JPH06272683A - Lubrication pump device for compressor - Google Patents

Abstract

PURPOSE:To ensure proper lubrication with a simple structure using a small quantity of parts by arranging a pump cylinder having an eccentric cylinder chamber at the end of a rotary shaft laid for connecting the electric motor section of a compressor to the compression mechanism section thereof. CONSTITUTION:The end of a rotary shaft 23 to connect the electric motor section of a compressor to the compression mechanism section thereof is provided with a pump cylinder 56 having a cylinder chamber 60 eccentric from the axial center of the shaft 23 for allowing the rolling contact of shaft external surface. Also, one edge of the pump cylinder 56 is fitted with a seal plate 55 for closing the opening thereof, while the other edge is fitted with a thrust plate 57 for closing the opening thereof and for slidable contact with the shaft 23. Also, an oil sucking section 62 is provided on the thrust plate 57. On the other hand, a notched groove 53 is formed on the shaft 53, and a roller pin 54 is laid in the groove 53 for dividing the cylinder chamber 60 and sucking lubricating oil. Then, this lubricating oil is introduced from a delivery passage 52 to the compression mechanism section via a lubrication passage 51.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is provided on a rotary shaft of a compressor and is for supplying oil to a compression mechanism section.
In particular, it relates to improvement of a positive displacement type oil supply pump device.

[0002]

2. Description of the Related Art Regardless of the type of structure of a compression mechanism such as a rotary compressor or a scroll compressor, an oil supply means is provided to ensure the compression mechanism and ensure smooth sliding. .

Although there are various structures for the oil supply means in such a compressor, it is necessary to secure a sufficient amount of oil supply and to meet the requirement that no accidental seizure damage will occur.
The positive displacement type oil supply pump device is most suitable. So-called trochoid pumps and gear pumps are typical of positive displacement pumps, and it is conceivable to apply these as refueling pumps. However, in the case of these pumps, the structure is complicated, the number of parts is large, the workability and the assemblability are poor, and the cost is a problem, and it is not general. FIG. 5 (A) and FIG. 5 (B) show a positive displacement type oil supply pump device that has been developed and used to eliminate these problems as much as possible.

In the figure, reference numeral 1 is a rotary shaft, and the oil supply pump device provided at the lower end portion is immersed in the lubricating oil surface of the oil sump portion. An oil supply hole 2 is provided along the axis from the lower end surface of the rotary shaft 1. The oil supply hole 2 extends to a compression mechanism portion (not shown).

A concave groove 3 is provided on the tip end surface of the rotary shaft 1 in the radial direction, and a detent 5 of a connecting pin 4 is engaged with the groove. The connecting pin 4 is in the shape of a hollow pipe, and the upper part from the rotation stopper 5 is fitted in the oil supply hole 2.

The lower portion from the rotation preventing portion 5 is rotatably engaged with the thrust plate 6 and is fitted and integrated with the pump shaft 7. Further, the lower end surface of the connecting pin 4 is supported while being placed on the seal plate 8 and the fixed plate 9.

The outer peripheral surface of the pump shaft 7 is eccentric with respect to the connecting pin and the rotary shaft 1, and the pump cylinder 10
It is housed in the cylinder chamber 11 formed in. In the state where the cylinder chamber 11 is eccentrically rotated, a part of its peripheral surface constantly contacts the part of the peripheral surface of the cylinder chamber 11.

The fixed plate 9, the seal plate 8, the pump cylinder 10 and the thrust plate 6 are stacked in this order, and are mounted and fixed via a fixing bolt 12 to an auxiliary bearing which also serves as the pump device body 13.

A cutout groove 14 is formed in a part of the peripheral surface of the pump shaft 7.
Is provided, and the slide pin 15 is movably engaged therewith. If the pump shaft 7 rotates together with the rotary shaft 1 through the connecting pin 4, the centrifugal force acts on the slide pin 15
Moves to the peripheral end side of the notch groove 14 and comes into sliding contact with the peripheral surface of the cylinder chamber 11. At the same time, the slide pin 15 divides the cylinder chamber into two parts except when the position where the pump shaft 7 contacts the cylinder chamber 11 coincides with the position of the slide pin 15.

Oil suction holes 16, 16 are formed through the fixed plate 9 and the seal plate 8 so as to penetrate through the plate thickness, and in an oil suction groove 17 provided facing the cylinder chamber 11 of the pump cylinder 10. Communicate.

An oil discharge notch 18 is provided at another position facing the cylinder chamber 11 of the pump cylinder 10, and an oil discharge hole 19 provided in the seal plate 8 and an oil guide groove 20 provided in the fixed plate 9 are provided. Connect to one end.

The oil guide groove 20 is provided only on the overlapping surface with the seal plate 8, and the other end thereof extends so as to communicate with the support portion of the connecting pin 4 and at least the hollow portion of the connecting pin 4. Set up.

Since the oil supply pump device is constructed as described above, the pump shaft 7 rotates eccentrically in the cylinder chamber 11 as the rotary shaft 1 rotates, and the slide pin 15 divides the cylinder chamber 11 into two cylinders. Slide on the peripheral wall of the chamber 11.

Negative pressure is generated as the volume of the divided cylinder chamber 11 changes, and the lubricating oil in the oil sump portion is sucked from the oil suction hole 16 and introduced into the cylinder chamber 11. This lubricating oil collects in the cylinder chamber 11 portion divided into the rotation direction side, and is further subjected to pressure due to the decrease in the volume of the cylinder chamber 11 accompanying the movement of the slide pin 15.

The lubricating oil that has risen to a predetermined pressure is discharged from the oil discharge notch portion 18, and the oil discharge hole 19 and the oil guide groove 20 are provided.
Is guided to the hollow part of the connecting pin 4 via the
Will be supplied to the compression mechanism section.

[0016]

As described above, it is undeniable that reliable oil supply is performed, but it still has a large number of parts and poor assemblability, which causes a cost problem.

Further, as a feature of positive displacement pumps including the above-mentioned trochoid pump, oil is supplied in proportion to the rotation speed of the rotary shaft 1, so that when the rotation speed becomes high, Unnecessary and excessively refueled,
The amount of oil discharged to the outside of the compressor increases with the passage of time, and the oil level in the oil sump decreases. That is, there remains a problem in terms of reliability.

The present invention has been made in view of the above circumstances. The first object of the present invention is that the number of parts is smaller, the structure is simple, the workability and the assemblability are improved, and (EN) Provided is an oil supply pump device in a compressor, which can reliably perform oil supply and can improve oil supply efficiency.

A second object of the present invention is that when the rotary shaft rotates at a high speed, the amount of oil supply is suppressed to drastically reduce the oil level in the oil sump and to reduce the amount of oil discharge, thereby improving reliability. An oil supply pump device in a compressor is provided.

[0020]

In order to satisfy the above object, an oil supply pump device for a compressor according to claim 1 of the present invention comprises:

A pump cylinder having a cylinder chamber which is provided at the end of the rotary shaft and is formed eccentrically with respect to the axis of the rotary shaft so that a part of the peripheral surface of the rotating rotary shaft is always in rolling contact with a fixed portion. A seal plate provided on one end surface of the pump cylinder and closing one end opening surface of the cylinder chamber,
A thrust plate which is provided on the other end surface of the pump cylinder and closes the other end opening surface of the cylinder chamber and which is in sliding contact with the tip end surface of the rotating shaft, and an oil which is provided on the thrust plate and opens to the lubricating oil in the oil reservoir. A notch groove that is provided radially from the outer peripheral surface at the suction portion, a portion of the rotary shaft that faces the cylinder chamber, and a notch groove that is displaceably engaged with the notch groove and that is rotated by the centrifugal force that acts on the cylinder chamber circumference. A roller pin that abuts the surface to divide the cylinder chamber and suck the lubricating oil in the oil sump from the oil suction part into the cylinder chamber,
A discharge passage that is provided on the rotating shaft and that guides the lubricating oil in the cylinder chamber by pressure increase due to the pressure increase accompanying the decrease in the cylinder chamber capacity, and an oil supply passage that guides the lubricating oil pressure-fed from the discharge passage to the compression mechanism section. And is provided. The oil supply pump device in the compressor according to claim 2 of the present invention is

The oil supply passage according to claim 1 is provided along the axial direction from the end face of the rotary shaft, and the discharge passage communicating with the oil supply passage is provided along the radial direction from the peripheral surface of the rotary shaft. It is characterized by

[0023]

According to the first aspect of the present invention, the substantial parts constituting the oil supply pump device are only the seal plate, the pump cylinder, the thrust plate, the roller pin, etc. in addition to the rotating shaft.
Moreover, simple processing is sufficient for both.

Since the cylinder chamber and the rotary shaft are eccentric to each other, the rotary shaft is eccentrically rotated with respect to the cylinder chamber, and the roller pin divides the cylinder chamber to perform a pumping operation exactly the same as the conventional one. Eggplant According to the second aspect, as the rotating shaft rotates at a higher speed, a strong centrifugal force is generated in the discharge passage, and the pressure in the cylinder chamber increases.

The lubricating oil in the cylinder chamber easily leaks from the sliding contact portion, and a sufficient amount cannot be guided from the oil discharge passage to the oil supply passage. That is, if the rotation speed is high, the oil supply efficiency is lowered, and the oil level is not extremely lowered.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows a scroll compressor used in, for example, a refrigeration system.

Reference numeral 21 in the drawing denotes a closed case, a support frame 22 is provided in the closed case 21, and a rotary shaft 23 is provided.
Is rotatably supported. A compression mechanism section 24, which will be described later, is provided above the rotary shaft 23, and an electric motor section 27 including a stator 25 and a rotor 26 is provided below the rotary shaft 23.

The compression mechanism portion 24 has a fixed scroll blade 28 mounted and fixed to the support frame 22, an orbiting scroll blade 29 pivotally supported by an eccentric portion 23a at the upper end of the rotary shaft 23, and the fixed scroll blade 28 side. The back pressure guide means 30 applies a gas pressure to the back side.

The fixed scroll vane 28 and the orbiting scroll vane 29 are both end plate portions 32, 33 and a spiral wing portion 34 provided integrally with the end plate portions 32, 33.
And 35. The wing portions 34 and 35 are meshed with each other, and a compression chamber S which is a spiral space surrounded by the end plate portions 32 and 33 is formed.

A concave portion 36 is provided at the center of the upper surface of the fixed scroll blade end plate portion 32, and a discharge port 37 communicating with the spiral center of the compression chamber S is provided through the end plate portion 33.

Further, on the upper surface side of the fixed scroll blade end plate portion 32, an annular concave portion 38 is provided around the discharge port 37, and an intermediate pressure introducing hole 39 communicating with the compression chamber S is opened therein. .

A back pressure plate 40 for partitioning the inside of the closed case 21 into an upper end space and a lower space is provided on the upper surface side of the fixed scroll blade 29, and is attached and fixed to the closed case 21.
The back pressure plate 40 has a check valve 41 at the center,
It communicates with the discharge port 37.

Further, the fixed scroll vanes 29 are moved in the axial direction within the narrow gap with the back pressure plate 40 by the seal rings 42 and 43 provided along the inner peripheral portion and the outer peripheral portion of the recess 38. However, a reliable seal is made. A discharge pipe 44 is connected to the upper side surface of the closed case 21 and a portion communicating with the upper space of the back pressure plate 40, and communicates with a condenser (not shown) of the refrigeration system. The closed case 21
A suction pipe 45 is connected to the lower side surface of the refrigerator and communicates with an evaporator (not shown) of the refrigeration system. On the other hand, the lower end portion of the rotary shaft 23 projects downward from the electric motor portion 27 and is rotatably supported by a sub bearing 46 attached to the sealed case 21.

An oil sump 47 for collecting lubricating oil is formed on the inner bottom of the closed case 21, and the lower end of the rotary shaft 23 and a later-described oil supply provided at the end of the rotary shaft 23 are formed therein. The pump device P is immersed. Next, the oil supply pump device P will be described based on FIGS. 2 (A) and 2 (B).
The device main body 46 also serves as the auxiliary bearing, and pivotally supports the lower end portion, which is the front end portion of the rotary shaft 23, via the metal 50. An oil supply passage 51, which is an oil supply hole, is provided from the lower end surface of the rotary shaft 23 to the compression mechanism portion 24 described above and along the axial direction. At a portion near the lower end of the oil supply passage 51, a discharge passage 52 formed of a lateral hole provided in the radial direction from the peripheral surface of the rotary shaft 23 is provided.

Further, a cutout groove 53 is provided at the lower end of the rotary shaft 23 along the radial direction from the peripheral surface and in a range not reaching the oil supply passage 51. The notch groove 53 is formed so as to have a completely parallel surface from the peripheral surface of the rotary shaft 23 to the middle portion thereof, and has a semicircular shape having a diameter at a distance between the parallel surfaces at a tip portion. .

A roller pin 54 is engaged with the notch groove 53. The axial length of the roller pin 54 matches the depth dimension of the cutout groove 53. The diameter of the roller pin 54 is very slightly smaller than the diameter of the semicircular portion formed at the end of the cutout groove 53, and is therefore movable with respect to the groove 53.

At the lower end of the rotary shaft 23, the seal plate 5
5 and the pump cylinder 56 are engaged with each other in an overlapped state. Further, both the seal plate 55 and the pump cylinder 56 are supported by the thrust plate 57. The thrust plate 57 is supported by a snap ring 58 provided on the main body 46 of the apparatus so that the lower end surface of the rotary shaft 23 is in sliding contact. The seal plate 55 has a ring shape of equal diameter,
The rotating shaft 23 is inserted and engaged with the inner diameter portion, and the outer diameter portion is equal to the outer diameter portion of the pump cylinder 56.

The plate thickness of the pump cylinder 56 is equal to the depth dimension of the cutout groove 53 and the axial length of the slide pin 54. Inside, a cylinder port 56a having a center eccentric to the axis of the rotary shaft 23 and having a diameter larger than the diameter of the rotary shaft 23 is provided. In other words, the pump cylinder 56 is an eccentric ring.

The cylinder port 56a is assembled such that a part of the peripheral surface of the rotary shaft 23 is in rolling contact with the cylinder port 56a. That is,
The cylinder port 56a is eccentric with respect to the axis of the rotary shaft 23,
And since it is larger than this diameter, this assembly is possible.

A seal plate 55 and a thrust plate 57 are superposed on the upper and lower end surfaces of the pump cylinder 56, and the open portion of the cylinder port 56a is closed regardless of the rotation of the rotary shaft 23 to form a closed space. It This closed space,
It is called a cylinder chamber 60.

An oil suction notch 61 is provided around the cylinder port 56a on the lower surface of the pump cylinder 56, and is located at a position facing the cylinder chamber 60 in the assembled state.

The thrust plate 57 is provided with an oil suction portion 62 which is a long hole communicating with the oil suction notch 61.
The oil suction portion 62 opens into the lubricating oil of the oil sump portion 47.

In the scroll type compressor having the hot water supply pump device P constructed as described above, the electric motor section 27 is used.
When the compression mechanism section 24 is driven by energizing, the low-pressure refrigerant gas is guided from the suction pipe 45 through the evaporator, and fills the space below the back pressure plate 30 in the closed case 21.

This refrigerant gas is sucked into the outer peripheral portion of the compression chamber S formed by the orbiting scroll blade 28 and the fixed scroll blade 29, and is gradually transferred to the central portion as the orbiting scroll blade 29 orbits. In addition, the compression capacity is reduced so that the image is compressed. When the pressure has risen to the specified level,
It is discharged from the discharge port 37 to the upper space of the back pressure plate 40 via the check valve 41, and is further guided to the condenser via the discharge pipe 44.

A part of the high-pressure refrigerant gas discharged from the discharge port 37 once fills the concave portion 36, and back pressure is applied to the central portion of the fixed scroll blade 29. On the other hand, an intermediate-pressure gas is introduced from the compression chamber S through the intermediate-pressure introduction hole 39 to the recess 38, which is an intermediate-pressure chamber, and is filled there with the fixed scroll blade 29.
Apply back pressure to the peripheral edge of.

As described above, in a normal operating state, the back pressure guide means 30 exerts an effective back pressure on the fixed scroll vanes 29 to regulate the movement in the axial direction to form the compression chamber S. The clearance with the wing 28 is optimally maintained.

When the compression chamber S has an abnormally high pressure under some condition, the pressure in the compression chamber S exceeds the back pressure of the back pressure guide means 30, and the fixed scroll blade 29 moves in the axial direction. The clearance between the orbiting scroll vane 28 and the compression chamber S expands, and the abnormal high-pressure gas in the compression chamber S escapes into the sealed case 21. It exerts a so-called compliance function in which the stress of the scroll wings 34 and 35 is eliminated.

On the other hand, in the oil supply pump device P, the rotary shaft 23 rotates in a state of rolling contact with a part of the peripheral surface of the cylinder chamber 60. And with this rotation, the roller pin 54
A centrifugal force acts on the roller pin 54, and the roller pin 54 rotates (revolves) together with the rotary shaft 23 in a state in which the roller pin 54 is always in rolling contact with the circumferential surface of the cylinder chamber 60. Except when the roller pin 54 coincides with the rolling contact portion between the rotary shaft 23 and the peripheral surface of the cylinder chamber 60,
The roller pin 54 divides the cylinder chamber 60 into two.

To explain further, in the state shown in FIG. 3A, the roller pin 54 is in a state immediately after passing through the suction notch 61, and the portion of the cylinder chamber 60 between here and the roller pin 54 is under negative pressure. As a result, the lubricating oil of the oil sump portion 47 is transferred to the cylinder chamber 60 via the oil suction portion 62.
Inhale.

Lubricating oil has already been sucked into the portion of the cylinder chamber 60 that is sectioned on the rotational direction side of the roller pin 54, and a portion of the lubricating oil has been compressed from the discharge passage 52 through the oil supply passage 51 while being compressed to some extent. Is refueled to the compression mechanism section 24.

When the rotary shaft 23 rotates clockwise from the position (a) in the figure to the position (b) by 90 °, the capacity of the cylinder chamber 60 communicating with the suction notch 61 increases. And add more lubricating oil to the oil reservoir 47
Inhale from On the other hand, in the cylinder chamber 60 portion on the rotation direction side, the capacity is further reduced, and the amount of lubricating oil pumped to the discharge passage 52 is increased.

As shown in (c), at the position further displaced by 90 °, the cylinder chamber 6 communicating with the suction notch 61 is formed.
The capacity of the 0 part becomes larger and the lubricating oil is sucked in continuously. The volume of the cylinder chamber 60 on the rotation direction side is almost zero, and almost no lubricating oil is discharged to the discharge passage 52.

As shown in (d), at the position further displaced by 90 °, the rolling contact portion of the roller pin 54 with respect to the circumferential surface of the cylinder chamber 60 coincides with the rolling contact portion between the rotary shaft 23 and the circumferential surface of the cylinder chamber 60. The cylinder chamber 60 that communicates with the suction notch 61 is all. On the other hand, the suction notch 61 and the discharge passage 52 communicate with each other, and no lubricating oil is discharged from the discharge passage 52. Then, return to the state of (a) again,
The above refueling action is repeated. In this way, the refueling pump device P normally performs refueling operation with extremely high efficiency.

However, in order to increase the circulation amount of the refrigerant, the rotation speed of the compressor may be operated at a higher speed. In this case, the oil supply pump device P reduces the oil supply efficiency as the number of revolutions increases, and suppresses the sudden increase in the discharge amount. That is, the discharge passage 52 provided in the rotary shaft 23
Is provided along the radial direction from the peripheral surface of the rotary shaft 23 and communicates with the oil supply passage 51. Due to the form of the discharge passage 52, a stronger centrifugal force is generated in the lubricating oil in the discharge passage 52 as the rotating shaft 23 rotates at a higher speed.

Originally, the lubricating oil in the discharge passage 52 is pumped from the peripheral surface side of the rotary shaft 23 toward the oil supply passage 51 which is the axial center side by the pump action, but this time due to the influence of the centrifugal force. The pressure in the cylinder chamber 60 increases, and the components easily leak from the abutting portions.

For example, the rolling contact portion of the rotary shaft 23 and the rolling contact portion of the roller pin 54 with respect to the peripheral surface of the cylinder chamber 60,
Leakage easily occurs from the peripheral surface and upper and lower end surface portions of the roller pin 54 with respect to the notch groove 53, the overlapping surface of the seal plate 55 and the thrust plate 57 with respect to the upper and lower end surfaces of the pump cylinder 56, and the like.

Therefore, by suppressing an excessive amount of oil supply when the rotary shaft 23 rotates at a high speed, as shown by the change A in FIG. The rate of increase of a certain pump oil discharge amount is reduced.

On the other hand, in the oil supply pump device having the conventional structure, as shown by a change B in the figure, the oil discharge amount increases linearly with the increase of the rotation speed, which causes various problems described above. Occurrence will occur. Although the discharge passage 52 is provided in the rotary shaft 23 in the above embodiment, it may be replaced with the oil guide groove 20 provided in the conventionally used fixed plate 9, for example.

Although the scroll compressor is applied as the hermetic compressor, the compressor is not limited to the compressor provided with this type of compression system. It can also be used in compressors that compress other types of compressed gas or air.

[0060]

As described above, according to the first invention,

A pump cylinder having a cylinder chamber eccentric to the axis of the rotary shaft, a seal plate closing one end opening surface of the cylinder chamber, and a rotary shaft tip end surface closing the other end opening surface of the pump cylinder. Thrust plates that slide in contact with each other, roller pins, etc. are the components of the oil supply pump device, and the structure is simple with a smaller number of parts, workability and assembly are improved, and reliable oil supply is achieved. This has the effect of improving refueling efficiency. According to the second invention, the oil supply passage is provided along the axial direction from the end face of the tip end portion of the rotating shaft,
Since the discharge passage communicates with the oil supply passage and is provided along the radial direction from the peripheral surface of the rotating shaft,

At the time of high speed rotation of the rotary shaft, a strong centrifugal force is generated by the discharge passage to increase the pressure in the cylinder chamber so that the sliding contact portion is liable to leak, and the amount of oil supply is suppressed to minimize the oil sump portion. This has the effect of reducing the oil level and the amount of oil discharged to the outside, and improving reliability.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a scroll compressor showing an embodiment of the present invention.

FIG. 2A is a vertical cross-sectional view of an oil supply pump device of the same embodiment. FIG. 3B is an exploded perspective view of the oil supply pump device of the embodiment.

FIG. 3 is a view for sequentially explaining the pump action of the same embodiment.

FIG. 4 is a diagram comparing the oil supply characteristics of the pump device of the present invention and a pump device of a conventional structure.

FIG. 5A is a vertical cross-sectional view of an oil supply pump device showing a conventional example of the present invention. FIG. 6B is an exploded perspective view of the oil supply pump device of the conventional example.

[Explanation of symbols]

23 ... Rotating shaft, 27 ... Electric motor part, 24 ... Compression mechanism part, 2
1 ... Airtight case, 47 ... Oil sump, 60 ... Cylinder chamber,
56 ... Pump cylinder, 55 ... Seal plate, 57 ... Thrust plate, 62 ... Oil suction part, 53 ... Notch groove, 54 ... Roller pin, 52 ... Discharge passage, 51 ... Oil supply passage.

Claims (2)

[Claims] 1. An oil supply pump device for a compressor, wherein an electric motor section and a compression mechanism section, which are connected to each other via a rotary shaft, are housed in a sealed case. A pump cylinder having a cylinder chamber formed eccentrically with respect to the axial center of the rotary shaft so that a part of the peripheral surface of the rotary shaft is always in rolling contact with a constant portion; and the cylinder chamber provided on one end surface of the pump cylinder. A seal plate for closing one end opening surface of the pump cylinder, a thrust plate provided on the other end surface of the pump cylinder for closing the other end opening surface of the cylinder chamber and in sliding contact with the tip end surface of the rotating shaft, and provided on the thrust plate. An oil suction portion that opens into the lubricating oil of the oil sump portion, a notch groove that is radially provided from the outer peripheral surface at a portion of the rotating shaft that faces the cylinder chamber, and a notch groove that is displaceably engaged with the notch groove for rotation. axis A roller pin that abuts the circumferential surface of the cylinder chamber by the centrifugal force acting with rotation to partition the cylinder chamber and sucks the lubricating oil in the oil sump from the oil suction part into the cylinder chamber, and the reduction of the cylinder chamber capacity. Due to the increase in pressure due to
An oil supply pump device for a compressor, comprising: a discharge passage that guides the lubricating oil in the cylinder chamber by pressure; and an oil supply passage that guides the lubricating oil that is sent from the discharge passage to the compression mechanism section. 2. The oil supply passage is provided along an axial direction from an end surface of a tip end portion of a rotary shaft, and the discharge passage communicating with the oil supply passage is provided along a radial direction from a peripheral surface of the rotary shaft. The oil supply pump device in the compressor according to claim 1.