JP3206219B2 - Scroll fluid machine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll fluid machine, and more particularly, to a casing having a pair of scrolls on one side in the longitudinal direction of a casing and a motor mounted on the other side. The present invention relates to a scroll fluid machine that supports one side and supports the other side in the axial direction of the drive shaft on the side opposite to the scroll of the motor.

[0002]

2. Description of the Related Art Generally, in this kind of scroll fluid machine, at least one axial side of a drive shaft extending from a motor is supported by a rolling bearing including an inner ring, an outer ring, and a rolling element. At this time, the outer ring is fixedly supported by a bearing member provided in a casing, and the inner ring is fitted to an outer peripheral portion of the drive shaft. However, in order to smoothly roll the rolling element between the inner and outer rings, the above-mentioned rolling bearing is provided with a slight rolling gap between the inner and outer rings and the rolling element. When the shaft is moved in the axial direction, the inner race follows the drive shaft, and accordingly, the rolling element is moved within the range of the rolling gap and collides with the inner and outer races. There was a sound.

In order to prevent the occurrence of the above-mentioned abnormal noise, Japanese Patent Laid-Open Publication No. 3-149381 has conventionally proposed a technique described in FIG. An inner race E1 and an outer race E2 are provided between an upper side of a drive shaft C extending in a vertical direction from a motor B disposed in a closed casing A and a bearing member D fixed to an inner upper side of the casing A. Rolling bearing E composed of rolling element E3
, A wave washer F is disposed on the inner ring E1 side, and a floating suppression plate G is provided above the rolling bearing E.
Specifically, a small diameter portion is formed on the upper end side of the drive shaft C,
The inner ring E1 is loosely inserted into the outer peripheral portion of the small diameter portion of the drive shaft C,
Further, the outer ring E2 is inserted and fixed in a bearing hole of the bearing member D, and the drive shaft C is provided below the inner ring E1.
The wave washer F that constantly pushes the inner race E1 upward with respect to the outer race E2 is disposed on the stepped surface formed by the small-diameter portion of the rolling member E, while the rolling bearing E is disposed on the bearing member D. Above, there is provided a floating suppression plate G that prevents the drive shaft C from moving abnormally in the upward direction and prevents the rolling bearing E from being damaged by abnormal pressing of the wave washer F, that is, Assuming that the initial clearance between the suppression plate G and the upper end of the drive shaft C is T1, and that the elastic deflection of the wave washer F is T2, the elastic deflection T2 is smaller than the limit pressing amount. The initial clearance amount T1 is set so as to be small, and only the axial movement of the drive shaft C over the range of the initial clearance amount T1 is allowed, and the elastic deflection amount at which the drive shaft C becomes the limit pressing amount is set. T2 It is to be prevented from moving in the axial direction I.

According to the above construction, the inner race E1 is constantly pushed upward by the wave washer F with respect to the outer race E, and accordingly the rolling element E3 is moved below the rolling groove in the inner race E1. Since the side edge and the upper edge of the rolling groove in the outer race E2 are in contact with each other, the inner and outer races E1, E2 and the rolling element E3 are always kept in contact with each other. Even when the axis C moves in the axial direction, no collision occurs between the rolling element E3 and the inner and outer races E1 and E2, and the generation of abnormal noise due to the collision of these persons can be prevented. In addition, the initial clearance T1 between the suppression plate G and the upper end of the drive shaft C is set to be smaller than the elastic deflection T2 which is the limit pressing amount of the wave washer F. When the drive shaft C moves in the axial direction, Prior to attempting to move beyond the limit pressing amount T2 Sha F, the drive shaft C is brought into contact with the suppression plate G, the limit pressing amount of the wave washer F T2
Therefore, it is possible to prevent the axial movement of the drive shaft C beyond the above. Therefore, it is possible to prevent the rolling bearing E from being damaged, and to exert the effect of preventing the rolling bearing E from generating abnormal noise.

In order to lubricate the rolling bearing E, a scroll-type compression element (not shown) that is driven to rotate by the drive shaft C is provided at a lower portion inside the casing A.
The gas compressed by the compression element is discharged to the upper side of the motor B via an air gap of the motor B, and the discharged gas is further discharged to the inside of the rolling bearing E, between the outer rings E1, E2, and Discharge hole D provided in the bearing member D
1 to the discharge space A1 defined by the bearing member D on the inner upper side of the casing A.
When the discharge gas passes through the rolling bearing E so as to be discharged to the outside from the discharge pipe A2 opened at 1, the lubricating oil contained in the discharge gas is supplied to the rolling bearing E, and the bearing E Lubrication.

[0006]

However, according to the above arrangement, when the scroll fluid machine is transported, when the drive shaft C is moved in the axial direction due to vibration or the like, this drive is performed. Although the axis C is not moved upward by the presence of the suppression plate G by more than the critical compression amount of the wave washer F, the repulsive force of the wave washer F is caused by the movement of the wave washer F in the axial direction of the drive shaft C. That is, since the spring force fluctuates, the pressing force applied to each component of the rolling bearing E also fluctuates. Therefore, when a large pressing force acts while fluctuating, the inside of the rolling bearing E is easily damaged.

Further, during operation of the scroll fluid machine, the rotor of the motor B supporting the drive shaft C is lifted upward by the discharge gas discharged from the compression element, whereby the drive shaft C is also moved upward. However, since the flying height of the rotor due to the discharge gas varies depending on the operating conditions of the scroll fluid machine,
The amount of movement of the drive shaft C upward also fluctuates,
Therefore, the spring force of the wave washer F changes according to the operating condition due to the change of the movement amount of the drive shaft C, and accordingly, the pressing force of the inner ring E1 against the rolling element E3 also changes. There is also a problem that the rolling resistance of the rolling element E3 with respect to the inner and outer rings E1 and E2 fluctuates, and the bearing performance of the drive shaft C by the rolling bearing E becomes unstable. In addition, in order to prevent the rolling bearing E from being damaged by abnormal pressing by the wave washer F, it is necessary to separately provide a floating suppression plate G for preventing the drive shaft C from moving in the axial direction over a predetermined amount. However, there was a problem that the number of parts increased accordingly. In addition, the lubrication of the rolling bearing E is performed when the discharge gas passes through the rolling bearing E by lubricating oil mixed in the discharge gas discharged from the compression element. When the amount of gas discharged from the compression element fluctuates, the amount of oil supplied to the bearing E also fluctuates. Therefore, stable lubrication to the bearing E cannot be performed. The amount of lubrication to the bearing E is also reduced, which may cause poor lubrication of the bearing E.

An object of the present invention is to use a lubricating oil pumped into a lubrication passage of a drive shaft without using a conventional wave washer or a floating suppression plate, etc., so that each part of a rolling bearing collides. While preventing generation of abnormal noise, these parts are not damaged, and also, regardless of operating conditions, it is possible to stably support the drive shaft with the rolling bearing, Moreover, it is another object of the present invention to provide a scroll fluid machine capable of constantly supplying a constant amount of lubricating oil to the rolling bearing and performing stable lubrication of the bearing.

[0009]

In order to achieve the above object, according to the first aspect of the present invention, a pair of scrolls 2 and 3 are provided on one side in a longitudinal direction of a casing 1 and a motor 5 is provided on the other side. The drive shaft 4 is provided on the scroll side of the motor 5.
A first bearing housing 5 for supporting one side in the axial direction of the motor, and a second bearing housing 8 for supporting the other side in the axial direction of the drive shaft 4 on the side opposite to the scroll of the motor 5. , An oil supply pump 17 for supplying oil to an oil supply passage 15 of the drive shaft 4 is provided at the other axial end of the drive shaft 4, and the second bearing housing 8 is provided.
A rolling bearing 14 having an inner ring 14a, an outer ring 14b, and a rolling element 14c; fixing the outer ring 14b in a bearing hole 8a of the second bearing housing 8;
4a is held movably in the axial direction with respect to the drive shaft 4,
A pressure chamber 18 communicating with the discharge side of the oil supply pump 17 and pressing the inner race 14a against the outer race 14b on the scroll side is provided on the back surface of the rolling bearing 14 on the side opposite to the scroll.

Further, in the invention described in claim 2, the rolling bearing 14 is provided with a shielding plate 14d for covering an annular gap S between the inner ring 14a and the outer ring 14b.

[0011]

According to the first aspect of the present invention, the oil supply pump 17 is provided.
The lubricating oil pumped in the pressure chamber 18 is introduced into the pressure chamber 18, and the lubricating oil introduced into the pressure chamber 18 is axially movably inserted into the drive shaft 4 of the inner race 14 a of the rolling bearing 14.
Is applied to the inner ring 1 as a back pressure.
4a is pressed to the scroll side against the outer ring 14b, and the rolling element 14c is brought into contact with the pressing-side rear edge of the rolling groove in the inner ring 14a and the front-side edge of the rolling groove in the outer ring 14b. . Therefore, these inner and outer rings 14
a, 14b and the rolling elements 14c can be kept in a constant contact state. Therefore, even when the driving shaft 4 moves in the axial direction, the rolling elements 14c and the inner and outer rings 14a, 1
No collision occurs between the inner ring 14a and the outer ring 14b, and the noise is always filled between the inner ring 14a and the outer ring 14b. Therefore, since the periphery of the rolling element 14c can be always covered with the lubricating oil, the rolling noise of the rolling element 14c can be reduced, and the generation of abnormal noise can be prevented more favorably.

In the above construction, the inner ring 14a is connected to the outer ring 1 by the elastic force of the wave washer as in the prior art.
4b, instead of being pressed against
The lubricating oil introduced into the pressure chamber 18 from the inner ring 14
a, and the amount of lubricating oil pumped by the oil supply pump 17 is always kept substantially constant irrespective of operating conditions.
4a, a stable pressing force is always applied, that is, the rolling resistance of the rolling element 14c with respect to the inner and outer rings 14a, 14b is always kept constant, and the rolling bearing 14 supports the driving shaft 4 stably. In addition, since no sudden load is applied to each part of the rolling bearing 14, it is possible to prevent each of these parts from being damaged.

Further, the lubricating oil pumped by the oil supply pump 17 is introduced into the pressure chamber 18, and the lubricating oil introduced into the pressure chamber 18 is used for the inner and outer races 14 of the rolling bearing 14.
a, lubrication of the rolling bearing 14 is performed, so that a constant amount of lubricating oil can always be supplied to the rolling bearing 14 irrespective of operating conditions and the like, so that the bearing 14 is stabilized. Lubrication can be performed.

According to the second aspect of the present invention, the rolling bearing 14 is provided with a shielding plate 14d for covering the annular gap S between the inner ring 14a and the outer ring 14b.
4d, the amount of oil leakage from the pressure chamber 18 to the outside can be reduced, that is, the lubricating oil supplied to the pressure chamber 18 can be maintained at a high pressure, and a large pressing force is applied to the inner ring 14a. As a result, generation of abnormal noise can be more reliably prevented.

[0015]

FIG. 3 shows a horizontal scroll compressor as a scroll fluid machine. A fixed scroll 2 having a scroll 2a and a scroll 2a of the fixed scroll 2 are provided on one longitudinal side of a horizontal casing 1. A movable scroll 3 having a spiral body 3a that meshes therein is provided therein, and a motor 5 having a drive shaft 4 for revolving the movable scroll 3 is provided on the other side in the longitudinal direction of the casing 1; A first bearing housing 6 is provided on the back side of the scroll 3 to support the scroll side of the drive shaft 4 via a bearing 6a in the bearing housing 6, and a first bearing housing 6 is provided between the bearing housing 6 and the movable scroll 3. Is provided with an Oldham coupling 7 that prevents the orbiting of the movable scroll 3 from rotating and revolves, while the anti-scroll side of the motor 5 is provided with:
A second bearing housing 8 for supporting the drive shaft 4 on the side opposite to the scroll is provided. Further, a suction pipe 10 is opened in a motor chamber 9 in which the motor 5 is housed to form a low-pressure dome shape for reducing the pressure in the motor chamber 9, and an image wall 11 is provided on the back side of the fixed scroll 2. A discharge chamber 12 which is disposed and communicates with the discharge port 2b of the fixed scroll 2;
The discharge pipe 13 is opened in the discharge chamber 12.

In the above-described scroll compressor, a small-diameter stepped portion 4a is formed at the shaft end of the drive shaft 4 projecting outside from the side opposite to the scroll of the motor 5, and the small-diameter stepped portion 4a and the (2) an inner ring 14a, an outer ring 14b, and a rolling element 14 between a bearing hole 8a provided in the bearing housing 8;
In this case, the inner ring 14a is inserted into the small step portion 4a of the drive shaft 4 so as to be movable in the axial direction, and the outer ring 14b is connected to the second bearing housing. 8 is fixedly held in the bearing hole 8a.

The small-diameter step portion 4a of the drive shaft 4
Extending axially outward from the distal end side of the small diameter step portion 4a,
An oil supply cylinder 16 having an oil supply passage 16a communicating with an oil supply passage 15 penetratingly formed inside the shaft center of the drive shaft 4 is mounted, and an oil supply pump 17 is provided on an outer peripheral portion of a distal end of the cylinder 16 to provide the oil supply pump. Pump oil from the oil supply passage 16
a to the space between the drive shaft 4 and the bearing 6 a of the first bearing housing 6 via the oil supply passage 15, and from the branch passage 6 b provided in the first bearing housing 6 to the first bearing housing. While lubricating the sliding surface between the movable scroll 6 and the movable scroll 3 and other lubrication points, the bearing hole 8a is formed on the scroll side of the second bearing housing 8, and the diameter of the bearing hole 8a is larger than that of the bearing hole 8a. A small insertion portion 8b through which the oil supply cylinder 16 is inserted is formed continuously, and a pump mounting portion 8c for mounting the pump housing 22 on the anti-scroll side of the insertion portion 8b is formed. And
When the rolling bearing 14 is installed in the bearing hole 8a,
A space portion is formed inside the bearing hole 8a, and the space portion is formed as a pressure chamber 18 formed on the back side of the rolling bearing 14 and communicated with the discharge side of the oil supply pump 17, By supplying lubricating oil pumped by the oil supply pump 17 to the pressure chamber 18, the rolling bearing 14
The inner ring 14a is constantly pressed against the outer ring 14b toward the motor.

More specifically, the outer diameter of the projecting portion of the cylindrical body 16 from the distal end of the small-diameter stepped portion 4a is determined by the fitting portion of the cylindrical body 16 to the small-diameter stepped portion 4a, and the second A communication passage 81 is formed between the outer peripheral surface of the small diameter portion 16c and the insertion portion 8b formed inside the second bearing housing 8 so as to be smaller in diameter than the insertion portion 8b in the bearing housing 8, Further, a communication hole 16b communicating with the communication passage 81 is formed in the refueling cylinder 16, and the communication hole 16b is formed.
b, the communication passage 81 and the oil supply passage 1 in the cylindrical body 16
6a, and a plurality of radially extending notches 4b are formed on the opposite end surface of the small diameter step 4a provided on the drive shaft 4 on the side opposite to the motor, and one end of the notch 4b is connected to the pressure chamber 18 by the pressure chamber 18. The other end is opened to the communication passage 81, and the lubricating oil pumped to the oil supply passage 16a by the oil supply pump 17 is supplied to the communication passage 81 from the communication hole 16b. The pressure chamber 18 passes through each notch 4b.
It is made to introduce.

In the embodiment shown in FIG. 1, the oil supply pump 1 is disposed on the outer peripheral portion of the cylindrical body 16 protruding from the small diameter step portion 4a of the drive shaft 4 on the side where the oil supply pump 17 is provided.
The pump 7 is provided in parallel with the
An oil storage chamber 21 defined by a partition plate 20 is formed on the back side of the bearing housing 8, and lubricating oil in the storage chamber 21 is pumped up by the oil supply pump 17, and an oil supply passage 16 a of the cylinder 16 is provided. The lubricating oil is supplied to the respective lubricating points via the oil supply passage 15 of the drive shaft 4, and the lubricating oil returned to the bottom of the motor chamber 9 after the lubricating points are lubricated is stored in the pumping pump 19. It is pumped to the room 21.

More specifically, as shown in an enlarged manner in FIG. 2, the oil supply pump 17 and the pumping pump 19 are of a trochoid type.
A pump housing 22 for each of the pumps 17 and 19 is provided around the outer periphery of the cylindrical body 16 inside the pump mounting portion 8c, and the pump housing 22 is fixed to the second bearing housing 8 via an end plate 23. Inside the pump housing 22, a pump inner 17a and a pump outer 17b constituting the oil supply pump 17 and a pump inner 19a and a pump outer 19b constituting the pumping pump 19 are arranged in parallel via a partition plate 24, respectively. It is arranged in a shape. Then, the respective pump inners 17a, 19a of the pumps 17, 19 are integrally connected to the outer peripheral portion of the cylindrical body 16, and the respective pump outers 17b,
The pump housing 22 is rotatably supported by the pump housing 22, and the outer peripheral surfaces of the pump inners 17a, 19a are engaged with the inner peripheral surfaces of the pump outers 17b, 19b.

The second bearing housing 8 is provided with a first oil supply passage 25 whose one end is open to the oil storage chamber 21, and the end plate 23 is provided with a first oil supply passage 25 other than the first oil supply passage 25. A second refueling suction passage 26 communicating with an end of the refueling pump 17 and communicating with a suction side of the refueling pump 17;
7 and the oil supply passage 1 in the cylinder 16
6a and a refueling discharge passage 27 communicating with the fuel supply passage 6a.
By driving the oil supply pump 17 with the rotation of the drive shaft 4, the lubricating oil in the oil storage chamber 21 is removed from the first and second lubrication oils.
The oil is sucked between the pump inner 17a and the pump outer 17b of the oil supply pump 17 through the oil supply suction passages 25 and 26, and the sucked oil is discharged from the oil supply discharge passage 27 to the oil supply passage 16a of the cylindrical body 16. While the oil in the oil supply passage 16a is sent to the oil supply passage 15, a part of the lubricating oil in the oil supply passage 16a is transferred from the communication hole 16b to the communication passage 81 formed in the outer peripheral portion of the cylindrical body 16 and the drive. The pressure is introduced into the pressure chamber 18 through the notch grooves 4b provided in the small diameter step portion 4a of the shaft 4.

Further, the second bearing housing 8 is located at a position different from the portion where the first oil supply passage 25 is formed.
A first pumping suction passage 28 having a distal end opening to the motor chamber 9 is provided, and the pump housing 22 communicates with the first pumping suction passage 28 and the pumping pump 19
A second pumping suction passage 29 communicating with the suction side of the pump and a first pumping discharge passage 30 communicating with the discharge side of the pumping pump 19 are formed, and the first pumping discharge passage 30 is connected to the second bearing housing 8. Is opened to the oil storage chamber 21 through a second pumping discharge passage 31 provided in the motor shaft 9, and the lubricating oil in the motor chamber 9 is discharged by the pumping pump 19 accompanying the rotation of the drive shaft 4. The oil is sucked between the pump inner 19a and the pump outer 19b of the pumping pump 19 via the first and second pumping suction passages 28 and 29, and the sucked oil is supplied from the first and second pumping discharge passages 30 and 31. The oil storage chamber 21
I try to put it back inside.

Next, the operation of the scroll compressor having the above configuration will be described. First, when the drive shaft 4 is driven by the motor 5, the orbiting scroll 3 is revolved with respect to the fixed scroll 2, and the gas refrigerant introduced into the motor chamber 9 from the suction pipe 10 is supplied to each of the scrolls 2. , 3 are sucked and compressed between the spiral bodies 2a, 3a, discharged from the discharge port 2b of the fixed scroll 3 to the discharge chamber 12, and discharged from the discharge pipe 13 to the outside.

The drive of the drive shaft 4 activates the oil supply pump 17 and the pumping pump 19, and the operation of the oil supply pump 17 causes the lubricating oil stored in the oil storage chamber 21 to be removed from the first and the first oil storage chambers 21. The refueling passage 1 in the cylinder 16 is pumped from the second refueling suction passages 25 and 26 and from the refueling discharge passage 27
6a, and a part of the lubricating oil from the oil supply passage 16a to the oil supply passage 15 in the drive shaft 4 is supplied to the communication hole 16b.
Through the communication passage 81 formed on the outer periphery of the cylindrical body 16 and the notch grooves 4b provided in the small-diameter step portion 4a of the drive shaft 4, and is introduced into the pressure chamber 18.

When lubricating oil is introduced into the pressure chamber 18, the lubricating oil is axially movably inserted into the small-diameter stepped portion 4a of the drive shaft 4, and the inner ring 1 of the rolling bearing 14 is moved.
4a is applied as back pressure, and the inner ring 14a is
Is pressed to the scroll side. Therefore, as is clear from FIG. 2, the rolling element 14c of the rolling bearing 14 is provided with a pressing groove rear side edge b of the inner ring 14a and a rolling groove provided in the outer ring 14b. c and the inner and outer races 14a, 14a, 1c.
4b and the rolling elements 14c can be held in contact with each other, and therefore, even when the drive shaft 4 moves in the axial direction, the rolling elements 14c and the inner and outer races 14c can be held.
Collisions do not occur between the members a and b, and the generation of abnormal noise due to the collision of these persons can be reliably prevented. Further, the pressure chamber 18 is formed on the back side of the inner ring 14a and the outer ring 14b in the rolling bearing 14, and the lubricating oil supplied to the pressure chamber 18 is supplied to the inner and outer rings 14a, 14a.
14b, the rolling element 1 is always supplied and filled.
4c is covered with the lubricating oil, so that the rolling noise when the rolling element 14c rolls through each of the rolling grooves a and c can be reduced, and the generation of abnormal noise can be prevented more favorably. it can.

In applying a pressing force to the inner ring 14a of the rolling bearing 14, lubricating oil pumped by the oil supply pump 17 is used.
7, the pumping amount of the lubricating oil is always kept substantially constant irrespective of the operating conditions and the like, so that a stable pressing force is always applied to the inner race 14a, that is, the inner and outer races 14a, 14b of the rolling element 14c. The rolling resistance to the rolling bearing 14b can be kept constant at all times, so that the rolling bearing 14 can stably support the drive shaft 4 and furthermore, a sudden load can be applied to each part of the rolling bearing 14. Therefore, it is possible to prevent each of these components from being damaged.

Further, the lubricating oil pumped by the oil supply pump 17 is introduced into the pressure chamber 18, and the lubricating oil introduced into the pressure chamber 18 is used for the inside of the rolling bearing 14, the outer ring 14a, and the outer ring 14a.
14b, the rolling bearing 14 is lubricated, and therefore, regardless of operating conditions and the like,
A constant amount of lubricating oil can always be supplied to the rolling bearing 14, so that the bearing 14 can be stably lubricated.

The inner ring 1 of the rolling bearing 14
On both sides in the axial direction of the outer ring 4a and the outer ring 14b, the annular space S between the inner and outer rings 14a and 14b is covered, and the pressure chamber 1 is formed.
8 to reduce the amount of oil leaking to the outside, maintain the lubricating oil supplied to the pressure chamber 18 at a high pressure, and increase the pressing force of the inner ring 14a against the outer ring 14b. Shielding plates 14d, 14d are attached. These shielding plates 14d form mounting grooves extending in the circumferential direction on both left and right sides of the inner and outer rings 14a and 14b, and the shielding plates 14d are inserted and mounted in the respective mounting grooves. ,
The size of the mounting groove in the radial direction and the width direction is determined by the shielding plate 1.
4d is formed larger than the diameter and thickness of the shielding plate 14d.
At the time of attachment to the above-mentioned attachment groove, the gap is formed so as to secure a gap between the two so as to allow the flow of the lubricating oil.

With the above configuration, the amount of leakage of the lubricating oil supplied to the pressure chamber 18 to the outside can be reduced by the respective shield plates 14d, that is, the lubricating oil supplied to the pressure chamber 18 is It is possible to hold the inner ring 14a at a large level, and to apply a large pressing force to the inner ring 14a to more reliably prevent the generation of abnormal noise.

In the above embodiment, the horizontal scroll compressor has been described. However, the present invention can be applied to, for example, a vertical scroll compressor and other scroll fluid machines.

[0031]

As described above, according to the first aspect of the present invention, a pair of scrolls 2 and 3 are provided on one side in the longitudinal direction of the casing 1 and the motor 5 is provided on the other side. A first bearing housing 5 for supporting one side of the drive shaft 4 in the axial direction is provided on the scroll side of the motor 5.
In a scroll fluid machine provided with a second bearing housing 8 for supporting the other side in the axial direction of the drive shaft 4 on the side opposite to the scroll, the drive shaft 4 is provided on the other end in the axial direction of the drive shaft 4. And a rolling bearing 14 having an inner ring 14a, an outer ring 14b, and a rolling element 14c in the second bearing housing 8, and the outer ring 14b is connected to the second bearing housing 8. And the inner ring 14a is held movably in the axial direction with respect to the drive shaft 4 so that the rolling bearing 1
4, a pressure chamber 18 communicating with the discharge side of the refueling pump 17 and pressing the inner ring 14a toward the scrolling side with respect to the outer ring 14b is provided on the back side of the anti-scroll side. The lubricating oil introduced into the pressure chamber 18 presses the inner ring 14a of the rolling bearing 14 on the scroll side against the outer ring 14b to keep the inner and outer rings 14a, 14b and the rolling elements 14c in a constant contact state. Therefore, even when the drive shaft 4 moves in the axial direction, the rolling elements 14c and the inner and outer races 14
a and 14b can be reliably prevented from generating an unusual sound due to the collision of each of them without collision.
Moreover, since the lubricating oil in the pressure chamber 18 is constantly supplied and filled between the inner ring 14a and the outer ring 14b, the periphery of the rolling element 14c is covered with the lubricating oil and the rolling element 14c is covered.
The rolling noise of c can also be reduced, and the occurrence of abnormal noise can be prevented more favorably.

As described above, the oil supply pump 17
The lubricating oil introduced into the pressure chamber 18 from the inner ring 14
When the pressing force is applied to the inner ring 14a, the pumping amount of the lubricating oil by the oil supply pump 17 is always kept substantially constant irrespective of the operating conditions and the like. The rolling resistance of the rolling element 14c with respect to the inner and outer races 14a, 14b is always kept constant, so that the rolling bearing 14 can stably support the drive shaft 4 and furthermore, the rolling bearing 1
Since no sudden load is applied to each of the components 4, it is possible to prevent the components from being damaged.

Further, the lubricating oil pumped by the oil supply pump 17 is introduced into the pressure chamber 18, and the lubricating oil introduced into the pressure chamber 18 is supplied to the inner and outer races 14 of the rolling bearing 14.
a, lubrication of the rolling bearing 14 is performed, so that a constant amount of lubricating oil can always be supplied to the rolling bearing 14 irrespective of operating conditions and the like, so that the bearing 14 is stabilized. Lubrication can be performed.

According to the second aspect of the present invention, since the rolling bearing 14 is provided with the shielding plate 14d for covering the annular gap S between the inner ring 14a and the outer ring 14b, the pressure plate is formed by the shielding plate 14d. It is possible to reduce the amount of oil leaking from the pressure chamber 18 to the outside, that is, to maintain the lubricating oil supplied to the pressure chamber 18 at a high pressure, and to apply a large pressing force to the inner ring 14a to generate abnormal noise. Can be more reliably prevented.

[Brief description of the drawings]

FIG. 1 is a partially omitted longitudinal sectional view of a horizontal scroll compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of the main part.

FIG. 3 is a sectional view showing a conventional example.

[Explanation of symbols]

 Reference Signs List 1 casing 2, 3 scroll 4 drive shaft 5 motor 6 first bearing housing 8 second bearing housing 14 rolling bearing 14a inner ring 14b outer ring 14c rolling element 14d shielding plate S annular gap 15 oil supply passage 17 oil supply pump 18 pressure chamber

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masanori Yanagisawa 3-12 Chikushinmachi, Sakai City, Osaka Prefecture Daikin Industries Co., Ltd. Address Daikin Industries, Ltd. Sakai Plant Rinkai Plant (58) Field surveyed (Int. Cl. ⁷ , DB name) F04C 18/02 311 F04C 29/00 F04C 29/02 311

Claims (2)

(57) [Claims] 1. A pair of scrolls (2) and (3) are provided on one side in the length direction of a casing (1), and a motor (5) is provided on the other side, and a drive is provided on the scroll side of the motor (5). A first bearing housing (6) for supporting one side of the shaft (4) in the axial direction is provided, and a first bearing housing (6) for supporting the other side in the axial direction of the drive shaft (4) on the anti-scroll side of the motor (5). (2) In a scroll fluid machine provided with a bearing housing (8), an oil supply pump (1) for supplying oil to an oil supply passage (15) of the drive shaft (4) at the other axial end of the drive shaft (4).
7) and the second bearing housing (8).
The inner ring (14a), the outer ring (14b) and the rolling elements (14
c) and a rolling bearing (14) having the outer ring (1).
4b) is a bearing hole (8) of the second bearing housing (8).
a), the inner ring (14a) is held movably in the axial direction with respect to the drive shaft (4), and a discharge of the oil supply pump (17) is provided on the back of the anti-scroll side of the rolling bearing (14). A pressure chamber (18) communicating with the outer ring (14a) and pressing the inner ring (14a) against the outer ring (14b) toward the scroll side. 2. The rolling bearing (14) includes an inner ring (14a).
The scroll fluid machine according to claim 1, further comprising a shielding plate (14d) for covering an annular gap (S) between the outer ring (14b) and the outer ring (14b).