JP6132747B2 - Hermetic compressor and equipment having hermetic compressor - Google Patents

Description

  The present invention relates to a hermetic compressor and a device having the hermetic compressor.

  In recent years, demands for energy saving in refrigerators are increasing. When the inside of the refrigerator is cooled to the set temperature, the operation of the compressor is an intermittent operation that repeats stopping and starting. When the compressor is stopped, the pressure difference and temperature difference of the refrigerant in the refrigeration cycle are made uniform, so that extra power is required to start again and create the same pressure difference and temperature difference. Therefore, when the refrigerator reaches the set temperature, if the pressure difference and temperature difference are maintained by operating at low speed without stopping the compressor, the number of times the operation of the compressor stops will decrease. The extra power mentioned above can be reduced, leading to a reduction in power consumption of the refrigerator. However, when the compressor operating speed is low, the amount of oil supplied to the sliding portion tends to be insufficient due to the characteristics of an oil pump in the compressor described later.

  A centrifugal pump using a centrifugal force generated by rotation of a crankshaft is known as an oil supply pump in a hermetic compressor related to the background art of this technical field. Since the amount of oil supplied to the centrifugal pump is proportional to the square of the operating speed at an operating speed equal to or higher than the threshold value, the amount of oil supplied greatly decreases as the operating speed decreases.

  On the other hand, there is a viscous pump as an oil supply pump that can secure an oil supply amount even during low-speed operation. The viscous pump is an oil supply mechanism that makes use of a shearing force that acts on lubricating oil generated by a speed difference between a stationary member provided in the compressor and a crankshaft that rotates. FIG. 2 is a diagram showing the relationship between the operation speed and the amount of oil supply in the centrifugal pump and the viscous pump. The oil supply amount of the viscous pump has a characteristic of increasing in proportion to the operation speed, and the oil supply amount does not decrease as much as the centrifugal pump even if the operation speed decreases. For this reason, when operating with the same crankshaft diameter, the lower limit of the operating speed range is lower for the viscous pump than for the centrifugal pump. In this way, the viscosity pump can secure a sufficient amount of oil supply during low-speed operation than the centrifugal pump, so there is a strong demand for an increase in oil supply by the viscous pump in order to supply sufficient lubricating oil even during low-speed operation. .

  The structure of the viscous pump is shown in Patent Document 1, for example. The hermetic compressor of Patent Document 1 has a stationary member (sleeve 136) inserted coaxially with the rotating shaft of the crankshaft in a cylindrical cavity portion in the crankshaft (cylindrical member 133). A rotating member (insertion member 138) that rotates with the crankshaft is provided in the cylindrical cavity in the crankshaft. The outer peripheral surface of the stationary member and the outer peripheral surface of the rotating member that rotates with the crankshaft are provided with spiral grooves.

JP 2005-337158 A

  Although the required oil supply amount to the compressor depends on the operation speed of the compressor, the centrifugal pump can function in the middle speed region as shown in FIG. 2, while the oil supply amount of the viscous pump is small. For this reason, in a configuration having only a viscous pump as in Patent Document 1, there is a possibility that a necessary oil supply amount cannot be ensured when the operating speed of the compressor is lowered.

  The present invention has been made in view of the above circumstances, and provides a hermetic compressor capable of securing a sufficient amount of oil supply even in a low speed region.

As an example of an aspect for achieving the above-described object, at least a part of the lubricating oil storage part storing lubricating oil below the sealed container, a rotatable crankshaft having a cylindrical cavity part, and the cylindrical cavity part is provided. A rotating member rotatable on the same rotating shaft as the crankshaft, and a stationary member provided between the crankshaft and the rotating member with a gap between the crankshaft and the rotating member. A hermetic compressor including an oil supply means, wherein the rotating member is hollow inside, and has a lower communication portion in the lower part for supplying the lubricating oil to the inside of the rotating member. A first oil supply path including a path spiral groove in a gap between the stationary member and the rotating member; a second oil supply path including a second oil supply path spiral groove in a gap between the stationary member and the crankshaft; and the rotating member. The lower communication part and the The upper end of the rolling possess a third oil supply path and an internal member, wherein the inner and the stationary member the outlet hole provided with an outlet hole communicating with the cylindrical hollow portion to said rotating member of said rotary member having the a height above the height, or the side surface of the rotary member, characterized in that it have a degassing hole.

  According to the present invention, it is possible to provide a hermetic compressor capable of securing a sufficient amount of oil supply even in a low speed region.

It is a longitudinal section of the hermetic compressor concerning a 1st embodiment. It is a figure which shows the relationship between the operating speed and oil supply amount in a centrifugal pump and a viscous pump. It is the top view which permeate | transmitted the top | zenith part of the hermetic compressor of 1st Embodiment. It is a principal part enlarged view which represents typically the oil supply means which concerns on 1st Embodiment. It is sectional drawing of the crankshaft and crankshaft lower part which concern on 1st Embodiment. The It is a front view of the stationary member concerning a 1st embodiment. It is sectional drawing of the stationary member which concerns on 1st Embodiment. It is sectional drawing which shows the oil level in the rotating member which rotates with the oil supply path | route which concerns on 1st Embodiment. It is the schematic which showed the relationship between the oil supply amount of each of the 1st oil supply path | route of the oil supply means of 1st Embodiment, the 2nd oil supply path | route, the 3rd oil supply path | route, the sum total oil supply quantity of three oil supply path | routes, and an operating speed. It is a schematic diagram which shows the oil-surface shape observed at the time of the compressor operation of 1st Embodiment. It is a principal part expanded sectional view which represents typically the oil supply means which concerns on 2nd Embodiment. It is sectional drawing of the stationary member which concerns on 2nd Embodiment. It is a principal part expanded sectional view which represents typically the oil supply means which concerns on 3rd Embodiment. It is a principal part expanded sectional view which represents typically the oil supply means which concerns on 4th Embodiment. It is a principal part expanded sectional view which represents typically the oil supply means which concerns on 5th Embodiment. It is a longitudinal cross-sectional view of the refrigerator in which any of the hermetic compressors according to each embodiment is mounted.

  Embodiments according to the present invention will be described below with reference to the drawings. In all the drawings, the same reference numerals are given to the same components, and the description will be omitted as appropriate. Further, the present invention is not necessarily limited to each embodiment, and a known configuration other than the configuration described in each embodiment can be adopted within the scope of the concept of the present invention.

  The various components of the present invention do not necessarily have to be independent of each other. A plurality of components are formed as a single member, and a single component is formed of a plurality of members. A certain component is a part of another component, a part of a certain component overlaps a part of another component, and the like.

[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. 1 and 3 to 10. First, the overall configuration of the hermetic compressor will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a hermetic compressor according to the first embodiment of the present invention, and FIG. 3 is a top view of the hermetic compressor according to the present embodiment that is transmitted through the zenith. The hermetic compressor 50 according to this embodiment houses an electric element 2 including a stator 2 a and a rotor 2 b and a compression element 3 in a hermetic container 1. The compression element 3 is a reciprocating compression mechanism, and the piston 7 connected to the eccentric shaft 8a of the crankshaft 8 by the connecting rod 6 reciprocates in the cylinder 5a. A crankshaft 8 is rotatably fitted to the radial bearing 5c of the cylinder block 5. The compression element 3 is elastically supported on the bottom of the hermetic container 1 by a coil spring 23 via a stator 2a fixed to the lower part of the frame part 5b. As the rotor 2b rotates, the crankshaft 8 rotates and the eccentric shaft 8a rotates eccentrically. As the eccentric shaft 8a rotates eccentrically, the piston 7 reciprocates in the cylinder 5a. The inside of the cylinder 5 a is closed by a cylinder head 10 in which a suction valve and a discharge valve (not shown) are incorporated, and a compression working chamber 12 is formed between the cylinder 5 a and the piston 7. The head cover 11 in which the discharge chamber 11 a is formed is fixed to the cylinder block 5 with a fastening bolt 13. The suction silencer 15 reduces the noise by attenuating the pressure pulsation of the working fluid in the suction path, and is located above the frame portion 5 b of the cylinder block 5.

  Next, the refrigerant path inside the compressor will be described. The refrigerant flowing in through the suction pipe 14 connected to the sealed container 1 passes through the suction silencer 15 and enters the compression working chamber 12 of the cylinder 5a from the suction port of the cylinder head 10. In the compression working chamber 12, the refrigerant is sucked and compressed by the reciprocating motion of the piston 7 and discharged from the discharge port. The compressed refrigerant enters the discharge chamber 11 a in the head cover 11 from the discharge port of the cylinder head 10, passes through the discharge silencer 16 integrally formed with the cylinder block 5 from here, and passes through the discharge pipe 17 through the discharge pipe 22. Outflow to external refrigeration cycle.

  The oil supply means of this embodiment is demonstrated in detail using FIG. 4 thru | or FIG. FIG. 4 is an enlarged view of a main part schematically showing the oil supply means according to this embodiment, and FIG. 5 is a cross-sectional view of the crankshaft 8 and the lower part of the crankshaft 8 according to this embodiment. FIG. 6 is a front view of the stationary member 20 according to the present embodiment, and FIG. 7 is a cross-sectional view of the stationary member 20 according to the present embodiment. FIG. 8 is a cross-sectional view showing an oil supply path and an oil level in a rotating rotating member according to the present embodiment.

  In the present embodiment, a large-diameter cylindrical hollow portion 30a that opens to the lower end side of the crankshaft 8 and can accommodate the substantially cylindrical rotating member 18 is provided in the substantially cylindrical crankshaft 8 and the upper portion thereof. A cylindrical cavity 30 including a small-diameter cylindrical cavity 30b is provided. A hollow rotating member 18 is mounted inside the cylindrical cavity 30 so as to rotate coaxially with the rotating shaft of the crankshaft 8 and according to the rotation of the crankshaft 8. Preferably, the rotating member 18 is provided so as not to rotate relative to the crankshaft 8, and the crankshaft 8 and the rotating member 18 rotate at the same angular velocity. The bottom of the rotating member 18 is immersed in the lubricating oil 4 in the lubricating oil reservoir 4a provided below the hermetic container 1 and is, for example, circular as a lower communication portion so as to supply the lubricating oil to the inside of the rotating member 18. The lower hole 18a is provided.

  The cylindrical cavity 30 has a small-diameter cylindrical cavity 30b in which the rotating member 18 can be mounted on the crankshaft 8, and a large-diameter cylindrical cavity 30a so that a gap is provided in the radial direction between the crankshaft 8 and the rotating member 18. The large-diameter cylindrical cavity 30a is provided with a substantially cylindrical stationary member 20 with a gap between each of the crankshaft 8 and the rotating member 18.

  The stationary member 20 is made of a resin such as polyphenylene sulfide resin (PPS). The stationary member 20 is a hollow bottomless substantially cylindrical shape having an open upper end and a lower end, and a part of the rotating member 18 can be accommodated with a gap. The radial gap between the crankshaft 8 and the stationary member 20 is set to 0.2 to 0.3 mm, and the radial gap between the rotating member 18 and the stationary member is similarly set to 0.2 to 0.3 mm. Is set.

  In the present embodiment, a second oil supply path spiral groove 20 b and a first oil supply path spiral groove 20 c are provided on the outer peripheral surface and the inner peripheral surface of the stationary member 20. The depths of the second oil supply path spiral groove 20b and the first oil supply path spiral groove 20c are set to 0.6 to 1.2 mm, respectively. The stationary member 20 has a convex portion 20a having a hole in the bottom surface. A wire 21 as a rotation suppressing means passes through the hole of the convex portion 20a. The wire 21 is fixed to the stator 2a. Thereby, the motion of the stationary member 20 can be suppressed. For example, when the crankshaft 8 or the rotating member 18 is rotated, the rotational force is transmitted to the stationary member 20 and the rotation is suppressed. That is, the crankshaft 8 and the rotating member 18 are restrained from applying a rotational force to the stationary member 20 and rotate efficiently with respect to the stationary member 20.

  When the compressor is operated, the crankshaft 8 and the rotating member 18 rotate with the rotation of the rotor 2b. Due to the difference in speed generated between the rotating member 18 fixed to the crankshaft 8 and the stationary member 20 due to the rotation of the crankshaft 8, the lubricating oil in the radial gap between the rotating member 18 and the stationary member 20 has a shearing force. The lubricating oil passes through the radial groove between the stationary member 20 and the rotating member 18 along the first oil supply path spiral groove 20 c on the inner peripheral surface of the stationary member 20, and ascends inside the rotating member 18. This is referred to as a first oil supply path.

  Further, due to the speed difference between the crankshaft 8 and the stationary member 20, a shearing force acts on the lubricating oil in the radial gap between the crankshaft 8 and the stationary member 20, and the lubricating oil is the second of the outer peripheral surface of the stationary member 20. Along the oil supply path spiral groove 20b, it passes through a radial gap between the crankshaft 8 and the stationary member 20, and ascends inside the crankshaft. This is referred to as a second oil supply path.

  Furthermore, the lubricating oil enters the inside of the cylindrical rotating member 18 fixed to the crankshaft 8 from a lower hole 18 a that is a lower communication portion provided at the bottom of the rotating member 18. The lubricating oil that has entered the rotary member 18 is subjected to centrifugal force by the rotation of the rotary member 18, and rises inside the rotary member 18. This is referred to as a third oil supply path.

  The lubricating oil that has risen inside the crankshaft 8 through the first, second, and third oil supply paths is conveyed to the communication hole 8b that communicates the outer surface of the crankshaft 8 and the large-diameter cylindrical cavity 30a. The position of the communication hole 8b is not particularly limited as long as the lubricating oil 4 raised by the oil supply means such as the first oil supply path can be supplied to the crank outer surface spiral groove 8c, but preferably the upper end of the stationary member 20 It is provided at a height in the vicinity, more preferably at a height including the upper end of the stationary member 20. Lubricating oil that has reached the radial gap between the outer surface of the crankshaft 8 and the radial bearing 5c (see FIG. 1, etc.) via the communication hole 8b is generated on the outer surface of the crankshaft 8 and the radial bearing 5c. Shear force works due to the speed difference. The shearing force acting on the lubricating oil serves as a driving force, and the lubricating oil moves along the crank outer surface spiral groove 8c (see FIGS. 4 and 5, etc.) provided on the outer surface of the crankshaft 8. Guided upward.

  Thereafter, the lubricating oil passes through the communication hole 8d in the outer surface of the crankshaft 8 and enters the crankshaft 8 again. The lubricating oil that has entered the crankshaft 8 passes through the eccentric shaft 8a and passes through a hole (not shown) that passes through the connecting rod 6 that is rotatably fitted to the eccentric shaft 8a. The lubricating oil that has passed through the connecting rod 6 lubricates the ball joint 19 that connects the connecting rod 6 and the piston 7. Furthermore, it injects from the hole (not shown) provided in the form which penetrates the balance weight 9 attached to the upper end of the eccentric shaft 8a, and is finally injected to the circumference | surroundings from the upper end part of the eccentric shaft 8a. Lubrication and sealing between the piston 7 and the cylinder 5a are performed mainly by the injected lubricating oil 4.

  FIG. 9 is a schematic diagram showing the relationship between the operating speed and the oil supply amount of each of the first oil supply path, the second oil supply path, and the third oil supply path of the oil supply means of this embodiment, and the total oil supply amount of these three oil supply paths. It is. During low speed operation, the oil level inside the rotating member 18 constituting the centrifugal pump does not reach the outlet hole 18c on the side surface of the rotating member 18. Therefore, the oil supply by the viscous pump is dominant in the oil supply means inside the compressor. That is, the amount of oil supplied from the compressor oil supply means is the sum of the amounts of oil passing through the first oil supply path and the second oil supply path. When the oil level in the rotary member 18 constituting the centrifugal pump reaches an operation speed that reaches the outlet hole 18c on the side of the rotary member 18, both the centrifugal pump and the viscous pump supply oil. This is the total amount of oil passing through the first oil supply path, the second oil supply path, and the third oil supply path. And if it becomes more than the predetermined speed in a medium speed area and a high speed area, the oil supply capability of a viscous pump will become smaller than a centrifugal pump. Therefore, the oil supply by the centrifugal pump is dominant in the oil supply means in the compressor.

  As described above, the dominant oil supply path of the oil supply means in the compressor changes depending on the operation speed, and therefore, the amount of oil supplied by the oil supply means of this embodiment becomes a curve as shown in FIG. In the low speed range where the centrifugal pump alone cannot be refueled, lubrication is performed by the viscous pump, and in the middle speed region, the centrifugal pump and the viscous pump are used together, so that a larger amount of oil can be secured than the viscous pump alone. For this reason, in this embodiment, it becomes possible to ensure a sufficient amount of oil supply at any operating speed.

  Next, the position of the outlet hole 18c that is provided in the rotating member 18 and that supplies the lubricating oil 4 that has moved up the third oil supply path to the large-diameter cylindrical cavity 30a will be described. The lower end of the outlet hole 18c provided in the rotating member 18 is the same height as the upper end of the stationary member 20 in the large-diameter cylindrical cavity 30a, or above the upper end (height higher than the height of the upper end of the stationary member 20). Is located. Thereby, it can prevent that the lubricating oil which raised the 1st oil supply path | route and / or the 2nd oil supply path | route falls into the inside of the rotating member 18, and can ensure sufficient oil supply amount. The upper limit of the height of the lower end of the outlet hole 18c is not particularly limited, but is preferably provided in view of the height at which the lubricating oil rises through the third oil supply path.

  When the lower end of the outlet hole 18c is positioned below the upper end of the stationary member 20, the lubricating oil that has risen in the first oil supply path and / or the second oil supply path reaches the outlet hole 18c, and the rotating member 18 is caused by the gravity of the lubricating oil. There is a possibility of falling into the interior. The number of outlet holes 18c is not particularly limited and may be one or more.

  FIG. 10 is a schematic diagram showing the oil surface shape observed when the compressor is operated in this embodiment. Lubricating oil present in the crankshaft 8 is subjected to centrifugal force in the outer circumferential direction of the crankshaft 8 by the rotation of the rotating member 18. Therefore, the oil level near the outer periphery of the crankshaft 8 is higher than the central oil level that is the rotation axis of the crankshaft 8. When the lower end 20d of the second oil supply path is below the lower end of the rotating member 18 constituting a part of the centrifugal pump, the lubricating oil at the lower part of the crankshaft 8 preferentially enters the second oil supply path. As a result, the amount of lubricating oil entering the rotating member 18 decreases, and the amount of oil supplied to the centrifugal pump decreases. However, according to the present embodiment, the lower end 20 d of the second oil supply path is located above the lower end of the rotating member 18. Therefore, the lubricating oil sufficiently enters both the viscous pump and the centrifugal pump, so that the lubricating oil can be sufficiently supplied.

  Further, if the crankshaft 8 rotates during operation of the compressor, the refrigerant dissolved in the lubricating oil may be discharged as a gas, possibly blocking the lubricating oil path. When the refrigerant gas blocks the lubricating oil path, the amount of oil supply decreases. However, according to this embodiment, the gas vent hole 18b is provided in the large-diameter cylindrical cavity 30a on the side surface of the rotating member 18. The lower end of the gas vent hole 18b is located above the upper end of the stationary member 20, preferably located above the upper end of the outlet hole 18c, and more preferably located near the upper end of the large-diameter cylindrical cavity 30a. . With this structure, for example, the refrigerant gas generated in the viscous pump with the rotation of the crankshaft 8 rises inside the crankshaft 8, passes through the gas vent hole 18 b, and escapes from the gas vent path 8 g inside the crankshaft 8 to the sealed space. . Furthermore, when the lower end of the gas vent hole 18b is located above the outlet hole 18c, the gas refrigerant flowing from the third oil supply path to the large-diameter cylindrical cavity 30a can be efficiently sent to the gas vent path 8g. Therefore, it becomes difficult for the refrigerant gas to block the lubricating oil path. Thereby, the stable amount of oil supply can be ensured.

[Second Embodiment]
Next, the structure of the hermetic compressor according to the second embodiment will be described with reference to FIGS. 11 and 12. FIG. 11 is an enlarged cross-sectional view of the main part schematically showing the oil supply means according to the present embodiment, and FIG. 12 is a cross-sectional view of the stationary member 20.

  This embodiment is the same as the first embodiment except that the first oil supply path spiral groove 20 c on the inner peripheral surface of the stationary member 20 is provided in a part above the stationary member 20. The inner diameter b at the lower position where the first oil supply path spiral groove 20c is not provided is set to be larger than the inner diameter a at the upper position where the first oil supply path spiral groove 20c is provided. Therefore, compared with 1st Embodiment, the direction of this embodiment can reduce the sliding area of the stationary member 20 and the rotation member 18, and can reduce a sliding loss.

  In this embodiment, the same effect as that of the first embodiment can be obtained. Further, the lubricating oil in the gap between the stationary member 20 and the rotating member 18 receives a shearing force due to the speed difference between the stationary member 20 and the rotating member 18, and follows the first oil supply path spiral groove 20c on the inner peripheral surface of the stationary member. Try to rise upward. As a result, the lubricating oil that has risen in the radial gap (second oil supply path) between the outer peripheral surface of the stationary member 20 and the inner peripheral surface of the crankshaft 8 is moved in the radial direction between the inner peripheral surface of the stationary member 20 and the outer peripheral surface of the rotating member 18. It is possible to prevent a downward drop from the gap (first oil supply path). Therefore, a sufficient amount of oil can be ensured even in the low speed range. Also in the present embodiment, by arranging the viscous pump and the centrifugal pump in parallel, the compressor equipped with the inverter can sufficiently supply oil at any operation speed, and the compressor performance can be improved.

[Third Embodiment]
Next, the structure of the hermetic compressor according to the third embodiment will be described with reference to FIG. In this embodiment, the lower end of the crankshaft 8 is located above the upper end of the convex portion 20a of the wire 21 that is the rotation suppressing means, and a part of the second oil supply path spiral groove 20b of the stationary member 20 is exposed. Except for, the configuration is the same as that of the first or second embodiment. As a result, it is possible to prevent the wire 21 and the lower end of the crankshaft 8 from colliding with each other due to vibration during operation of the compressor, leading to noise reduction and improved reliability. Also in this embodiment, the same effects as those of the first or second embodiment can be obtained. Further, by arranging the viscous pump and the centrifugal pump in parallel, the compressor mounted with the inverter can sufficiently supply oil at any operating speed, and the compressor performance can be improved.

[Fourth Embodiment]
Next, the structure of the hermetic compressor according to the fourth embodiment will be described with reference to FIG. The present embodiment is the first to third except that the first oil supply path spiral groove 20c ′ is provided on the outer peripheral surface of the rotating member 18 instead of the first oil supply path spiral groove 20c on the inner peripheral surface of the stationary member 20. The configuration is the same as that of the embodiment. Thereby, it is easier to process than the installation of a spiral groove on the inner peripheral surface of the stationary member 20, and the cost can be reduced. In this embodiment, the same effects as those of the first to third embodiments can be obtained. Further, by arranging the viscous pump and the centrifugal pump in parallel, the compressor mounted with the inverter can sufficiently supply oil at any operating speed, and the compressor performance can be improved.

[Fifth Embodiment]
Next, the structure of the hermetic compressor according to the fifth embodiment will be described with reference to FIG. The present embodiment is the first to fourth except that the second oil supply path spiral groove 20b ′ is provided on the inner peripheral surface of the rotating member 18 instead of the second oil supply path spiral groove 20b on the outer peripheral surface of the stationary member 20. The configuration is the same as that of the embodiment. In this embodiment, the same effects as those of the first to third embodiments can be obtained. Further, by arranging the viscous pump and the centrifugal pump in parallel, the compressor mounted with the inverter can sufficiently supply oil at any operating speed, and the compressor performance can be improved.

[refrigerator]
FIG. 16 is a longitudinal sectional view of a refrigerator equipped with any of the hermetic compressors according to the first to fifth embodiments. In FIG. 16, the hermetic compressor 50 of this embodiment includes a cooler 66 and is mounted on a refrigerator 60 using a natural refrigerant R600a having a small warming coefficient, and includes a refrigerator room 62, an upper freezer room 63, and a lower freezer room. 64 and the vegetable compartment 65 are cooled by operating a refrigeration cycle (not shown) by driving the hermetic compressor 50.

  By using the compressors of the above-described embodiments described in detail above, the viscous pump and the centrifugal pump can be arranged in parallel, so that sufficient oil can be supplied even at an operating speed at which the oil supply of the viscous pump may be insufficient. , The compressor performance can be improved.

  Further, in both the low speed operation and the high speed operation, the lubricating oil can be efficiently and stably pumped, and sufficient oil can be supplied to the sliding portion to improve the compressor efficiency. Moreover, the hermetic compressor of the present invention can be applied not only to a refrigerator but also to a room air conditioner, a refrigerator, and the like for refrigeration and air conditioning applications, and the efficiency of these devices can be greatly improved.

  DESCRIPTION OF SYMBOLS 1 ... Sealed container, 2 ... Electric element, 2a ... Stator, 2b ... Rotor, 3 ... Compression element, 4 ... Lubricating oil, 4a ... Lubricating oil storage part, 5 ... Cylinder block, 5a ... Cylinder, 5b ... Frame part, 5c ... Radial bearing, 6 ... Connecting rod, 7 ... Piston, 8 ... Crankshaft, 8a ... Eccentric shaft, 8b ... Communication hole, 8c ... Spiral groove on the outer surface of the crank, 8d ... Communication hole to the pin part, 8g ... Inside the crankshaft Degassing path, 9 ... balance weight, 10 ... cylinder head, 11 ... head cover, 11a ... discharge chamber, 11b ... suction silencer mounting port, 11c ... bolt hole, 12 ... compression working chamber, 13 ... clamping bolt, 14 ... suction Pipe, 15 ... Suction silencer, 16 ... Discharge silencer, 17 ... Discharge pipe, 18 ... Rotating member, 18a ... Lower hole (lower communication part), 18b ... Gas vent hole, 18c ... Outlet hole DESCRIPTION OF SYMBOLS 19 ... Ball joint, 20 ... Static member, 20a ... Convex part, 20b, 20b '... Second oil supply path spiral groove, 20c, 20c' ... First oil supply path spiral groove, 20d ... Static member lower end, 21 ... Wire (rotation Suppression means), 22 ... discharge pipe, 30 ... cylindrical cavity, 30a ... large diameter cylindrical cavity, 30b ... small diameter cylindrical cavity, 50 ... hermetic compressor, 60 ... refrigerator, 61 ... refrigerator body, 62 ... refrigerator compartment 63 ... Upper freezer, 64 ... Lower freezer, 65 ... Vegetable room, 66 ... Cooler

Claims (5)

A lubricating oil reservoir that stores the lubricating oil below the sealed container;
A rotatable crankshaft having a cylindrical cavity;
A rotating member provided at least in part in the cylindrical cavity, and rotatable on the same rotating shaft as the crankshaft;
A hermetic compressor comprising oil supply means having a stationary member provided between the crankshaft and the rotating member with a gap between the crankshaft and the rotating member,
The rotating member is hollow inside, and has a lower communication part at the lower part for supplying the lubricating oil to the inside of the rotating member,
The refueling means is
A first oiling path including a first oiling path spiral groove in a gap between the stationary member and the rotating member;
A second oil supply path including a second oil supply path spiral groove in a gap between the stationary member and the crankshaft;
Have a, and a third oil supply path including the inside of the rotary member and the lower communicating portion of said rotary member,
An outlet hole that communicates the inside of the rotating member and the cylindrical cavity is provided in the rotating member and the outlet hole has a height that is equal to or higher than the height of the upper end of the stationary member, or
A side surface of said rotary member, hermetic compressors, characterized by have a gas vent hole. An outlet hole for communicating the inside of the rotating member and the cylindrical cavity is provided in the rotating member,
2. The hermetic compressor according to claim 1, wherein a lower end of the outlet hole has a height equal to or higher than a height of the upper end of the stationary member. An outlet hole for communicating the inside of the rotating member and the cylindrical cavity is provided in the rotating member, and the outlet hole has a height equal to or higher than the height of the upper end of the stationary member, and
The hermetic compressor according to claim 1, wherein a gas vent hole is provided on a side surface of the rotating member. An outlet hole for communicating the inside of the rotating member and the cylindrical cavity is provided in the rotating member,
The cylindrical cavity includes a small-diameter cylindrical cavity and a large-diameter cylindrical cavity below the small-diameter cylindrical cavity having the stationary member,
The hermetic compressor according to claim 3 , wherein a lower end of the gas vent hole is located above an upper end of the outlet hole and in the vicinity of an upper end of the large-diameter cylindrical cavity.   An apparatus comprising the hermetic compressor according to any one of claims 1 to 4.