JP5503494B2 - Hermetic compressor and refrigerator using the same - Google Patents

Description

  The present invention relates to a reciprocating hermetic compressor and a refrigerator using the same.

  As a conventional hermetic compressor, for example, the one described in Patent Document 1 is known. This hermetic compressor is provided with a thrust rolling bearing, and an upper tubular extension with a radial bearing hub extending is located on the inner diameter side of the thrust rolling bearing. The upper tubular extension has an overlapping portion with the upper race of the thrust rolling bearing, and the amount of oil supplied to the thrust rolling bearing is defined by the gap between the upper tubular extension and the upper race in the overlapping portion.

  Further, as another conventional hermetic compressor, for example, the one described in Patent Document 2 is known. This hermetic compressor is provided with a thrust rolling bearing above the upper end of the spiral groove provided on the outer surface of the crankshaft, and supplies lubricating oil to the thrust rolling bearing from the lubricating oil flow path inside the crankshaft. A branch flow path is provided.

Japanese Patent No. 4268519 (see FIG. 4b) Japanese Patent Laying-Open No. 2007-32562 (see FIG. 2)

  However, when the structures described in Patent Document 1 and Patent Document 2 are applied, there are the following problems. That is, in the structure described in Patent Document 1, since the upper race of the thrust rolling bearing that performs the rotational motion and the stationary upper tubular extension are in contact in the radial direction, there is a risk that sliding loss may occur. It was. Further, in the structure of Patent Document 1, since the inner diameter surface of the cage that holds the rolling elements of the thrust rolling bearing is configured to slide directly on the entire outer diameter surface of the upper tubular extension, the sliding situation is There was a risk of loss due to severe conditions.

  Further, in the structure described in Patent Document 2, since the branch flow path for supplying the lubricating oil from the lubricating oil flow path inside the crankshaft to the thrust rolling bearing is provided, the outer surface of the crankshaft is thrust rolled. It faces the entire inner diameter side of the bearing. For this reason, the entire inner diameter surface of the cage that holds the rolling elements of the thrust rolling bearing and the entire inner diameter surface of the lower race (lower thrust washer) that holds the lower side of the rolling elements may slide with the crankshaft. As a result, the sliding condition became severe and there was a risk of loss.

  This invention solves the above-mentioned conventional problem, and makes it a subject to provide the hermetic compressor which can reduce the loss which generate | occur | produces in a thrust rolling bearing, and a refrigerator provided with the same.

The present invention relates to a hermetic compressor in which an electric element and a compression element are housed in a hermetic container, wherein the electric element includes a stator and a rotor, and the compression element reciprocates a piston in a cylinder. A crankshaft for compressing the refrigerant, and a frame having a radial bearing for supporting the crankshaft, the frame is provided with a thrust rolling bearing for supporting the crankshaft, and an end of the radial bearing is The inner diameter side has an annular protrusion facing the crankshaft surface and the outer diameter side facing the inner diameter side of the thrust rolling bearing, and the crankshaft has a predetermined clearance from the upper surface of the annular protrusion. annular step portion is provided in a corresponding position, the upper surface of the annular projection holds the rolling elements of the thrust rolling bearing holding Te And it is located at a height between the upper and lower surfaces.

  ADVANTAGE OF THE INVENTION According to this invention, the hermetic compressor which can reduce the loss which generate | occur | produces in a thrust rolling bearing can be provided. Furthermore, if the hermetic compressor is mounted on a refrigerator, a refrigerator with low power consumption can be provided.

It is a longitudinal section of the hermetic compressor concerning a 1st embodiment. It is a perspective view showing a frame simple substance. It is a side view which shows a crankshaft. It is a longitudinal cross-sectional view of the state which assembled | attached the balance weight and the oil supply piece to the crankshaft. It is a disassembled perspective view of each component attached to the end surface of a cylinder. It is a longitudinal cross-sectional view which shows a thrust rolling bearing and its periphery. It is a longitudinal cross-sectional view when a thrust rolling bearing and its periphery are cut | disconnected in the position of a flame | frame communicating hole and an oil drain groove. It is a longitudinal cross-sectional view of the refrigerator in which the hermetic compressor is mounted. It is explanatory drawing which shows the flow of the refrigerant | coolant of a hermetic compressor. It is a longitudinal cross-sectional view which shows the thrust rolling bearing and its periphery in the hermetic compressor which concerns on 2nd Embodiment.

  Hereinafter, hermetic compressors 100 </ b> A and 100 </ b> B and a refrigerator 60 including the same will be described with reference to FIGS. 1 to 10. In addition, the same code | symbol in the figure of each embodiment shows the same thing or an equivalent.

(First embodiment)
As shown in FIG. 1, the hermetic compressor 100 </ b> A according to the first embodiment is a so-called reciprocating compressor that is configured by vertically arranging a compression element 20 and an electric element 30 in a hermetic container 3. The compression element 20 and the electric element 30 are elastically supported in the sealed container 3 via a plurality of coil springs 9.

  The electric element 30 is disposed below the frame 1 and includes the stator 5 and the rotor 6. The stator 5 is fixed to the frame 1 and the rotor 6 is fixed to a crankshaft 7 described later. The rotor 6 has a structure composed of a rotor core 6a in which electromagnetic steel plates are laminated.

  The compression element 20 includes a frame 1 including a crankshaft 7 that compresses refrigerant by reciprocating the piston 4 in the cylinder 1a, and a radial bearing 1b that supports the crankshaft 7.

  As shown in FIG. 2, the frame 1 is integrally formed including a cylinder 1a and a radial bearing 1b. The frame 1 has a substantially plate-like base 1c, and the cylinder 1a is positioned above the frame 1 (base 1c), and the radial bearing 1b is positioned at the center of the base 1c. .

  The cylinder 1a has a cylinder chamber 1d (see FIG. 1) in which the piston 4 (see FIG. 1) reciprocates. Further, the outer upper surface of the cylinder 1a has an inclined surface 1a1 that is inclined toward the crankshaft 7 (see FIG. 1).

  The radial bearing 1b is formed in a cylindrical shape having a through-hole 1e on which the crankshaft 7 is pivotally supported, and protrudes downward from the base 1c. A substantially circular recess 1f is formed on the upper surface of the base 1c, and the opening 1g of the through hole 1e is located in the recess 1f.

  An annular installation portion 1h on which a thrust rolling bearing 50 to be described later is placed is formed in the recess 1f at the periphery of the opening 1g. Further, in the recess 1f, there is a frame communication hole 1i that penetrates the base 1c in the vertical direction (vertical direction) around the installation portion 1h, and a slit-shaped oil discharge that communicates the frame communication hole 1i and the installation portion 1h. A groove 1j is formed. Further, the bottom surface of the installation portion 1h and the bottom surface of the oil drain groove 1j are configured to communicate with each other at the same height position, in other words, on the same plane. The frame communication holes 1i and the oil drain grooves 1j according to the present embodiment are formed at four positions at equal intervals in the circumferential direction, but are not limited to the present embodiment and can be changed as appropriate. The bottom surface of the oil drain groove 1j may be lower than the bottom surface of the installation portion 1h.

  As shown in FIG. 3, the crankshaft 7 is inserted into a radial bearing 1b (see FIG. 1) including a through hole 1e (see FIG. 1) and extends upward from below the frame 1 (see FIG. 1). The pin 7a is provided so as to be positioned above the frame 1 (see FIG. 1). The crank pin 7a is provided at a position eccentric from the center of rotation of the crank shaft 7 (the rotation axis O, see FIG. 1) at the upper end of the crank shaft 7.

  The crankshaft 7 has a flange portion 7h extending in a direction (horizontal direction) orthogonal to the rotation axis O (see FIG. 1). Further, a bored hole 7b is formed in the crankshaft 7 from the lower end to the upper side, forming a hollow space. The boring hole 7b is formed to a position approximately in the middle of the distance from the lower end of the crankshaft 7 to the flange portion 7h. The position of the boring hole 7b may be below or above the middle. In addition, the crankshaft 7 is formed with a lower communication hole 7c penetrating from the upper end of the boring hole 7b to the outside of the crankshaft 7.

  A spiral groove 7d is formed on the outer peripheral surface of the crankshaft 7 up to the lower edge of the flange portion 7h. The spiral groove 7d is formed with a width substantially the same as the diameter of the lower communication hole 7c.

  As shown in FIG. 4, the crankshaft 7 is formed with an upper communication hole 7e extending from the upper end 7j of the spiral groove 7d to the inside of the crank pin 7a in the vertical direction. The upper communication hole 7e extends through the flange portion 7h and extends partway in the height direction of the crank pin 7a. Further, the upper communication hole 7e is formed so as to be shifted toward the rotation axis O (see FIG. 1) of the crankshaft 7 from the axis center of the crankpin 7a. Further, the crankshaft 7 is configured such that a lateral hole 7j1 is formed with the upper end portion 7j of the spiral groove 7d directed toward the axial center, and a part of the upper surface side of the lateral hole 7j1 communicates with the upper communication hole 7e.

  Further, inside the crank pin 7a, there is formed a pin portion boring hole 7f that communicates with the upper communication hole 7e and extends upward. The pin portion boring hole 7f has an opening 7f1 whose upper end is open, and a pin portion lower communication hole 7g and a pin portion upper communication hole 7k are formed. The pin portion lower communication hole 7g communicates with a groove 7g1 formed on the outer peripheral surface of the crank pin 7a. The pin upper communication hole 7k is formed to penetrate the crankpin 7a and communicate with a small hole (not shown) formed to penetrate the balance weight 25. The balance weight 25 has a weight portion located on the side opposite to the crankpin 7a to prevent the compressor from vibrating.

  The crankshaft 7 is fitted with an oil supply piece 8 in the opening of the bore 7b. The oil supply piece 8 has a U-shape in a longitudinal sectional view, and an oil supply piece front end hole 8a is formed at the front end (lower end). Further, a stirring plate 8 b that stirs the lubricating oil 35 is provided in the oil supply piece 8.

  As shown in FIG. 1, the crankshaft 7 configured as described above is configured such that a lower portion thereof is coupled to the rotor 6 and the crankshaft 7 is rotated by the power of the electric element 30.

  The compression element 20 includes a cylinder 1a that forms a cylinder chamber 1d, a piston 4 that reciprocates in the cylinder chamber 1d, a connecting rod 2 that is coupled to the piston 4, and a discharge valve device 40 that is assembled to the end surface of the cylinder 1a. And a head cover 17 that forms a part of the discharge chamber space.

  The piston 4 is connected to the crank pin 7a via the large end 2b of the connecting rod 2, and reciprocates in the cylinder chamber 1d by the eccentric rotation of the crank pin 7a. In addition, a connecting rod communication hole 2 a is formed in the connecting rod 2 from the large end 2 b to the small end 2 c connected to the piston 4. The base end portion of the connecting rod communication hole 2a communicates with the groove 7g1 (see FIG. 4) formed in the crank pin 7a.

  As shown in FIG. 5, the top packing 41, the suction valve plate 42, the valve plate 43, the packing 44, the head cover 17, the suction silencer packing 45a, the suction silencer 45, and the suction silencer are arranged on the end surface of the cylinder 1a in this order from the cylinder 1a side. The fixing members 45b are arranged in this order.

  Further, bolt insertion holes b (partially not shown) are formed at four corners (partially not shown) of the top packing 41, the suction valve plate 42, the valve plate 43, the packing 44 and the head cover 17, and the bolt B (see FIG. 9). ) Are inserted into the respective bolt insertion holes b and screwed into bolt fastening holes c formed in the end face of the cylinder 1a, whereby the discharge valve device 40 and the head cover 17 are fastened to the end face of the cylinder 1a. Incidentally, the valve plate 43 is adjacent to the suction valve plate 42 to form a suction structure, and a discharge chamber space is formed by the valve plate 43, the packing 44 and the head cover 17. Note that the discharge chamber space in the head cover 17 is not shown.

  As shown in FIG. 6, the thrust rolling bearing 50 is provided between a flange portion 7 h formed on the crankshaft 7 and an end portion 1 b 1 of the radial bearing 1 b formed on the frame 1.

  The thrust rolling bearing 50 includes a plurality of rolling elements 50 a, a cage 50 b, an upper race 50 d and a lower race 50 c, and is placed on a groove-shaped installation portion 1 h formed on the frame 1. A plurality of rolling elements 50a are arranged at equal intervals in the circumferential direction, and each rolling element 50a is held around the horizontal direction (radial direction) by a cage 50b.

  The cage 50b holds the rolling element 50a such that the rolling element 50a protrudes upward from the upper surface 50b1 and downward from the lower surface 50b2 of the cage 50b. Further, the inner diameter side between the upper surface 50b1 and the lower surface 50b2 of the cage 50b is constituted by a surface 50b3 extending in the vertical direction.

  Thus, the rolling element 50a constituting the thrust rolling bearing 50, together with the cage 50b, rotates the load in the thrust direction of the crankshaft 7 while rolling between the upper race 50d and the lower race 50c as the crankshaft 7 rotates. It comes to support.

  An annular protrusion 1 s is formed integrally with the frame 1 at the end (upper end) 1 b 1 of the radial bearing 1 b. The annular protrusion 1s has a positional relationship in which the inner diameter side faces the outer diameter surface (surface) of the crankshaft 7 and the outer diameter side faces the inner diameter side (surface 50b3) of the thrust rolling bearing 50. It is configured as follows.

  On the other hand, the crankshaft 7 is formed with an annular step portion 7s that is opposed to the upper end surface 1s1 of the annular protrusion 1s with a predetermined gap S. The annular stepped portion 7s is configured such that the outer peripheral surface 7s2 is in a positional relationship facing the inner diameter side (surface 50b3) of the thrust rolling bearing 50.

  That is, the overall height of the thrust rolling bearing 50 is Hb, the height from the lower surface 50c1 of the lower race 50c to the upper end surface 1s1 of the annular protrusion 1s is Hf, and the upper surface of the upper race 50d from the lower end surface 7s1 of the annular step 7s. Assuming that the height up to 50d3 is Hs and the gap S is h, Hb = Hf + Hs + h is established.

  Further, the gap S between the annular protrusion 1s and the annular step 7s is set to be located at a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b. That is, the upper end surface 1s1 of the annular protrusion 1s and the lower end surface 7s1 of the annular stepped portion 7s are set to be positioned at a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b.

  As shown in FIG. 7, the frame 1 has a frame communication hole 1i communicating with the upper and lower sides, and the frame communication hole 1i communicates with an installation portion 1h in which the thrust rolling bearing 50 is installed via an oil drain groove 1j. doing.

  Next, the operation of the hermetic compressor 100A according to the first embodiment will be described. When the crankshaft 7 rotates with the rotation of the rotor 6, centrifugal force is applied to the lubricating oil 35 in the oil supply piece 8, and the lubricating oil 35 rises in the bore hole 7b provided at the lower end of the crankshaft 7, Further, it is carried to the lower communication hole 7c.

  The lubricating oil 35 that has reached the lower communication hole 7c is guided to the spiral groove 7d (see FIG. 3). In the lubricating oil passage formed by the wall surface of the spiral groove 7d and the wall surface of the radial bearing 1b (see FIG. 1), the lubricating oil 35 is dragged to the wall surface due to the viscous effect as the wall surface is moved by the rotation of the crankshaft 7. Ascends in the spiral groove 7d. At this time, the lubricating oil 35 simultaneously lubricates the radial bearing 1b.

  The lubricating oil 35 rising in the spiral groove 7d and reaching the upper end 7j of the spiral groove 7d again passes through the upper communication hole 7e shown in FIG. It is conveyed to 7f. Incidentally, at this time, in order to more effectively utilize the lubricating oil conveying ability due to the viscous effect in the spiral groove 7d, the position of the upper end portion 7j of the spiral groove 7d is made as close as possible to the flange portion 7h, and the upper communication hole 7e. It is preferable to shorten the length. This is because by bringing the position of the upper end portion 7j of the spiral groove 7d to the upper portion, the lubricating oil conveying section due to the viscous effect can be lengthened and the head of the lubricating oil 35 can be earned.

  The pin portion boring hole 7f is provided with a pin portion lower communication hole 7g, and the lubricating oil 35 reaching the pin portion lower communication hole 7g is connected to the connecting rod via a groove 7g1 formed on the outer peripheral surface of the crank pin 7a. It is carried to the communication hole 2a (see FIG. 1), and has a structure for lubricating the sliding portion between the connecting rod 2 and the piston 4.

  Further, a part of the lubricating oil 35 that has reached the pin portion boring hole 7f further rises due to centrifugal force and scatters from the open end of the pin portion communicating hole 7k and the pin portion boring hole 7f at the upper end of the crankshaft 7. To do. Part of the scattered lubricating oil 35 falls on the sliding surface of the piston 4 to lubricate the sliding surface between the piston 4 and the cylinder 1a. Further, the lubricating oil 35 scattered on the upper surface of the cylinder 1a is dropped to the piston 4 side according to the inclined surface 1a1 provided on the upper surface of the cylinder 1a, and is used for lubrication between the piston 4 and the cylinder 1a.

  Next, the operation of the lubricating oil around the thrust rolling bearing 50 will be described mainly with reference to FIGS. Incidentally, the lower race 50c of the thrust rolling bearing 50 is disposed so as to be in contact with the bottom surface 1h1 of the installation portion 1h of the frame 1, and the upper race 50d is in contact with the ceiling surface 7h1 formed in the flange portion 7h of the crankshaft 7. Is arranged. Further, since the lower race 50c is placed on the stationary frame 1, the surface 1s2 on the outer diameter side of the annular protrusion 1s and the lower race 50c do not slide, and the upper race 50d Since the relative speed is the same when rotating together with the crankshaft 7, the outer peripheral surface 7s2 of the annular stepped portion 7s and the upper race 50d do not slide.

  The lubricating oil 35 rising in the spiral groove 7d reaches the upper end 7j of the spiral groove 7d and then moves up through the upper communication hole 7e. At this time, a part of the lubricating oil 35 is supplied from the gap S formed between the annular protrusion 1s and the annular step 7s to the thrust rolling bearing 50 side. The supply amount of the lubricating oil 35 at this time can be determined by the size (height in the vertical direction) of the gap S between the annular protrusion 1s and the annular step portion 7s. During rotation of the crankshaft 7, the inner surface 50b3 of the cage 50b slides with the outer surface 1s2 of the annular protrusion 1s and the outer peripheral surface 7s2 of the annular step 7s. Since the gap S between the stepped portions 7s is located at the same height as the cage 50b, the inner surface 50b3 of the cage 50b, the outer surface 1s2 of the annular protrusion 1s and the annular stepped portion 7s. The sliding surface with the outer peripheral surface 7 s 2 has a structure in which the pressure of the lubricating oil 35 is directly applied to the sliding surface by centrifugal force, so that it is difficult to come into solid contact, that is, a structure that is easily lubricated by the lubricating oil 35.

  Lubricating oil 35 coming out of the gap S between the annular protrusion 1s and the annular step 7s lubricates the cage 50b and the rolling element 50a, and then drains without accumulating a large amount in the installation portion 1h of the thrust rolling bearing 50. Oil passes through the oil groove 1j (see FIG. 7) and is dropped by dropping from the frame communication hole 1i (see FIG. 7). Incidentally, when the lubricating oil 35 accumulates in a large amount in the installation portion 1h of the thrust rolling bearing 50, the rolling element 50a moves in the lubricating oil 35 and stirs, and power loss occurs. However, in the case of the structure of this embodiment, Since the lubricating oil 35 supplied to the thrust rolling bearing 50 is quickly discharged through the oil drain groove 1j and the frame communication hole 1i, it is possible to suppress the generation of power loss by the rolling element 50a. Therefore, even when the lubricating oil 35 is excessively supplied to the thrust rolling bearing 50 during the high-speed operation of the hermetic compressor 100A, the loss generated in the thrust rolling bearing 50 can be achieved by quickly discharging the lubricating oil 35. Can be suppressed. The frame communication hole 1i is formed so as to penetrate the frame 1 in the vertical direction, and the lubricating oil 35 discharged to the frame communication hole 1i is dropped onto the electric element 30 side.

  As described above, according to the hermetic compressor 100A according to the first embodiment, the end portion 1b1 of the radial bearing 1b of the frame 1 is provided with the annular protrusion 1s at the position facing the inner diameter side of the thrust rolling bearing 50. The crankshaft 7 is provided with the annular step 7s at a position corresponding to the upper end surface 1s1 of the annular protrusion 1s via the gap S, so that the lubricating oil 35 is applied to the thrust rolling bearing 50 using centrifugal force. Since it can be directly supplied, the sliding surface can be more easily lubricated than before, and the sliding resistance (sliding loss) can be reduced.

  Further, according to the hermetic compressor 100A according to the first embodiment, the upper end surface 1s1 of the annular protrusion 1s is high between the upper surface 50b1 and the lower surface 50b2 of the cage 50b that holds the rolling element 50a of the thrust rolling bearing 50. Therefore, the sliding area between the outer surface 1s2 of the annular protrusion 1s and the inner surface 50b3 of the cage 50b can be reduced. Loss) can be reduced.

  Further, according to the hermetic compressor 100A according to the first embodiment, the lower end surface 7s1 of the annular stepped portion 7s has a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b that holds the rolling element 50a of the thrust rolling bearing 50. Therefore, the sliding area between the outer peripheral surface 7s2 of the annular stepped portion 7s and the inner surface 50b3 of the cage 50b can be reduced, and the sliding resistance (sliding loss) is also reduced in this respect. Can be reduced.

  By the way, it is known that the lubricating oil 35 can be supplied more stably when transported by viscous force than when transported by centrifugal force (see, for example, JP-A-2005-337158).

  However, the structure described in Patent Document 2 has the following various problems. That is, in the structure of Patent Document 2, the lubricating oil rises in the spiral groove due to the viscous force accompanying the rotation of the crankshaft to the lower side of the thrust rolling bearing, and the vicinity of the thrust rolling bearing is in the flow path provided inside the crankshaft. Is raised by centrifugal force. For this reason, for example, when compared with the case where the spiral groove extends to the thrust surface of the crankshaft, the section in which the lubricant is transported by the viscous force is shortened, and the section in which the lubricant is transported by the centrifugal force is lengthened. Further, when the compressor is operated at a low speed, there is a fear that the lubricating oil conveying ability is insufficient and the amount of oil supplied to the thrust rolling bearing is insufficient. Further, in the structure in which the lubricating oil is supplied to the piston from the upper part of the crankshaft, there is a possibility that the lubricity of the piston sliding surface may be impaired due to an insufficient amount of oil supplied to the upper part of the crankshaft. Furthermore, since it is necessary to form the lubricating oil flow path from the upper end of the spiral groove to the eccentric part of the crankshaft at a position close to the rotating shaft side of the crankshaft, the centrifugal force obtained in the lubricating oil path is reduced, There was a risk that the amount of oil supplied to the upper part of the crankshaft would be insufficient during low-speed operation of the compressor.

  However, according to the hermetic compressor 100A according to the first embodiment, at least a part of the upper end portion 7j of the spiral groove 7d is located above the lower surface 50c1 of the lower race 50c of the thrust rolling bearing 50. The lubricating oil 35 can be raised to the thrust rolling bearing 50 by viscous force, and it is possible to prevent the lubricating oil supply amount to the thrust rolling bearing 50 from being insufficient. Furthermore, according to the first embodiment, since it is possible to prevent the amount of oil supplied to the upper portion of the crankshaft 7 from being insufficient, the lubricity of the piston sliding surface is not impaired. The piston sliding surface means a sliding surface between the piston 4 and the connecting rod 2 and a sliding surface between the piston 4 and the cylinder 1a.

  Further, according to the hermetic compressor 100A according to the first embodiment, the frame communication hole 1i communicating downward is formed in the frame 1, and the frame communication is performed from the installation portion 1h where the lower race 50c of the thrust rolling bearing 50 is installed. Since the oil drain groove 1j is formed in communication with the hole 1i, the lubricating oil 35 supplied to the thrust rolling bearing 50 is quickly drained through the oil drain groove 1j and the frame communication hole 1i. For this reason, it becomes possible to suppress generation | occurrence | production of the power loss by the rolling element 50a. Thereby, even when the lubricating oil 35 is excessively supplied to the thrust rolling bearing 50 during the high speed operation of the hermetic compressor 100A, the loss generated in the thrust rolling bearing 50 can be suppressed.

  Next, the refrigerator 60 equipped with the hermetic compressor 100A will be described with reference to FIG. FIG. 8 is a longitudinal sectional view of the refrigerator 60 on which the hermetic compressor 100A of this embodiment is mounted.

  As shown in FIG. 8, the refrigerator 60 includes a refrigerator main body 61, a refrigerator compartment 62, an upper freezer compartment 63, a lower freezer compartment 64, and a vegetable compartment 65. In addition, the positional relationship of the refrigerator compartment 62, the upper freezer compartment 63, the lower freezer compartment 64, and the vegetable compartment 65 is not restricted to FIG. The refrigerant discharged from the hermetic compressor 100A passes through a condenser (not shown) and a decompression mechanism (not shown) provided in the refrigerator 60, absorbs heat in the refrigerator by the cooler 66, and again It is returned to the hermetic compressor 100A. Note that a hydrocarbon refrigerant such as propane or isobutane is used in the refrigeration cycle including the hermetic compressor 100A, the condenser, the decompression mechanism, and the cooler 66.

  Moreover, with reference to FIG. 9, the flow of the refrigerant in the hermetic compressor 100A will be described. That is, the refrigerant that has returned from the cooler 66 and is introduced from the suction pipe 3 a that is connected through the sealed container 3 is sucked from the suction port 45 c (see FIG. 5) of the suction silencer 45, and then the head cover 17. It is introduced into the cylinder chamber 1d (see FIG. 1) through a circular introduction hole 17a and the like. The refrigerant compressed by the piston 4 in the cylinder chamber 1d passes through the discharge chamber space formed by the valve plate 43, the packing 44, and the head cover 17, and passes through the discharge silencers 1m, 1n and the pipe 3c formed in the frame 1. It passes through the discharge pipe 3b and is sent to the condenser.

  As described above, by mounting the hermetic compressor 100A with reduced sliding loss on the refrigerator 60, the operating efficiency of the refrigerator 60 can be improved, and as a result, the power consumption of the refrigerator 60 can be reduced.

  By the way, in general, when the compressor is driven by an inverter, if an oil supply path structure is used so that the amount of oil supplied to the thrust rolling bearing 50 is appropriate during low speed operation, the oil supply to the thrust rolling bearing 50 during high speed operation. Since the amount is excessive and there is no oil draining mechanism (corresponding to the frame communication hole 1i and the oil draining groove 1j) in the groove where the thrust rolling bearing 50 is installed in the structure as described in Patent Document 2, A part of the lubricating oil 35 may stay in the thrust rolling bearing portion 50, and may be lost due to stirring. Therefore, there is a problem that it is difficult to apply to a compressor having a wide operating speed range.

  However, the configuration is such that the hermetic compressor 100A of the present embodiment is driven by an inverter and is operated at a plurality of operating speeds (rotational speeds of the motor), so that the lubricating oil is excessive with respect to the thrust rolling bearing 50 during high-speed operation. Even when the oil is supplied to the thrust rolling bearing 50, the lubricating oil supplied to the thrust rolling bearing 50 is quickly discharged from the frame communication hole 1i through the oil drain groove 1j, so that the lubricating oil 35 stays in the thrust rolling bearing 50. It is possible to prevent the occurrence of loss (such as power loss due to the rolling element 50a).

  Therefore, the power loss can be suppressed by configuring the hermetic compressor 100A of the present embodiment so that it can be operated at a plurality of operating speeds as an inverter driven one. By applying the hermetic compressor 100A to the refrigerator 60, the power consumption of the refrigerator 60 can be further reduced.

(Second Embodiment)
Next, the hermetic compressor 100B of the second embodiment will be described with reference to FIG. The basic configuration is the same as that of the first embodiment, and only different points will be described. FIG. 10 is a longitudinal sectional view showing a thrust rolling bearing and its periphery in a hermetic compressor according to the second embodiment.

  As shown in FIG. 10, in the hermetic compressor 100B according to the second embodiment, the cylindrical member 70 is disposed in the gap between the inner diameter side of the thrust rolling bearing 50 and the outer diameter side of the crankshaft 7, that is, the cylindrical member. 70 is configured to be extrapolated to the crankshaft 7.

  The crankshaft 7 has an annular step portion 7t facing the upper surface 70a of the cylindrical member 70 with a predetermined gap S. The surface of the annular step portion 7t (outer peripheral surface 7t2) and the inner diameter side of the thrust rolling bearing 50 The positional relationship is such that the surfaces of each face in opposite directions. Similarly to the first embodiment, the height of the thrust rolling bearing 50 is Hb, the height from the lower surface 50c1 of the lower race 50c to the upper surface 70a of the cylindrical member 70 is Hf, and the lower end surface (lower surface) of the annular stepped portion 7t. When the height from 7t1 to the upper surface 50d3 of the upper race 50d is Hs, Hb = Hf + Hs + h is established.

  Further, in the hermetic compressor 100B, the gap S between the cylindrical member 70 and the annular step portion 7t is positioned at a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b. That is, the upper surface 70a of the cylindrical member 70 and the lower end surface 7t1 of the annular step portion 7t are positioned at the height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b, respectively.

  The operation of the lubricating oil 35 in the second embodiment will be described. The lubricating oil 35 that has reached the upper end portion 7j of the spiral groove 7d rises in the upper communication hole 7e, and a part of the lubricating oil 35 is annular with the cylindrical member 70. Supplied from the gap S with the stepped portion 7t to the thrust rolling bearing 50 side. Note that the supply amount of the lubricating oil 35 at this time is determined by the size (the height in the vertical direction) of the gap S between the cylindrical member 70 and the annular stepped portion 7t. When the crankshaft 7 rotates, the inner surface 50b3 of the cage 50b slides with the outer surface 70b of the cylindrical member 70 and the outer peripheral surface 7t2 of the annular step portion 7t. Since the gap S of 7t is located at the same height as the cage 50b, the sliding surface between the inner surface 50b3 of the cage 50b and the outer surface 7t2 of the upper surface 70a of the cylindrical member 70 and the annular stepped portion 7t. Since the pressure of the lubricating oil 35 is directly applied to the sliding surface by centrifugal force, the structure is difficult to come into solid contact, that is, the structure is easily lubricated by the lubricating oil 35.

  Further, the lubricating oil 35 that has come out of the gap S between the cylindrical member 70 and the annular stepped portion 7t is lubricated to the retainer 50b and the rolling element 50a, and then is not collected in a large amount in the installation portion 1h of the thrust rolling bearing 50. Oil passes through 1j (see FIG. 7) and is drained by dropping from the frame communication hole 1i (see FIG. 7). When a large amount of the lubricating oil 35 accumulates in the installation portion 1h of the thrust rolling bearing 50, the rolling element 50a moves in the lubricating oil 35 and stirs, and power loss occurs. Since the lubricating oil supplied to the bearing 50 is quickly drained, it is possible to suppress the occurrence of power loss by the rolling elements 50a. From this, even when the lubricating oil 35 is excessively supplied to the thrust rolling bearing 50 during the high speed operation of the compressor 100B, the loss generated in the thrust rolling bearing 50 can be suppressed.

  As described above, according to the hermetic compressor 100B according to the second embodiment, the cylindrical member 70 is provided at the position facing the inner diameter side of the thrust rolling bearing 50 at the end 1b1 of the radial bearing 1b of the frame 1. By providing the crankshaft 7 with the annular stepped portion 7t at a position corresponding to the upper surface 70a of the cylindrical member 70 via the gap S, the lubricating oil 35 is directly supplied to the thrust rolling bearing 50 using centrifugal force. Therefore, the sliding surface can be lubricated more easily than before, and the sliding resistance (sliding loss) can be reduced.

  Further, according to the hermetic compressor 100B according to the second embodiment, the upper surface 70a of the cylindrical member 70 is at a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b that holds the rolling elements 50a of the thrust rolling bearing 50. Therefore, the sliding area between the outer diameter side surface 70b of the cylindrical member 70 and the inner diameter side surface 50b3 of the cage 50b can be reduced. Also in this respect, the sliding resistance (sliding loss) can be reduced. Can be reduced.

  Further, according to the hermetic compressor 100B according to the second embodiment, the lower end surface 7t1 of the annular stepped portion 7t has a height between the upper surface 50b1 and the lower surface 50b2 of the cage 50b that holds the rolling element 50a of the thrust rolling bearing 50. Therefore, the sliding area between the outer peripheral surface 7t2 of the annular stepped portion 7t and the inner surface 50b3 of the cage 50b can be reduced, and the sliding resistance (sliding loss) can be reduced also in this respect. Can be reduced.

  Further, according to the hermetic compressor 100B according to the second embodiment, the gap S between the cylindrical member 70 and the annular stepped portion 7t can be easily adjusted by changing the length (height) of the cylindrical member 70. Is possible. More specifically, since the hermetic compressor 100B having such a structure is configured by stacking various components, there is a concern that a stacking error may increase. Therefore, according to the second embodiment, by providing the cylindrical member 70 configured separately, a plurality of cylindrical members 70 having different heights are prepared and matched to each member (sealed compressor 100B). By selecting the cylindrical member 70, clearance management becomes easier.

  Further, the power loss can be suppressed by configuring the hermetic compressor 100B of the second embodiment as an inverter-driven one so that it can be operated at a plurality of operating speeds. Further, by applying this hermetic compressor 100 </ b> B to the refrigerator 60, the power consumption of the refrigerator 60 can be reduced.

  In the above description, the case where the hermetic compressors 100A and 100B are mounted on the refrigerator 60 has been described as an example. However, the present invention is not limited to the refrigerator, and is mounted for a vending machine or a refrigerator / air conditioner. be able to.

1 Frame 1b Radial bearing 1i Frame communication hole (communication hole)
1j Oil drain groove 1s Annular protrusion 1s1 Upper end surface (upper surface)
DESCRIPTION OF SYMBOLS 3 Sealing container 5 Stator 6 Rotor 7 Crankshaft 7a Crankpin 7d Spiral groove 7h Flange part 7j Upper end part 7s, 7t Annular level | step difference part 7s1, 7t1 Lower end surface (lower surface)
DESCRIPTION OF SYMBOLS 20 Compression element 30 Electric element 35 Lubricating oil 50 Thrust rolling bearing 50a Rolling body 50b Cage 50c Lower race 50d Upper race 60 Refrigerator 70 Cylindrical member 70a Upper surface 100A, 100B Sealed compressor S Crevice

Claims (9)

In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
The frame is provided with a thrust rolling bearing that supports the crankshaft,
The end portion of the radial bearing has an annular protrusion whose inner diameter side faces the crankshaft surface and whose outer diameter side faces the inner diameter side of the thrust rolling bearing,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the annular protrusion with a predetermined gap ,
The hermetic compressor , wherein an upper surface of the annular protrusion is located at a height between an upper surface and a lower surface of a cage that holds a rolling element of the thrust rolling bearing . In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
The frame is provided with a thrust rolling bearing that supports the crankshaft,
The end portion of the radial bearing has an annular protrusion whose inner diameter side faces the crankshaft surface and whose outer diameter side faces the inner diameter side of the thrust rolling bearing,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the annular protrusion with a predetermined gap ,
The hermetic compressor , wherein a lower surface of the annular step portion is positioned at a height between an upper surface and a lower surface of a cage that holds a rolling element of the thrust rolling bearing . In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
In the frame, communication hole communicating to Rutotomoni downward thrust rolling bearing is provided for supporting the crank shaft is formed,
The end portion of the radial bearing has an annular protrusion whose inner diameter side faces the crankshaft surface and whose outer diameter side faces the inner diameter side of the thrust rolling bearing,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the annular protrusion with a predetermined gap ,
An hermetic compressor, wherein an oil drain groove extends from a surface on which a lower race of the thrust rolling bearing is installed to the communication hole . In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
The frame is provided with a thrust rolling bearing that supports the crankshaft,
A cylindrical member is disposed in the gap between the inner diameter side of the thrust rolling bearing and the outer diameter side of the crankshaft,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the cylindrical member with a predetermined gap ,
The hermetic compressor , wherein an upper surface of the cylindrical member is located at a height between an upper surface and a lower surface of a cage that holds a rolling element of the thrust rolling bearing . In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
The frame is provided with a thrust rolling bearing that supports the crankshaft,
A cylindrical member is disposed in the gap between the inner diameter side of the thrust rolling bearing and the outer diameter side of the crankshaft,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the cylindrical member with a predetermined gap ,
The hermetic compressor , wherein a lower surface of the annular step portion is positioned at a height between an upper surface and a lower surface of a cage that holds a rolling element of the thrust rolling bearing . In a hermetic compressor in which an electric element and a compression element are housed in a hermetic container,
The electric element includes a stator and a rotor,
The compression element includes a crankshaft that compresses a refrigerant by reciprocating a piston in a cylinder, and a frame having a radial bearing that supports the crankshaft.
In the frame, communication hole communicating to Rutotomoni downward thrust rolling bearing is provided for supporting the crank shaft is formed,
A cylindrical member is disposed in the gap between the inner diameter side of the thrust rolling bearing and the outer diameter side of the crankshaft,
The crankshaft is provided with an annular step at a position corresponding to the upper surface of the cylindrical member with a predetermined gap ,
An hermetic compressor, wherein an oil drain groove extends from a surface on which a lower race of the thrust rolling bearing is installed to the communication hole . The crankshaft has a spiral groove;
The hermetic compression according to any one of claims 1 to 6 , wherein at least a part of an upper end portion of the spiral groove is located above a lower surface of a lower race of the thrust rolling bearing. Machine.   The hermetic compressor according to any one of claims 1 to 7, wherein the hermetic compressor is operated at a plurality of operating speeds by inverter drive. A refrigerator equipped with the hermetic compressor according to any one of claims 1 to 8 .

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