JP6611648B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor that prevents a shaft and a bearing from being damaged by contact.

  The rotating machine is provided with a radial bearing that supports a load acting on a rotating body such as a rotating shaft. There are two types of radial bearings: rolling bearings and sliding bearings. The sliding bearing has a structure in which an oil film is formed between the rotating shaft and the bearing, and an oil film pressure is generated by the effect of the wedge to support the bearing load. Generally, oil film pressure is likely to occur when the rotational speed is high. Further, when the oil film pressure is generated, the rotating shaft and the bearing are separated by the oil film and contact can be avoided, so that the rotating shaft and the bearing are not worn or seized. In addition, the rolling bearing generally has a lower friction than the sliding bearing because the rolling elements disposed between the outer ring and the inner ring roll. However, rolling bearings have a finite life. For this reason, in a rolling bearing that has exceeded its service life, peeling occurs on the surface of the outer ring, inner ring, or rolling element, and the function as a bearing cannot be achieved. A refrigerant compressor mounted on an air conditioner cannot basically perform maintenance and replacement of parts after shipment. For this reason, in a refrigerant compressor, a slide bearing with a long life is often used as a radial bearing.

  In a refrigerant compressor mounted on an air conditioner, a low-pressure and low-temperature refrigerant gas is compressed by a compression mechanism and sent to a condenser. The load acting on the compression mechanism at that time is called a gas load. The gas load acts on the bearing via a drive shaft (rotating shaft) that transmits a driving force to the compression mechanism. Even when a gas load acts on the bearing, it is possible to operate the refrigerant compressor so that seizure and abnormal wear do not occur by forming an oil film between the drive shaft and the bearing. For this reason, in the design of the bearing in the refrigerant compressor, it is necessary to select bearing specifications and operating conditions for forming an oil film.

  The refrigerant compressor always supplies lubricating oil between the drive shaft and the bearing, and operates so as not to cause seizure and abnormal wear. Specifically, an oil reservoir for storing lubricating oil is formed in a sealed container that is an outer shell of the refrigerant compressor. The drive shaft includes an oil supply passage extending from the oil reservoir between the drive shaft and the bearing, and a positive displacement pump that pumps up the lubricating oil stored in the oil reservoir in the oil supply passage. Then, the lubricating oil stored in the oil reservoir is supplied between the drive shaft and the bearing by the above-described pump and oil supply passage. Here, the refrigerant gas which is the working fluid of the air conditioner is dissolved in the lubricating oil in the refrigerant compressor. This refrigerant gas is characterized in that the amount of dissolution varies with temperature and pressure, and is easily dissolved in the lubricating oil when the pressure is high and the temperature is low, while foaming from the lubricating oil when the pressure is low and the temperature is high. Cheap.

  In a sliding bearing often used in a refrigerant compressor, when the lubricating oil flows from the oil supply passage between the drive shaft and the bearing, the pressure of the lubricating oil decreases due to the expansion of the lubricating oil passage. Therefore, there has been a problem that the refrigerant gas is foamed from the lubricating oil, and the lubricating oil and the refrigerant gas are simultaneously supplied into the bearing.

  Therefore, conventionally, an oil supply mechanism that suppresses foaming of the refrigerant gas from the lubricating oil when the lubricating oil flows between the drive shaft and the bearing from the oil supply passage has been proposed. For example, in the scroll compressor described in Patent Document 1, an oil supply groove is formed in a range facing the slide bearing on the outer peripheral surface of the drive shaft. This oil supply groove provides resistance to the flow of lubricating oil in the bearing, and pressure is generated in the oil film in the oil supply groove. By supplying the lubricating oil to the oil supply groove where pressure is generated in the oil film, it is possible to suppress a sudden pressure drop when the lubricating oil flows from the oil supply passage between the drive shaft and the bearing. Foaming can be suppressed.

JP 7-12068 A

  In a slide bearing often used in a refrigerant compressor, the rotation center of the drive shaft is eccentric from the center of the bearing due to a gas load applied to the drive shaft. For this reason, the oil film between the drive shaft and the bearing forms a wedge shape. Here, an oil film whose cross-sectional area decreases in the rotation direction of the drive shaft is referred to as a wedge oil film, and an oil film whose cross-sectional area increases in the rotation direction of the drive shaft is referred to as a reverse wedge oil film.

  The wedge oil film is pulled by the rotation of the drive shaft, and the lubricating oil enters the narrower gap of the wedge type, so that pressure is generated in the oil film. On the other hand, the reverse wedge oil film is pulled by the rotation of the drive shaft, and the lubricating oil flows to the wider side of the wedge gap. For this reason, in the reverse wedge oil film, the pressure of the oil film is reduced, and the dissolved refrigerant gas is foamed from the oil film. The refrigerant gas foamed in the slide bearing is pulled by the rotation of the drive shaft and spreads to the wedge oil film side. As a result, the lubricating oil in the slide bearing is drained, the inside of the slide bearing causes a state of running out of the oil film, and there is a concern that the drive shaft and the slide bearing come into contact with each other and are damaged.

  Here, the scroll compressor described in Patent Document 1 can suppress the foaming of the refrigerant gas from the lubricating oil when the lubricating oil flows into the slide bearing from the oil supply passage by the oil supply groove. However, the scroll compressor described in Patent Document 1 does not take measures against the refrigerant gas foamed from the reverse wedge oil film. For this reason, the scroll compressor described in Patent Document 1 still has a problem that the drive shaft and the bearing are contacted and damaged by the refrigerant gas foamed from the lubricating oil.

  The present invention is for solving the above-described problems, and provides a scroll compressor that can prevent the drive shaft and the slide bearing from being contacted and damaged by the refrigerant gas foamed from the lubricating oil. With the goal.

A scroll compressor according to the present invention includes a compression mechanism having a fixed scroll and a swing scroll that form a compression chamber between the spiral teeth by combining the spiral teeth, a motor, the motor, and the swing scroll. And a drive shaft that transmits the driving force of the electric motor to the orbiting scroll, a radial bearing and a thrust bearing that rotatably support the drive shaft, and the compression mechanism, the electric motor, and the drive shaft. An oil reservoir in which an oil reservoir in which lubricating oil is stored is formed, and the drive shaft has an oil supply passage from the oil reservoir to the drive shaft and the radial bearing, A scroll compressor in which the lubricating oil supplied from the oil supply passage between the drive shaft and the radial bearing is supplied between the drive shaft and the thrust bearing, The radial bearing is a sliding bearing, and the outer peripheral surface position of the drive shaft where the oil film between the drive shaft and the radial bearing is thickest is defined as a 0 ° position, and the outer peripheral surface of the drive shaft is defined from the 0 ° position. Is observed in the rotational direction of the drive shaft, the rotation of the drive shaft is in the range of 180 ° to 360 ° from the thrust bearing side toward the opposite side of the thrust bearing. At least one first groove inclined in the direction opposite to the direction is formed.
Furthermore, the scroll compressor according to the present invention includes any of the following configurations in addition to the above configuration.
In the scroll compressor according to the present invention, the oil supply passage has an opening at a position where the first groove is not formed between 180 ° and 360 ° in a range facing the radial bearing. ing.
In the scroll compressor according to the present invention, an end of the first groove on the thrust bearing side is closer to the thrust bearing than an end on the thrust bearing side in a facing range of the drive shaft and the radial bearing. Is on the opposite side.
In the scroll compressor according to the present invention, the oil supply passage has an opening between 180 ° and 360 ° in a range facing the radial bearing, and the rotation of the drive shaft is more than the opening. At least one of the first grooves is disposed at a position on the front side in the direction.
In the scroll compressor according to the present invention, the rotation direction of the drive shaft from the opposite side of the thrust bearing to the thrust bearing side is between 0 ° and 180 ° in a range facing the radial bearing. A second groove inclined in the opposite direction is formed.

  On the outer peripheral surface of the drive shaft of the scroll compressor according to the present invention, the rotation direction of the drive shaft from the thrust bearing side to the opposite side of the thrust bearing is between 180 ° and 360 ° in the range facing the radial bearing. Is formed with a first groove inclined in the opposite direction. For this reason, in the scroll compressor according to the present invention, when the refrigerant gas is generated from the lubricating oil in the radial bearing which is a slide bearing, the refrigerant gas can be discharged to the opposite side of the thrust bearing by the first groove. . For this reason, in the scroll compressor which concerns on this invention, it can prevent that a drive shaft and a radial bearing contact and are damaged by the refrigerant gas foamed from lubricating oil.

It is a longitudinal cross-sectional view which shows typically the structure of the scroll compressor 100 which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows typically the subbearing 11 vicinity of the scroll compressor 100 which concerns on Embodiment 1 of this invention. In scroll compressor 100 concerning Embodiment 1 of the present invention, it is an explanatory view for explaining a state of an oil film formed between radial bearing 11a of sub bearing 11, and main shaft part 6a of drive shaft 6. In scroll compressor 100 concerning Embodiment 1 of the present invention, it is a perspective view showing main axis part 6a and radial bearing 11a of auxiliary bearing 11. It is an expanded view of the outer peripheral surface of the main-shaft part 6a in the scroll compressor 100 which concerns on Embodiment 1 of this invention. It is a perspective view which shows another example of the groove | channel 20 in the scroll compressor 100 which concerns on Embodiment 1 of this invention. It is a perspective view which shows another example of the groove | channel 20 in the scroll compressor 100 which concerns on Embodiment 1 of this invention. In the scroll compressor 100 which concerns on Embodiment 2 of this invention, it is the perspective view which showed the main-shaft part 6a and the radial bearing 11a of the subbearing 11. FIG. It is an expanded view of the outer peripheral surface of the main-shaft part 6a in the scroll compressor 100 which concerns on Embodiment 2 of this invention. It is a perspective view which shows another example of the groove | channel 22 in the scroll compressor 100 which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view schematically showing a configuration of a scroll compressor 100 according to Embodiment 1 of the present invention. FIG. 2 is a longitudinal sectional view schematically showing the vicinity of the auxiliary bearing 11 of the scroll compressor 100.
In FIG. 1, hatching is omitted in order to make it easy to see the lead lines indicating the respective components. In FIG. 2, the grooves 20 formed on the outer peripheral surface of the drive shaft 6 are not shown in order to make the flow path of the lubricating oil easier to see. Details of the groove 20 will be described with reference to FIGS.

  A scroll compressor 100 according to the first embodiment includes a compression mechanism 101, an electric motor 10, a drive shaft 6, and a sealed container 13 for storing them.

  The compression mechanism 101 includes a fixed scroll 1 and a swing scroll 2. The fixed scroll 1 has a base plate and spiral teeth provided on the lower surface of the base plate. The orbiting scroll 2 has a base plate and spiral teeth provided on the top surface of the base plate. Further, the base plate of the orbiting scroll 2 is provided with a boss portion 2a into which an eccentric shaft portion 6b of the drive shaft 6 described later is inserted on the surface opposite to the surface on which the spiral teeth are formed. A compression chamber 5 is formed between the spiral teeth by combining the spiral teeth of the fixed scroll 1 and the spiral teeth of the orbiting scroll 2. The suction port 3 for sucking the refrigerant into the compression chamber 5 is formed on the outer peripheral side of the compression chamber 5. A discharge port 4 that discharges the refrigerant compressed in the compression chamber 5 is formed at the center of the fixed scroll 1. The compression mechanism 101 is disposed in the upper part in the sealed container 13.

  The electric motor 10 is disposed in the sealed container 13 between the upper housing 8a and the lower housing 8b. The electric motor 10 includes a rotor 10a and a stator 10b. The stator 10 b has a hollow and substantially cylindrical shape, and is fixed to the sealed container 13. The rotor 10a has a hollow, substantially cylindrical shape, and is disposed on the inner peripheral side of the stator 10b via a predetermined gap.

  The drive shaft 6 connects the electric motor 10 and the orbiting scroll 2 and transmits the driving force of the electric motor 10 to the orbiting scroll 2. The drive shaft 6 includes a main shaft portion 6a and an eccentric shaft portion 6b. The main shaft portion 6a is fixed to the rotor 10a of the electric motor 10, and rotates together with the rotor 10a. The upper portion of the main shaft portion 6a is rotatably supported by a main bearing 19 provided in the upper housing 8a, and the lower portion is rotatably supported by a sub bearing 11 provided in the lower housing 8b. The eccentric shaft portion 6b is provided at the upper end portion of the main shaft portion 6a. The central axis of the eccentric shaft portion 6b is eccentric with respect to the central axis (rotary shaft) of the main shaft portion 6a. The eccentric shaft portion 6b is rotatably inserted into the rocking bearing 17 press-fitted into the boss portion 2a of the rocking scroll 2. The drive shaft 6 is provided with a balancer 6c above the main shaft portion 6a.

  The upper housing 8a is fixed to the inner surface of the side wall of the sealed container 13, and a main bearing 19 that rotatably supports the main shaft portion 6a of the drive shaft 6 is provided. A fixed scroll 1 is fixed to the upper portion of the upper housing 8a. A thrust bearing 18 is provided on the upper portion of the upper housing 8a. The thrust bearing 18 supports the oscillating scroll 2 slidably from below. Further, an Oldham coupling 12 that prevents the swing scroll 2 from rotating is also provided on the upper portion of the upper housing 8a.

  The lower housing 8b is fixed to the inner surface of the side wall of the hermetic container 13, and a sub-bearing 11 that rotatably supports the main shaft portion 6a of the drive shaft 6 is provided. As shown in FIGS. 1 and 2, the auxiliary bearing 11 includes a radial bearing 11a that supports the radial load of the main shaft portion 6a, and a thrust bearing 11b that supports the thrust load of the main shaft portion 6a. Of these bearings, at least the radial bearing 11a is a slide bearing.

  The airtight container 13 that houses the above-described components is provided with a refrigerant suction pipe 15 for sucking refrigerant into the scroll compressor 100, for example, on a side wall. Moreover, the airtight container 13 is provided with the refrigerant | coolant discharge pipe 16 for discharging the refrigerant | coolant compressed with the scroll compressor 100 outside, for example in the upper part. The scroll compressor 100 according to the first embodiment has a configuration in which the refrigerant sucked from the refrigerant suction pipe 15 is temporarily stored in the sealed container 13 and then compressed by the compression mechanism 101 and directly discharged. ing. For this reason, the refrigerant suction pipe 15 is connected to the sealed container 13 so as to communicate with the internal space of the sealed container 13. The refrigerant discharge pipe 16 is connected to the discharge port 4 of the compression mechanism 101.

  An oil sump 14 is formed at the bottom of the sealed container 13 to store lubricating oil that lubricates sliding parts such as bearings. The lubricating oil stored in the oil reservoir 14 is supplied to the radial bearing 11 a of the rocking bearing 17, the main bearing 19, and the auxiliary bearing 11 by the oil supply mechanism 7. The oil supply mechanism 7 includes, for example, a positive displacement pump 7 b attached to the lower end portion of the main shaft portion 6 a of the drive shaft 6, and an oil supply passage provided in the drive shaft 6. That is, the pump 7 b immersed in the lubricating oil in the oil reservoir 14 together with the drive shaft 6 rotates, so that the pump 7 b pumps up the lubricating oil stored in the oil reservoir 14, and the rocking bearing 17 and the main bearing 19. In addition, the lubricating oil is supplied to the radial bearing 11a of the auxiliary bearing 11.

  As shown in FIG. 2, the oil supply passage is formed by an oil supply hole 7a and an oil supply inlet 7c. The oil supply hole 7a is a through hole formed so as to penetrate in the axial direction of the main shaft portion 6a. The oil supply inlet 7c is a through hole having one end opened to the oil supply hole 7a and the other end opened between the drive shaft 6 and each bearing. For example, the oil supply inlet 7 c is formed so as to be orthogonal to the axial direction of the radial bearing 11 a of the rocking bearing 17, the main bearing 19, and the auxiliary bearing 11. In FIG. 2, an oil supply inlet 7 c that opens between the drive shaft 6 and the radial bearing 11 a of the auxiliary bearing 11 is shown as an example of the oil supply inlet 7 c. Here, the oil supply inlet 7c and the oil supply hole 7a opened between the drive shaft 6 and the radial bearing 11a of the auxiliary bearing 11 are the “oil supply passage from the oil reservoir to the drive shaft and the radial bearing” according to the present invention. Equivalent to.

The scroll compressor 100 configured as described above operates as follows as one of the configurations of the refrigeration cycle circuit.
When the drive shaft 6 rotates together with the rotor 10 a of the electric motor 10, the orbiting scroll 2 performs a revolving motion while being prevented from rotating by the Oldham joint 12. As a result, the compression chamber 5 formed by the combination of the spiral teeth of the orbiting scroll 2 and the fixed scroll 1 moves toward the center while gradually reducing the volume. For this reason, the refrigerant sucked into the compression chamber 5 from the suction port 3 gradually increases its pressure, and is sent to the condenser of the refrigeration cycle circuit through the discharge port 4 and the refrigerant discharge pipe 16.

  Since the refrigerant in the sealed container 13 is discharged to the outside in this way, the inside of the sealed container 13 has a negative pressure. Therefore, the refrigerant is sucked into the sealed container 13 from the outside of the sealed container 13 through the refrigerant suction pipe 15. The refrigerant is sucked into the compression chamber 5 from the suction port 3 after cooling the electric motor 10.

  Further, as the drive shaft 6 rotates, the lubricating oil in the oil reservoir 14 is pumped up to the oil supply hole 7 a by the pump 7 b of the oil supply mechanism 7. The lubricating oil pumped up into the oil supply hole 7 a is supplied from the oil supply inlet 7 c to the drive shaft 6 between the radial bearing 11 a of the rocking bearing 17, the main bearing 19, and the auxiliary bearing 11. Lubricating oil supplied between the rocking bearing 17 and the eccentric shaft portion 6b of the drive shaft 6 lubricates the space between them, and then is supplied to the thrust bearing 18 and the Oldham joint 12 to lubricate the sliding portions. The lubricating oil supplied to the Oldham joint 12 is returned to the oil sump 14 through the oil return hole 9.

  Lubricating oil supplied between the main bearing 19 and the main shaft portion 6 a of the drive shaft 6 lubricates the space, then flows out from the lower end side of the main bearing 19 and returns to the oil reservoir 14. Further, the lubricating oil supplied between the radial bearing 11a of the auxiliary bearing 11 and the main shaft portion 6a of the drive shaft 6 is lubricated between the two, and then a part thereof flows into the lower thrust bearing 11b. This lubricating oil covers the lubrication of the thrust bearing 11b and returns to the lower oil sump 14 from the gap between the thrust bearing 11b and the main shaft portion 6a. Here, the lubricating oil supplied between the radial bearing 11a of the auxiliary bearing 11 and the main shaft portion 6a of the drive shaft 6 forms the following oil film therebetween.

  FIG. 3 is an explanatory diagram for explaining a state of an oil film formed between the radial bearing 11a of the auxiliary bearing 11 and the main shaft portion 6a of the drive shaft 6 in the scroll compressor 100 according to the first embodiment of the present invention. FIG. FIG. 3 shows the radial bearing 11a of the auxiliary bearing 11 and the main shaft portion 6a of the drive shaft 6 observed in a cross section perpendicular to the central axis (rotary shaft) of the main shaft portion 6a of the drive shaft 6. In addition, the white arrow shown in FIG. 3 has shown the rotation direction of the main-shaft part 6a (namely, drive shaft 6).

  In the scroll compressor 100, a load is applied to the swing scroll 2 by the refrigerant gas compressed in the compression chamber 5. As indicated by W in FIG. 3, this load acts on the radial bearing 11a via the main shaft portion 6a. In the case of the scroll compressor 100, the direction of the load W is rotated by the eccentric motion of the orbiting scroll 2, and the load acts in the eccentric direction of the eccentric shaft in the radial bearing 11a. That is, in the case of the scroll compressor 100, since the load W rotates in synchronization with the main shaft portion 6a, the angular position of the load W acting on the main shaft portion 6a does not change. When the load W acts on the main shaft portion 6a, the shaft center (rotation center) of the main shaft portion 6a is decentered from the center of the radial bearing 11a by the rotation of the main shaft portion 6a and the action of the load W. For this reason, the oil film between the main shaft portion 6a and the radial bearing 11a forms a wedge shape. Here, the oil film whose cross-sectional area decreases in the rotation direction of the main shaft portion 6a is referred to as a wedge oil film 21a, and the oil film whose cross-sectional area increases in the rotation direction of the main shaft portion 6a is referred to as a reverse wedge oil film 21b.

  Specifically, the position of the outer peripheral surface of the main shaft portion 6a where the oil film between the main shaft portion 6a and the radial bearing 11a is thickest is defined as the 0 ° position. Further, it is defined that the value of the angle increases in the rotation direction of the main shaft portion 6a. In this case, the outer peripheral surface position where the oil film between the main shaft portion 6a and the radial bearing 11a is the thinnest is a position of 180 °. Further, in the range of 0 ° to 180 °, the oil film 21a is a wedge oil film 21a in which the flow area of the oil film becomes narrower in a wedge shape. In the range of 180 ° to 360 °, the flow area of the oil film becomes a reverse wedge oil film 21b spreading in a reverse wedge shape.

  In the wedge oil film 21a, since the flow path is gradually narrowed, the lubricating oil enters the narrower one of the wedge-shaped gaps by being pulled by the rotation of the main shaft portion 6a. For this reason, the oil film pressure 21c is generated in the oil film, and the load W acting on the main shaft portion 6a is supported by the oil film pressure 21c. On the other hand, in the reverse wedge oil film 21b, since the flow path gradually increases, the lubricating oil flows by being pulled by the rotation of the drive shaft 6 to the wider side of the wedge gap. For this reason, in the reverse wedge oil film 21b, the oil film pressure 21c rapidly decreases, and the oil film pressure 21c is not generated in the majority of the reverse wedge oil film 21b.

  Here, the refrigerant gas in the airtight container 13 is dissolved in the lubricating oil in the oil reservoir 14 in accordance with the temperature and pressure. For this reason, in the reverse wedge oil film 21b, the pressure of the oil film decreases, and the dissolved refrigerant gas foams from the oil film. The refrigerant gas foamed in the radial bearing 11a is pulled by the rotation of the main shaft portion 6a and spreads to the wedge oil film 21a side. As a result, the lubricating oil in the radial bearing 11a is drained, and the inside of the radial bearing 11a causes a state such as running out of the oil film, and there is a concern that the main shaft portion 6a and the radial bearing 11a come into contact with each other and are damaged.

  Therefore, in the scroll compressor 100 according to the first embodiment, the outer peripheral surface of the main shaft portion 6a in the range facing the radial bearing 11a is configured as follows.

FIG. 4 is a perspective view showing the main shaft portion 6a and the radial bearing 11a of the auxiliary bearing 11 in the scroll compressor 100 according to Embodiment 1 of the present invention. FIG. 5 is a development view of the outer peripheral surface of the main shaft portion 6 a in the scroll compressor 100.
In FIG. 4, in order to facilitate understanding of the configuration of the outer peripheral surface of the main shaft portion 6a, a part of the radial bearing 11a of the auxiliary bearing 11 is shown as a cross section. Moreover, the arc-shaped arrow shown in FIG. 4 has shown the rotation direction of the main-shaft part 6a, and the white arrow shown in FIG. 4 has shown the flow of the lubricating oil.

When the outer peripheral surface of the main shaft portion 6a is observed in the rotational direction of the main shaft portion 6a, the main shaft portion 6a has a range of 180 ° to 360 ° from the lower portion to the upper portion in the range facing the radial bearing 11a. At least one groove 20 inclined in the direction opposite to the rotation direction of 6a is formed. In other words, the groove 20 is inclined in the direction opposite to the rotation direction of the main shaft portion 6a from the thrust bearing 11b side of the auxiliary bearing 11 toward the opposite side of the thrust bearing 11b. In the groove 20, for example, the upper portion is always at an angle where the circumferential position is smaller than the lower portion. Further, the position of the lower end portion (end portion on the thrust bearing 11b side) of the groove 20 is substantially the same position as the lower end portion (end portion on the thrust bearing 11b side) of the radial bearing 11a. Further, the position of the upper end of the groove 20 (the end opposite to the thrust bearing 11b side) is substantially the same position as the upper end of the radial bearing 11a (the end opposite to the thrust bearing 11b). Yes.
Here, the groove 20 corresponds to the first groove of the present invention.

  That is, the groove 20 is formed on the reverse wedge oil film 21b side. Further, since the groove 20 is a resistance component with respect to the rotation of the main shaft portion 6a, the rotation of the main shaft portion 6a causes the lubricating oil to be directed upward (on the opposite side to the thrust bearing 11b side) in the groove 20. A pumping effect is obtained. Further, the groove 20 is arranged from the upper part to the lower part of the radial bearing 11a. For this reason, the groove 20 can discharge the refrigerant gas generated in the reverse wedge oil film 21b in the radial bearing 11a to the upper side of the radial bearing 11a. Therefore, the scroll compressor 100 according to the first embodiment can prevent the refrigerant gas foamed by the reverse wedge oil film 21b from being pulled by the rotation of the main shaft portion 6a and spreading to the wedge oil film 21a side. That is, it is possible to prevent the lubricating oil in the radial bearing 11a from being discharged and to cause a state such as the oil film running out, and it is possible to prevent the main shaft portion 6a and the radial bearing 11a from coming into contact with each other and being damaged. In addition, the refrigerant gas discharge action of the groove 20 can prevent the refrigerant gas from flowing into the thrust bearing 11b. The groove 20 does not have to be a straight line as long as the groove 20 does not have an opposite inclination when moving from the lower part to the upper part.

  As described above, in the scroll compressor 100 according to the first embodiment, when the refrigerant gas is generated from the lubricating oil in the radial bearing 11a, the refrigerant gas can be discharged to the outside of the radial bearing 11a by the groove 20. For this reason, the scroll compressor 100 according to the first embodiment can prevent the main shaft portion 6a and the radial bearing 11a from being contacted and damaged by the refrigerant gas foamed from the lubricating oil.

  In the scroll compressor 100 according to the first embodiment, the refrigerant gas generated in the radial bearing 11a is discharged to the side opposite to the thrust bearing 11b side. Therefore, in the scroll compressor 100 according to the first embodiment, the refrigerant gas does not flow into the thrust bearing 11b, and the lubricant is sufficiently supplied also in the thrust bearing 11b, so that the stable operation of the scroll compressor 100 is possible. It becomes.

  The refrigerant gas discharge effect described above can be obtained if at least one groove 20 is provided, but it is preferable to have a plurality of grooves 20. By discharging the refrigerant gas through the plurality of grooves 20, the above-described refrigerant gas discharge effect can be further improved.

  The formation position of the oil supply inlet 7c is not particularly limited, but is preferably formed in a range of 180 ° to 360 °. In other words, the oil supply passage preferably has an opening between 180 ° and 360 ° in a range facing the radial bearing 11a. When the lubricating oil flows from the oil supply inlet 7c between the main shaft portion 6a and the radial bearing 11a, the pressure of the lubricating oil decreases due to the expansion of the lubricating oil flow path, and the refrigerant gas foams from the lubricating oil. At this time, the refrigerant gas can also be discharged by the groove 20 by forming the oil supply inlet 7c in a range of 180 ° to 360 °. For this reason, when forming the oil supply inlet 7c in the said position, it is preferable that the at least 1 groove | channel 20 is arrange | positioned in the position which becomes the front side of the rotation direction of the main-shaft part 6a rather than the oil supply inlet 7c.

  Moreover, the position of the upper end part and lower end part of the groove | channel 20 will not be limited to said position, if refrigerant gas can be discharged | emitted above the radial bearing 11a. For example, the groove 20 may be formed as follows.

  6 and 7 are perspective views showing another example of the groove 20 in the scroll compressor 100 according to Embodiment 1 of the present invention. 6 and 7 are views of the main shaft portion 6a and the radial bearing 11a as in FIG.

  For example, as shown in FIG. 6, the upper end portion of the groove 20 may extend upward from the upper end portion of the radial bearing 11a. In other words, the end of the groove 20 opposite to the thrust bearing 11b may extend to a range where the main shaft portion 6a and the radial bearing 11a are not opposed to each other. By forming the groove 20 in this way, the refrigerant gas can be discharged more smoothly from the upper part of the radial bearing 11a.

  For example, as shown in FIG. 7, the lower end part of the groove | channel 20 may be located above the lower end part of the radial bearing 11a. In other words, the end on the thrust bearing 11b side in the groove 20 may be located on the opposite side of the thrust bearing 11b from the end on the thrust bearing 11b side in the opposing range of the main shaft portion 6a and the radial bearing 11a. Good. By configuring the groove 20 in this way, it is possible to further prevent the refrigerant gas from flowing into the thrust bearing 11b.

Embodiment 2. FIG.
In the range facing the radial bearing 11a in the main shaft portion 6a, the following groove 22 may be formed between 0 ° and 180 °. In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 8 is a perspective view showing the main shaft portion 6a and the radial bearing 11a of the auxiliary bearing 11 in the scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 9 is a developed view of the outer peripheral surface of the main shaft portion 6 a in the scroll compressor 100.
In FIG. 8, a part of the radial bearing 11a of the auxiliary bearing 11 is shown as a cross section in order to facilitate understanding of the configuration of the outer peripheral surface of the main shaft portion 6a. Moreover, the arc-shaped arrow shown in FIG. 8 has shown the rotation direction of the main-shaft part 6a, and the white arrow shown in FIG. 8 has shown the flow of lubricating oil.

At least one groove 22 inclined in the direction opposite to the rotation direction of the main shaft portion 6a from the upper portion to the lower portion is formed in the range of the main shaft portion 6a facing the radial bearing 11a from 0 ° to 180 °. Has been. In other words, the groove 22 is inclined in the direction opposite to the rotation direction of the main shaft portion 6a from the opposite side of the thrust bearing 11b of the auxiliary bearing 11 toward the thrust bearing 11b side. For example, the groove 22 is always at an angle such that the upper portion always has a larger circumferential position than the lower portion. Further, the position of the lower end portion (end portion on the thrust bearing 11b side) of the groove 22 is substantially the same position as the lower end portion (end portion on the thrust bearing 11b side) of the radial bearing 11a. Further, the position of the upper end of the groove 22 (end opposite to the thrust bearing 11b side) is substantially the same position as the upper end of the radial bearing 11a (end opposite to the thrust bearing 11b). Yes.
Here, the groove 22 corresponds to the second groove of the present invention.

  That is, the groove 22 is formed on the wedge oil film 21a side. In addition, since the groove 22 is a resistance component with respect to the rotation of the main shaft portion 6a, the pump effect of flowing downward in the groove 22 is obtained by the rotation of the main shaft portion 6a. As described above, a part of the lubricating oil after being used for lubrication in the radial bearing 11a is supplied to the lower thrust bearing 11b. By providing the groove 22 according to the second embodiment, lubricating oil can be preferentially supplied to the thrust bearing 11b.

  Further, by actively feeding the lubricating oil into the thrust bearing 11b through the groove 22, the pressure of the lubricating oil in the thrust bearing 11b can be increased, and the foaming of the refrigerant in the thrust bearing 11b can be suppressed. For this reason, the thrust bearing 11b is not in a state of running out of oil. Further, since the lubricating oil is positively fed, the lubricating oil is sufficiently present in the thrust bearing 11b, and the operation can be performed with low loss.

  The positions of the upper end portion and the lower end portion of the groove 22 are not limited to the above positions as long as the amount of lubricating oil supplied to the thrust bearing 11b can be increased. For example, the groove 22 may be formed as follows.

FIG. 10 is a perspective view showing another example of the groove 22 in the scroll compressor 100 according to Embodiment 2 of the present invention. FIG. 10 shows the main shaft portion 6a and the radial bearing 11a observed as in FIG.
For example, as shown in FIG. 10, the upper end portion of the groove 22 may be positioned below the upper end portion of the radial bearing 11a. In other words, the end of the groove 22 on the side opposite to the thrust bearing 11b is located closer to the thrust bearing 11b than the end on the opposite side of the thrust bearing 11b in the opposing range of the main shaft portion 6a and the radial bearing 11a. May be. Lubricating oil discharged above the radial bearing 11a can be reduced, and the amount of lubricating oil supplied to the thrust bearing 11b can be further increased. In consideration of positively supplying the lubricating oil to the thrust bearing 11b, it is preferable that the lower end portion of the groove 22 extends to the lower end portion of the radial bearing 11a.

  As described above, in the first embodiment and the second embodiment, the present invention has been described by using the vertical scroll compressor 100 arranged so that the axis of the drive shaft 6 is in the vertical direction. It will be easily understood that the present invention can be implemented not only in this case but also in a horizontal type scroll compressor in which the axis of the drive shaft is arranged in the horizontal direction.

  DESCRIPTION OF SYMBOLS 1 Fixed scroll, 2 Swing scroll, 2a Boss part, 3 Suction inlet, 4 Discharge port, 5 Compression chamber, 6 Drive shaft, 6a Main shaft part, 6b Eccentric shaft part, 6c Balancer, 7 Oil supply mechanism, 7a Oil supply hole, 7b Pump, 7c Oil supply inlet, 8a Upper housing, 8b Lower housing, 9 Oil return hole, 10 Electric motor, 10a Rotor, 10b Stator, 11 Sub bearing, 11a Radial bearing, 11b Thrust bearing, 12 Oldham joint, 13 Sealed container, 14 Oil Pool, 15 Refrigerant suction pipe, 16 Refrigerant discharge pipe, 17 Swing bearing, 18 Thrust bearing, 19 Main bearing, 20 Groove, 21a Wedge oil film, 21b Reverse wedge oil film, 21c Oil film pressure, 22 groove, 100 Scroll compressor, 101 Compression mechanism.

Claims (6)

A compression mechanism having a fixed scroll and an orbiting scroll that form a compression chamber between the spiral teeth by combining the spiral teeth;
An electric motor,
A drive shaft that connects the electric motor and the orbiting scroll and transmits the driving force of the electric motor to the orbiting scroll;
A radial bearing and a thrust bearing that rotatably support the drive shaft;
An airtight container that houses the compression mechanism, the electric motor, and the drive shaft, and in which an oil sump for storing lubricating oil is formed;
With
The drive shaft has an oil supply passage extending from the oil reservoir to the drive shaft and the radial bearing,
A scroll compressor in which the lubricating oil supplied from the oil supply passage between the drive shaft and the radial bearing is supplied between the drive shaft and the thrust bearing;
The radial bearing is a slide bearing,
The position of the outer peripheral surface of the drive shaft where the oil film between the drive shaft and the radial bearing is the thickest is defined as a 0 ° position, and the outer peripheral surface of the drive shaft from the 0 ° position in the rotational direction of the drive shaft. When observing
A first groove inclined in a direction opposite to the rotational direction of the drive shaft from the thrust bearing side toward the opposite side of the thrust bearing is provided between 180 ° and 360 ° in a range facing the radial bearing. At least one is formed ,
A scroll compressor characterized in that the oil supply passage has an opening at a position where the first groove is not formed between 180 ° and 360 ° in a range facing the radial bearing. . A compression mechanism having a fixed scroll and an orbiting scroll that form a compression chamber between the spiral teeth by combining the spiral teeth;
An electric motor,
A drive shaft that connects the electric motor and the orbiting scroll and transmits the driving force of the electric motor to the orbiting scroll;
A radial bearing and a thrust bearing that rotatably support the drive shaft;
An airtight container that houses the compression mechanism, the electric motor, and the drive shaft, and in which an oil sump for storing lubricating oil is formed;
With
The drive shaft has an oil supply passage extending from the oil reservoir to the drive shaft and the radial bearing,
A scroll compressor in which the lubricating oil supplied from the oil supply passage between the drive shaft and the radial bearing is supplied between the drive shaft and the thrust bearing;
The radial bearing is a slide bearing,
The position of the outer peripheral surface of the drive shaft where the oil film between the drive shaft and the radial bearing is the thickest is defined as a 0 ° position, and the outer peripheral surface of the drive shaft from the 0 ° position in the rotational direction of the drive shaft. When observing
A first groove inclined in a direction opposite to the rotational direction of the drive shaft from the thrust bearing side toward the opposite side of the thrust bearing is provided between 180 ° and 360 ° in a range facing the radial bearing. At least one is formed ,
The end on the thrust bearing side in the first groove is located on the opposite side of the thrust bearing from the end on the thrust bearing side in the opposed range of the drive shaft and the radial bearing. A featured scroll compressor. A compression mechanism having a fixed scroll and an orbiting scroll that form a compression chamber between the spiral teeth by combining the spiral teeth;
An electric motor,
A drive shaft that connects the electric motor and the orbiting scroll and transmits the driving force of the electric motor to the orbiting scroll;
A radial bearing and a thrust bearing that rotatably support the drive shaft;
An airtight container that houses the compression mechanism, the electric motor, and the drive shaft, and in which an oil sump for storing lubricating oil is formed;
With
The drive shaft has an oil supply passage extending from the oil reservoir to the drive shaft and the radial bearing,
A scroll compressor in which the lubricating oil supplied from the oil supply passage between the drive shaft and the radial bearing is supplied between the drive shaft and the thrust bearing;
The radial bearing is a slide bearing,
The position of the outer peripheral surface of the drive shaft where the oil film between the drive shaft and the radial bearing is the thickest is defined as 0 ° position, and the outer peripheral surface of the drive shaft from the 0 ° position in the rotational direction of the drive shaft. When observing
A first groove inclined in a direction opposite to the rotational direction of the drive shaft from the thrust bearing side toward the opposite side of the thrust bearing is provided between 180 ° and 360 ° in a range facing the radial bearing. At least one is formed ,
The oil supply passage has an opening between 180 ° and 360 ° in a range facing the radial bearing,
A scroll compressor characterized in that at least one of the first grooves is disposed at a position on the front side in the rotational direction of the drive shaft with respect to the opening . A compression mechanism having a fixed scroll and an orbiting scroll that form a compression chamber between the spiral teeth by combining the spiral teeth;
An electric motor,
A drive shaft that connects the electric motor and the orbiting scroll and transmits the driving force of the electric motor to the orbiting scroll;
A radial bearing and a thrust bearing that rotatably support the drive shaft;
An airtight container that houses the compression mechanism, the electric motor, and the drive shaft, and in which an oil sump for storing lubricating oil is formed;
With
The drive shaft has an oil supply passage extending from the oil reservoir to the drive shaft and the radial bearing,
A scroll compressor in which the lubricating oil supplied from the oil supply passage between the drive shaft and the radial bearing is supplied between the drive shaft and the thrust bearing;
The radial bearing is a slide bearing,
The position of the outer peripheral surface of the drive shaft where the oil film between the drive shaft and the radial bearing is the thickest is defined as a 0 ° position, and the outer peripheral surface of the drive shaft from the 0 ° position in the rotational direction of the drive shaft. When observing
A first groove inclined in a direction opposite to the rotational direction of the drive shaft from the thrust bearing side toward the opposite side of the thrust bearing is provided between 180 ° and 360 ° in a range facing the radial bearing. At least one is formed ,
In the range facing the radial bearing, there is a second groove inclined in a direction opposite to the rotational direction of the drive shaft from 0 ° to 180 ° from the opposite side of the thrust bearing toward the thrust bearing side. A scroll compressor characterized by being formed . The end of the second groove opposite to the thrust bearing is positioned closer to the thrust bearing than the end opposite to the thrust bearing in the facing range of the drive shaft and the radial bearing. The scroll compressor according to claim 4 , wherein the scroll compressor is provided. 6. The end of the first groove opposite to the thrust bearing extends to a range where the drive shaft and the radial bearing are not opposed to each other. 6. The scroll compressor according to one item .

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