JPH10141256A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor capable of always securing the sufficient amount of supplying oil and capable of improving reliability of a driving bearing without enlarging a device and without increasing manufacturing cost. SOLUTION: In a scroll compressor, a compression chamber is formed by engaging a lap part of a fixed scroll with a lap part 22 of a turning scroll which are so arranged as to be faced to each other. A turning bearing and a drive bush are fitted in a space in a boss part 24 provided on the back surface of an end plate 21 of the turning scroll on the opposite side to the fixed scroll, a crank part of the driving shaft is connected to the drive bush, the turning scroll is revolved, the compression chamber is moved to the center parts of the fixed scroll and the turning scroll while decreasing the capacity with the revolution of the turning scroll, and gas is compressed. An oil supplying passage 60 communicated with the space part in the boss part 24 from the high compression range of the compression chamber is formed on the end plate 21 of the turning scroll.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001] The present invention relates to a scroll compressor, and more particularly to an oil supply structure for a bearing of an orbiting scroll.

[0002]

2. Description of the Related Art Generally, in the case of a so-called car air conditioner, a scroll compressor includes a housing, a fixed scroll fixed in the housing, a drive shaft having a crank portion, and a drive bearing mounted on the crank portion. And a revolving scroll that is rotatably provided through the main body.
A spiral wrap portion extends from one surface of the end plate or end plate of the orbiting scroll toward the fixed scroll, and the wrap portion meshes with a similar wrap portion provided on the fixed scroll to define a compression chamber, and the orbiting scroll When turning, the wrap portions cooperate to perform a compression operation. A boss is extended on the other surface of the end plate of the orbiting scroll, and a crank is fitted to the drive bearing in the boss.

[0003] As far as the present inventors know, the lubrication of the drive bearing is self-lubricated by adhering mist-like oil sucked and discharged by the compressor and mixed into the refrigerant circulating in the refrigeration system to the drive bearing. It is a method.

On the other hand, in scroll compressors for residential and commercial refrigeration systems, an oil supply pump is provided at an end of a drive shaft, and lubricating oil is provided inside the drive shaft by the oil supply pump. It is sent to the drive bearing through the passage in a forced lubrication system.

[0005] Further, as a scroll compressor in which a fine-diameter hole is provided in the end plate of the orbiting scroll and the spaces (compression chamber, back pressure chamber) on both sides of the end plate are communicated, for example,
JP-A-5-149270, JP-A-2-30899
No. 2 and JP-A-58-67983 are known.

However, the fine-diameter hole in the end plate described in Japanese Patent Application Laid-Open No. 149270/1993 makes the compression chamber between the wrap portions of the fixed scroll and the orbiting scroll a back pressure chamber at the back of the end plate of the orbiting scroll. The back pressure chamber is set to a high pressure, and the high pressure presses the orbiting scroll against the fixed scroll to seal the compression chamber.
Does not teach lubrication of drive bearings,
In any case, there is no suggestion about lubrication of the drive bearing by the fluid passing through the fine hole.

Next, a fine-diameter hole (back pressure introducing hole) in the head plate described in Japanese Patent Application Laid-Open No. 2-3088992 guides fluid in the compression chamber to the back pressure chamber, and thrusts on the back of the head plate of the orbiting scroll. Direction pressing force is applied, and is only substantially the same as the hole described in JP-A-5-149270. In the scroll compressor disclosed in Japanese Patent Application Laid-Open No. Hei 2-3088992, a orbiting bearing for a drive shaft of an orbiting scroll is disclosed. A seal ring is interposed between the orbital bearing and a back pressure chamber. It does not even suggest lubrication of the drive bearing by fluid passing through the diameter hole.

Finally, in the scroll compressor described in Japanese Patent Application Laid-Open No. 58-67983, a fine-diameter hole is radially formed in the end plate of the orbiting scroll (FIGS. 1 to 3). FIG. 3), the lubrication system of this scroll compressor is essentially forced lubrication, and the holes allow the fluid in the compression chamber between the wrap portions of the fixed scroll and the orbiting scroll to pass through the back of the orbiting scroll head plate on the back side. Not leading to the pressure chamber.

[0009]

A self-lubricating system in which mist-like oil mixed in a refrigerant circulating in a refrigeration system adheres to a bearing to supply oil tends to be insufficient in the amount of oil supplied, and therefore, the heat generated in the bearing is reduced. In the high-speed operation region where the amount is large, it may lead to damage of the bearing. The forced lubrication system can secure a sufficient amount of oil to be sent to the drive shaft.However, it is necessary to provide an oil supply pump and to form a passage in the drive shaft to guide oil to the drive bearing. Instead, the manufacturing cost increases. Accordingly, an object of the present invention is to provide a scroll compressor that can always secure a sufficient amount of lubrication and increase the reliability of a drive bearing without inviting an increase in the size of the device and an increase in manufacturing cost. It is.

[0010]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a compression chamber formed by engaging wrap portions of a fixed scroll and an orbiting scroll which are arranged to face each other. A revolving bearing and a drive bush are fitted in a space inside a boss provided on the back side of the end plate of the revolving scroll on the opposite side, and a crank portion of a drive shaft is connected to the drive bush to revolve the revolving scroll. A scroll compressor that drives and moves the compression chamber to the center of the fixed scroll and the orbiting scroll while reducing the volume of the orbiting scroll with the orbital driving of the orbiting scroll, thereby compressing gas.
In the end plate of the orbiting scroll, an oil supply passage communicating from the high compression region of the compression chamber to the space in the boss portion is formed.

It is preferable that the oil supply passage has a communication hole having a diameter of about 0.2 mm or less in order to prevent a decrease in compressor performance.

An insert comprising a core portion and a ring surrounding the core portion is fixed in the oil supply passage, and the core portion and the ring have a gap between their threads and valleys for oil supply. If the lubrication passage is formed into a slant with a small diameter, the drill will not break, and the size of the gap and its length can be changed. It is preferable that the optimum refueling amount can be easily secured. Further, in order to prevent the drill from being broken even when the processing of the oil supply passage is performed with a slanting process having a small diameter, an insert having a flow control oil supply hole may be fitted into the oil supply passage. In this case, since the aperture can be manufactured as a separate part, it is possible to easily realize an aperture having an optimum diameter.) In the oil supply passage, a female screw to be screwed into an insert having an external thread is formed. The insert and the internal thread may be screwed together with a gap for refueling between their threads and valleys.

The oil supply passage is provided with an oil supply valve urged by urging means toward the compression chamber side, and an insert having a valve seat and a flow control oil supply hole. When the oil supply valve reaches a predetermined size exceeding the urging force of the urging means, the oil supply valve is seated on the valve seat and the oil supply hole for flow rate control is closed to ensure reliability and performance. It is preferable from the viewpoint of compatibility. That is, the discharge pressure of the compressor increases at the time of high heat load requiring performance. When the pressure exceeds a certain set pressure, the oil supply valve closes the oil supply hole, stops the bypass of the discharge gas from the high pressure region of the compression chamber to the suction side, and prevents performance degradation. In this case, it is preferable that the refueling valve is a ball type refueling valve having a ball seated on the valve seat and closing the flow rate control refueling hole.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a preferred embodiment of the present invention will be described with reference to the accompanying drawings.
In the drawings, the same reference numerals indicate the same or corresponding parts.
FIG. 1 is a longitudinal sectional view showing an example of a scroll compressor for a car cooler, for example, in which an oil supply structure for a drive bearing is incorporated according to an embodiment of the present invention. In the figure,
Reference numeral 1 denotes a closed housing, which comprises a cup-shaped main body 2, a cover 4 fastened to the main body by bolts 3, and a tubular member 6 fastened to the main body by bolts (not shown). The drive shaft 7 that penetrates the cylindrical member 6 as shown in the drawing,
It is rotatably supported by the tubular member 6 of the sealed housing 1 via bearings 8 and 9.

A fixed scroll 10 and an orbiting scroll 20 are provided in the closed housing 1. The fixed scroll 10 includes an end plate 11 fastened to the cup-shaped main body 2 by bolts 13, and a spiral wrap portion 12 erected on the inner surface facing the orbiting scroll 20. The inside of the sealed housing 1 is partitioned by bringing the outer peripheral surface of the end plate 11 into close contact with the inner peripheral surface of the cup-shaped main body 2, and a high-pressure chamber 30 is defined on the outer surface side of the end plate, and on the inner surface side of the end plate. Defines a low pressure chamber 31. On the other hand, a suction chamber 32 and a discharge chamber 33 are formed at the joint between the cover 4 and the cup-shaped main body 2. The high-pressure chamber 30 communicates with the discharge chamber 33 through a passage (not shown), and the low-pressure chamber 31 is Inhalation chamber 3
It communicates with 2. A discharge port 14 is formed in the center of the end plate 11, and the discharge port 14 is opened and closed by a discharge valve 15.

The orbiting scroll 20 has an end plate 21 and a spiral wrap portion 22 erected on the inner surface facing the fixed scroll 10.
It is eccentric with respect to the center axis of 0 by an amount corresponding to the turning radius. The wrap portion 22 has substantially the same shape as the wrap portion 12 of the fixed scroll 10, and the wrap portions 1
2 and 22 are in mesh with each other as is well known. The tip seal 23 buried in the tip end surface of the wrap portion 22 is
1, the tip seal 16 buried in the tip end surface of the wrap portion 12 is in close contact with the inner surface of the end plate 21. Thus, the side surfaces of the wrap portions 12 and 22 come into line contact at a plurality of locations and spiral A plurality of compression chambers 19a and 19b which are substantially point-symmetrical with respect to the center of are defined.

A drive bush 25 is rotatably fitted via a slewing bearing 26 inside a cylindrical boss 24 projecting from the center of the outer surface of the end plate 21. The crank part 27 is slidably fitted. It is preferable to attach a balance weight 28 to the drive bush 25 to balance dynamic imbalance due to the orbiting movement of the orbiting scroll.

Reference numeral 29 denotes a rotation preventing mechanism comprising an Oldham ring for allowing the orbiting movement of the orbiting scroll 20 and preventing its rotation. A rotation preventing mechanism 36 comprises an outer peripheral edge of the Oldham ring 29 and an inner surface of the cylindrical member 6. The thrust bearing 35 interposed therebetween is a balance weight appropriately fixed. Reference numeral 50 denotes a relief valve which discharges gas from the holes 51 and 54 to the outside of the compressor when the gas pressure in the discharge chamber 33 increases due to the force of the spring 53 pressing the valve body 52. During normal operation in which the gas pressure is lower than the force of the spring 53, the valve body 52 is closed. Reference numeral 56 denotes an O-ring for connecting the relief valve 50 to the cover 4 without gas leakage. 55, when the gas pressure in the discharge chamber 33 rises abnormally, the valve body 52 opens, and gas is ejected to the outside from the hole 54,
3 shows a cover for blocking gas flow and diffusing in all directions.

In operation, the power from the traveling engine (not shown) is transmitted to the drive shaft 7 via the belt 38 and the electromagnetic clutch 37 by joining the electromagnetic clutch 37. When the drive shaft 7 rotates, the orbiting scroll 20 is driven via an orbiting drive mechanism including a crank portion 27, a drive bush 25, a boss portion 24, and the like, and the orbiting scroll 20 is prevented from rotating by an anti-rotation mechanism 29. In addition, it makes a revolving motion on a circular orbit whose radius is the eccentric distance between the drive shaft 7 and the axis of the crank part 27. As a result, since the line contact portions on the side surfaces of the wrap portions 12 and 22 gradually move toward the center of the spiral, the compression chambers 19a and 19b move toward the center of the spiral while reducing their volume, thereby defining a high-pressure region. . Accordingly, gas flowing into the low-pressure chamber 31 from the suction port (not shown) via the suction chamber 32 is
22 is taken into the compression chambers 19a and 19b from the opening at the outer peripheral end, returns to the central chamber 19c while being compressed, and pushes the discharge valve 15 through the discharge port 14 to open the discharge valve 15 to discharge into the high-pressure chamber 30. After passing through the chamber 33, it flows out through a discharge port (not shown).

During the orbiting movement of the orbiting scroll 20, a centrifugal force toward the eccentric direction of the orbiting scroll and a gas force due to the compressed gas in each of the compression chambers 19a and 19b act. By the force, the orbiting scroll 20 is pushed in the direction in which the orbiting radius increases, and the side surface of the wrap portion 22 is fixed to the wrap portion 1 of the fixed scroll 10.
2. The gas leaks from the compression chambers 19a and 19b in close contact with the side surfaces of the compression chambers 19a and 19b. Then, as the side surface of the wrap portion 12 and the side surface of the wrap portion 22 slide in close contact with each other, the turning radius of the orbiting scroll 20 automatically changes, and accordingly, the crank portion 27 moves inside the drive bush 25. To slide.

Now, according to the first embodiment of the present invention,
The end plate 21 of the orbiting scroll 20 includes the compression chamber 1 described above.
Space 24 defined by 9a, 19b and boss 24
The fuel supply passage 60 is formed so as to communicate with a. FIG. 2 shows the orbiting scroll 20 having the oil supply passage 60 alone, and FIG. 3 shows the details of the portion A in FIG.

2 and 3, the oil supply passage 60 is
It is preferable to machine by a drill (not shown). For the convenience of the machining, one end of the oil supply passage 60 is formed by a cylindrical space 24 defined by the boss 24 of the orbiting scroll 20.
An opening is provided at a predetermined position on the periphery of the bottom of a, and the other end of the oil supply passage 60 is opened to the above-described compression chambers 19a and 19b.

With reference to the position where the one end of the oil supply passage 60 is open as shown in FIGS. 2 and 3, the range of the position where the other end of the oil supply passage 60 can be opened to the compression chamber will be described. The outermost point 60a on the back surface 22a side of the wrap portion 22 is indicated by oblique lines shown in FIG.
It is determined by the longitudinal axis 60b of 0 and is obtained from the following equation. θ = tan ⁻¹ (D / L) R = t · tan θ where D is the inner diameter of the boss 24, L is the axial length of the space 24 a defined by the boss 24, and t is the wrap 2
2 and the inner surface of the end plate of the orbiting scroll 20 and the space 24
a is the axial length from the bottom of the space a to the vertical distance from the lowermost surface of the space 24a to the point where the axis 60b intersects the inner surface of the end plate 21 (ie, 60a); 60
b is the angle made with respect to the horizontal plane. That is, a locus LO drawn with a radius [(D / 2) + R] separated by a distance R from the inner peripheral surface 24b of the boss portion 24 indicated by a dotted line in FIG. 4 and the back surface 22a of the wrap portion 22 of the orbiting scroll 20 The intersection 60a is obtained as a limit point at which processing is possible. On the other hand, the processing limit on the abdominal surface 22b side of the lap portion 22 is obtained as an intersection 60c between the inner peripheral surface 24b of the boss portion 24 and the abdominal surface 22b. Therefore, the processable range of the position where the other end of the oil supply passage 60 is open is from the intersection 60a to the center to the intersection 60c.

Since the oil supply passage 60 must be machined obliquely, it is necessary to use a drill having a sufficient length so that a drill holder (not shown) does not interfere with the wall of the boss portion 24. In order to prevent the performance of the compressor from being substantially reduced due to the drilling of the oil supply passage 60, the diameter of the oil supply passage needs to be approximately 0.2 mm or less. If such a condition is to be satisfied, the drill diameter may be reduced and breakage may occur, which may not be suitable for mass production of the orbiting scroll.

Therefore, in the first embodiment of the present invention,
As best shown in FIG. 3, the oil supply passage 60 includes an inner small-diameter portion 60A, an outer large-diameter portion 60B, and a conical portion 60C connecting both portions. Part 4
1 and an insert 40 comprising a ring 42 surrounding the core
Is housed. With this configuration, the length of the small-diameter portion 60A can be reduced as much as possible without reducing the diameter of the small-diameter portion 60A to 0.2 mm, and the drill can be prevented from being broken. . In this embodiment, the core portion 41 is screwed to the ring 42, and the ring 42 can be fixed to the large diameter portion by appropriate means such as press fitting or bonding.

As can be seen from the threaded state of the core 41 and the ring 42 shown in FIG. 5, a moderately designed cross-sectional area (small diameter of 0.2 mm or less) is provided between each thread and valley. ) Is provided, and suitable lubrication of the bearing can be performed without deteriorating the performance of the compressor. In addition, a slot 41a is formed in the outer end surface of the core portion 41 so that the core portion 41 can be easily attached and detached. The average diameter of the coil-shaped gap g is smaller than the maximum outer diameter of the conical portion 60C in this embodiment. Therefore, the discharge gas that has passed through the small diameter portion 60A flows into the space portion 24a defined by the boss portion 24 via the gap g, and reliably lubricates the swing bearing 26 (see FIG. 1).

Next, in the second embodiment shown in FIG. 7, instead of the insert 40, an appropriate method such as press-fitting or bonding is performed in the large-diameter portion 60B of the oil supply passage 60 so as not to leak from the outer periphery. A ring 43 which can be fixed by means is inserted. The ring 43 has a small diameter portion 60A of the oil supply passage.
A smaller throttle or oil supply hole 43a having a diameter of about 0.2 mm is formed in part. The oil supply hole 43a does not need to have a uniform diameter from the end face to the end face of the ring,
As shown in the figure, the outside can be expanded so that the whole is funnel-shaped.

In the third embodiment shown in FIG. 8, a female screw portion 71 is formed at the outer end of the oil supply passage 70 itself consisting of only a large diameter portion.
Are formed, and a disk-shaped insert 72 is screwed into the female screw portion 71. 72a is a slot for facilitating attachment and detachment of the insert 72. There is a gap (not shown) similar to the gap shown in FIG. 5 between the female threads and the threads and valleys of the insert to allow controlled passage of lubricating oil.

FIG. 9 shows a fourth embodiment. In this embodiment, the oil supply passage 80 includes a compression chamber-side small-diameter portion 80A, an intermediate-diameter portion 80B including a conical seating surface, and a large-diameter portion 80C. A ball 81 is provided to be brought into contact with the conical seat surface by a coil spring (biasing means) 82, and a large diameter portion 80C has an oil supply hole 83a for adjusting or reducing the flow rate and a valve seat 83b. A disk-shaped insert 83 is inserted. The insert 83 is screwed into the large diameter portion 80C,
It is fixed by appropriate means such as press-fitting or bonding.

In general, a condition requiring performance is a high heat load and a low speed operation (idle operation or the like). At this time, the discharge pressure of the compressor increases. In this case, the compression chambers 19a,
The pressure at 19b increases, and the pressure in the space 24a defined by the boss also increases, but the pressure difference increases.
Therefore, when the force due to the pressure difference applied to the ball 81 overcomes the force due to the coil spring 82, the ball 81
b to close the oil supply hole 83a to prevent oil and refrigerant gas from bypassing.

On the other hand, the discharge pressure does not increase as described above in the intermediate load, high to medium speed operation range.
The magnitude of the differential pressure due to the compressed gas applied to the first and second balls is medium to small, the ball 81 moves to a position balanced with the force of the coil spring 82, and the small diameter portion 80A of the oil supply passage and the insert 8
3 is in communication with the oil supply hole 83a, and the compression chambers 19a,
Oil is bypassed to the space portion 24a together with the compressed refrigerant gas in 19b, and lubrication of the slewing bearing is performed. Thus, at the time of high heat load where performance is required, performance is not reduced,
Refuel if necessary.

Although the preferred embodiment of the present invention has been described above, the scope of the present invention is not limited to the embodiment and can include various modifications. For example,
In the embodiment, only one oil supply passage is formed in the end plate of the orbiting scroll, but a plurality of oil supply passages may be provided.
Also, for example, in the embodiment of FIG.
Instead of 3a, a plurality of refueling holes may be formed. Further, in the embodiment of FIG. 8, a gap formed in a threaded portion between the female screw portion 71 and the insert 72 is not used as a refueling passage. The threaded portion has a tight fastening structure with substantially no gap.
One or more lubrication holes may be formed.

[0033]

According to the first, second and fifth aspects of the present invention, the end plate of the orbiting scroll is provided with an oil supply passage communicating from the high compression region of the compression chamber to the space in the boss. Because of the perforation, a sufficient amount of lubrication can always be ensured and the reliability of the drive bearing can be increased without incurring an increase in the size of the device and an increase in manufacturing cost. According to the present invention as set forth in claims 3 to 5, a gap for refueling is formed between the thread and the valley of the core and the ring of the insert fixed in the refueling passage, so that the refueling passage is formed. The drill does not break even if the process is a small-diameter diagonal process, and if the size of the gap and the length thereof are changed, the optimum amount of lubrication can be easily secured. Furthermore, when an insert having a flow control oil supply hole is fitted into the oil supply passage as in the present invention as described in claim 4, a throttle can be manufactured as a separate part, so that the throttle having the optimum diameter can be easily manufactured. Can be realized.

Generally, the condition that the performance of the compressor is required is a high heat load and a low speed operation (idle operation or the like). At this time, the discharge pressure of the compressor increases. According to the present invention as set forth in claim 6 and claim 7, the fuel supply passage has a fuel supply valve urged by the urging means toward the compression chamber side, and a valve seat and a flow control oil supply hole. When the pressure in the compression chamber exceeds the urging force of the urging means, the lubrication valve is seated on the valve seat to close the flow control lubrication hole. When the discharge pressure of the compressor rises and exceeds a certain set pressure, the refueling valve closes the refueling hole, stops the bypass of the discharge gas from the high-pressure area of the compression chamber to the suction side, prevents performance degradation and ensures reliability Can be achieved.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing the entire structure of a scroll compressor having an oil supply structure according to a first embodiment of the present invention.

FIG. 2 is a sectional view of a single orbiting scroll used in the scroll compressor of FIG. 1;

FIG. 3 is an enlarged cross-sectional view showing a region indicated by reference numeral A in FIG.

FIG. 4 is a side view of FIG. 2 viewed from the left side, for explaining an opening range of an oil supply hole to the orbiting scroll.

FIG. 5 is a partially enlarged cross-sectional view for explaining a screwed state of members constituting an insert inserted into the oil supply passage of FIG. 2;

FIG. 6 is a partial cross-sectional view for explaining the above-described opening range of the oil supply hole to the orbiting scroll.

FIG. 7 shows a refueling structure according to a second embodiment of the present invention.
FIG.

FIG. 8 is a diagram illustrating a fuel supply structure according to a third embodiment of the present invention;
FIG.

FIG. 9 is a diagram illustrating a fuel supply structure according to a fourth embodiment of the present invention;
FIG.

[Explanation of symbols]

Reference numeral 72: drive shaft, 10: fixed scroll, 12: fixed scroll wrap, 19a, 19b: compression chamber, 20: revolving scroll, 21: revolving scroll end plate, 22: revolving scroll wrap, 24: boss , 24a: space defined by the boss, 25: drive bush,
26 ... Slewing bearing, 27 ... Crank part of drive shaft, 40 ... Insert, 41 ... Core part, 42 ... Ring, 43 ... Insert, 43a ... Oil supply hole (communication hole), 60 ... Oil supply passage, 70
... refueling passage, 71 ... female screw part, 72 ... insert, 80
... refueling passage, 81 ... ball (refueling valve), 82 ... coil spring, 83 ... insert, 83a ... refueling hole, 83b ... valve seat, g ... gap.

Claims (7)

[Claims] 1. A boss portion provided on a back surface of an end plate of the orbiting scroll opposite to the fixed scroll while engaging a wrap portion of the fixed scroll and the orbiting scroll arranged opposite to each other to form a compression chamber. A revolving bearing and a drive bush are fitted in the space of the drive bush, a crank portion of a drive shaft is connected to the drive bush, and the revolving scroll is driven to revolve and revolve. In a scroll compressor, which moves a chamber to the center of the fixed scroll and the orbiting scroll while reducing the volume thereof to compress gas, the end plate of the orbiting scroll includes a high compression area of the compression chamber and an inside of the boss portion. Wherein a fuel supply passage communicating with the space is formed. 2. The scroll compressor according to claim 1, wherein the oil supply passage has a communication hole having a diameter of 0.2 mm or less. 3. An insert comprising a core portion and a ring surrounding the core portion is fixed in the oil supply passage, and the core portion and the ring are provided with a gap for refueling between their threads and valleys. The scroll compressor according to claim 1, wherein the scroll compressor is screwed together. 4. The scroll compressor according to claim 1, wherein an insert having a flow control oil supply hole is fitted into said oil supply passage. 5. The oil supply passage is machined with a female screw that is screwed into an insert having a male screw, and the insert and the female screw have a gap between their threads and valleys for oil supply. The scroll compressor according to claim 1, wherein the scroll compressor is screwed together. 6. An oil supply valve urged by urging means toward the compression chamber side, and an insert having a valve seat and a flow control oil supply hole are provided in the oil supply passage,
2. The oil supply valve according to claim 1, wherein the oil supply valve is seated on the valve seat when the pressure in the compression chamber reaches a predetermined value exceeding the urging force of the urging means, thereby closing the oil supply hole for flow control. The scroll compressor as described. 7. The scroll compressor according to claim 6, wherein the refueling valve is a ball type refueling valve having a ball seated on the valve seat and closing the flow rate control refueling hole.