JP2012215086A - Oil supply pump device of compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply pump device capable of supplying lubricating oil in a required amount to each sliding part in a compressor.SOLUTION: An oil supply pump mechanism 100 is installed at one end side of a main shaft 21 that drives a compressor 10 housed inside a hermetic housing 11, the pump mechanism including a rotor R that is fitted to an eccentric shaft 24a of the main shaft 21 and driven and a cylinder 30 housing the rotor R. Lubricating oil reserved in an oil reservoir by the oil supply pump mechanism 100 through a suction passage is sucked and supplied to a sliding part of the compressor 10 through an oil supply hole 27 formed inside the shaft 21. An oil supply chamber 31a and an oil discharge chamber 31b are disposed between the cylinder 30 and the rotor R, and an oil supply chamber 31c and an oil discharge chamber 31d are formed between the eccentric shaft 24a and the rotor R. The lubricating oil is sucked to the oil supply chamber 31a and the oil supply chamber 31c through the suction passage, and the sucked lubricating oil is supplied to the oil supply hole 27 from the oil discharge chamber 31b and the oil discharge chamber 31d.

Description

  The present invention relates to an oil supply pump device for a compressor.

Conventionally, in a compressor constituting an air conditioner, lubrication is used to lubricate each sliding portion in the compressor.
Lubricating oil is sucked and introduced by an oil pump from an oil sump provided at the bottom of the housing constituting the compressor, and is supplied to the refrigerant sucked into the housing. An oil separator is provided outside the compressor, and the lubricating oil is separated and recovered from the refrigerant discharged from the compressor, and the lubricating oil is circulated to the oil sump via the circulation path.

  As such an oil supply pump, a rotary positive displacement pump is used (Patent Document 1, Patent Document 2). A conventional oil pump includes a rotor and a cylinder that houses the rotor. The rotor is revolved by the operation of an eccentric portion provided at one end of the main shaft rotated by the motor. The respective volumes of the oil supply chamber and the oil discharge chamber formed between the cylinder and the rotor change relative to each other as the rotor moves. Lubricating oil is sucked into the oil supply chamber as the volume of the oil supply chamber increases, and the lubricating oil in the oil discharge chamber is pressurized and formed on the main shaft as the volume of the oil discharge chamber decreases. Into the hole.

Japanese Patent Laid-Open No. 10-9175 JP 2006-177239 A

However, during high-speed operation of the compressor (when the operating speed is high), the amount of lubricating oil sucked in by this negative pressure does not catch up with the negative pressure generated by the oil pump, and the lubricating oil is sucked into the oil pump. Efficiency is reduced. As a result, there is a possibility that the sliding portions in the compressor are not sufficiently lubricated.
The present invention has been made based on such a technical problem, and an object thereof is to provide an oil supply pump device capable of supplying a necessary amount of lubricating oil to each sliding portion in a compressor.

For this purpose, the present invention provides an oil supply pump device for a compressor having the following configuration. That is, the oil pump device of the present invention includes a rotor that is fitted to and driven by an eccentric portion of the main shaft on one end side of the main shaft that drives the compression mechanism housed in the hermetic housing, and a cylinder that houses the rotor. The lubricating oil stored in the oil sump is sucked by the oil pump through the suction passage, and is supplied to the sliding portion of the compression mechanism through the oil passage formed in the main shaft. To do.
In the present invention, in addition to providing the first oil supply chamber and the first oil discharge chamber between the cylinder and the rotor, the second oil supply chamber and the second oil discharge chamber are provided between the eccentric portion and the rotor. Establish an oil chamber. Then, the lubricating oil is sucked into the first oil supply chamber and the second oil supply chamber through the suction passage, and the sucked lubricating oil is supplied from the first oil discharge chamber and the second oil discharge chamber to the oil supply passage. It is characterized by that.
In addition to providing the first oil supply chamber and the first oil discharge chamber between the cylinder and the rotor, the oil supply pump device according to the present invention includes the second oil supply chamber and the second oil supply between the eccentric portion and the rotor. Two oil discharge chambers are provided, the lubricating oil is sucked into the first oil supply chamber and the second oil supply chamber via the suction passage, and the sucked lubricating oil is supplied to the first oil discharge chamber and the second oil discharge chamber. Therefore, a larger amount of lubricating oil can be supplied compared to a conventional oil supply pump device having only a first oil supply chamber and a first oil discharge chamber. Therefore, according to the oil pump device of the present invention, it is possible to supply a necessary amount of lubricating oil to each sliding portion in the compressor.

In the oil pump device of the present invention, the oil supply passage can be made into one system, but the first oil supply passage corresponding to the first oil discharge chamber and the second oil supply passage corresponding to the second oil discharge chamber. That is, it is possible to provide two systems of oil supply passages for supplying lubricating oil.
By doing so, since it can lubricate independently to the sliding part of a different compression mechanism, a required quantity of lubricating oil can be supplied to each sliding part.

In the fuel pump device of the present invention, the suction passage can be made into one system, but the first suction passage corresponding to the first fueling chamber, the second suction passage corresponding to the second fueling chamber, As described above, it is possible to provide two systems of suction paths for sucking lubricating oil.
In this case, the timing for supplying the lubricating oil from the oil discharge chamber to the oil supply passage via the first suction passage, and the timing for supplying the lubricating oil from the oil discharge chamber to the oil supply passage via the second suction passage, Since it can shift, the space | interval which supplies lubricating oil to each sliding part can be shortened.
By disposing a partition member between the eccentric portion and the rotor, the second oil supply chamber and the second oil discharge chamber can be partitioned.

  According to the present invention, in addition to providing the first oil supply chamber and the first oil discharge chamber between the cylinder and the rotor, the second oil supply chamber and the second oil discharge chamber are provided between the eccentric portion and the rotor. An oil chamber is provided, and the lubricating oil is sucked into the first oil supply chamber and the second oil supply chamber via the suction passage, and the sucked lubricating oil is drawn from the first oil discharge chamber and the second oil discharge chamber to the main shaft. Since the oil can be supplied to the oil supply passage formed in the inside, more lubricating oil can be supplied as compared with the conventional oil supply pump device including only the first oil supply chamber and the first oil discharge chamber. Therefore, according to the oil pump device of the present invention, it is possible to supply a necessary amount of lubricating oil to each sliding portion in the compressor.

It is sectional drawing which shows the structure of the scroll compressor in 1st Embodiment. It is principal part sectional drawing which shows the oil supply pump mechanism in 1st Embodiment. It is a plane sectional view of an oil supply pump mechanism in a 1st embodiment. It is principal part sectional drawing which shows the oil supply pump mechanism in 2nd Embodiment. It is a plane sectional view of an oil supply pump mechanism in a 2nd embodiment. It is a sectional side view which shows arrangement | positioning of the suction hole of the cover plate in 2nd Embodiment, and the oil supply hole of a main shaft. It is principal part sectional drawing which shows the oil supply pump mechanism in 3rd Embodiment. It is a plane sectional view of an oil supply pump mechanism in a 3rd embodiment. It is a sectional side view which shows arrangement | positioning of the suction hole of the cover plate in 3rd Embodiment, and the oil supply hole of a main shaft.

[First Embodiment]
Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.
FIG. 1 is a diagram illustrating a configuration of a scroll compressor 10 according to the present embodiment.
The compressor 10 includes a main shaft 21, a turning scroll 22 that rotates together with the main shaft 21, and a fixed scroll 23 fixed to the housing 11 in a cylindrical sealed housing 11.
In such a compressor 10, the refrigerant is introduced into the housing 11 from the refrigerant introduction port 12 formed on one end side of the housing 11, and the refrigerant is stored in the compression chamber formed between the orbiting scroll 22 and the fixed scroll 23. Is compressed. The compressed refrigerant is discharged from a refrigerant discharge port 13 formed above the housing 11.

  The main shaft 21 is integrally provided with a motor rotor 37 of a motor 36 for rotating the main shaft 21. A motor stator 38 is fixed to the inner peripheral surface of the housing 11 so as to face the outer peripheral portion of the motor rotor 37.

  In the orbiting scroll 22 and the fixed scroll 23, spiral scroll walls 22b and 23b are erected on one side of the disk-shaped end plates 22a and 23a, respectively. The orbiting scroll 22 and the fixed scroll 23 combine the scroll walls 22b and 23b with each other to form a compression chamber between the scroll walls 22b and 23b.

An eccentric shaft 24 a is formed at the upper end portion of the main shaft 21 at a position eccentric from the central axis of the main shaft 21 by a predetermined dimension. The orbiting scroll 22 is rotatably held on the eccentric shaft 24a via a drive bearing 25. Thereby, the orbiting scroll 22 is provided eccentrically by a predetermined dimension with respect to the center of the main shaft 21.
In the end plate 22 a of the orbiting scroll 22, a boss portion 22 c is formed at the center portion on the side facing the main shaft 21. A bottomed hole that accommodates the drive bearing 25 is formed in the boss portion 22c, and the drive bearing 25 is press-fitted into the bottomed hole.
A bearing 14 is provided on the outer peripheral side of the boss portion 22 c, and a main frame 15 that supports the orbiting scroll 22 is provided on the outer peripheral side of the bearing 14. A cylindrical frame inner wall surface 15s having an axial line in the vertical direction is formed at the center in the width direction of the main frame 15. A main bearing MB is disposed between the inner wall surface 15s of the frame and the main shaft 21.
An eccentric shaft (eccentric portion) 24 b is formed at the lower end portion of the main shaft 21 at a position eccentric from the central axis of the main shaft 21 by a predetermined dimension.
Both ends of the main shaft 21 are rotatably supported. When the main shaft 21 rotates around its axis, the orbiting scroll 22 rotates (revolves) with an eccentric dimension as a radius with respect to the center of the main shaft 21. Do. An Oldham ring is interposed between the orbiting scroll 22 and the main shaft 21 so that the orbiting scroll 22 does not rotate while revolving.

The bottom of the housing 11 is an oil sump 50 for accumulating lubricating oil 51.
Below the motor 36 and above the oil sump 50, a cylinder 30 that houses the lower end of the main shaft 21 is provided. A cylindrical cylinder inner wall surface 30 </ b> S having an axial line in the vertical direction is formed at the center in the width direction of the cylinder 30. The cylinder inner wall surface 30S functions as a sub bearing.

A cylinder chamber 31 is formed on the lower surface of the cylinder 30, and an eccentric shaft 24 b and an annular rotor R are disposed in the cylinder chamber 31.
The cylinder chamber 31 is closed by a thrust plate 32 and a cover plate 33 attached to the cylinder 30.

FIG. 2 is a cross-sectional view of a main part showing an oil supply pump mechanism 100 of the compressor 10. FIG. 3 is a plan sectional view of the oil supply pump mechanism 100 showing the flow of the lubricating oil.
The eccentric shaft 24 b functions as a drive shaft of the oil supply pump mechanism 100. The rotor R is rotatably fitted on the outer periphery of the eccentric shaft 24b.
As shown in FIG. 3, the inner diameter of the rotor R is the outer diameter of the eccentric shaft 24b so that a space having a crescent-shaped cross section is formed between the inner peripheral surface of the rotor R and the outer peripheral surface of the eccentric shaft 24b. Is set slightly larger.
A protrusion R1 is formed on the outer peripheral surface of the rotor R, and the protrusion R1 is slidably inserted into a slot S1 formed on the inner peripheral surface of the cylinder chamber 31. The length of the protrusion R1 is set slightly shorter than the length of the slot S1. The protrusion R1 partitions the cylinder chamber 31 located on the outer peripheral side of the rotor R into an oil supply chamber 31a and an oil discharge chamber 31b, and prevents the rotor R from rotating. The rotor R has a circular outer periphery excluding the protrusion R1.
A slot S2 that can accommodate the partition member R3 is formed at a position facing the protrusion R1 on the inner peripheral surface side of the rotor R. The partition member R3 includes a spring R31 and a partition body R32. The partition main body R32 is formed to be slidable in the slot S2, one end is in contact with the outer peripheral surface of the eccentric shaft 24b, and the other end is fixed to one end of the spring R31. The other end of the spring R31 is fixed to the bottom of the slot S2. The partition main body R32 is pressed against the outer peripheral surface of the eccentric shaft 24b by the spring R31. The partition main body R32 reciprocates and slides in the slot S2 as the eccentric shaft 24b rotates, and one end of the partition main body R32 protrudes from the slot S2 into the cylinder chamber 31 depending on the rotational position of the eccentric shaft 24b. (State of FIG. 3). The partition main body R32 partitions the cylinder chamber 31 located between the inner peripheral surface of the rotor R and the outer peripheral surface of the eccentric shaft 24b into an oil supply chamber 31c and an oil discharge chamber 31d.

As shown in FIG. 2, the cover plate 33 is formed with a suction hole 34 a for sucking the lubricating oil 51 stored in the oil reservoir 50 and a discharge hole 34 b for discharging the lubricating oil 51 to the thrust plate 32 side. ing. The thrust plate 32 is formed with a suction port 35 communicating with the discharge hole 34b, the oil supply chamber 31a of the cylinder chamber 31, and the oil supply chamber 31c.
The cover plate 33 is formed with a discharge hole 39, and the thrust plate 32 is formed with a discharge port 45 that communicates the discharge hole 39 with the oil discharge chamber 31 b and the oil discharge chamber 31 d of the cylinder chamber 31. ing. Further, the thrust plate 32 is formed with a communication hole 46 that communicates the discharge hole 39 and the oil supply hole 27 of the main shaft 21.

  As shown in FIG. 1, the oil supply hole 27 is formed in the main shaft 21 along the axial direction from the lower end to the upper end. Further, in the region above the motor 36 and below the drive bearing 25, the oil supply hole 27 is branched in the radial direction. The drive bearing 25 is lubricated by the lubricating oil discharged from the upper end of the oil supply hole 27, and the main bearing MB is lubricated by the lubricating oil discharged from the branch portion of the oil supply hole 27.

In the oil supply pump mechanism 100 configured as described above, the eccentric shaft 24 b is eccentrically rotated together with the main shaft 21 rotated by the motor 36. The rotor R is pushed by the eccentric shaft 24 b that rotates eccentrically, and revolves while the outer peripheral surface is in sliding contact with the inner peripheral surface of the cylinder chamber 31 along a line. As the rotor R rotates, the volumes of the oil supply chamber 31a and the oil discharge chamber 31b in the cylinder chamber 31 are relatively increased and decreased.
As the volume of the oil supply chamber 31a increases, the lubricating oil 51 stored at the bottom of the housing 11 passes through the suction hole 34a, the discharge hole 34b of the cover plate 33, and the suction port 35 of the thrust plate 32. It is sequentially sucked into 31a. Further, as the volume of the oil discharge chamber 31 b of the cylinder chamber 31 decreases, the lubricating oil 51 in the oil discharge chamber 31 b is pressurized and discharged from the discharge port 45 of the thrust plate 32. The lubricating oil discharged from the discharge port 45 reaches the oil supply hole 27 of the main shaft 21 through the discharge hole 39 and then moves upward from the lower end portion of the oil supply hole 27 as shown in FIG.

In the oil supply pump mechanism 100 of the present application, the cylinder body 31 positioned on the inner peripheral side of the rotor R is partitioned into an oil supply chamber 31c and an oil discharge chamber 31d by the partition main body R32. The oil supply chamber 31 c communicates with the suction hole 34 a and the discharge hole 34 b through the suction port 35. The oil discharge chamber 31 d communicates with the discharge hole 39 and the oil supply hole 27 of the main shaft 21 through the discharge port 45.
As the eccentric shaft 24b rotates, the volumes of the oil supply chamber 31c and the oil discharge chamber 31d in the cylinder chamber 31 are relatively increased and decreased. That is, as the volume of the oil supply chamber 31c increases, the lubricating oil 51 stored at the bottom of the housing 11 passes through the suction hole 34a, the discharge hole 34b of the cover plate 33, and the suction port 35 of the thrust plate 32. It is sequentially sucked into the oil supply chamber 31c. Further, as the volume of the oil discharge chamber 31 d decreases, the lubricating oil 51 in the oil discharge chamber 31 b is pressurized and discharged from the discharge port 45 of the thrust plate 32, and reaches the oil supply hole 27 of the main shaft 21.

  As described above, the lubricating oil introduced from the suction port 35 flows in a direction crossing the oil supply chamber 31 a and the oil supply chamber 31 c of the cylinder chamber 31. In the process, the lubricating oil is also introduced into the oil supply chamber 31c. As the eccentric shaft 24b revolves (clockwise), the lubricating oil introduced into the oil supply chamber 31a reaches the oil discharge chamber 31b, and the lubricant introduced into the oil supply chamber 31c enters the oil discharge chamber 31d. To reach. Thus, the lubricating oil is supplied to the oil supply hole 27 of the main shaft 21 from the two oil discharge chambers 31b and 31d, and is supplied upward as shown in FIG.

  As described above, the oil supply pump mechanism 100 includes the oil supply chamber 31a and the oil discharge chamber 31b between the rotor R and the cylinder chamber 31, and the oil supply chamber 31c and the oil discharge chamber 31d between the rotor R and the eccentric shaft 24b. It was made to provide. Thereby, the oil absorption amount and the discharge amount of the lubricating oil can be increased. Therefore, a required amount of lubricating oil can be supplied to each sliding portion in the compressor even during high-speed operation.

[Second Embodiment]
Next, an oil supply pump mechanism 101 according to a second embodiment of the present invention will be described with reference to FIGS. Note that parts having functions common to the parts shown in the first embodiment are denoted by reference numerals corresponding to those of the first embodiment, and description of the functions is omitted.
In the first embodiment, the lubricating oil discharged from both the oil discharge chamber 31 b and the oil discharge chamber 31 d is supplied to the upper side of the main shaft 21 through one oil supply hole 27. In contrast, in the second embodiment, the first oil supply hole (second oil supply passage) 27a corresponding to the oil discharge chamber 31d and the second oil supply hole (first oil supply hole) corresponding to the oil discharge chamber 31b are used. Road) 27b is provided independently. The first oil supply hole 27 a is formed in the main shaft 21 along the axial direction from the lower end to the upper end. The drive bearing 25 is lubricated by the lubricating oil discharged from the upper end of the first oil supply hole 27a. The second oil supply hole 27 b extends upward from the lower end inside the main shaft 21, but changes its direction along a radial direction from a predetermined position and opens on the outer peripheral surface of the main shaft 21. The main bearing MB is lubricated by the lubricating oil discharged from the opening.

In response to the provision of the two independent first oil supply holes 27a and second oil supply holes 27b, the oil supply pump mechanism 101 has a first lubricating oil that extends from the oil discharge chamber 31d to the first oil supply hole 27a. A path and a second path of lubricating oil from the oil discharge chamber 31b to the second oil supply hole 27b are provided independently.
That is, the cover plate 33 is formed with a first discharge hole 39a, and the thrust plate 32 is formed with a first discharge port 45a that communicates the first discharge hole 39a with the oil discharge chamber 31b of the cylinder chamber 31. Has been. Further, the thrust plate 32 is formed with a first communication hole 46 a that communicates the first discharge hole 39 a and the oil supply hole 27 b of the main shaft 21. As a result, the first path is formed.
The cover plate 33 is formed with a second discharge hole 39b, and the thrust plate 32 is formed with a second discharge port 45b that communicates the second discharge hole 39b with the oil discharge chamber 31d of the cylinder chamber 31. Has been. Further, the thrust plate 32 is formed with a second communication hole 46 b that communicates the second discharge hole 39 b and the oil supply hole 27 a of the main shaft 21. As a result, the second path is formed.
In addition, the route of the oil supply regarding the oil supply chambers 31a and 31b is the same as that of 1st Embodiment.

In the oil supply pump mechanism 101 described above, as in the first embodiment, the lubricating oil is sucked into the oil supply chamber 31a and the oil supply chamber 31c, and the oil discharge chamber 31b and the oil discharge chamber 31d are accompanied by the revolution turning motion of the eccentric shaft 24b. To reach.
Then, as the volume of the oil discharge chamber 31 b of the cylinder chamber 31 decreases, the lubricating oil 51 in the oil discharge chamber 31 b is pressurized and discharged from the first discharge port 45 a of the thrust plate 32. The lubricating oil discharged from the first discharge port 45a moves in the radial direction in the first discharge hole 39a, passes through the first communication hole 46a formed in the thrust plate 32, and the second oil supply hole of the main shaft 21. After reaching 27b, as shown in FIG. 6, it moves upward from the lower end of the second oil supply hole 27b.
Further, as the volume of the oil discharge chamber 31d of the cylinder chamber 31 decreases, the lubricating oil 51 in the oil discharge chamber 31d is pressurized and discharged from the second discharge port 45b of the thrust plate 32. The lubricating oil discharged from the second discharge port 45b moves in the radial direction in the second discharge hole 39b, passes through the second communication hole 46b formed in the thrust plate 32, and passes through the first oil supply hole of the main shaft 21. After reaching 27a, as shown in FIG. 6, it moves upward from the lower end of the first oil supply hole 27a.

  The oil supply pump mechanism 101 according to the second embodiment is provided with a first oil supply hole 27a and a second oil supply hole 27b in the main shaft 21 in addition to the first embodiment. Thereby, the lubricating oil path (first oil supply hole 27a) for the drive bearing 25 and the lubricating oil path (second oil supply hole 27b) for the main bearing MB can be provided independently. . Therefore, the ratio of the oil amount distribution to the main bearing MB and the drive bearing 25 is not easily biased, and it becomes easy to secure the oil amount necessary for lubrication of the main bearing MB and the drive bearing 25.

[Third Embodiment]
Next, an oil supply pump mechanism 102 according to a third embodiment of the present invention will be described with reference to FIGS. Note that parts having functions common to those shown in the second embodiment are denoted by reference numerals corresponding to those of the second embodiment, and description of the functions is omitted.
In the second (first) embodiment, lubricating oil is supplied to the oil supply chamber 31a and the oil supply chamber 31c from a common oil supply path. In contrast, in the third embodiment, lubricating oil is supplied by providing independent oil supply paths in the oil supply chamber 31a and the oil supply chamber 31c. That is, as shown in FIG. 7, in the third embodiment, the cover plate 33 </ b> A has a first suction hole (suction path, second suction path) for sucking the lubricating oil 51 stored in the oil reservoir 50. 340a and a second suction hole (suction path, first suction path) 341a are formed. The first suction hole 340a communicates with a first discharge hole (suction path, second suction path) 340b for discharging the lubricating oil 51 to the thrust plate 32 side, and the second suction hole (suction path). The first suction path 340b communicates with a discharge hole 341b for discharging the lubricating oil 51 to the thrust plate 32 side.
The thrust plate 32 is formed with a first suction port 35a communicating with the first discharge hole 340b and the oil supply chamber 31a. The thrust plate 32 is formed with a second suction port 35b communicating with the second discharge hole 341b and the oil supply chamber 31c. As shown in FIG. 8, the first suction port 35a and the second suction port 35b are independent from each other and do not communicate with each other.

In the above-described oil supply pump mechanism 102, as the volume of the oil supply chamber 31a increases, the lubricating oil 51 stored at the bottom of the housing 11 is transferred to the first suction hole 340a and the first discharge hole of the cover plate 33A. 340b and the first suction port 35a are sequentially sucked into the oil supply chamber 31a.
On the other hand, as the volume of the oil supply chamber 31c increases, the lubricating oil 51 stored in the bottom of the housing 11 is transferred to the second suction hole 341a, the second discharge hole 341b, and the second suction hole of the cover plate 33A. The oil is sequentially sucked into the oil supply chamber 31c through the port 35b.
The lubricating oil sucked into the oil supply chamber 31a and the oil supply chamber 31c is supplied to the second oil supply hole 27b and the first oil supply hole 27a in the same manner as in the second embodiment.

  In the oil supply pump mechanism 102 according to the third embodiment, in addition to the second embodiment, the first oil supply chamber 31a has a first intake hole 340a, a second intake hole 341a, and an intake opening 35a. In addition, lubricating oil is independently supplied to the second oil supply chamber 31c via the second suction hole 340b, the second suction hole 341b, and the second suction port 35b. Thereby, independent oil supply to the drive bearing 25 and the main bearing MB can be performed, and it is possible to eliminate the influence of the rotational speed of the oil supply distribution ratio to the drive bearing 25 and the main bearing MB.

In the above embodiment, the slot S2 that can accommodate the partition member R3 is formed at a position facing the inner peripheral surface side of the rotor R and the protrusion R1, but the position is inverted by 180 ° from another position, for example, the protrusion R1. A slot S2 may be formed at the position. By doing so, it is possible to shift the timing at which the lubricating oil is supplied from the first oil discharge chamber 31b to the oil supply hole 27 and the timing at which the lubricating oil is supplied from the second oil discharge chamber 31d to the oil supply hole 27. It becomes easy and the oiling interval can be shortened.
Further, it is not essential that the rotor R has an annular shape, and other shapes such as a star shape may be adopted as long as the volume between the eccentric shaft 24b and the rotor R can be varied.
Although the example which applied oil supply pump mechanisms 100-102 to scroll type compressor 10 was shown, you may apply to a rotary type compressor etc.
In addition to this, as long as it does not depart from the gist of the present invention, the configuration described in the above embodiment can be selected or changed to another configuration as appropriate.

10 Compressor 11 Housing 21 Main shaft 24b Eccentric shaft (eccentric part)
25 Drive bearing (sliding part of compression mechanism)
27 Oil supply hole (oil supply path)
27a 1st oil supply hole (2nd oil supply path)
27b Second oil supply hole (first oil supply passage)
30 Cylinder 31 Cylinder chamber 31a Oiling chamber (first oiling chamber)
31b Oil discharge chamber (first oil discharge chamber)
31c Refueling chamber (second refueling chamber)
31d Oil discharge chamber (second oil discharge chamber)
34a Suction hole (suction channel)
34b Discharge hole (suction path)
35 Suction port 35a First suction port 35b Second suction port 100, 101, 102 Oil pump mechanism (oil pump device)
340a Suction hole (suction path, second suction path)
340b Discharge hole (suction path, second suction path)
341a Suction hole (suction path, first suction path)
341b Discharge hole (suction path, first suction path)
MB main bearing (sliding part of compression mechanism)
R Rotor R3 Partition member

Claims (4)

Installed on one end side of the main shaft that drives the compression mechanism housed in the hermetic housing is a rotor that is fitted to the eccentric portion of the main shaft and driven, and a cylinder that houses the rotor. Then, the lubricating oil stored in the oil sump by the oil supply pump is sucked through the suction passage, and is supplied to the sliding portion of the compression mechanism through the oil passage formed in the main shaft. Machine oil pump device,
A first oil supply chamber and a first oil discharge chamber are provided between the cylinder and the rotor; and
A second oil supply chamber and a second oil discharge chamber are provided between the eccentric portion and the rotor,
The lubricating oil is sucked into the first oil supply chamber and the second oil supply chamber through the suction passage, and the sucked lubricating oil is discharged from the first oil discharge chamber and the second oil discharge chamber. An oil supply pump device for a compressor, which is supplied to the oil supply passage. The oil supply path is
A first oil supply passage corresponding to the first oil discharge chamber;
A second oil supply passage corresponding to the second oil discharge chamber,
The oil supply pump apparatus of the compressor of Claim 1. The suction path is
A first suction passage corresponding to the first oil supply chamber;
A second suction path corresponding to the second oil supply chamber,
The oil supply pump apparatus of the compressor of Claim 1 or Claim 2.   4. The partition member according to claim 1, wherein a partition member that partitions the second oil supply chamber and the second oil discharge chamber is disposed between the eccentric portion and the rotor. 5. Compressor oil pump device.