JP5338966B1 - Hermetic compressor and refrigerator-freezer - Google Patents

Abstract

When the flatness of the flange portion is poor, the upper race and the flange portion slip, so that loss increases and efficiency decreases.
A flange portion 123 of a shaft 120 is provided with a pressing portion 169, and an upper race 154 is provided with a pressure receiving portion 172. The outer diameter of the pressing portion 169 is equal to or larger than the revolution track diameter of a ball 153, and the inner diameter of the pressing portion 169 is provided. Since the ball 153 is configured to be smaller than the diameter of the revolving track, the friction torque applied between the upper race 154 and the flange portion 123 can be increased, so that slipping can be prevented and efficiency can be improved.
[Selection] Figure 1

Description

  The present invention relates to a hermetic compressor used for a freezer and the like.

  In recent years, with regard to hermetic compressors used in refrigeration apparatuses such as refrigerators and refrigerators, high efficiency, low noise, and high reliability for reducing power consumption are desired. At the same time, cost reduction is required.

  Conventionally, this type of hermetic compressor employs a thrust ball bearing to improve efficiency and reliability (for example, see Patent Document 1).

  Hereinafter, the conventional hermetic compressor will be described with reference to the drawings.

  FIG. 5 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, and FIG. 6 is an enlarged view of a main part of a thrust ball bearing of the conventional hermetic compressor described in Patent Document 1.

  5 and 6, the lubricating oil 2 is stored in the sealed container 1, and the electric element 5 having the stator 3 and the rotor 4 and the compression element 6 driven by the electric element 5 are accommodated. Yes.

  The compression element 6 includes a shaft 12 having a main shaft portion 10 and an eccentric shaft portion 11 to which the rotor 4 is fixed, a cylinder block 14 having a compression chamber 13, a piston 15 reciprocating in the compression chamber 13, A connecting means 16 for connecting the piston 15 and the eccentric shaft portion 11, a main bearing 17 provided on the cylinder block 14 for supporting the main shaft portion 10, and a thrust ball bearing 19 disposed on a thrust surface 18 of the main bearing 17. It has.

  The main bearing 17 includes a thrust surface 18 that is a plane portion substantially perpendicular to the shaft center, and a bearing extension portion 30 that extends further upward than the thrust surface 18 and has an inner surface facing the main shaft portion 10.

  The thrust ball bearing 19 includes a plurality of balls 21 held by a holder portion 20, and an upper race 22 and a lower race 23 disposed above and below the balls 21.

  The upper race 22 and the lower race 23 are annular and metal flat plates, and the upper and lower surfaces are parallel. Further, the holder portion 20 has an annular shape, and a ball 21 is rotatably accommodated in a plurality of holes (not shown) provided in the circumferential direction.

  The support member 29, the lower race 23, the ball 21, and the upper race 22 are stacked in contact with each other in this order on the thrust surface 18, and the flange portion 31 of the shaft 12 is seated on the upper surface of the upper race 22. A predetermined axial gap 32 is provided between the upper end of the shaft 12 and the flange portion 31 of the shaft 12.

  The inner diameter portion 33 of the upper race 22 is brought close to the outer diameter of the main shaft portion 10, and the inner diameter of the upper race 22 is configured to be smaller than the inner diameters of the lower race 23 and the holder portion 20.

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

  When the electric element 5 is energized, the shaft 12 is rotated together with the rotor 4 by the rotating magnetic field generated in the stator 3. The rotational movement of the eccentric shaft portion 11 of the shaft 12 is transmitted to the piston 15 through the connecting means 16, so that the piston 15 reciprocates in the compression chamber 13. Accordingly, the refrigerant gas from the cooling system (not shown) is repeatedly sucked and compressed into the compression chamber 13 and then discharged again to the cooling system.

  When the shaft 12 rotates, the flange portion 31 and the upper race 22 of the shaft 12 are brought into close contact with each other by friction due to a vertical downward thrust load caused by the weight of the rotor 4 and the shaft 12. The ball 21 makes revolution and rotation while being guided by the holder portion 20 by contacting the upper race 22.

JP 2010-255556 A

  However, in the above conventional configuration, the flatness of the flange portion 31 of the shaft 12 is poor, for example, when the vicinity of the outer diameter of the main shaft portion has a convex shape, that is, from the side farther from the main shaft portion of the flange portion 31 to the main shaft portion. When the convex shape is formed in a vertically downward direction toward the near side, the portion where the flange portion 31 and the upper race 22 are in contact is in the vicinity of the outer diameter of the main shaft portion and in a small area, so the upper race 22 is integrated with the shaft 12. May cause slippage without being able to rotate, and if slippage occurs, the slideability of the ball bearing will deteriorate, the slide loss will increase, and the efficiency of the compressor will decrease. There was sex.

  SUMMARY OF THE INVENTION The present invention solves the above-described conventional problems, and an object thereof is to provide a highly efficient hermetic compressor that can suppress sliding of an upper race and a flange portion.

  In order to solve the above-described conventional problems, a hermetic compressor according to the present invention stores lubricating oil in a hermetic container, and includes an electric element having a stator and a rotor, and a compression driven by the electric element. The compression element includes a shaft having a main shaft portion, an eccentric shaft portion, and a flange portion to which the rotor is fixed, a cylinder block having a compression chamber, and a piston that reciprocates in the compression chamber. A connecting means for connecting the piston and the eccentric shaft portion, a main bearing provided on the cylinder block for supporting the main shaft portion, and a thrust disposed between the main bearing and the flange portion A ball bearing, wherein the thrust ball bearing includes a plurality of balls held by a holder portion, and an upper race and a lower race arranged above and below the balls, and the flange It is provided with a pressing portion for pressing the upper race.

  Accordingly, the friction torque applied between the upper race and the pressing portion of the flange portion is set to be higher than the friction torque between the upper race and the ball, thereby preventing the flange portion and the upper race from slipping, The slidability of the bearing is improved and the sliding loss is reduced.

  Since the hermetic compressor of the present invention can reduce the sliding loss on the thrust surface, it is possible to provide a hermetic compressor that realizes efficient and energy saving.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Sectional drawing of the principal part of the hermetic compressor in the same embodiment Exploded perspective view of shaft and thrust ball bearing in the same embodiment Friction torque ratio characteristic diagram in the same embodiment Vertical sectional view of a hermetic compressor according to Embodiment 2 of the present invention Sectional drawing of the principal part of the hermetic compressor in the same embodiment Exploded perspective view of shaft and thrust ball bearing in the same embodiment Vertical section of a conventional hermetic compressor Cross section of the main part of a conventional hermetic compressor

  According to a first aspect of the present invention, lubricating oil is stored in a sealed container, and an electric element including a stator and a rotor and a compression element driven by the electric element are accommodated, and the compression element is A shaft having a main shaft portion to which a child is fixed, an eccentric shaft portion, and a flange portion, a cylinder block having a compression chamber, a piston that reciprocates in the compression chamber, and the piston and the eccentric shaft portion are coupled to each other. A coupling means; a main bearing provided on the cylinder block for supporting the main shaft portion; and a thrust ball bearing disposed between the main bearing and the flange portion, wherein the thrust ball bearing comprises a holder portion A plurality of balls held on the upper and lower sides of the balls, and an upper race and a lower race are provided on the upper and lower sides of the balls, respectively, and a pressing portion that presses the upper race is provided on the flange portion. It is.

  Thereby, the friction torque applied between the pressure receiving portion of the upper race and the pressing portion of the flange portion can be set higher than the friction torque between the upper race and the ball, and the flange portion and the upper race are prevented from slipping. An efficient hermetic compressor can be provided.

  According to a second aspect of the present invention, the pressing portion is formed as a convex portion on the flange surface, and a flange center diameter connecting a center line between the outer diameter of the convex portion and the inner diameter of the convex portion is set as the diameter of the revolution orbit of the ball. It is formed larger.

  As a result, the upper race can be reliably pressed with a convex shape, and the friction torque applied between the pressure receiving portion of the upper race and the pressing portion of the flange portion is set higher than the friction torque between the upper race and the ball. Since the flange portion and the upper race are prevented from slipping, an efficient hermetic compressor can be provided.

  According to a third aspect of the present invention, the convex portion is constituted by the flange surface and an edge of the concave portion formed on the flange surface, and the pressure receiving portion that receives the pressing force of the convex portion is the upper surface of the upper race and the flange surface. It is constructed by closely contacting.

  Thereby, even if the flatness is poor such that the flange portion is convex downward in the vertical direction with the main shaft portion as the central axis, the pressing portion is formed without providing high processing accuracy of the flange portion by providing the concave portion. be able to.

  In a fourth aspect of the present invention, the pressing portion is formed by a pressing member provided between the upper race and the flange surface.

  As a result, the pressing member absorbs the change in the contact state between the pressing portion and the pressure receiving portion due to compression load fluctuation and the like, and the friction torque can be stabilized, so that the flange portion and the upper race are prevented from slipping, so that the efficiency is further improved. A good hermetic type compressor can be provided.

According to a fifth aspect of the present invention, the thickness of the upper race is 1 mm or more, so that even when the flange portion and the upper race become slippery due to the accuracy of the flange portion, the friction torque is increased, and the flatness of the upper race is increased. It can be improved and the rolling of the ball can be stabilized, so that the efficiency of the compressor can be further increased.

  According to a sixth aspect of the present invention, the upper race and the lower race have raceways facing each other, and the raceway is provided with a raceway formed by an annular groove. In addition, since the center of the main shaft portion of the shaft and the center of the ring of the raceway ring can be made substantially coincident with each other, the ball rolling motion is stabilized and noise can be reduced.

  7th invention mounts the closed type compressor as described in 1st-8th invention in the refrigerator, and since the efficient closed type compressor is used, it provides the refrigerator-freezer which can reduce power consumption. Can do.

  Embodiments of a compressor according to the present invention will be described below with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention, FIG. 2 is a sectional view of essential parts of the hermetic compressor according to the same embodiment, and FIG. 3 is a shaft according to the same embodiment. It is a disassembled perspective view of a thrust ball bearing. FIG. 4 is a characteristic diagram of a friction torque ratio between the flange surface and the upper race in the same embodiment.

  In FIG. 1 to FIG. 3, lubricating oil 102 is stored in a sealed container 101 and a refrigerant (not shown) is sealed, and is driven by an electric element 105 including a stator 103 and a rotor 104, and the electric element 105. A compression element 106 is received.

  Both the electric element 105 and the compression element 106 are accommodated in a sealed container 101 and supported by a spring 110.

  A terminal 111 fixed to the sealed container 101 supplies electricity (not shown), and supplies electricity to the electric element 105 through the lead wire 112.

  An inverter control circuit 113 is connected to the terminal 111, and a commercial power supply 114 is supplied to the inverter control circuit 113.

  Next, the configuration of the compression element 106 will be described.

  The shaft 120 connects a main shaft portion 121 to which the rotor 104 is fixed, an eccentric shaft portion 122 disposed above the main shaft portion 121 and formed eccentric to the main shaft portion 121, the main shaft portion 121, and the eccentric shaft portion 122. And flange portion 123.

  The cylinder block 130 has a substantially cylindrical compression chamber 131, and a main bearing 132 that supports the main shaft 121 is integrally processed. The piston 133 is inserted into the compression chamber 131 of the cylinder block 130 so as to be slidable back and forth, and is connected to the eccentric shaft portion 122 by a connecting means 134.

  In the vicinity of the upper end of the main bearing 132 of the cylinder block 130, a thrust surface 140 formed in an annular shape substantially perpendicular to the axis of the main bearing 132, and an inner surface that extends further upward than the thrust surface 140 and faces the main shaft portion 121. And a bearing extension 141 having the same.

  The thrust ball bearing 150 is disposed on the thrust surface 140, and a plurality of balls 153 held by the lower race 151 and the holder portion 152 and the upper race 154 are sequentially stacked so that the bearing extension portion 141 is in contact with each other. A predetermined axial gap 156 is provided between the upper end of the upper race 154 and the upper race 154 to constitute an oil supply path to the thrust ball bearing 150.

  As described above, in the present embodiment, in the compressor in which the inside of the hermetic container 101 is a low-pressure type compressor, the bearing that supports the shaft 120 is only one of the main bearings 132 provided below the compression chamber 131. There is a configuration in which the compression chamber 131 is cantilevered in the vertical direction.

  The revolution track diameter D1 determined by the ball 153 and the holder portion 152 is set to 27 mm. The diameter of the ball 153 is 3.2 mm.

  The inner diameter portion 155 of the upper race 154 is close to the outer diameter of the main shaft portion 121, and the inner diameter D 2 of the upper race 154 is smaller than the inner diameter D 3 of the lower race 151 and the inner diameter D 4 of the holder portion 152. The upper race 154 has a thickness of 1 mm or more as a bearing steel having a thickness of 1.3 mm. Each of the upper race 154 and the lower race 151 has a raceway surface 160 that faces each other, and the raceway surface 160 is provided with a raceway ring 161 that is formed by an annular groove.

  A pressing portion 169 is formed in a convex shape on the flange portion 123 of the shaft 120. Specifically, a convex shape is formed by the edge of the concave portion 171 formed on the flange surface 170.

  The flange surface 170 is brought into close contact with the pressure receiving portion 172 on the upper surface of the upper race 154 that receives the pressing force of the pressing portion 169, and the outer diameter of the pressing portion 169, that is, the outer diameter D5 of the flange surface 170 is equal to or greater than the revolution track diameter D 1 of the ball 153. The inner diameter of the pressing portion 169, that is, the outer diameter D6 of the recess 171 is less than the revolution track diameter D1 of the ball 153 and is equal to or more than 25.4 mm, which is equal to or more than the diameter obtained by subtracting the diameter of the ball 153 from the revolution track diameter D1 of the ball 153. It is set.

  Further, the pressing portion 169 in the present embodiment is a convex portion formed in a convex shape on the flange surface 170, and the flange center diameter D7 connecting the center line between the outer diameter D5 of the convex portion and the inner diameter D6 of the convex portion is a ball. Is formed larger than the orbital diameter D1.

  As shown in FIG. 2, in the cross-sectional shape, the contact distance 169 a between the upper race 154 and the pressing portion 169 is smaller than the distance 140 a between the lower race 151 and the thrust surface 140.

  Here, the revolution trajectory diameter D1 of the ball 153 in the present embodiment is a diameter of a circle connecting a trajectory passing through the center of the ball 153 as the shaft rotates.

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

  The rotor 104 of the electric element 105 rotates the shaft 120, and the rotational movement of the eccentric shaft portion 122 is transmitted to the piston 133 via the connecting means 134, so that the piston 133 reciprocates in the compression chamber 131. Thereby, the refrigerant is sucked into the compression chamber 131 from the cooling system (not shown), compressed, and then discharged to the cooling system again.

When the shaft 120 rotates, the flange surface 170 of the shaft 120 and the upper surface of the upper race 154 are brought into close contact with each other by friction due to a downward thrust load caused by the weight of the rotor 104 and the shaft 120. The ball 153 makes a revolution and rotation with the lower race 151 while being guided by the holder 152 by contacting the upper race 154.

  Further, since the axial gap 156 is provided between the upper race 154 and the upper end of the bearing extension portion 141, the upper race 154 and the upper end of the bearing extension portion 141 do not come into contact with each other. Roll smoothly between the upper race 154 and the lower race 151.

  By using this thrust ball bearing 150, the friction coefficient becomes smaller than that of the thrust slide bearing, so that the sliding loss in the thrust bearing can be reduced. Therefore, input is reduced and high efficiency is realized.

  Here, the manufacturing process of the shaft 120 will be described. After each part of the shaft 120 is machined by a lathe, the main shaft part 121 and the flange surface 170 are simultaneously finished and polished by a centerless grinding machine. In order to ensure the accuracy such as the perpendicularity and flatness of the main shaft portion 121 and the flange surface 170, maintenance is required to periodically dress the grinding wheel.

  FIG. 4 shows the result of calculating the friction torque ratio between the upper race 154 and the flange surface 170 using the outer diameter D6 of the recess 171 as a parameter. Further, the results for the cases where the outer diameter of the flange surface 170 is 27 mm and 30 mm, and the white circles indicate the friction torque between the ball 153 and the upper race 154. In the conventional product, when the flatness is poor and the main shaft portion 121 is a convex shape downward in the vertical direction with respect to the central axis (calculated result of the shaded portion in FIG. 4), the portion where the flange portion 123 and the upper race 154 come into contact with each other Since the upper race 154 is in contact with the main shaft portion 121 in the vicinity of the outer diameter and in a small area, there is a possibility that the upper race 154 cannot slide together with the shaft 120 and slides.

  On the other hand, the product of the present invention (punishment mark in FIG. 4) has the upper race 154 and the flange surface 170 even when the flatness is poor such that the flange surface 170 is convex downward in the vertical direction about the main shaft 121. Can be set higher than the friction torque between the upper race 154 and the ball 153, so that the flange surface 170 and the upper race 154 can be prevented from slipping.

  Thereby, the friction torque of the contact portion between the upper race 154 and the flange surface 170 is made higher than the friction torque between the upper race 154 and the ball 153, and the flange surface 170 and the upper race 154 are prevented from slipping. An efficient hermetic compressor can be provided.

  Further, the pressing portion 169 in the present embodiment is a convex portion formed in a convex shape on the flange surface 170, and the flange center diameter D7 connecting the center line between the outer diameter D5 of the convex portion and the inner diameter D6 of the convex portion is a ball. Therefore, the friction torque at the contact portion between the upper race 154 and the flange surface 170 can be further increased by applying a pressing force from the outer side of the center of the ball 153. Therefore, the effect of preventing the upper race 154 from slipping is enhanced.

  As shown in FIG. 2, in the cross-sectional shape, the contact distance 169 a between the upper race 154 and the pressing portion 169 is smaller than the distance 140 a between the lower race 151 and the thrust surface 140.

  Accordingly, the lower race 151 and the thrust surface 14 can be stably installed, and the friction torque at the contact portion between the upper race 154 and the flange surface 170 can be further increased.

  In addition, even when the flatness is poor such that the flange surface is convex downward in the vertical direction with the main shaft as the central axis, there is no need to obtain high machining accuracy of the flange surface 170, so maintenance of the grinding wheel and equipment can be performed. Since it can be reduced, productivity can be improved.

In addition, the flange surface 170 is in contact with the upper surface of the revolving track diameter D1 of the ball 153 and can support a thrust load in a state where the upper race 154 can be prevented from being deformed and vibrated, thereby further reducing efficiency and noise. can do.

  Further, the outer diameter of the upper race 154 needs to be increased along with the outer diameter of the flange surface 170 in order to increase the friction torque, but as shown by the dotted line in FIG. Since the frictional torque can be increased without increasing the diameter by setting the diameter 153 or more to the diameter obtained by subtracting the diameter of the ball 153 from the revolution track diameter D1, the cost can be reduced.

  Further, by setting the thickness of the upper race 154 to 1 mm or more, even if the flange surface 170 and the upper race 154 become slippery due to the influence of the accuracy of the flange surface 170, the friction torque is increased and the ball of the upper race 154 is increased. Since the flatness of the raceway surface 160 of 153 can be improved and the rolling of the ball 153 can be stabilized, the reliability can be further improved.

  Further, since the raceway surface 160 is provided with a raceway ring 161 formed of an annular groove, it is possible to prevent the flange surface 170 and the upper race 154 from slipping, and the shaft center of the main shaft portion 121 of the shaft 120. Since the centers of the rings of the races 161 can be made substantially coincident, the rolling and revolving motion of the ball 153 is stabilized, so that noise can be reduced.

  When the inverter control circuit 113 is used to operate at a frequency lower than the commercial frequency, the ratio of the loss due to the slip between the upper race 154 and the flange portion 123 to the total loss increases, but the flange surface 170 and the upper race 154 slide. Since this can be prevented, the efficiency can be further increased in low-speed operation.

  The flange portion 123 of the shaft 120 is provided with the flange surface 170 and the recessed portion 171. However, even when the plurality of recessed portions 171 are provided and the flange surface 170 is divided, the friction torque between the upper race 154 and the flange surface 170 is increased. Since it can raise, the same effect is acquired.

  In addition, in the vicinity of the upper end of the main bearing 132, a bearing extending portion 141 is provided that extends further upward than the thrust surface 140 and has an inner surface facing the main shaft portion 121, but the upper end of the main shaft portion 121 is provided at the thrust surface 140. Since the friction torque between the upper race 154 and the flange surface 170 can be increased even when the bearing extension 141 is not provided, the same effect can be obtained.

  The lower race 151 is disposed on the thrust surface 140. However, a support means having a protruding protrusion formed vertically is disposed between the thrust surface 140 and the lower race 151 so that the lower race 151 is thrust. Even when vibration motion is enabled with respect to the surface 140, the frictional torque between the upper race 154 and the flange surface 170 can be increased, and the same effect can be obtained.

(Embodiment 2)
FIG. 5 is a longitudinal sectional view of a hermetic compressor according to the second embodiment of the present invention, FIG. 6 is a cross-sectional view of main parts of the hermetic compressor according to the same embodiment, and FIG. 7 is a shaft according to the same embodiment. It is a disassembled perspective view of a thrust ball bearing.

  In FIGS. 5 to 7, lubricating oil 202 is stored in a sealed container 201 and a refrigerant (not shown) is sealed, and is driven by an electric element 205 including a stator 203 and a rotor 204, and the electric element 205. The compression element 206 is housed.

Both the electric element 205 and the compression element 206 are accommodated in the hermetic container 201 and the spring 210.
It is supported by.

  A terminal 211 fixed to the sealed container 201 supplies electricity (not shown), and supplies electricity to the electric element 205 through the lead wire 212.

  An inverter control circuit 213 is connected to the terminal 211, and a commercial power source 214 is supplied to the inverter control circuit 213.

  Next, the configuration of the compression element 206 will be described.

  The shaft 220 connects a main shaft portion 221 to which the rotor 204 is fixed, an eccentric shaft portion 222 that is disposed above the main shaft portion 221 and formed eccentric to the main shaft portion 221, and the main shaft portion 221 and the eccentric shaft portion 222. And a flange portion 223.

  The cylinder block 230 has a substantially cylindrical compression chamber 231, and a main bearing 232 that supports the main shaft portion 221 is integrally processed. The piston 233 is inserted into the compression chamber 231 of the cylinder block 230 so as to be slidable back and forth, and is connected to the eccentric shaft portion 222 by a connecting means 234.

  In the vicinity of the upper end of the main bearing 232 of the cylinder block 230, a thrust surface 240 formed in an annular shape substantially perpendicular to the axis of the main bearing 232, and an inner surface that extends further upward than the thrust surface 240 and faces the main shaft portion 221. And a bearing extension 241 having the same.

  The thrust ball bearing 250 is disposed on the thrust surface 240 and is stacked in a state where the plurality of balls 253 held by the lower race 251 and the holder portion 252 and the upper race 254 are in contact with each other in order, and the bearing extension portion 241. A predetermined axial gap 256 is provided between the upper end of the upper race 254 and the upper race 254, and constitutes an oil supply path to the thrust ball bearing 250.

  As described above, in the present embodiment, in the compressor in which the inside of the hermetic container 201 is a low pressure type, the bearing that supports the shaft 220 is only one of the main bearings 232 provided below the compression chamber 231. There is a configuration in which the compression chamber 231 is pivotally supported in a cantilever direction.

  The revolution trajectory diameter D11 determined by the ball 253 and the holder portion 252 is set to 27 mm. The diameter of the ball 253 is 3.2 mm.

  The inner diameter portion 255 of the upper race 254 is close to the outer diameter of the main shaft portion 221, and the inner diameter D12 of the upper race 254 is smaller than the inner diameter D13 of the lower race 251 and the inner diameter D14 of the holder portion 252. The upper race 254 has a thickness of 1 mm or more as a bearing steel having a thickness of 1.3 mm. The upper race 254 and the lower race 251 each have a raceway surface 260 facing each other, and the raceway surface 260 is provided with a raceway ring 261 formed by an annular groove.

  A pressing member 273 is provided on the flange portion 223 of the shaft 220 between the flange surface 270 and the concave portion 271 to constitute a pressing portion 269.

  A pressing member 273 formed of a thin plate is provided between the flange surface 270 that is the pressing portion 269 and the pressure receiving portion 272 on the upper surface of the upper race 254 that receives the pressing force, and the outer diameter of the pressing portion 269, that is, the flange surface 270. The outer diameter D15 of the ball 253 is set to 29 mm, which is not less than the revolution orbit diameter D11 of the ball 253. The pressing member 273 made of a thin plate is a metal hollow disc having a thickness of 0.2 mm.

  Here, the revolution trajectory diameter D11 of the ball 253 in the present embodiment is a diameter of a circle connecting a locus passing through the center of the ball 253 as the shaft 220 rotates.

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

  The rotor 204 of the electric element 205 rotates the shaft 220, and the rotational movement of the eccentric shaft portion 222 is transmitted to the piston 233 via the connecting means 234, so that the piston 233 reciprocates in the compression chamber 231. Thereby, the refrigerant is sucked into the compression chamber 231 from the cooling system (not shown), compressed, and then discharged to the cooling system again.

  When the shaft 220 rotates, it receives a vertical downward thrust load due to the weight of the rotor 204 and the shaft 220, and the flange surface 270 of the shaft 220, the pressing member 273 made of a thin plate, and the upper surface of the upper race 254 are in close contact with each other due to friction. Rotate together. The ball 253 makes revolution and rotation with the lower race 251 while being guided by the holder portion 252 by coming into contact with the upper race 254.

  In addition, since the axial clearance 256 is provided between the upper race 254 and the upper end of the bearing extension 241, the upper race 254 and the upper end of the bearing extension 241 do not come into contact with each other. Roll smoothly between the upper race 254 and the lower race 251.

  By using this thrust ball bearing 250, the friction coefficient becomes smaller than that of the thrust slide bearing, so that the sliding loss in the thrust bearing can be reduced. Therefore, input is reduced and high efficiency is realized.

  Since the friction torque applied between the flange surface 270 as the pressing portion 269 and the pressure receiving portion 272 on the upper surface of the upper race 254 can be set higher than the friction torque between the upper race 254 and the ball 253, Since the race 254 is prevented from slipping, an efficient hermetic compressor can be provided.

  Here, when the refrigerant is sucked / compressed, the compression load changes, and therefore, the movement of the axis of the shaft 220 tilting with respect to the axis of the main bearing 221 is repeated. Therefore, the flange portion 223 of the shaft 220 also moves to incline with respect to the thrust surface 240, the load applied between the pressing portion 269 and the pressure receiving portion 272 changes, and the contact state changes. In the product of the present invention, since the pressing member 273 made of a thin plate is provided between the pressing portion 269 and the pressure receiving portion 272, the change in the contact state between the pressing portion 269 and the pressure receiving portion 272 is caused by unevenness on the surface of the pressing member 273 made of a thin plate. Absorbing and stabilizing the friction torque can prevent the flange surface 270 and the upper race 254 from slipping, thereby further improving the efficiency.

  Further, the thrust load can be supported with the flange surface 270 in contact with the upper surface of the revolution track diameter D11 of the ball 253 via a pressing member 273 made of a thin plate, and the upper race 254 is prevented from being deformed and vibrating. Therefore, the efficiency and noise can be further reduced.

  Further, by setting the thickness of the upper race 254 to 1 mm or more, even if the flange surface 270 and the upper race 254 become slippery due to the influence of the accuracy of the flange surface 270, the friction torque is increased and the ball of the upper race 254 is increased. Since the flatness of the raceway surface 260 of 253 can be improved and the rolling of the ball 253 can be stabilized, the reliability can be further increased.

  Further, since the raceway surface 260 is provided with a raceway ring 261 formed by an annular groove, the flange surface 270 and the upper race 254 are prevented from sliding, and the shaft center of the main shaft portion 221 of the shaft 220 is Since the center of the ring of the race 261 can be made substantially coincident, the rolling and revolving motion of the ball 253 is stabilized, so that the noise can be reduced.

  Note that if the inverter control circuit 213 is used to drive at a frequency lower than the commercial frequency, the loss due to the slip between the upper race 254 and the flange portion 223 increases in the total loss, but the flange portion 223 and the upper race 254 Since slipping can be prevented, the efficiency can be further increased in low-speed driving.

  In the present embodiment, the provision of a convex shape on the flange surface 270 of the shaft 220 is not described. However, in addition to the pressing member 273 having a function as a pressing portion of the present embodiment, further implementation is performed. In the case where the convex portion of the first aspect is provided, the pressing force of the pressing portion can be further increased, and the effect of preventing the flange portion 223 and the upper race 254 from slipping can be enhanced.

  Further, even when a plurality of concave portions are provided and the flange surface 270 is divided (in other words, when a plurality of convex portions are formed) as in the first embodiment, it is added between the pressing portion 269 and the pressure receiving portion 272. Since the friction torque can be set higher than the friction torque between the upper race 254 and the ball 253, it goes without saying that the same effect can be obtained.

  In addition, in the vicinity of the upper end of the main bearing 232, it is assumed that the bearing extending portion 241 having an inner surface facing the main shaft portion 221 and extending further upward than the thrust surface 240 is provided, but the upper end of the main shaft portion 221 is provided with the thrust. The friction torque applied between the pressing portion 269 and the pressure receiving portion 272 is higher than the friction torque between the upper race 254 and the ball 253 even when the height is the same as the surface 240 and the bearing extending portion 241 is not provided. Needless to say, the same effect can be obtained because it can be set.

  The lower race 251 is disposed on the thrust surface 240. However, a support means having convex protrusions arranged vertically is disposed between the thrust surface 240 and the lower race 251, and the lower race 251 is thrust. Even when vibration motion is enabled with respect to the surface 240, the friction torque applied between the pressing portion 269 and the pressure receiving portion 272 can be set higher than the friction torque between the upper race 254 and the ball 253. It goes without saying that it is obtained.

  As described above, since the hermetic compressor according to the present invention can increase productivity, the hermetic compressor is also suitable for use as a hermetic compressor of an air conditioner or a vending machine in addition to a refrigerator.

DESCRIPTION OF SYMBOLS 101 Airtight container 102 Lubricating oil 103 Stator 104 Rotor 105 Electric element 106 Compression element 120 Shaft 121 Main shaft part 122 Eccentric shaft part 123 Flange part 130 Cylinder block 131 Compression chamber 132 Main bearing 133 Piston 134 Connection means 140 Thrust surface 141 Bearing extension Protruding portion 150 Thrust ball bearing 151 Lower race 152 Holder portion 153 Ball 154 Upper race 155 Inner diameter portion 160 Track surface 161 Track ring 169 Pressing portion 170 Flange surface 171 Concavity 172 Pressure receiving portion 201 Sealed container 202 Lubricating oil 203 Stator 204 Rotor 205 Electric element 206 Compression element 220 Shaft 221 Main shaft part 222 Eccentric shaft part 223 Flange part 230 Cylinder block 231 Compression chamber 232 Main bearing 233 Piston 34 coupling means 240 thrust surface 241 bearing extending section 250 thrust ball bearing 251 lower race 252 holder 253 a ball 254 upper race 255 bore 260 raceway surface 261 bearing ring 269 pressing portion 270 flange surface 271 recess 272 receiving portion 273 sheet

Claims (6)

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 on which the rotor is fixed. A shaft having a portion, an eccentric shaft portion, and a flange portion, a cylinder block having a compression chamber, a piston reciprocating in the compression chamber, a connecting means for connecting the piston and the eccentric shaft portion, and the cylinder A main bearing provided on the block and supporting the main shaft portion; and a thrust ball bearing disposed between the main bearing and the flange portion, wherein the thrust ball bearing includes a plurality of holders held by a holder portion. a ball, the upper race and lower race are disposed respectively above and below the ball, provided the pressing portion for pressing the upper race to the flange portion, the pressing portion is the The flange surface is formed with a convex portion, and the flange center diameter connecting the center line between the outer diameter of the convex portion and the inner diameter of the convex portion is formed larger than the revolution orbit diameter of the ball, and the outer shape is larger than the center of the ball. A hermetic compressor that applies pressure from the side . The convex portion is configured by the flange surface and an edge of the concave portion formed in the flange surface, and the pressure receiving portion that receives the pressing force of the convex portion is configured by bringing the upper surface of the upper race and the flange surface into close contact with each other. The hermetic compressor according to claim 1 . The pressing portion is hermetic compressor according to claim 1 or 2 formed by the pressing member provided between the upper race and the flange surface. The hermetic compressor according to any one of claims 1 to 3 , wherein the upper race has a thickness of 1 mm or more. The hermetic seal according to any one of claims 1 to 4 , wherein the upper race and the lower race have raceways facing each other, and the raceway is provided with a raceway formed by an annular groove. Mold compressor. A refrigerator-freezer equipped with the hermetic compressor according to any one of claims 1 to 5 .