JP2014058930A - Sealed compressor and refrigeration device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a sealed compressor with low noise, high efficiency and high reliability, which performs sufficient oil supply to a thrust ball bearing.SOLUTION: A sealed compressor has oil supply means 140 for supplying lubricating oil 102 in an inner periphery of a thrust ball bearing 132 from an outer periphery of a shaft 110, and a predetermined axial gap 146 is provided between an upper end of a bearing extension part 144 and an upper race 135. Thereby, the sealed compressor with low noise, high efficiency and high reliability can be provided by: supporting a load in the vertical direction such as self-weight of the shaft 110 and a rotor 104 only by the thrust ball bearing 132; preventing contact between the upper end of the bearing extension part 144 and the upper race 135; and performing sufficient oil supply to the thrust ball bearing 132.

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.

  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. 7 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, and FIG. 8 is an enlarged view of a main part of a thrust ball bearing of the conventional hermetic compressor described in Patent Document 1.

  7 and 8, 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 has the structure of the cantilever bearing supported with the main shaft part 20 and the main bearing 26 which are arrange | positioned only with respect to the eccentric shaft part 22 to which a load acts.

  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 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. 4, 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. ing.

  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. The eccentric shaft portion 22 is eccentrically moved by the rotation of the main shaft portion 20, and the eccentric motion of the eccentric shaft portion 22 is compressed by the piston 30 via the connecting means 36, and the compressed refrigerant is sent out from the sealed container 2 through 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 | action which ensures a direction clearance.

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.

The longitudinal cross-sectional view seen from the side of the hermetic compressor in an embodiment of the 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 Sectional drawing of the principal part of the cylinder block in the side surface direction in the same embodiment The perspective view of the cylinder block in the same embodiment Longitudinal sectional view from the side 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 arranged in a vertical direction. A shaft having an extended main shaft portion and an eccentric 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 the compression A piston inserted in a chamber so as to be capable of reciprocating; a connecting means for connecting the piston and the eccentric shaft portion; the main bearing provided on the cylinder block for supporting the main shaft portion; A plurality of balls disposed on a thrust surface of a main bearing 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, The shaft has a first oil supply path for conveying the lubricating oil from the lower part to the upper part of the main shaft part, and a bearing extension part in which the main bearing extends is disposed on the inner peripheral part of the holder part. A second oil supply path for supplying the lubricating oil to the inner periphery of the thrust ball bearing, and a predetermined gap between the upper end of the bearing extension portion and the upper race. An axial gap is provided, and the axial gap is formed as a flow path for the lubricating oil. By securing the axial gap, the thrust of the shaft and rotor can be reduced by using only a thrust ball bearing. Supports the load in the vertical direction, prevents contact between the upper end of the bearing extension and the upper race, and the lubricating oil is supplied to the thrust ball bearing through the axial clearance, so low noise, high efficiency and high reliability Provided hermetic compressor It can be.

  According to a second aspect of the present invention, the second oil supply path is a slit-like groove having one end connected to the first oil supply path and the other end communicating with the upper end of the bearing extension portion. The axial flow is extended to the outer peripheral portion of the main shaft portion, and the flow rate of the lubricating oil supplied to the inner periphery of the thrust ball bearing is adjusted by changing the flow resistance of the second oil supply path. Therefore, since the lubricating oil can stably supply a desired flow rate to the thrust ball bearing, a highly reliable hermetic compressor can be provided in addition to the effects of the first aspect of the invention.

  According to a third aspect of the present invention, the main shaft portion includes a third oil supply passage that has one end communicating with the first oil supply passage and extending upward from the eccentric shaft portion, and the flow resistance of the second oil supply passage is reduced. By changing, the lubricating oil conveyed by the first oil supply path is formed so as to be distributed at a desired ratio between the flow to the thrust ball bearing and the flow to the third oil supply path. Therefore, the lubricating oil can be supplied to the thrust ball bearing of the lubricating oil and each part of the compression element at a desired ratio, so that in addition to the effect of the invention according to claim 1, the highly reliable hermetic compressor Can be provided.

According to a fourth aspect of the present invention, a support member having an elastic force in a vertical direction is provided between the lower race and the thrust surface of the main bearing, and the support member is deformed even when a large external force is applied. By suppressing the contact load between the ball and the upper race and lower race,
Since 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 first to third inventions, further low noise, high efficiency and high reliability A hermetic compressor can be provided.

  According to a fifth aspect of the present invention, a vertical impact load is applied by forming an axial gap between the upper end of the bearing extension and the upper race so as to be smaller than an elastic deformation amount of the support member. Further, the upper end of the bearing extension and the upper race are in contact with each other to support an impact load, and the contact load between the ball and the upper race and the lower race is extremely increased. In addition to the effects of the invention according to claim 4, in addition to the effects of the invention according to claim 4, it is possible to prevent the thrust ball bearing from being plastically deformed and maintain the sliding of the thrust ball bearing in a good state. A highly efficient and highly reliable hermetic compressor can be provided.

  According to a sixth aspect of the invention, there is provided a discharge path for discharging the lubricating oil after the thrust ball bearing has been lubricated to a space in the sealed container, and the lubricating oil is always supplied to the thrust ball bearing. Since it circulates and is not stored, it is possible to prevent accumulation of wear powder and the like, and in addition to the effects of the first to fifth inventions, it is possible to provide a highly reliable hermetic compressor. .

  The seventh invention is a refrigeration apparatus equipped with a hermetic compressor, and has a low noise, high efficiency and high reliability by installing a hermetic compressor with low noise, high efficiency and high reliability. A refrigeration apparatus can be provided.

  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 an embodiment of the present invention, FIG. 2 is a sectional view of an essential part in the side surface direction of the shaft in the embodiment, and FIG. 3 is a front view of the shaft in the embodiment. 4 is a cross-sectional view of the main part in the side surface direction of the shaft in the same embodiment, FIG. 5 is a cross-sectional view of the main part in the side surface direction of the cylinder block in the same embodiment, and FIG. It is a perspective view of a block.

  1 to 6, 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 has a second oil supply path 152 formed of a slit-like groove whose one end communicates with the upper end of the bearing extension 144 on the inner side of the bearing extension 144, and the bearing extension A discharge path 168 communicating vertically downward is provided outside 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 longer from the thrust surface 130 to the bearing extension. Since the distance (height) to the upper end 170 of the protruding portion 144 is long, a predetermined axial gap 146 is formed between the upper end of the bearing extending portion 144 and the upper race 135 due to the dimensional difference.

  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 has 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.

  Here, the first oil supply path 150 includes a concentric pump 150 a provided at the lower portion of the shaft 110, a horizontal hole 150 b that communicates with the upper portion of the concentric pump 150 a and extends in the radial direction, and a lower end at the outer peripheral portion of the shaft 110. The upper end of the cylinder block 114 includes a spiral oil supply groove 150c that communicates with a second oil supply path 152 that is provided inside the bearing extension portion 144.

  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. Thereby, 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 part of the main shaft portion 111 by the first oil supply path 150 is supplied from the first flow supplied to the thrust ball bearing 132 through the second oil supply path 152 and from the upper end of the first oil supply path 150. It is distributed to a third flow supplied above 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-like groove of the second oil supply path 152.

That is, the flow resistance in the first flow can be changed without changing the axial gap 146 by changing the cross-sectional area of the slit-like groove, and the flow resistance in the first flow is increased to increase the third flow resistance. The flow lubricating oil 102 can be increased, or vice versa, the flow resistance in the first flow can be reduced to reduce 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).

  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.

  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.

DESCRIPTION OF SYMBOLS 100 Sealed compressor 101 Sealed container 102 Lubricating oil 103 Stator 104 Rotor 105 Electric element 106 Compression element 110 Shaft 111 Main shaft part 112 Eccentric shaft part 114 Cylinder block 116 Compression chamber 120 Main bearing 126 Piston 128 Connecting means 130 Thrust surface 132 Thrust ball bearing 133 Holder portion 134 Ball 135 Upper race 136 Lower race 140 Oil supply means 144 Bearing extension portion 146 Axial clearance 150 First oil supply route 152 Second oil supply route 150b, 158 Horizontal hole 160 Third oil supply route 162 Support member 168 Discharge Route

Claims (7)

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 the shaft A first oil supply path for conveying the lubricating oil from the lower part to the upper part of the shaft part; a bearing extension part in which the main bearing extends from the inner peripheral part of the holder part; A second oil supply path for supplying the lubricating oil to the inner periphery of the thrust ball bearing is provided on the inner periphery of the extension portion, and a predetermined axial clearance is provided between the upper end of the bearing extension portion and the upper race. The hermetic compressor is characterized in that the axial gap is formed as a flow path for the lubricating oil. The second oil supply path is a slit-shaped groove having one end connected to the first oil supply path and the other end communicating with the upper end of the bearing extension part, and the slit-shaped groove is an outer peripheral part of the main shaft 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. Hermetic compressor. The main shaft part includes a third oil supply path that is communicated with the first oil supply path at one end and extends above the eccentric shaft part, and changes the flow resistance of the second oil supply path, thereby changing the flow resistance of the second oil supply path. The said lubricating oil conveyed by 1 oil supply path | route is formed so that a desired ratio may be distributed to the flow to the said thrust ball bearing, and the flow to the said 3rd oil supply path | route. Hermetic compressor. The hermetic compressor according to any one of claims 1 to 3, 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. 5. The hermetic compressor according to claim 4, wherein an upper end of a portion and the upper race are in contact with each other to support an impact load. 6. The hermetic compressor according to claim 1, further comprising a discharge path for discharging the lubricating oil after lubricating the thrust ball bearing to a space in the hermetic container. A refrigeration apparatus equipped with the hermetic compressor according to any one of claims 1 to 6.