JP5353414B2 - Hermetic compressor and refrigeration system - Google Patents

Abstract

The invention provides an enclosed compressor and a refrigeration device. Lubricating oil is stored in an enclosed container, and an electric element and compression elements are accommodated in the enclosed container; the compression elements comprise a shaft, a cylinder body, a piston, a connecting part, a main bearing, a plurality of balls and a thrust ball bearing; the shaft is provided with an oil supply part for supplying the lubricating oil to the inner circumference of the thrust ball bearing from the outer circumference of the shaft; the inner circumference of a holding part is provided with a bearing extending part extended by the main bearing, and an axial clearance is formed between the upper end of the bearing extending part and an upper seat ring; and the axial clearance forms a flow passage of the lubricating oil.

Description

  The present invention relates to a hermetic compressor mainly used in a refrigeration cycle such as a refrigerator-freezer.

  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.

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

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

  FIG. 16 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, and FIG. 17 is an enlarged view of a main part of a thrust ball bearing of the conventional hermetic compressor.

  16 and 17, 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 and a compression element 12 disposed above the electric element 10. The electric element 10 includes a stator 14 and a rotor 16.

  The shaft 18 of the compression element 12 includes a main shaft portion 20 and an eccentric shaft portion 22. The main shaft portion 20 is rotatably supported by a main bearing 26 of the cylinder block 24 and the rotor 16 is fixed. . And it is the structure of the cantilever bearing supported with the main axis | shaft part 20 and the main bearing 26 which are arrange | positioned only to the lower side of the eccentric shaft part 22 with respect to the eccentric shaft part 22 to which a load acts.

  Further, the shaft 18 includes an oil supply mechanism 28 formed of a spiral groove or the like provided on the surface of the main shaft portion 20, and includes an oil supply path 29 that communicates with the upper end of the oil supply mechanism 28 and extends even above the eccentric shaft portion 22. ing.

  The piston 30 is reciprocally inserted into a cylinder 34 having a substantially cylindrical inner surface formed in the cylinder block 24. Further, the connecting means 36 is configured such that holes (not shown) provided at both ends are fitted into the piston pin 38 and the eccentric shaft portion 22 attached to the piston 30, respectively, so that the eccentric shaft portion 22 and the piston 30 are connected. It is connected.

  The cylinder 34 and the piston 30 form a compression chamber 48 together with the valve plate 46 attached to the opening end surface of the cylinder 34. Further, the cylinder head 50 is fixed so as to cover the valve plate 46 and cover it.

  The suction muffler 52 is molded from a resin such as PBT, forms a silencing space inside, and is attached to the cylinder head 50.

  Next, the thrust ball bearing 76 will be described.

In FIG. 17, the main bearing 26 has a thrust surface 60 that is a flat portion perpendicular to the shaft center, and a bearing extending portion 62 that extends further upward than the thrust surface 60 and has an inner surface facing the main shaft portion 20. doing.

  A thrust ball bearing 76 including an upper race 64, a ball 66 held by a holder portion 68, a lower race 70, and a support member 72 is disposed on the outer diameter side of the bearing extension portion 62.

  The upper race 64 and the lower race 70 are annular and metal flat plates, and the upper and lower surfaces are parallel. Further, the holder portion 68 has an annular shape and accommodates the balls 66 in a plurality of holes (not shown) provided in the circumferential direction so as to be freely rollable.

  Then, the support member 72, the lower race 70, the ball 66, and the upper race 64 are stacked in contact with each other in this order on the thrust surface 60, and the flange portion 74 of the shaft 18 is seated on the upper surface of the upper race 64. A predetermined axial gap 78 is provided between the upper end of the protruding portion 62 and the flange portion 74 of the shaft 18.

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

  When the electric element 10 is energized, the rotor 16 rotates together with the main shaft portion 20 by the rotating magnetic field generated in the stator 14. Due to the rotation of the main shaft portion 20, the eccentric shaft portion 22 moves eccentrically, and the eccentric movement of the eccentric shaft portion 22 is transmitted to the piston 30 through the connecting means 36, and the piston 30 reciprocates in the cylinder 34.

  The refrigerant returned from the refrigeration cycle (not shown) outside the hermetic container 2 is introduced into the compression chamber 48 via the suction muffler 52, and is compressed by the piston 30 in the compression chamber 48, and the compressed refrigerant is sealed. It is sent out from the container 2 to the refrigeration cycle.

  Further, the lower end of the shaft 18 is immersed in the lubricating oil 4, and when the shaft 18 rotates, the lubricating oil 4 lubricates the main shaft portion 20 by the oil supply mechanism 28, and then the thrust ball bearing 76 from the axial gap 78. And supply to each part of the compression element 12 through the oil supply path 29 to lubricate the sliding part.

JP 2005-500476 Gazette

  However, in the above conventional configuration, it is difficult to distribute the supply of the lubricating oil 4 to the thrust ball bearing 76 and the supply to each part of the compression element 12 at a desired ratio. It has been found that the axial gap 78 is narrowed and the upper end of the bearing extension 62 and the flange portion 74 of the shaft 18 come into contact with each other, which may reduce noise, efficiency, and reliability. .

  The present invention solves the above-described conventional problems, and an object thereof is to provide a hermetic compressor that secures an axial clearance, and is low noise, high efficiency, and high reliability.

In order to solve the above-described conventional problems, the hermetic compressor of the present invention has oil supply means for supplying lubricating oil from the outer peripheral portion of the shaft to the inner periphery of the thrust ball bearing, and the upper end and the upper end of the bearing extension portion. A predetermined axial clearance is provided between the race and the raceway. The supply of the lubricating oil to the thrust ball bearing and the supply to each part of the compression element are distributed at a desired ratio, and the shaft is provided. It has the effect of securing a directional gap.

  The hermetic compressor of the present invention supports the load in the vertical direction such as the shaft and rotor weight by only the thrust ball bearing by securing the axial clearance, and the upper end of the bearing extension and the upper race It is possible to provide a hermetic compressor with low noise, high efficiency and high reliability by preventing the contact of oil and supplying abundant oil to the thrust ball bearing.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Cross-sectional view of the main part in the shaft side surface direction in the same embodiment Cross-sectional view of main parts in the shaft front direction in the same embodiment Cross-sectional view of the main part in the shaft side surface direction in the same embodiment The perspective view of the cylinder block in the same embodiment Vertical sectional view of a hermetic compressor according to Embodiment 2 of the present invention Cross-sectional view of the main part in the shaft side surface direction in the same embodiment Sectional drawing of the principal part of the front direction of the shaft in the same embodiment Sectional drawing of the principal part of the shaft side direction in the same embodiment The perspective view of the cylinder block in the same embodiment Vertical sectional view of a hermetic compressor according to Embodiment 3 of the present invention Cross-sectional view of the main part in the shaft side surface direction in the same embodiment Sectional drawing of the principal part of the front direction of the shaft in the same embodiment Sectional drawing of the principal part of the shaft side direction in the same embodiment The perspective view of the cylinder block in the same embodiment Vertical section of a conventional hermetic compressor Enlarged view of the main parts of a thrust ball bearing of a conventional hermetic compressor

The invention according to claim 1 stores lubricating oil in an airtight container, accommodates an electric element including a stator and a rotor, and a compression element driven by the electric element. A shaft having a main shaft portion and an eccentric shaft portion extending in the vertical direction, a main bearing forming a cantilever bearing by pivotally supporting the main shaft portion of the shaft, and a cylinder block forming a cylindrical compression chamber; A piston inserted in the compression chamber so as to be capable of reciprocating; a connecting means for connecting the piston and the eccentric shaft portion; and the main bearing provided on the cylinder block for supporting the main shaft portion. A plurality of balls disposed on a thrust surface of the main bearing and held by a holder, and a thrust ball bearing having an upper race and a lower race respectively disposed above and below the balls. The shaft has oil supply means for supplying the lubricating oil from the outer peripheral portion of the shaft to the inner periphery of the thrust ball bearing, and the bearing extension in which the main bearing extends to the inner peripheral portion of the holder portion Is provided with an axial gap having a predetermined width in the vertical direction between the upper end of the bearing extension and the upper race, and the axial gap is formed as a flow path for the lubricating oil. By securing an axial clearance, the thrust ball bearing alone supports vertical loads such as the weight of the shaft and rotor, and the upper end of the bearing extension and the upper race Since the lubricating oil is supplied to the thrust ball bearing from the axial clearance, a hermetic compressor with low noise, high efficiency and high reliability can be provided.

According to a second aspect of the present invention, in the first aspect of the present invention, the oil supply means includes a first oil supply path for conveying the lubricating oil from a lower part to an upper part of the main shaft part, and one end of the first oil supply. A second oil supply path that communicates with the upper end of the path and communicates with the upper end of the bearing extension portion at the other end, and supplies the inner circumference of the thrust ball bearing by changing the flow resistance of the second oil supply path In addition to the effect of the invention according to claim 1, in addition to the effect of the invention according to claim 1, the lubricant can supply a desired flow rate to the thrust ball bearing. A hermetic compressor can be provided.

  According to a third aspect of the present invention, in the second aspect of the present invention, the second oil supply path has a slit shape in which one end communicates with the first oil supply path and the other end communicates with the upper end of the bearing extension. The slit-like groove is characterized in that it extends in the axial direction on the outer peripheral portion of the main shaft portion, and can stably supply the lubricating oil to the thrust ball bearing. In addition to the effect of the invention described in Item 2, a highly reliable hermetic compressor can be provided.

  The invention according to claim 4 is the invention according to claim 2, wherein the second oil supply path is an inclined surface provided on an inner periphery of an upper end of the bearing extension part. Since the lubricating oil can be stably supplied to the thrust ball bearing, a highly reliable hermetic compressor can be provided in addition to the effect of the second aspect of the invention.

  The invention according to claim 5 is the invention according to any one of claims 2 to 4, wherein one end of the main shaft portion communicates with the first oil supply path and extends above the eccentric shaft portion. The third oil supply path is provided, and the flow resistance of the second oil supply path is changed to change the flow of the lubricating oil conveyed by the first oil supply path to the thrust ball bearing and the third oil supply path. It is characterized in that it is formed so as to be distributed at a desired ratio to the flow of water, and the lubricating oil can be supplied to each part of the thrust ball bearing and the compression element at a desired ratio. In addition to the effects of the invention described in 1., a highly reliable hermetic compressor can be provided.

  A sixth aspect of the present invention is the support according to any one of the first to fifth aspects, wherein an elastic force in a vertical direction is provided between the lower race and the thrust surface of the main bearing. It is equipped with a member, and even when a large external force is applied, the support member is deformed to prevent the contact load between the ball, the upper race and the lower race from increasing, and the plastic deformation of the thrust ball bearing is prevented. In addition to the effects of the inventions according to claims 1 to 5, there is further provided a hermetic compressor with low noise, high efficiency and high reliability. can do.

  According to a seventh aspect of the invention, in the sixth aspect of the invention, the axial clearance between the upper end of the bearing extension and the upper race is formed to be smaller than the elastic deformation amount of the support member. Thus, when a vertical impact load is applied, the upper end of the bearing extension and the upper race are in contact with each other to support the impact load. The contact load between the upper race and the lower race can be prevented from being extremely increased, the plastic deformation of the thrust ball bearing can be prevented, and the sliding of the thrust ball bearing can be maintained in a good state. In addition to the effects of the invention described in (1), it is possible to provide a hermetic compressor with further low noise, high efficiency and high reliability.

  The invention according to claim 8 is the invention according to any one of claims 1 to 7, wherein the bearing extension portion of the main bearing extending to the inner peripheral portion of the holder portion is an inner periphery. The fourth oil supply path that communicates with the outer circumference in the radial direction is provided, and the supply of the lubricating oil to the thrust ball bearing can be made more abundant. Therefore, the effects of the invention according to claims 1 to 7 In addition, a highly reliable hermetic compressor can be provided.

The invention according to claim 9 is the invention according to any one of claims 1 to 8, wherein a discharge path for discharging the lubricating oil after lubricating the thrust ball bearing to a space in the sealed container is provided. The lubricating oil is always circulated to and stored in the thrust ball bearing, so that accumulation of wear powder or the like can be prevented. In addition to the effects of the invention, a highly reliable hermetic compressor can be provided.

  The invention according to claim 10 is equipped with the hermetic compressor according to any one of claims 1 to 9, and is equipped with a hermetic compressor with lower noise, higher efficiency and higher reliability than before. By doing so, it is possible to provide a refrigeration apparatus with low noise, high efficiency and high reliability.

  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 Embodiment 1 of the present invention, FIG. 2 is a sectional view of an essential part in the side surface direction of the shaft in the same embodiment, and FIG. FIG. 4 is a cross-sectional view of the main part in the shaft side surface direction in the same embodiment, and FIG. 5 is a perspective view of the cylinder block in the same embodiment.

  That is, in FIG. 2, the shaft shows an enlarged main portion of FIG.

  1 to 5, lubricating oil 102 is stored in a sealed container 101, and an electric element 105 including a stator 103 and a rotor 104 and a compression element 106 driven by the electric element 105 are accommodated. The shaft 110 includes a main shaft portion 111 to which the rotor 104 is fixed, and an eccentric shaft portion 112 that is disposed above the main shaft portion 111 and is formed eccentric to the main shaft portion 111.

  The cylinder block 114 has a substantially cylindrical compression chamber 116, and a main bearing 120 that supports the main shaft portion 111 is fixed thereto. The piston 126 is inserted into the compression chamber 116 of the cylinder block 114 so as to be slidable back and forth, and is connected to the eccentric shaft portion 112 by a connecting means 128.

  The main bearing 120 of the cylinder block 114 includes a thrust surface 130 formed in an annular shape substantially at right angles to the axis of the main bearing 120, and a bearing extension having an inner surface facing the main shaft portion 111 and extending further upward than the thrust surface 130. And a discharge path 168 that communicates vertically downward with the outside of the bearing extension 144.

  In order to support the shaft 110 in the vertical direction, the support member 162, the lower race 136, the plurality of balls 134, and the holder portion 133 that holds the balls 134 are directed upward from the outer thrust surface 130 of the bearing extension portion 144. The upper race 135 is arranged in this order.

  The lower race 136, the plurality of balls 134, the holder portion 133 that holds the balls 134, and the upper race 135 constitute a thrust ball bearing 132.

  Further, the support member 162, the lower race 136, the plurality of balls 134 and the holder portion 133 that holds the balls 134 are all arranged outside the bearing extension portion 144 with a radial clearance.

On the other hand, the upper race 135 is disposed further above the upper end 170 of the bearing extension 144, and the distance (height) from the thrust surface 130 to the top of the ball 134 is the thrust surface 1.
Since the distance (height) from 30 to the upper end 170 of the bearing extension 144 is long, a predetermined axial gap 146 is formed between the upper end of the bearing extension 144 and the upper race 135 due to the difference in dimensions. ing.

  Here, the support member 162 is a member that has an elastic force in the vertical direction and can be elastically deformed, such as a wave washer having relatively high rigidity or a hard elastic member. The elastic deformation amount of the support member 162 in the vertical direction is set to be larger than the axial gap 146.

  Next, a detailed configuration related to the oil supply path of the shaft 110 will be described.

  The shaft 110 has oil supply means 140 that conveys the lubricating oil 102 upward. The oil supply means 140 includes a first oil supply path 150 that conveys the lubricating oil 102 from the lower part to the upper part of the main shaft part 111, and an axial extension to the outer peripheral part of the main shaft part 111, and one end of the first oil supply path 150. The second oil supply path 152 communicates with the upper end of the bearing extension portion 144 and communicates with the upper end of the bearing extension 144.

  In the embodiment of the present invention, the second oil supply path 152 includes a slit-shaped groove 154.

  Here, the first oil supply path 150 includes a concentric pump 150a provided at the lower portion of the shaft 110, a horizontal hole 150b extending in a radial direction from the upper portion of the concentric pump 150a, and a lower end at the outer peripheral portion of the shaft 110. The upper end is configured by a spiral oil supply groove 150 c that communicates with the horizontal hole 150 b and the upper end communicates with the slit-like groove 154 of the second oil supply path 152.

  Further, the main shaft portion 111 further includes a horizontal hole 158 extending in the radial direction of the main shaft portion 111 from the upper end of the spiral oil supply groove 150 c constituting the first oil supply path 150, and a lower end communicating with the vicinity of the bottom portion of the horizontal hole 158. And a third oil supply path 160 extending upward from the shaft portion 112.

  The third oil supply path 160 inclines away from the axis of the main shaft 111 as it extends upward in order to increase the conveying ability of the lubricating oil 102 by the rotation of the shaft 110, and the uppermost portion is the eccentric shaft 112. The upper end 112a is open.

  Further, in the present embodiment, the refrigerant used for the hermetic compressor 100 is a hydrocarbon-based refrigerant that is a natural refrigerant with a low global warming coefficient represented by R134a and R600a whose ozone depletion coefficient is zero, Each is combined with a highly compatible lubricating oil 102.

  The operation of the hermetic compressor 100 configured as described above will be described below.

  The rotor 104 of the electric element 105 rotates the shaft 110, and the rotational movement of the eccentric shaft portion 112 is transmitted to the piston 126 via the connecting means 128, so that the piston 126 reciprocates in the compression chamber 116. Thus, the refrigerant is sucked into the compression chamber 116 from the cooling system (not shown), compressed, and then discharged to the cooling system again.

  The weight of the shaft 110 and the rotor 104 is supported by a thrust ball bearing 132, and when the shaft 110 rotates, the ball 134 rolls between the upper race 135 and the lower race 136, so that the rotation becomes smooth.

By using the thrust ball bearing 132, the torque for rotating the shaft 110 is smaller than that of a thrust slide bearing that does not use a ball, so that the loss in the thrust bearing can be reduced. Therefore, the input can be reduced and the efficiency can be improved.

  Next, the lubricating oil 102 stored in the sealed container 101 is removed from the lower portion of the main shaft portion 111 by the first oil supply path 150 which is the oil supply means 140 provided in the shaft 110 due to the centrifugal force generated by the rotation of the shaft 110. Pumped up to the top.

  The lubricating oil 102 conveyed to the upper portion of the main shaft portion 111 by the first oil supply path 150 is supplied to the thrust ball bearing 132 through the slit-shaped groove 154 that is the second oil supply path, and the first flow The oil is distributed to a third flow supplied from above the upper end of the oil supply path 150 to the upper side of the eccentric shaft portion 112 through a lateral hole 158 extending in the radial direction of the main shaft portion 111.

  The first flow flows in the radial direction through the axial gap 146 because the predetermined axial gap 146 is formed between the upper end of the bearing extension 144 and the upper race 135, and the thrust flows. The flow is toward the ball bearing 132.

  In particular, the first flow is a direct flow toward the rolling position between the ball 134 and the upper race 135, effectively reducing the loss in the ball 134 and the upper race 135, reducing heat generation, and insufficient lubrication. It is possible to prevent occurrence of damage such as peeling due to, and to obtain high reliability.

  Further, by changing the axial gap 146 between the upper end of the bearing extension 144 and the upper race 135, the flow resistance in the first flow can be changed, and the flow resistance in the first flow is increased. The amount of the third flow lubricating oil 102 can be increased, and conversely, the flow resistance in the first flow can be reduced to decrease the amount of the third flow lubricating oil 102.

  Therefore, the lubricating oil 102 conveyed to the upper part of the main shaft portion 111 by the first oil supply path 150 is used to flow the lubricating oil 102 to the thrust ball bearing 132 (first flow) and the lubricating oil upward to the eccentric shaft portion 112. The flow can be distributed to the flow 102 (third flow) at a desired ratio, and the flow rate of the lubricating oil 102 supplied to the thrust ball bearing 132 can be optimally adjusted.

  Therefore, the optimum amount of the lubricating oil 102 can be supplied to both the thrust ball bearing 132 and the eccentric shaft portion 112, and the sliding loss can be reduced, and the heat generation is reduced and damage such as peeling due to insufficient lubrication occurs. Can be prevented and high reliability can be obtained.

  Further, the distribution of the lubricating oil 102 can be similarly performed by the slit-shaped groove 154 of the second oil supply path 152.

  That is, by changing the cross-sectional area of the slit-shaped groove 154, the flow resistance in the first flow can be changed without changing the axial gap 146, and the flow resistance in the first flow is increased to increase the third. It is possible to increase the amount of the lubricating oil 102 in the first flow, and conversely, to decrease the flow resistance in the first flow to reduce the amount of the third flow lubricating oil 102.

  Therefore, the lubricating oil 102 conveyed by the first oil supply path 150 is used to flow the lubricating oil 102 to the thrust ball bearing 132 (first flow) and the flow of the lubricating oil 102 above the eccentric shaft 112 (third). The flow rate of the lubricating oil 102 supplied to the thrust ball bearing 132 can be optimally adjusted.

  Therefore, the optimum amount of the lubricating oil 102 can be supplied to both the thrust ball bearing 132 and the eccentric shaft portion 112, and the sliding loss can be reduced, and the heat generation is reduced and damage such as peeling due to insufficient lubrication occurs. Can be prevented and high reliability can be obtained.

  By adjusting both the axial clearance 146 and the cross-sectional area of the slit-shaped groove 154, the flow of the lubricating oil 102 to the thrust ball bearing 132 (first flow) and the eccentric shaft 112 are moved upward. It goes without saying that the flow of the lubricating oil 102 (third flow) can be distributed at a finer rate.

  Next, when the hermetic compressor 100 is transported, a shocking load in the vertical direction such as dropping may be applied. At this time, a vertical load is also applied to the thrust ball bearing 132, the elastically deformable support member 162 is elastically deformed, and the upper end of the bearing extension 144 is within the deformation region in which the support member 162 is elastically deformable. The axial clearance 146 between the upper race 135 and the upper race 135 becomes zero and comes into contact.

  This is because the amount of elastic deformation of the support member 162 in the vertical direction is set to be larger than the axial gap 146.

  Thus, when a shocking load in the vertical direction is applied, the load can be supported not by the thrust ball bearing 132 but by the upper end of the bearing extension 144 and the upper race 135. It is possible to prevent the contact load between the upper race 135 and the lower race 136 from increasing extremely.

  Therefore, the plastic deformation of the thrust ball bearing 132 can be prevented and the sliding of the thrust ball bearing 132 can be maintained in a good state, so that low noise, high efficiency and high reliability can be obtained.

  Next, the flow of the lubricating oil 102 supplied to the thrust ball bearing 132 will be described.

  The lubricating oil 102 supplied to the thrust ball bearing 132 is stored outside the bearing extension 144 so that the thrust ball bearing 132 is immersed after the thrust ball bearing 132 is lubricated. It is discharged to the space in the sealed container 101 by its own weight through the discharged discharge path 168.

  Therefore, since it is possible to prevent the new lubricating oil 102 from being constantly circulated and supplied and stored in the thrust ball bearing 132, it is possible to prevent the accumulation of wear powder and the like and to obtain high reliability. it can.

  In the present embodiment, the example in which the second oil supply path is provided has been described. However, the thrust ball bearing 132 is lubricated only by the axial gap 146 between the upper end of the bearing extension 144 and the upper race 135. The oil 102 may be distributed at a desired ratio between the flow of the oil 102 (first flow) and the flow of the lubricating oil 102 above the eccentric shaft portion 112 (third flow).

  Moreover, although the slit-shaped groove 154 extending in the axial direction on the outer peripheral portion of the main shaft portion has been described as the second oil supply path, the same applies to other shapes of grooves and other forms of oil supply paths. It can be implemented.

Further, the example in which the discharge path 168 is provided in the cylinder block 114 has been described. However, the thrust ball bearing 132 is lubricated after the thrust ball bearing 132 is lubricated so that the new lubricating oil 102 can be circulated and supplied to the thrust ball bearing 132 at all times. Any other configuration can be used as long as it can be discharged into the space.

  Moreover, although the example which conveys the lubricating oil 102 to the 3rd oil supply path | route 160 via the horizontal hole 158 extended in the radial direction of the main shaft part 111 from the upper end of the 1st oil supply path | route 150 was demonstrated, The same operation can be performed by conveying the lubricating oil 102 directly from the upper end to the third oil supply path 160.

  Moreover, although the example provided with the support member 162 provided with the elastic force with respect to the vertical direction between the lower race 136 and the thrust surface 130 of the main bearing 120 has been described, the thrust is provided even when the support member 162 is not provided. Effects such as supply of the lubricating oil 102 to the ball bearing 132 and distribution of the lubricating oil 102 can be maintained.

  Moreover, by mounting the hermetic compressor 100, not only high efficiency as a refrigeration apparatus can be obtained, but also high reliability can be ensured.

(Embodiment 2)
6 is a longitudinal sectional view of a hermetic compressor according to the second embodiment of the present invention, FIG. 7 is a sectional view of a main part in the side surface direction of the shaft in the same embodiment, and FIG. FIG. 9 is a cross-sectional view of the main part in the side surface direction of the shaft in the same embodiment, and FIG. 10 is a perspective view of the cylinder block in the same embodiment.

  That is, in FIG. 7, the shaft shows an enlarged main part of FIG.

  6 to 10, lubricating oil 202 is stored in an airtight container 201, and an electric element 205 including a stator 203 and a rotor 204 and a compression element 206 driven by the electric element 205 are accommodated. The shaft 210 includes a main shaft portion 211 to which the rotor 204 is fixed, and an eccentric shaft portion 212 that is disposed above the main shaft portion 211 and is formed eccentric to the main shaft portion 211.

  The cylinder block 214 has a substantially cylindrical compression chamber 216, and a main bearing 220 that supports the main shaft portion 211 is fixed thereto. The piston 226 is inserted into the compression chamber 216 of the cylinder block 214 so as to be slidable back and forth, and is connected to the eccentric shaft portion 212 by a connecting means 228.

  The main bearing 220 of the cylinder block 214 includes a thrust surface 230 formed in an annular shape substantially perpendicular to the axis of the main bearing 220, and a bearing extension having an inner surface facing the main shaft portion 211 and extending further upward than the thrust surface 230. And a discharge path 268 that communicates vertically downward with the outside of the bearing extension 244.

  In order to support the shaft 210 in the vertical direction, the support member 262, the lower race 236, the plurality of balls 234, and the holder portion 233 that holds the balls 234 upward from the thrust surface 230 outside the bearing extension portion 244. The upper race 235 is arranged in this order.

  A thrust ball bearing 232 is configured by the lower race 236, the plurality of balls 234, the holder portion 233 that holds the balls 234, and the upper race 235.

  Further, the support member 262, the lower race 236, the plurality of balls 234, and the holder portion 233 that holds the balls 234 are all arranged outside the bearing extension portion 244 with a radial clearance.

  On the other hand, the upper race 235 is disposed further above the upper end 270 of the bearing extension 244, and the distance (height) from the thrust surface 230 to the uppermost part of the ball 234 is longer than the thrust surface 230. Since the distance (height) to the upper end 270 of the protruding portion 244 is long, a predetermined axial gap 246 is formed between the upper end of the bearing extending portion 244 and the upper race 235 due to the dimensional difference.

  Here, the support member 262 is a member that is elastically deformable with an elastic force in the vertical direction, such as a wave washer having a relatively high rigidity or a hard elastic member. The elastic deformation amount of the support member 262 in the vertical direction is set to be larger than the axial gap 246.

  Next, a detailed configuration related to the oil supply path of the shaft 210 will be described.

  The shaft 210 has oil supply means 240 for conveying the lubricating oil 202 upward. The oil supply means 240 extends in the axial direction to the first oil supply path 250 that conveys the lubricating oil 202 from the lower part to the upper part of the main shaft part 211, and one end of the first oil supply path 250. The second oil supply path 252 communicates with the upper end of the bearing extension portion 244 and communicates with the upper end of the bearing extension 244.

  In the embodiment of the present invention, the second oil supply path 252 is provided on the inner periphery of the upper end of the bearing extension 244, and is configured by an inclined surface 256 inclined by 45 degrees with respect to the axis, with the lower end being the first. The upper end of the oil supply path 250 communicates with the upper end, and the upper end communicates with the upper end of the bearing extension 244 and opens.

  Here, the first oil supply path 250 includes a concentric pump 250 a provided at the lower portion of the shaft 210, a horizontal hole 250 b extending in a radial direction from the upper portion of the concentric pump 250 a, and a lower end at the outer peripheral portion of the shaft 210. It is comprised from the spiral oil supply groove | channel 250c connected with the horizontal hole 250b, and the upper end connected to the inclined surface 256 of the 2nd oil supply path | route 252. FIG.

  Further, the main shaft portion 211 further has a horizontal hole 258 extending in the radial direction of the main shaft portion 211 from the upper end of the spiral oil supply groove 250 c constituting the first oil supply path 250, and a lower end communicating with the vicinity of the bottom portion of the horizontal hole 258. And a third oil supply path 260 extending upward from the shaft portion 212.

  The third oil supply path 260 is inclined so as to be separated from the axis of the main shaft portion 211 as it extends upward in order to increase the conveying ability of the lubricating oil 202 by the rotation of the shaft 210, and the uppermost portion is the eccentric shaft portion 212. The upper end 212a is open.

  Further, in the present embodiment, the refrigerant used in the hermetic compressor 200 is a hydrocarbon refrigerant that is a natural refrigerant having a low global warming coefficient represented by R134a or R600a having an ozone depletion coefficient of zero, and the like. Each is combined with a highly compatible lubricating oil 202.

  The operation of the hermetic compressor 200 configured as described above will be described below.

  The rotor 204 of the electric element 205 rotates the shaft 210, and the rotational movement of the eccentric shaft portion 212 is transmitted to the piston 226 via the connecting means 228, so that the piston 226 reciprocates in the compression chamber 216. Thereby, the refrigerant is sucked into the compression chamber 216 from the cooling system (not shown), compressed, and then discharged to the cooling system again.

The weight of the shaft 210 and the rotor 204 is supported by a thrust ball bearing 232, and when the shaft 210 rotates, the ball 234 rolls between the upper race 235 and the lower race 236, so that the rotation becomes smooth.

  By using the thrust ball bearing 232, the torque for rotating the shaft 210 is smaller than that of a thrust slide bearing that does not use a ball, so that the loss in the thrust bearing can be reduced. Therefore, the input can be reduced and the efficiency can be improved.

  Next, the lubricating oil 202 stored in the sealed container 201 is removed from the lower portion of the main shaft portion 211 by the first oil supply path 250 that is the oil supply means 240 provided in the shaft 210 due to the centrifugal force generated by the rotation of the shaft 210. Pumped up to the top.

  The lubricating oil 202 conveyed to the upper portion of the main shaft portion 211 by the first oil supply path 250 is supplied to the thrust ball bearing 232 through the inclined surface 256 that is the second oil supply path, and the first oil supply path. It is distributed to a third flow supplied from above the upper end of 250 to the upper side of the eccentric shaft portion 212 through a lateral hole 258 extending in the radial direction of the main shaft portion 211.

  Since the predetermined flow gap 246 is formed between the upper end of the bearing extension portion 244 and the upper race 235, the first flow flows in the radial direction via the axial gap 246 and is thrust. The flow is toward the ball bearing 232.

  In particular, this first flow is a direct flow toward the rolling portion between the ball 234 and the upper race 235, effectively reducing the loss in the ball 234 and the upper race 235, reducing heat generation and insufficient lubrication. It is possible to prevent occurrence of damage such as peeling due to, and to obtain high reliability.

  Furthermore, the flow resistance in the first flow can be changed by changing the axial gap 246 between the upper end of the bearing extension 244 and the upper race 235, and the flow resistance in the first flow is increased. The amount of the third flow lubricating oil 202 can be increased, and conversely, the flow resistance in the first flow can be reduced to decrease the amount of the third flow lubricating oil 202.

  Therefore, the lubricating oil 202 conveyed to the upper portion of the main shaft portion 211 by the first oil supply path 250 is used to flow the lubricating oil 202 to the thrust ball bearing 232 (first flow) and to the lubricating shaft upward of the eccentric shaft portion 212. The flow can be distributed to the flow 202 (third flow) at a desired ratio, and the flow rate of the lubricating oil 202 supplied to the thrust ball bearing 232 can be optimally adjusted.

  Accordingly, the optimum amount of the lubricating oil 202 can be supplied to both the thrust ball bearing 232 and the eccentric shaft portion 212, and the sliding loss can be reduced, and the heat generation is reduced and damage such as peeling due to insufficient lubrication occurs. Can be prevented and high reliability can be obtained.

  The distribution of the lubricating oil 202 can be similarly performed by the inclined surface 256 of the second oil supply path 252.

  That is, the flow resistance in the first flow can be changed without changing the axial gap 246 by changing the cross-sectional area of the inclined surface 256, the flow path resistance, the inclination angle, and the like. It is possible to increase the amount of the third flow lubricating oil 202, and conversely to decrease the flow resistance in the first flow to reduce the third flow lubricating oil 202.

Therefore, the lubricating oil 202 conveyed by the first oil supply path 250 is used to flow the lubricating oil 202 to the thrust ball bearing 232 (first flow) and the lubricating oil 202 to flow above the eccentric shaft portion 212 (third). The flow rate of the lubricating oil 202 supplied to the thrust ball bearing 232 can be optimally adjusted.

  Accordingly, the optimum amount of the lubricating oil 202 can be supplied to both the thrust ball bearing 232 and the eccentric shaft portion 212, and the sliding loss can be reduced, and the heat generation is reduced and damage such as peeling due to insufficient lubrication occurs. Can be prevented and high reliability can be obtained.

In addition, the second oil supply path 252 is not a simple communication path, but is provided on the inner periphery of the upper end of the bearing extension 244 and is configured by an inclined surface 256 inclined by 45 degrees with respect to the shaft center. The lubricating oil 202 conveyed to the lower end is smoothly guided to the upper end of the bearing extension 244 along the inclination of the inclined surface 256 using the centrifugal force effectively and supplied to the thrust ball bearing 232. It is possible to adjust the flow rate of the lubricating oil 202 to the thrust ball bearing 232 (first flow) and to the upper side of the eccentric shaft portion 212 by changing and adjusting both the axial clearance 246 and the flow path resistance of the inclined surface 256. It goes without saying that the flow (the third flow) of the lubricating oil 202 can be distributed at a finer rate.

  Next, when the hermetic compressor 200 is transported, an impact load in the vertical direction such as dropping may be applied. At this time, a vertical load is also applied to the thrust ball bearing 232, the elastically deformable support member 262 is elastically deformed, and the upper end of the bearing extension 244 is within the deformation region in which the support member 262 is elastically deformable. The axial gap 246 between the upper race 235 and the upper race 235 becomes zero and comes into contact.

  This is because the amount of elastic deformation of the support member 262 in the vertical direction is set to be larger than the axial gap 246.

  As described above, when a shocking load in the vertical direction is applied, the load can be supported not by the thrust ball bearing 232 but by the upper end of the bearing extension 244 and the upper race 235. It is possible to prevent the contact load between the upper race 235 and the lower race 236 from increasing extremely.

  Therefore, since the plastic deformation of the thrust ball bearing 232 can be prevented and the sliding of the thrust ball bearing 232 can be maintained in a good state, low noise, high efficiency and high reliability can be obtained.

  Next, the flow of the lubricating oil 202 supplied to the thrust ball bearing 232 will be described.

  The lubricating oil 202 supplied to the thrust ball bearing 232 is stored outside the bearing extension 244 so that the thrust ball bearing 232 is immersed after the thrust ball bearing 232 is lubricated. It is discharged into the space in the sealed container 201 by its own weight through the discharged path 268.

  Therefore, since it is possible to prevent new lubricating oil 202 from being constantly circulated and supplied to the thrust ball bearing 232, accumulation of wear powder and the like can be prevented, and high reliability can be obtained. it can.

In addition, in this Embodiment, although demonstrated with the example provided with the 2nd oil supply path | route, it is the bearing extension part 24.
4, the flow of the lubricating oil 202 to the thrust ball bearing 232 (first flow) and the flow of the lubricating oil 202 above the eccentric shaft portion 212 (only in the axial gap 246 between the upper end of the upper race 235 and the upper race 235) The third flow) may be distributed at a desired ratio.

  In addition, as the second oil supply path, the inclined surface 256 extending in the axial direction on the outer peripheral portion of the main shaft portion has been described. It is.

  In addition, although the example in which the discharge path 268 is provided in the cylinder block 214 has been described, the thrust ball bearing 232 is lubricated after the thrust ball bearing 232 is lubricated so that new lubricating oil 202 can be constantly circulated and supplied to the thrust ball bearing 232. Any other configuration can be used as long as it can be discharged into the space.

  Moreover, although the example which conveys the lubricating oil 202 to the 3rd oil supply path 260 via the horizontal hole 258 extended in the radial direction of the main shaft part 211 from the upper end of the 1st oil supply path 250 was demonstrated, The same can be done by conveying the lubricating oil 202 directly from the upper end to the third oil supply path 260.

  Further, although the example in which the support member 262 having the elastic force in the vertical direction is provided between the lower race 236 and the thrust surface 230 of the main bearing 220 has been described, the thrust is provided even when the support member 262 is not provided. Effects such as supply of the lubricating oil 202 to the ball bearing 232 and distribution of the lubricating oil 202 can be maintained.

  Moreover, by mounting the hermetic compressor 200, not only high efficiency as a refrigeration apparatus can be obtained, but also high reliability can be ensured.

(Embodiment 3)
11 is a longitudinal cross-sectional view of a hermetic compressor according to Embodiment 3 of the present invention, FIG. 12 is a cross-sectional view of main parts in the side surface direction of the shaft in the same embodiment, and FIG. FIG. 14 is a cross-sectional view of the main part in the shaft side direction in the same embodiment, and FIG. 15 is a perspective view of the cylinder block in the same embodiment.

  That is, in FIG. 12, the shaft shows an enlarged main part of FIG.

  11 to 15, lubricating oil 302 is stored in a sealed container 301, and an electric element 305 including a stator 303 and a rotor 304, and a compression element 306 driven by the electric element 305 are accommodated. The shaft 310 includes a main shaft portion 311 to which the rotor 304 is fixed, and an eccentric shaft portion 312 that is disposed on the upper portion of the main shaft portion 311 and is eccentric with respect to the main shaft portion 311.

  The cylinder block 314 has a substantially cylindrical compression chamber 316, and a main bearing 320 that supports the main shaft portion 311 is fixed. The piston 326 is inserted into the compression chamber 316 of the cylinder block 314 so as to be slidable back and forth, and is connected to the eccentric shaft 312 by a connecting means 328.

  The main bearing 320 of the cylinder block 314 includes a thrust surface 330 formed in an annular shape substantially at right angles to the axis of the main bearing 320, and a bearing extension having an inner surface that extends further upward than the thrust surface 330 and faces the main shaft portion 311. And a discharge path 368 communicating downward in the vertical direction on the outside of the bearing extension 344.

In order to support the shaft 310 in the vertical direction, the support member 362, the lower race 336, the plurality of balls 334, and the holder portion 333 that holds the balls 334 upward from the thrust surface 330 outside the bearing extension portion 344. The upper race 335 is arranged in this order.

  The lower race 336, the plurality of balls 334, the holder portion 333 that holds the balls 334, and the upper race 335 constitute a thrust ball bearing 332.

  Further, the support member 362, the lower race 336, the plurality of balls 334, and the holder portion 333 for holding the balls 334 are all arranged outside the bearing extension portion 344 with a radial clearance.

  On the other hand, the upper race 335 is disposed further above the upper end 370 of the bearing extension 344, and the distance (height) from the thrust surface 330 to the top of the ball 334 is longer than the thrust surface 330. Since the distance (height) to the upper end 370 of the protruding portion 344 is long, a predetermined axial gap 346 is formed between the upper end of the bearing extending portion 344 and the upper race 335 due to the dimensional difference.

  Here, the support member 362 is a member that is elastically deformable with an elastic force in the vertical direction, such as a wave washer having a relatively high rigidity or a hard elastic member. The amount of elastic deformation of the support member 362 in the vertical direction is set to be larger than the axial gap 346.

  Next, a detailed configuration related to the oil supply path of the shaft 310 will be described.

  The shaft 310 has oil supply means 340 that conveys the lubricating oil 302 upward. The oil supply means 340 extends in the axial direction to the first oil supply path 350 that conveys the lubricating oil 302 from the lower part to the upper part of the main shaft part 311 and the outer periphery of the main shaft part 311, and one end thereof is the first oil supply path 350. The second oil supply path 352 communicates with the upper end of the bearing extension portion 344 and communicates with the upper end of the bearing extension 344.

  In the embodiment of the present invention, the second oil supply path 352 includes a slit-shaped groove 354.

  Here, the first oil supply path 350 includes a concentric pump 350 a provided at the lower portion of the shaft 310, a horizontal hole 350 b extending in a radial direction from the upper portion of the concentric pump 350 a, and a lower end at the outer peripheral portion of the shaft 310. The upper end is formed by a spiral oil supply groove 350 c that communicates with the horizontal hole 350 b and has an upper end that communicates with a slit-like groove 354 of the second oil supply path 352.

  Further, the bearing extension 344 is provided with a fourth oil supply path 366 that communicates the inner periphery and the outer periphery of the bearing extension 344 in the radial direction in the substantially horizontal direction of the ball 334.

  Further, the main shaft portion 311 further has a horizontal hole 358 extending in the radial direction of the main shaft portion 311 from the upper end of the spiral oil supply groove 350 c constituting the first oil supply path 350, and a lower end communicating with the vicinity of the bottom portion of the horizontal hole 358. And a third oil supply path 360 extending upward from the shaft portion 312.

  The third oil supply path 360 is inclined so as to be separated from the axis of the main shaft portion 311 as it extends upward in order to increase the conveying ability of the lubricating oil 302 by the rotation of the shaft 310, and the uppermost portion is the eccentric shaft portion 312. The upper end 312a is open.

Further, in the present embodiment, the refrigerant used for the hermetic compressor 300 is a hydrocarbon refrigerant that is a natural refrigerant with a low global warming coefficient represented by R134a and R600a having an ozone depletion coefficient of zero, and the like. Each is combined with a highly compatible lubricating oil 302.

  The operation of the hermetic compressor 300 configured as described above will be described below.

  The rotor 304 of the electric element 305 rotates the shaft 310, and the rotational movement of the eccentric shaft portion 312 is transmitted to the piston 326 via the connecting means 328, so that the piston 326 reciprocates in the compression chamber 316. As a result, the refrigerant is sucked into the compression chamber 316 from the cooling system (not shown), compressed, and then discharged to the cooling system again.

  The weight of the shaft 310 and the rotor 304 is supported by a thrust ball bearing 332, and when the shaft 310 rotates, the ball 334 rolls between the upper race 335 and the lower race 336, so that the rotation becomes smooth.

  By using this thrust ball bearing 332, the torque for rotating the shaft 310 is smaller than that of a thrust slide bearing that does not use a ball, so that the loss in the thrust bearing can be reduced. Therefore, the input can be reduced and the efficiency can be improved.

  Next, the lubricating oil 302 stored in the sealed container 301 is removed from the lower portion of the main shaft portion 311 by the first oil supply path 350 that is the oil supply means 340 provided in the shaft 310 due to the centrifugal force generated by the rotation of the shaft 310. Pumped up to the top.

  The lubricating oil 302 conveyed to the upper portion of the main shaft portion 311 by the first oil supply path 350 is supplied to the thrust ball bearing 332 through the slit-like groove 354 that is the second oil supply path, and the first flow The oil is distributed to a third flow that is supplied to the upper side of the eccentric shaft portion 312 from the upper end of the oil supply path 350 through a lateral hole 358 extending in the radial direction of the main shaft portion 311.

  This first flow flows in the radial direction through this axial gap 346 and has a thrust because a predetermined axial gap 346 is formed between the upper end of the bearing extension 344 and the upper race 335. The flow is toward the ball bearing 332.

  In particular, this first flow is a direct flow toward the rolling location between the ball 334 and the upper race 335, effectively reducing loss in the ball 334 and the upper race 335, reducing heat generation, and insufficient lubrication. It is possible to prevent occurrence of damage such as peeling due to, and to obtain high reliability.

  Furthermore, the flow resistance in the first flow can be changed by changing the axial gap 346 between the upper end of the bearing extension 344 and the upper race 335, and the flow resistance in the first flow is increased. The amount of the third flow lubricating oil 302 can be increased, or conversely, the flow resistance in the first flow can be reduced to decrease the amount of the third flow lubricating oil 302.

  Therefore, the lubricating oil 302 conveyed to the upper part of the main shaft portion 311 by the first oil supply path 350 is used to flow the lubricating oil 302 to the thrust ball bearing 332 (first flow) and the lubricating oil upward to the eccentric shaft portion 312. The flow can be distributed to the flow 302 (third flow) at a desired ratio, and the flow rate of the lubricating oil 302 supplied to the thrust ball bearing 332 can be optimally adjusted.

  Accordingly, the optimum amount of the lubricating oil 302 can be supplied to both the thrust ball bearing 332 and the eccentric shaft portion 312, reducing sliding loss, reducing heat generation, and causing damage such as peeling due to insufficient lubrication. Can be prevented and high reliability can be obtained.

  Further, the distribution of the lubricating oil 302 can be similarly performed by the slit-shaped groove 354 of the second oil supply path 352.

  That is, by changing the cross-sectional area of the slit-shaped groove 354, the flow resistance in the first flow can be changed without changing the axial gap 346, and the flow resistance in the first flow is increased to increase the third. The flow of lubricating oil 302 can be increased, or conversely, the flow resistance in the first flow can be reduced and the third flow of lubricating oil 302 can be reduced.

  Therefore, the lubricating oil 302 conveyed by the first oil supply path 350 is used to flow the lubricating oil 302 to the thrust ball bearing 332 (first flow) and the flow of the lubricating oil 302 above the eccentric shaft portion 312 (third The flow rate of the lubricating oil 302 supplied to the thrust ball bearing 332 can be optimally adjusted.

  Accordingly, the optimum amount of the lubricating oil 302 can be supplied to both the thrust ball bearing 332 and the eccentric shaft portion 312, reducing sliding loss, reducing heat generation, and causing damage such as peeling due to insufficient lubrication. Can be prevented and high reliability can be obtained.

  In addition, by changing and adjusting both the axial clearance 346 and the cross-sectional area of the slit-shaped groove 354, the flow of the lubricating oil 302 to the thrust ball bearing 332 (first flow) and the eccentric shaft portion 312 upward. It goes without saying that the flow (the third flow) of the lubricating oil 302 can be distributed at a finer rate.

  Further, the slit-like groove 354 of the second oil supply path 352 and the fourth oil supply path 366 are intermittently communicated when the shaft 310 rotates, and the lubricating oil is supplied to the streak bearing 332 without passing through the axial gap 346. 302 can be supplied intermittently.

  Therefore, the gasified refrigerant accumulated in the first oil supply path 350 and the second oil supply path 352 can be quickly released into the sealed container 301 to prevent the oil supply from being obstructed by the gasified refrigerant.

  Furthermore, the lubricating oil 302 can be supplied to the entire ball 334 of the strike ball bearing 332 through the fourth oil supply path 366, and further, sliding loss can be reduced, heat generation is reduced, and peeling due to insufficient lubrication, etc. Can be prevented, and high reliability can be obtained.

  Next, when the hermetic compressor 300 is transported, an impact load in the vertical direction such as dropping may be applied. At this time, a vertical load is also applied to the thrust ball bearing 332, the elastically deformable support member 362 is elastically deformed, and the upper end of the bearing extension 344 is within the deformation region where the support member 362 is elastically deformable. The axial clearance 346 between the upper race 335 and the upper race 335 becomes zero and comes into contact.

  This is because the amount of elastic deformation of the support member 362 in the vertical direction is set to be larger than the axial gap 346.

  Thus, when a shocking load in the vertical direction is applied, the load can be supported not by the thrust ball bearing 332 but by the upper end of the bearing extension 344 and the upper race 335, so that the ball 334 It is possible to prevent the contact load between the upper race 335 and the lower race 336 from increasing extremely.

  Therefore, since the plastic deformation of the thrust ball bearing 332 can be prevented and the sliding of the thrust ball bearing 332 can be maintained in a good state, low noise, high efficiency and high reliability can be obtained.

  Next, the flow of the lubricating oil 302 supplied to the thrust ball bearing 332 will be described.

  The lubricating oil 302 supplied to the thrust ball bearing 332 is stored in the cylinder block 314 while the thrust ball bearing 332 is immersed outside the bearing extension 344 after lubricating the thrust ball bearing 332. It is discharged to the space in the sealed container 301 by its own weight through the discharged discharge path 368.

  Therefore, since it is possible to prevent the new lubricating oil 302 from being constantly circulated and stored in the thrust ball bearing 332, accumulation of wear powder and the like can be prevented, and high reliability can be obtained. it can.

  In the present embodiment, the example in which the second oil supply path is provided has been described. However, the thrust ball bearing 332 is lubricated only by the axial gap 346 between the upper end of the bearing extension 344 and the upper race 335. The oil 302 may be distributed at a desired ratio between the flow of the oil 302 (first flow) and the flow of the lubricating oil 302 above the eccentric shaft portion 312 (third flow).

  Moreover, although the slit-like groove 354 extending in the axial direction on the outer peripheral portion of the main shaft portion has been described as the second oil supply passage, the same applies to other shapes of grooves and other forms of oil supply passages. It can be implemented.

  Further, although the example in which the discharge path 368 is provided in the cylinder block 314 has been described, after the thrust ball bearing 332 is lubricated so that new lubricating oil 302 can be constantly circulated and supplied to the thrust ball bearing 332, Any other configuration can be used as long as it can be discharged into the space.

  Further, the example in which the lubricating oil 302 is conveyed to the third oil supply path 360 from the upper end of the first oil supply path 350 via the horizontal hole 358 extending in the radial direction of the main shaft portion 311 has been described. The same can be done by conveying the lubricating oil 302 directly from the upper end to the third oil supply path 360.

  Moreover, although the example provided with the support member 362 provided with the elastic force with respect to the vertical direction between the lower race 336 and the thrust surface 330 of the main bearing 320 has been described, the thrust is provided even when the support member 362 is not provided. Effects such as supply of the lubricating oil 302 to the ball bearing 332 and distribution of the lubricating oil 302 can be maintained.

  Moreover, by mounting the hermetic compressor 300, not only high efficiency can be obtained as a refrigeration apparatus, but also high reliability can be ensured.

  As described above, the hermetic compressor according to the present invention secures a clearance in the axial direction between the upper race and the bearing extension, and the thrust ball bearing is sufficiently lubricated to enable low noise, high efficiency, and high reliability. Therefore, it can be applied to uses such as an air conditioner and a hermetic compressor of a refrigeration apparatus.

100, 200, 300 Sealed compressor 101, 201, 301 Sealed container 102, 202, 302 Lubricating oil 103, 203, 303 Stator 104, 204, 304 Rotor 105, 205, 305 Electric element 106, 206, 306 Compression Element 110, 210, 310 Shaft 111, 211, 311 Main shaft portion 112, 212, 312 Eccentric shaft portion 114, 214, 314 Cylinder block 116, 216, 316 Compression chamber 120, 220, 320 Main bearing 126, 226, 326 Piston 128 , 228, 328 Connecting means 130, 230, 330 Thrust surface 132, 232, 332 Thrust ball bearing 133, 233, 333 Holder part 134, 234, 334 Ball 135, 235, 335 Upper race 136, 236, 336 Lower race 140, 240, 340 Lubrication means 144, 244, 344 Bearing extension 146, 246, 346 Axial clearance 150, 250, 350 First oil passage 152, 252, 352 Second oil passage 154, 354 Grooves 158, 258, 358 Side holes 160, 260, 360 Third oil supply path 162, 262, 362 Support members 168, 268, 368 Discharge path 256 Inclined surface 366 Fourth oil supply path

Claims (10)

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 eccentric to a main shaft portion extending in a vertical direction. A shaft having a shaft portion, a main bearing that forms a cantilever bearing by pivotally supporting the main shaft portion of the shaft, a cylinder block that forms a cylindrical compression chamber, and a reciprocating motion inside the compression chamber A piston that can be inserted, a connecting means that connects the piston and the eccentric shaft portion, the main bearing that is provided in the cylinder block and supports the main shaft portion, and a thrust surface of the main bearing. A plurality of balls disposed and held by a holder portion, and a thrust ball bearing having an upper race and a lower race respectively disposed above and below the balls, and the shaft includes a front From the outer circumferential portion of the shaft has an oil supply means for supplying the lubricating oil to the inner periphery of the thrust ball bearing, with the bearing extension part the main bearing extending in the inner peripheral portion of the holder portion is disposed The upper race is disposed above the bearing extension, and an axial gap having a predetermined width in the vertical direction is provided between an upper end of the bearing extension and the upper race, and the axial gap is provided. A hermetic compressor formed as a flow path for the lubricating oil. The oil supply means includes a first oil supply path for conveying the lubricating oil from a lower part to an upper part of the main shaft part, one end communicating with an upper end of the first oil supply path, and the other end communicating with an upper end of the bearing extension part. The flow rate of the lubricating oil supplied to the inner periphery of the thrust ball bearing is adjusted by changing the flow path resistance of the second oil supply path. The hermetic compressor described in 1. The second oil supply path is a slit-shaped groove having one end communicating with the first oil supply path and the other end communicating with the upper end of the bearing extension, and the slit-shaped groove is formed on the outer periphery of the main shaft part. 3. The hermetic compressor according to claim 2, wherein the hermetic compressor is extended in an axial direction. The hermetic compressor according to claim 2, wherein the second oil supply path is an inclined surface provided on an inner periphery of an upper end of the bearing extension portion. One end of the main shaft portion communicates with the first oil supply path, and extends upward from the eccentric shaft portion.
An oil supply path is provided, and by changing the flow path resistance of the second oil supply path, the lubricating oil conveyed by the first oil supply path is changed into a flow to the thrust ball bearing and a flow to the third oil supply path. The hermetic compressor according to any one of claims 2 to 4, wherein the hermetic compressor is formed so as to be distributed at a desired ratio. The hermetic compressor according to any one of claims 1 to 5, further comprising a support member having an elastic force in a vertical direction between the lower race and the thrust surface of the main bearing. By forming the axial clearance between the upper end of the bearing extension and the upper race so as to be smaller than the elastic deformation amount of the support member, the bearing extension can be applied when a vertical impact load is applied. The hermetic compressor according to claim 6, wherein an upper end of a portion and the upper race are in contact with each other to support an impact load. The bearing extension portion of the main bearing that extends to the inner peripheral portion of the holder portion includes a fourth oil supply path that connects the inner periphery and the outer periphery in the radial direction. The hermetic compressor according to any one of the above. The hermetic compressor according to any one of claims 1 to 8, further comprising a discharge path for discharging the lubricating oil after the thrust ball bearing is lubricated to a space in the sealed container. A refrigeration apparatus equipped with the hermetic compressor according to any one of claims 1 to 9.