil film pressure can be reduced.

  Further, the opening 168 to the small end hole 156 is disposed on the opposite side to the opening 166 to the large end hole 158 with respect to the plane AA.

  For this reason, as shown in FIG. 6, in the region from I to J where a larger compressive load than the piston 136 acts, the opening 168 is located on the right side of the center. Closest to the side. Therefore, since lubrication can be performed when the load is small without hindering the generation of oil film pressure when the load is large, the sliding loss is reduced, the efficiency is improved, and the occurrence of wear is prevented. Reliability can be improved.

  As described above, by arranging the opening position of the oil supply hole 160 of the connecting rod 144 so as to avoid the center of the sliding surface, the generation of oil film pressure is not hindered. Therefore, the viscosity grade is VG8 or less. Even when the lubricating oil 104 is used, it is possible to maintain a good lubrication state with few ruptures of the oil film, so that the effect of reducing the sliding loss and improving the efficiency is remarkable.

(Embodiment 2)
FIG. 8 shows a schematic cross-sectional view of a refrigerator as a refrigeration apparatus in Embodiment 2 of the present invention.

  In FIG. 8, a heat insulation box 180 injects foam insulation 186 into a space formed by an inner box 182 formed by vacuum molding a resin body such as ABS and an outer box 184 using a metal material such as a pre-coated steel plate. It has a thermal insulation wall. As the heat insulator 186, for example, a hard urethane foam, a phenol foam, a styrene foam, or the like is used. Use of hydrocarbon-based cyclopentane as the foaming material is better from the viewpoint of preventing global warming.

  The heat insulation box 180 is divided into a plurality of heat insulation sections, and has a structure in which the upper part is a rotary door type and the lower part is a drawer type. From the top, there are a refrigerating room 188, a drawer type switching room 190 and an ice making room 192 arranged side by side, a drawer type vegetable room 194 and a drawer type freezing room 196. Each heat insulation section is provided with a heat insulation door via a gasket. From the top are 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.

  Moreover, the outer box 184 of the heat insulation box 180 is provided with the recessed part 208 which dented the top surface back.

  The refrigeration cycle includes a hermetic compressor 210 elastically supported in the recess 208, a condenser (not shown) provided on the side surface of the heat insulation box 180, a capillary 212 as a decompressor, and moisture removal. A dryer (not shown), an evaporator 216 provided with a cooling fan 214 in the vicinity of the back of the vegetable compartment 194 and the freezing compartment 196, and a suction pipe 218 are connected in an annular shape. .

  Here, the hermetic compressor 210 uses the compressor described in the first embodiment.

  About the refrigerator comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

First, the temperature setting and cooling method of each heat insulation section will be described. The refrigerator compartment 188 is normally set at 1 to 5 ° C. with the temperature not frozen for refrigerated storage as the lower limit.

  Switching room 190 can change temperature setting by a user's setting, and can make it predetermined temperature setting from a freezer compartment temperature zone to refrigeration and a vegetable compartment temperature zone. In addition, the ice making chamber 192 is an independent ice storage chamber, and includes an automatic ice making device (not shown) to automatically produce and store ice. Although it is a freezing temperature zone for storing ice, it can also be set at a freezing temperature of −18 ° C. to −10 ° C., which is relatively higher than the freezing temperature zone for the purpose of storing ice.

  The vegetable room 194 is often set to a temperature setting of 2 ° C. to 7 ° C., which is the same as or slightly higher than that of the refrigerator compartment 188. It is possible to maintain the freshness of leafy vegetables for a long period of time as the temperature is lowered so that it does not freeze.

  The freezer compartment 196 is normally set at −22 to −18 ° C. for frozen storage, but may be set at a low temperature of −30 or −25 ° C., for example, to improve the frozen storage state.

  Each chamber is divided by a heat insulating wall in order to efficiently maintain different temperature settings. However, as a method of improving the heat insulating performance at a low cost, it is possible to perform foam filling with the heat insulating body 186 integrally. Compared to the use of a heat insulating member such as polystyrene foam, the heat insulating performance can be increased by about twice, and the storage volume can be increased by thinning the partition.

  Next, the operation of the refrigeration cycle will be described.

  The cooling operation is started and stopped by a signal from a temperature sensor (not shown) and a control board according to the set temperature in the cabinet. The hermetic compressor 210 performs a predetermined compression operation according to the instruction of the cooling operation, and the discharged high-temperature and high-pressure refrigerant gas radiates heat by a condenser (not shown) to be condensed and liquefied, and is depressurized by the capillary 212. It becomes a low-temperature and low-pressure liquid refrigerant and reaches the evaporator 216.

  By the operation of the cooling fan 214, heat is exchanged with the air in the cabinet, the refrigerant gas in the evaporator 216 is evaporated, and the low-temperature cold air after the heat exchange is distributed by a damper (not shown) or the like. Cooling is performed.

  The refrigerator hermetic compressor 210 that performs the above operation is configured as described in the first embodiment. Specifically, the oil supply hole that communicates the large end hole 158 and the small end hole 156 with each other. 160, and includes a connecting rod 144 that connects the piston pin 142 and the eccentric shaft portion 122. The opening of the oil supply hole 160 of the connecting rod 144 is formed on the side opposite the bearing from the center of the vertical width of the large end hole 158. It is what.

  As a result, when a large load is applied to the sliding portion of the connecting rod 144 and the eccentric shaft portion 122 in the compression stroke, the oil film thickness is thin, and a high oil film pressure is generated, there is no opening of the oil supply hole at the center of the sliding portion. Therefore, it is possible to prevent the oil film pressure from being lowered, thereby preventing the occurrence of solid contact and reducing the sliding loss, thereby improving the efficiency of the hermetic compressor 210 and consequently reducing the power consumption of the refrigerator. can do.

  Further, by preventing the occurrence of solid contact between the connecting rod 144 and the eccentric shaft portion 122, it is possible to prevent the occurrence of wear on the sliding surface and improve the reliability, so that the reliability of the refrigerator is also improved. Can do.

  As described above, the present invention can improve the efficiency and reliability of the hermetic compressor, reduce the power consumption and improve the reliability of the refrigeration apparatus, and is not limited to a home electric refrigerator-freezer. It can be widely applied to vending machines, commercial refrigerators and other refrigerators.

DESCRIPTION OF SYMBOLS 102 Airtight container 104 Lubricating oil 110 Electric element 112 Compression element 114 Stator 116 Rotor 118 Shaft 120 Main shaft part 122 Eccentric shaft part 124 Cylinder block 126 Main bearing 130 Oil supply mechanism 134 Cylinder 136 Piston 142 Piston pin 144 Connecting rod 156 Small end hole 158 Large end hole 160 Oil supply hole 162 Oil reservoir 165 Opening part 166 Opening part 168 Opening part 210 Hermetic compressor

Claims (5)

The lubricating oil is stored in a sealed container, and an electric element having a stator and a rotor and a compression element driven by the electric element are accommodated, and the compression element is a main shaft to which the rotor is fixed. A shaft including a shaft portion, an eccentric shaft portion, and an oil supply mechanism, a cylinder block including a main bearing and a cylinder that pivotally supports the main shaft portion of the shaft, and a reciprocating motion inserted in the cylinder. A connecting rod connecting the piston and the piston pin to the eccentric shaft portion, the connecting rod fitting a small end hole provided at one end thereof to the piston pin of the piston and a large end hole provided at the other end; Is connected to the eccentric shaft portion of the shaft to connect the piston and the eccentric shaft portion, and the connecting rod has an oil supply hole communicating the large end hole and the small end hole, Refueling Openings, hermetic compressor wherein are formed the counter-bearing side of the center of the vertical width of the larger end hole. The opening to the large end hole and the small end hole of the oil supply hole is disposed at a position not on the plane with respect to a plane including a center line of the large end hole and the small end hole. The hermetic compressor according to 1. The plane including the center line of the large end hole and the small end hole intersects with the oil supply hole, and the opening of the oil supply hole to the large end hole has an angle in the rotation direction of the shaft from the plane. The hermetic compressor according to claim 2, wherein the hermetic compressor is disposed. The hermetic compressor according to any one of claims 1 to 3, wherein a viscosity grade of the lubricating oil is VG8 or less. A refrigeration apparatus using the hermetic compressor according to any one of claims 1 to 4.