JPH08247069A - Scroll compressor - Google Patents

Abstract

PURPOSE: To provide a scroll compressor capable of easily setting oiling quantity to a ball bearing pivotally supporting a lower end part of a spindle and preventing abrasion and seizure of the ball bearing due to shortage of the oiling quantity. CONSTITUTION: A first oil introducing hole 4b one end opening of which is formed on an oiling hole 4a and the other end opening of which is formed on a circumferential surface of a spindle 4 above a ball bearing 14 is provided on the spindle 4 of a scroll compressor. A part of lubricating oil rising in the oiling hole 4a in accordance with rotation of the spindle 4 is branched and introduced to the first oil introducing hole 4b by centrifugal force in accordance with rotation of the spindle 4 at the time when it reaches the one end opening of the first oil introducing hole 4b, discharged from the other end opening of the first oil introducing hole 4b and fed to the ball bearing 14.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used in, for example, an air conditioner or a refrigeration system.

[0002]

2. Description of the Related Art FIG. 16 shows, for example, an actual Kaihei 5-66292.
FIG. 1 is a cross-sectional view of a conventional scroll compressor shown in Japanese Patent Publication No. JP-A-2004-242242, in which reference numeral 1 is a fixed scroll, 2 is an orbiting scroll, and these are a base plate and a spiral protrusion protruding from the base plate, respectively. And the spiral protrusions are combined with each other to form a compression chamber. Reference numeral 3 denotes a frame that fixedly supports the fixed scroll 1 and slidably supports the orbiting scroll 2 in a thrust bearing 17, and a motor rotor 5 is externally fitted to an intermediate portion of the reference numeral 4, and a main bearing 6 of the frame 3 near the upper end. A main shaft that is rotatably pivoted to and has an upper end slidably fitted in the rocking bearing 7 of the rocking scroll 2,
4a is an oil supply hole formed through the main shaft 4 in the axial direction,
Reference numeral 8 is an electric motor stator provided around the electric motor rotor 5, 9 is a sub-bearing that is formed on the sub-frame 10 and rotatably supports the lower end of the main shaft 4, and 11 is a positive displacement pump 19 attached to the sub-frame 10. A pump case for accommodating 13
Is a closed container that accommodates all the above-mentioned components and has an oil sump 12 that stores lubricating oil at the bottom.

FIG. 17 is an enlarged sectional view of the vicinity of the lower end portion of the main shaft 4 when a ball bearing 14 is used as an example of the sub bearing 9, and in the figure, 14a is a ball bearing 1.
4 is the inner ring, 14b is the outer ring of the ball bearing 14, 11
a is a through hole formed in the pump case 11 for inserting the main shaft 4, 15 is a gap between the inner peripheral surface of the through hole 11a and the main shaft 4, 1
Reference numeral 6 denotes a concave portion formed on the upper surface of the pump case 11 and 10a.
Is an oil drain passage formed in the subframe 10.

Next, the operation of this scroll compressor will be described. The main shaft 4 is rotatably driven by an electric motor composed of an electric motor stator 8 and an electric motor rotor 5 while being pivotally supported by a main bearing 6 and a sub bearing 9 (ball bearing 14).
When the main shaft 4 rotates, the orbiting scroll 2 revolves and a compression action is generated in the compression chamber formed between the orbiting scroll 2 and the fixed scroll 1, whereby the low-temperature low-pressure gas refrigerant is sealed in the closed container 13.
The gas refrigerant is sucked into the inside, is made into a high-temperature and high-pressure gas refrigerant, and is sent out of the closed container 13. Further, some of the gas refrigerant sucked into the closed container 13 flows into the spaces above and below the electric motor to cool the electric motor.

Further, as the main shaft 4 rotates, the pump 19 connected to the main shaft 4 is rotated, whereby the oil sump 1
Lubricating oil inside 2 is sucked, and the main shaft 4 passes through the oil supply hole 4a.
Of the main bearing 6, the swing bearing 7, the thrust bearing 17 and the like, and then flows down in the closed container 13 to return to the oil sump 12. Further, as shown by the arrow in FIG. 17, a part of the lubricating oil sucked by the pump 19 is supplied to the ball bearing 14 through the gap 15 and the recessed portion 16, and after lubricating it, the oil is collected through the oil drain passage 10a. Return to 12.

[0006]

However, the conventional scroll compressor has the following problems.
That is, the amount of oil supplied to the ball bearing 14 is determined by the size of the gap 15 between the inner peripheral surface of the through hole 11 a and the main shaft 4. Therefore, in order to obtain a predetermined amount of lubrication, it was necessary to machine the through hole 11a and the spindle 4 with high accuracy, but such highly accurate machining is difficult in reality, and therefore the amount of lubrication may possibly be higher. There is a possibility that the ball bearing 14 may be worn out abnormally, seized, or generate an abnormal sound due to lack of heat.

The present invention has been made to solve the above problems, and the amount of oil supplied to the ball bearing that pivotally supports the lower end of the main shaft can be easily set. The object of the present invention is to obtain a scroll compressor capable of preventing abrasion and seizure of the scroll compressor.

[0008]

In order to achieve the above object, the present invention forms a compression chamber by combining a closed container having an oil sump at the bottom and spiral protrusions arranged at the upper part of the closed container with each other. A fixed scroll and an orbiting scroll, a main shaft that extends in the vertical direction and is slidably connected to the orbiting scroll at the upper end, and a ball bearing that inserts the lower end of the main shaft into a freely rotatable main shaft. In a scroll compressor provided with a sub-frame that pivotally supports and an oil supply hole that is formed to penetrate the main shaft in the axial direction and that supplies the lubricating oil in the oil sump to at least the sliding portion of the orbiting scroll, in the main shaft,
An opening at one end is formed in the oil supply hole, and an opening at the other end is formed on at least the upper peripheral surface of the ball bearing.
The oil guide hole is provided.

In addition to the above-mentioned structure, the ball bearing is provided with the lubricating oil discharged from the first oil guide hole, which is provided so as to surround the peripheral surface of the main shaft corresponding to the opening position of the first oil guide hole. It is equipped with a first oil-conducting ring body that leads to.

In addition to the above structure, the first oil guide ring body is integrally formed with the subframe.

Further, in addition to the above structure, the lubricating oil discharged from the first oil guide hole and supplied to the ball bearing is passed through the lower end opening of the gap formed between the inner ring and the outer ring of the ball bearing to form the sub-frame. The first oil discharge passage for discharging into the lower space is formed in at least the subframe.

Further, in addition to the above construction, an opening area limiting means for limiting the opening area of the first oil guide hole on the peripheral surface side of the main shaft is provided.

A closed container having an oil sump at the bottom,
A fixed scroll and an orbiting scroll that are arranged in the upper part of the closed container to form a compression chamber by combining the spiral protrusions with each other, and a main shaft that extends in the vertical direction and is slidably connected to the orbiting scroll at the upper end portion. , A sub-frame that rotatably supports the main shaft through a ball bearing that inserts the lower end of the main shaft, and lubricating oil in an oil sump that is formed through the main shaft in the axial direction of the main shaft. In a scroll compressor provided with an oil supply hole for supplying to a sliding portion, one end opening is formed in the main shaft, and the other end opening is formed in the main surface of the main shaft at a position to be fitted into a ball bearing. The second oil guide hole is provided, and the main shaft is notched in the radial direction from the peripheral surface to form the first cutout portion that communicates the space above the ball bearing with the second oil guide hole. .

In addition to the above construction, the second oil guide hole and the first notch are provided at separate and independent positions in the circumferential direction, and the peripheral surface of the main shaft is inserted into the ball bearing. An annular groove that connects the second oil guide hole and the first cutout portion is formed therein.

Further, in addition to the above structure, the lubricating oil discharged from the first cutout portion is provided so as to surround the peripheral surface position of the main shaft corresponding to the upper end position of the first cutout portion. The second oil-conducting ring body that leads to the sub-frame is integrally formed with the sub-frame.

Further, in addition to the above construction, the lubricating oil discharged from the first cutout portion and supplied to the ball bearing is passed through the lower end opening of the gap formed between the inner ring and the outer ring of the ball bearing to form the subframe. The second oil discharge passage for discharging to the space below is formed at least in the sub-frame.

A closed container having an oil sump at the bottom,
A fixed scroll and an orbiting scroll that are arranged in the upper part of the closed container to form a compression chamber by combining the spiral protrusions with each other, and a main shaft that extends in the vertical direction and is slidably connected to the orbiting scroll at the upper end portion. Formed between the inner ring and the outer ring of the ball bearing, which is provided in abutment with the lower end surface of the ball bearing, and a sub-frame that pivotally supports the main shaft via a ball bearing that inserts the lower end of the main shaft. Scroll compressor having a closing member that closes the lower end opening of the gap that is formed, and an oil supply hole that is formed through the main shaft in the axial direction and that supplies the lubricating oil in the oil sump to at least the sliding portion of the orbiting scroll. In the machine, a second notch is formed by radially notching the main shaft in the radial direction from the peripheral surface at a position corresponding to the lower end position of the ball bearing, and at the same time, the main shaft has one end opening formed in the oil supply hole. A third oil guide hole having the other end opening formed in the second cutout portion, and the closing member is cut downward from the contact surface with the ball bearing to form a second cutout portion. A third cutout portion that communicates with the void is formed.

[0018]

According to the scroll compressor of the present invention, when a part of the lubricating oil that rises in the oil supply hole reaches the opening at one end of the first oil guide hole, the first centrifugal force is generated by the rotation of the main shaft. Of the first oil guide hole, is discharged from the other end opening of the first oil guide hole, and is supplied to the ball bearing.

When the lubricating oil discharged from the first oil guide hole hits the inner peripheral wall of the first oil guide ring, the lubricating oil flows down along the inner peripheral wall and is guided to the ball bearing.

Further, the lubricating oil supplied to the upper end side of the ball bearing flows down through the gap formed between the inner ring and the outer ring of the ball bearing, and the sub oil is passed through the lower end opening of this gap and the first oil drain passage. It is discharged into the space below the frame and returned to the oil sump.

Furthermore, the amount of oil supplied to the ball bearing is set by the opening area of the first oil guide hole limited by the opening area limiting means.

Further, a part of the lubricating oil that rises in the oil supply hole is
When it reaches the one end opening of the second oil guide hole, it is branched and led out to the second oil guide hole by the centrifugal force caused by the rotation of the main shaft, and enters the first cutout portion from the second oil guide hole. , Discharged from the first cutout portion and supplied to the ball bearing.

The lubricating oil branched and led out to the second oil guide hole is supplied to the ball bearing through the annular groove and the first notch.

Further, when the lubricating oil discharged from the first cutout portion hits the inner peripheral wall of the second oil guide ring body, the lubricating oil flows down along the inner peripheral wall and is guided to the ball bearing.

Furthermore, the lubricating oil supplied to the upper end side of the ball bearing flows down through the gap formed between the inner ring and the outer ring of the ball bearing, and through the lower end opening of this gap and the second oil drain passage. It is discharged into the space below the subframe and returned to the oil sump.

Further, a part of the lubricating oil that rises in the oil supply hole is
When it reaches the one end opening of the third oil guide hole, it is branched and led out to the third oil guide hole by the centrifugal force accompanying the rotation of the main shaft, enters the second cutout portion from the third oil guide hole, and , Is supplied to the lower end side of the ball bearing through the third notch, and rises in the gap formed between the inner ring and the outer ring of the ball bearing,
It is discharged from the upper end opening of this gap.

[0027]

Embodiments of the present invention will be described below with reference to the drawings.

Embodiment 1 FIG. 1 is a sectional view of a scroll compressor according to Embodiment 1, FIG.
FIG. 3 is an enlarged cross-sectional view of a main part of the scroll compressor according to Embodiment 1. In these drawings, the same components as those of the conventional example are designated by the same reference numerals, and the description thereof will be omitted. In the present embodiment, the main shaft 4 is provided with a first oil guide hole 4b having one end opening formed in the oil supply hole 4a and the other end opening formed in the peripheral surface of the main shaft 4 above the ball bearing 14. First oil guide hole 4b
Is formed in a direction perpendicular to the axis of the main shaft 4 as shown in FIG. 2, and connects the oil supply hole 4a and the space near the upper portion of the ball bearing 14.

Next, the operation will be described. When the main shaft 4 rotates, the pump 19 connected to the main shaft 4 is rotated,
As a result, the lubricating oil in the oil sump 12 is sucked and the oil supply hole 4
After being supplied to the upper end of the main shaft 4 through a and lubricating the main bearing 6, the oscillating bearing 7, the thrust bearing 17, etc.,
It flows down in the closed container 13 and returns to the oil sump 12. Further, as shown by the arrow in FIG. 2, when a part of the lubricating oil rising in the oil supply hole 4a reaches the one end opening of the first oil guide hole 4b, the first centrifugal force generated by the rotation of the main shaft 4 causes Is branched and led to the oil guide hole 4b, and is discharged from the other end opening of the first oil guide hole 4b.
It is supplied to the ball bearing 14.

In the scroll compressor of the present embodiment as described above, the amount of oil supplied to the ball bearing 14 is determined by the cross-sectional area of the first oil guide hole 4b, so that the processing for setting the predetermined amount of oil supply is easy. Moreover, the set oil supply amount can be easily changed by changing the diameter of the drill blade used for drilling the first oil guide hole 4b. Therefore, it is possible to supply a necessary and sufficient amount of lubricating oil to the ball bearings 14, and it is possible to provide a highly reliable scroll compressor in which the ball bearings 14 hardly wear or seize.

If the first oil guide hole 4b is formed obliquely as shown in FIG. 3, the ball bearing 14 is supplied with oil more reliably than in the case where the first oil guide hole 4b is formed horizontally as shown in FIG. be able to. Further, the pump 1 is shown in FIGS.
Although the case where 9 is a positive displacement type is shown, the pump may be a centrifugal type or other type.

Second Embodiment FIG. 4 is an enlarged cross-sectional view of a main part of a scroll compressor according to a second embodiment. In FIG. 4, the same components as those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. In the present embodiment, a first oil guide ring body 21 is provided which surrounds the vicinity of the peripheral surface position of the main shaft 4 corresponding to the opening position of the first oil guide hole 4b. The first oil guide ring body 21 is formed in a substantially cylindrical shape, and has an integrally formed inward flange portion 22 at the upper end thereof. With the flange portion 22 facing upward, the electric motor It is attached to the lower end of the rotor 5. Further, the first oil guide ring body 21 is formed in such a size that its lower end does not come into contact with the upper end of the subframe 10 but faces through a slight gap.

Since the lubricating oil discharged from the first oil guide hole 4b hits the inner peripheral wall of the first oil guide ring 21 as shown by the arrow in FIG. ,
It flows down along this inner peripheral wall and is guided to the ball bearing 14. Therefore, for example, the lubricating oil discharged from the first oil guide hole 4b, which is predicted when the variable speed control scroll compressor is operated on the high speed side, scatters outside the ball bearing 14. Is wound up by the gas refrigerant flowing in the closed container 13,
A situation in which oil is sucked into the compression chamber and causes oil to rise is avoided, and the ball bearing 14 is lubricated more reliably.

The first oil guide ring body 21 applies the lubricating oil discharged from the first oil guide hole 4b to the ball bearing 14a.
Any shape and attachment method can be used as long as it guides to the above. For example, as shown in FIG. 5, the first oil guide ring body 21 may be attached to the upper end of the subframe 10.

Embodiment 3 FIG. 6 is an enlarged cross-sectional view of a main part of a scroll compressor according to Embodiment 3, in which the same components as those of Embodiment 2 are designated by the same reference numerals and their description is omitted. To do. In this embodiment, the tubular portion 10b of the subframe 10 supporting the outer ring 14b of the ball bearing 14 is extended upward to at least the same height as the opening of the first oil guide hole 4b, and this extended portion is the first portion. It is the oil guide ring body 21. Thus, even if the first oil guide ring body 21 is formed integrally with the sub-frame 10, the same effect as that of the above-described embodiment can be obtained, and moreover, the first oil guide ring body as in the above-mentioned embodiment is obtained. Two
The number of parts can be reduced as compared with the case where 1 is configured by a member independent of the subframe 10.

Fourth Embodiment FIG. 7 is an enlarged cross-sectional view of a main part of a scroll compressor according to a fourth embodiment. In FIG. 7, the same components as those of the third embodiment are designated by the same reference numerals and the description thereof will be omitted. To do. In this embodiment, the pump case 11 that abuts on the lower end surface of the ball bearing 14 is cut out from the upper surface of the pump case 11 so that the pump case 11 faces the space 14c formed between the inner ring 14a and the outer ring 14b of the ball bearing 14. A notch 11b is formed to reach the outer peripheral edge of the case 11. Further, the sub-frame 10 is radially cut away from the inner peripheral surface of the portion housing the pump case 11, and a cutout portion 10c is formed from a position facing the cutout portion 11b to a lower end portion of the subframe 10. There is. The cutout portion 11b and the cutout portion 10c constitute a first oil drain passage 23 that communicates the lower end opening of the void 14c with the space below the subframe 10.

With this structure, as shown by the arrow in FIG. 7, the lubricating oil discharged from the first oil guide hole 4b and supplied to the upper end side of the ball bearing 14 has a space 1
4c, and is discharged to the space below the sub-frame 10 through the lower end opening of the gap 14c and the first oil drain passage 23, and returned to the oil sump 12. Therefore, the void 14
As in the case where the lower end opening of c is blocked, the lubricating oil supplied to the ball bearing 14 overflows from the gap 14c, splatters over the first oil guide ring body 21 to the inside of the closed container 13. It is possible to prevent the oil from being sucked up by the circulating gas refrigerant and being sucked into the compression chamber. Further, since the lubricating oil is circulated smoothly, the ball bearing 14 is lubricated more reliably.

If the first oil drain passage 23 can take out the lubricating oil from the lower end opening of the gap 14c and discharge it into the space below the subframe 10, how and where it is formed in the subframe 10. It doesn't matter.

Embodiment 5 FIG. 8 is an enlarged cross-sectional view of a main part of a scroll compressor according to Embodiment 5, in which the same components as those of Embodiment 1 are designated by the same reference numerals and their description is omitted. To do. In the present embodiment, the opening area limiting means 24 for limiting the opening area of the first oil guide hole 4b on the peripheral surface side of the main shaft 4 is provided. The opening area limiting means 24 is a ring-shaped member that is externally fitted to the main shaft 4, and is positioned in the vertical direction by abutting the upper end thereof on the disconnection portion 4 c formed on the main shaft 4, and the pin 2 is positioned.
It is fixed to the main shaft 4 by means of 5.

When the amount of oil supplied to the ball bearing 14 is set by the hole diameter of the first oil guide hole 4b, when the set oil supply amount is small and the hole diameter of the first oil guide hole 4b is made small, a fine drill blade is used. In this case, a thin drill blade is inferior in durability, so that the tool cost becomes high. If the hole diameter is extremely small, the first oil guide hole 4b may not be opened with a drill. But,
In this embodiment, the amount of oil supplied to the ball bearing 14 is set by the opening area of the first oil guide hole 4b limited by the opening area limiting means 24, so that the first oil guide is performed even when the set oil supply amount is small. Since the hole diameter of the hole 4b can be increased to a certain extent or more, and a thick drill blade having high durability can be used, it is possible to reduce the cost for drilling the first oil guide hole 4b.

In this embodiment, the opening area limiting means 24
Is a ring-shaped member, but the opening area limiting means may have any shape and mounting method as long as it can limit the opening area of the first oil guide hole 4b on the circumferential surface side of the main shaft 4, and for example, a small plate. It is also possible to fix the opening area of the first oil guide hole 4b by fixing a cylindrical member to the peripheral surface of the main shaft 4.

Embodiment 6 FIG. 9 is an enlarged sectional view of an essential portion of a scroll compressor according to Embodiment 6, and FIG. 10 is a sectional view taken along the line AA of FIG. The same components are assigned the same reference numerals and explanations thereof are omitted. In this embodiment, the spindle 4
Is provided with a second oil guide hole 4e, one end opening of which is formed in the oil supply hole 4a and the other end opening of which is formed on the peripheral surface of the ball bearing insertion portion 4d of the main shaft 4, and the ball of the main shaft 4 is formed. The bearing insertion portion 4d is notched in the radial direction from the peripheral surface, and a first notch 4f is formed to connect the space above the ball bearing 14 and the second oil guide hole 4e.

With this configuration, as shown by the arrow in FIG. 9, part of the lubricating oil that rises in the oil supply hole 4a reaches the main shaft when it reaches the one end opening of the second oil guide hole 4e. 4 is branched and led out to the second oil guide hole 4e by the centrifugal force accompanying the rotation of 4, and enters the first cutout portion 4f via the second oil guide hole 4e.
Then, it is discharged from the upper end portion of the first cutout portion 4 f and supplied to the ball bearing 14.

In this embodiment, the amount of oil supplied to the ball bearing 14 is determined by the notch depth M (that is, the cross-sectional area) of the first notch portion 4f, so that the process for setting the predetermined amount of oil supply is easy. In addition, the set oil supply amount can be easily changed by changing the notch depth M. Further, even when the set oil supply amount is small, the hole diameter of the second oil guide hole 4e can be increased to a certain extent or more, and a thick drill blade having high durability can be used. The shape of the first cutout portion 4f is not limited to this embodiment, but may be any shape.

Embodiment 7 FIG. 11 is an enlarged sectional view of an essential part of a scroll compressor according to an embodiment 7, and FIG. 12 is a sectional view taken along line BB of FIG. 11, showing an embodiment 6 in these figures. The same components as those of the above are denoted by the same reference numerals, and description thereof will be omitted. In this embodiment, the second oil guide hole 4e and the first cutout portion 4f are formed at positions different by 180 ° in the circumferential direction. The second oil guide hole 4e and the first cutout portion 4f are communicated with each other by an annular groove 4g formed on the peripheral surface of the ball bearing insertion portion 4d of the main shaft 4.

With this configuration, as shown by the arrows in FIGS. 11 and 12, a part of the lubricating oil that rises in the oil supply hole 4a reaches the one end opening of the second oil guide hole 4e. At this time, the second oil guide holes 4e
To the annular groove 4g through the second oil guide hole 4e. Then, it flows in the annular groove 4g and flows into the first cutout portion 4f.
Enters, is discharged from the upper end portion of the first cutout portion 4f, and is supplied to the ball bearing 14.

In the present embodiment, the amount of oil supplied to the ball bearing 14 is determined by the depth L of the annular groove 4g, so that the processing for setting the predetermined amount of oil supply becomes easier.
In this embodiment, in order to increase the distance between the second oil guide hole 4e and the first cutout portion 4f to increase the resistance when the lubricating oil flows through the annular groove 4g, the second Oil guide hole 4e
The first cutout 4f and the first cutout 4f are formed at positions different by 180 ° in the circumferential direction, but how many times the second oil guide hole 4e and the first cutout 4f are formed at different positions in the circumferential direction. It may be.

Embodiment 8 FIG. 13 is an enlarged cross-sectional view of the essential parts of a scroll compressor according to Embodiment 8, in which the same components as those of Embodiment 7 are designated by the same reference numerals and their description is omitted. To do. In this embodiment, the tubular portion 10b of the sub-frame 10 which supports the outer ring 14b of the ball bearing 14 is extended upward to at least the same height as the upper end of the first cutout portion 4f, and this extended portion is the first portion. It is the oil guide ring body 26 of 2.

With this structure, as shown by the arrow in FIG. 13, the lubricating oil discharged from the upper end of the first cutout portion 4f is transferred to the inner peripheral wall of the second oil guide ring body 26. When it hits, it flows down along this inner peripheral wall and is guided to the ball bearing 14, so that the lubrication of the ball bearing 14 becomes more reliable. Further, since the second oil guide ring body 26 is formed integrally with the sub-frame 10, the number of parts does not increase because the second oil guide ring body 26 is provided.

[Embodiment 9] FIG. 14 is an enlarged cross-sectional view of a main part of a scroll compressor according to Embodiment 9, in which the same components as those of Embodiment 8 are designated by the same reference numerals and their description is omitted. To do. In this embodiment, the pump case 11 that abuts on the lower end surface of the ball bearing 14 is cut out from the upper surface of the pump case 11 so that the pump case 11 faces the space 14c formed between the inner ring 14a and the outer ring 14b of the ball bearing 14. A notch 11b is formed to reach the outer peripheral edge of the case 11. Further, the sub-frame 10 is formed with a communication hole 10d having an upper end communicating with the cutout portion 11b and a lower end opening to the bottom surface of the sub-frame 10. Then, from the cutout portion 11b and the communication hole 10d,
A second oil drain passage 27 is formed that connects the lower end opening of the void 14c and the space below the subframe 10.

With this structure, as shown by the arrow in FIG. 14, the lubricating oil supplied to the upper end side of the ball bearing 14 flows down through the gap 14c, and this gap 14c
The oil is discharged into the space below the sub-frame 10 through the lower end opening of the and the second oil discharge passage 27 and returned to the oil sump 12. Therefore, the circulation of the lubricating oil becomes smooth, and the ball bearing 14 can be lubricated more reliably.

The second drain passage 27 may be formed in any part of the subframe 10 and in any way, as long as the lubricating oil can be taken out from the lower end opening of the gap 14c and discharged into the space below the subframe 10. Absent.

Embodiment 10 FIG. 15 is an enlarged cross-sectional view of the main parts of a scroll compressor according to Embodiment 10, in which the same components as those of the conventional example are designated by the same reference numerals and the description thereof is omitted. . In the present embodiment, by chamfering the step portion of the main shaft 4 formed at a position corresponding to the lower end position of the ball bearing 14, the second cutout portion 4h forms an annular shape along the peripheral surface of the main shaft 4. Is formed in. Further, the main shaft 4 is provided with a third oil guide hole 28 having one end opening formed in the oil supply hole 4a and the other end opening formed in the second cutout portion 4h. Further, a pump case 11c (closure member) that abuts the lower end surface of the ball bearing 14 and closes the lower end opening of the space 14c formed between the inner ring 14a and the outer ring 14b is cut out downward from the upper surface thereof. , Second notch 4h and void 14c
A third cutout portion 11c is formed to communicate with and.

With this structure, the oil supply hole 4
When a part of the lubricating oil that rises a reaches the opening at one end of the third oil guide hole 28, the third lubricating oil 28 is a third centrifugal force generated by the rotation of the spindle 4.
Is branched and led out to the oil guide hole 28. Then, it enters into the second cutout portion 4h through the third oil guide hole 28, flows in the circumferential direction through the second cutout portion 4h, and enters the third cutout portion 11c. It is supplied to the lower end opening of the void 14c through the cut portion 11c. Then, while lubricating the ball bearing 14, it rises in the space 14c and is discharged from the upper end opening.

In this embodiment, the amount of oil supplied to the ball bearing 14 is determined by the chamfered dimension of the second notch 4h, so that the process for setting the predetermined amount of oil supply is extremely easy. Further, since the lubricating oil supplied to the lower end opening of the void 14c is discharged from the upper end opening of the void 14c, the lubricating oil is smoothly circulated, and the lubricating oil is supplied from the upper end side of the ball bearing 14. There is no need to form an oil drain passage in the.

In this embodiment, the case in which the closing member for closing the lower end opening of the space 14c is the pump case 11 is shown. However, the closing member is not limited to the pump case 11, and any kind of closing is possible. The third cutout portion 11c can be formed even with a member. The second cutout portion 4h is not limited to chamfering, and may be formed by notching the main shaft in a groove shape.

[0057]

As described above, according to the scroll compressor of the present invention, when a part of the lubricating oil that rises in the oil supply hole reaches the one end opening of the first oil guide hole, It is branched and led out to the first oil guide hole by the centrifugal force accompanying the rotation, discharged from the other end opening of the first oil guide hole, and supplied to the ball bearing. Therefore, since the amount of oil supplied to the ball bearing is set by the cross-sectional area of the first oil guide hole, it is easy to set a predetermined amount of oil supply, and wear and seizure of the ball bearing due to insufficient amount of oil supply can be prevented. It can be prevented.

When the lubricating oil discharged from the first oil guide hole hits the inner peripheral wall of the first oil guide ring, the lubricating oil flows down along the inner peripheral wall and is guided to the ball bearing. The ball bearing can be lubricated more reliably.

Further, by forming the first oil guide ring body integrally with the sub-frame, the number of parts can be reduced.

Further, the lubricating oil supplied to the upper end side of the ball bearing flows down through the gap formed between the inner ring and the outer ring of the ball bearing, and through the lower end opening of this gap and the first oil discharge passage. Since it is discharged to the space below the frame and returned to the oil sump, the lubricating oil circulates smoothly and the ball bearing can be lubricated more reliably.

Furthermore, since the amount of oil supplied to the ball bearing is set by the opening area of the first oil guide hole limited by the opening area limiting means, even if the set oil supply amount is small, the amount of oil supplied to the first oil guide hole is small. Since the hole diameter can be increased to a certain extent or more, it is possible to reduce the cost for forming the first oil guide hole.

Further, a part of the lubricating oil that rises in the oil supply hole is
When it reaches the one end opening of the second oil guide hole, it is branched and led out to the second oil guide hole by the centrifugal force caused by the rotation of the main shaft, and enters the first cutout portion from the second oil guide hole. , Discharged from the first cutout portion and supplied to the ball bearing. Therefore, the amount of oil supplied to the ball bearing is set by the cross-sectional area of the first cutout portion, so that it is easy to set a predetermined amount of oil supply, and wear or seizure of the ball bearing due to insufficient amount of oil supply is prevented. It can be prevented.

The lubricating oil branched and led out to the second oil guide hole is supplied to the ball bearing through the annular groove and the first notch. Therefore, the amount of oil supplied to the ball bearing can be set by the cross-sectional area of the annular groove, which makes it easier to set a predetermined amount of oil and prevents wear and seizure of the ball bearing due to insufficient oil supply. it can.

Further, when the lubricating oil discharged from the first notch collides with the inner peripheral wall of the second oil guide ring body, the lubricating oil flows down along the inner peripheral wall and is guided to the ball bearing. The ball bearing can be lubricated more reliably, and the second oil-conducting ring body is formed integrally with the sub-frame, so that the number of parts does not increase.

Furthermore, the lubricating oil supplied to the upper end side of the ball bearing flows down through the gap formed between the inner ring and the outer ring of the ball bearing, and through the lower end opening of this gap and the second oil drain passage. Since the oil is discharged to the space below the sub-frame and returned to the oil sump, the circulation of the lubricating oil becomes smooth and the ball bearing can be lubricated more reliably.

Further, a part of the lubricating oil that rises in the oil supply hole is
When it reaches the one end opening of the third oil guide hole, it is branched and led out to the second oil guide hole by the centrifugal force caused by the rotation of the main shaft, enters the second cutout portion from the third oil guide hole, and , Is supplied to the lower end side of the ball bearing through the third notch, and rises in the gap formed between the inner ring and the outer ring of the ball bearing,
It is discharged from the upper end opening of this gap. Therefore, the amount of oil supplied to the ball bearing can be set by the cross-sectional area of the second cutout portion, so that it becomes easy to set a predetermined amount of oil supply, and wear or seizure of the ball bearing due to insufficient amount of oil supply is possible. Can be prevented. Further, since the lubricating oil is circulated smoothly, it is not necessary to form an oil discharge passage as in the case where the lubricating oil is supplied from the upper end side of the ball bearing.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a scroll compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of a main part of the scroll compressor according to the first embodiment of the present invention.

FIG. 3 is an enlarged sectional view of an essential part of a scroll compressor showing another configuration of the first oil guide hole.

FIG. 4 is an enlarged sectional view of a main part of a scroll compressor according to a second embodiment of the present invention.

FIG. 5 is an enlarged cross-sectional view of a main part of a scroll compressor showing another configuration of the first oil guide ring body.

FIG. 6 is an enlarged sectional view of a main part of a scroll compressor according to a third embodiment of the present invention.

FIG. 7 is an enlarged cross-sectional view of a main part of a scroll compressor according to a fourth embodiment of the present invention.

FIG. 8 is an enlarged cross-sectional view of a main part of a scroll compressor according to a fifth embodiment of the present invention.

FIG. 9 is an enlarged cross-sectional view of a main part of a scroll compressor according to a sixth embodiment of the present invention.

10 is a cross-sectional view taken along the line AA of FIG.

FIG. 11 is an enlarged sectional view of a main part of a scroll compressor according to a seventh embodiment of the present invention.

FIG. 12 is a cross-sectional view taken along the line BB of FIG.

FIG. 13 is an enlarged sectional view of a main part of a scroll compressor according to an eighth embodiment of the present invention.

FIG. 14 is an enlarged cross-sectional view of a main part of a scroll compressor according to a ninth embodiment of the present invention.

FIG. 15 is an enlarged sectional view of a main part of a scroll compressor according to a tenth embodiment of the present invention.

FIG. 16 is a cross-sectional view of a scroll compressor according to a conventional example.

FIG. 17 is an enlarged sectional view of a main part of a scroll compressor according to a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Fixed scroll 2 Oscillating scroll 4 Main shaft 4a Oil feed hole 4b 1st oil guide hole 4e 2nd oil guide hole 4f 1st notch part 4g Annular groove 4h 2nd notch part 10 Sub-frame 11c 3rd Notch 12 Oil sump 13 Airtight container 14 Ball bearing 14a Inner ring 14b Outer ring 14c Gap 21 First oil guide ring body 23 First oil drain passage 24 Opening area limiting means 26 Second oil guide ring body 27 Second Oil discharge passage 28 Third oil guide hole

Claims (10)

[Claims] 1. A closed container having an oil sump at the bottom, and a fixed scroll and an orbiting scroll which are arranged at an upper part of the closed container to form a compression chamber by combining mutually spiral protrusions, and extend vertically. A main shaft slidably connected to the orbiting scroll at an upper end, a subframe rotatably supporting the main shaft via a ball bearing into which the lower end of the main shaft is inserted, and a shaft for the main shaft. In a scroll compressor provided with a lubricating oil hole penetrating in the axial direction and supplying the lubricating oil in the oil sump to at least the sliding portion of the orbiting scroll, the main shaft has one end opening at the oil supply hole. A scroll compressor, wherein a first oil guide hole is provided, the other end opening of which is formed in at least the peripheral surface of the main shaft above the ball bearing. 2. The first oil guide hole, which is provided so as to surround the vicinity of the peripheral surface position of the main shaft corresponding to the opening position of the first oil guide hole and guides the lubricating oil released from the first oil guide hole to the ball bearing. The scroll compressor according to claim 1, further comprising an oil guide ring body. 3. The scroll compressor according to claim 2, wherein the first oil guide ring body is formed integrally with the subframe. 4. The lubricating oil discharged from the first oil guide hole and supplied to the ball bearing is discharged to a space below the subframe through a lower end opening of a gap formed between an inner ring and an outer ring of the ball bearing. The first oil drain passage to be formed is formed at least in the sub-frame.
The scroll compressor according to item 2, item 2, or item 3. 5. An opening area limiting means for limiting the opening area of the first oil guide hole on the peripheral surface side of the main shaft.
The scroll compressor according to item 2, item 3, or item 4. 6. A closed container having an oil sump at the bottom thereof, a fixed scroll and an orbiting scroll which are arranged at an upper part of the closed container and form a compression chamber by combining mutually spiral protrusions, and extend vertically. A main shaft slidably connected to the orbiting scroll at an upper end, a subframe rotatably supporting the main shaft via a ball bearing into which the lower end of the main shaft is inserted, and a shaft for the main shaft. In a scroll compressor provided with a lubricating oil hole penetrating in the axial direction and supplying the lubricating oil in the oil sump to at least the sliding portion of the orbiting scroll, the main shaft has one end opening at the oil supply hole. And a second oil guide hole formed in the peripheral surface of the spindle at a position where the other end opening is inserted and fitted into the ball bearing,
A scroll compressor, characterized in that the main shaft is notched in a radial direction from a peripheral surface to form a first notch that communicates a space above the ball bearing with the second oil guide hole. 7. The second oil guide hole and the first cutout portion are provided at separate and independent positions in the circumferential direction, and the second guide hole is provided on the peripheral surface at a position to be fitted into the ball bearing of the main shaft. The scroll compressor according to claim 6, wherein an annular groove that connects the oil hole and the first cutout portion is formed. 8. A second bearing member, which is provided so as to surround a peripheral surface position of a main shaft corresponding to an upper end position of the first notch portion and guides lubricating oil discharged from the first notch portion to a ball bearing. The scroll compressor according to claim 6 or 7, wherein the oil guide ring body is formed integrally with the subframe. 9. The lubricating oil discharged from the first notch and supplied to the ball bearing is discharged to a space below the subframe through a lower end opening of a gap formed between an inner ring and an outer ring of the ball bearing. 7. A second oil drain passage that is formed in at least the sub-frame.
A scroll compressor according to item 7, paragraph 7, or paragraph 8. 10. An airtight container having an oil sump at the bottom, a fixed scroll and an orbiting scroll arranged in an upper part of the airtight container to form a compression chamber by combining spiral protrusions of each other, and extending vertically. A main shaft slidably connected to the orbiting scroll at an upper end portion; a subframe rotatably supporting the main shaft via a ball bearing into which a lower end portion of the main shaft is inserted; A closing member which is provided in contact with the lower end surface and closes a lower end opening of a gap formed between an inner ring and an outer ring of the ball bearing, and an inside of the oil sump formed so as to penetrate the main shaft in an axial direction. A lubricating oil supply hole for supplying the lubricating oil of at least to the sliding portion of the orbiting scroll, the peripheral surface of the main shaft at a position corresponding to the lower end position of the ball bearing. A second notch is formed by annularly notching from the radial direction, and one end opening is formed in the oil supply hole and the other end opening is formed in the second notch in the main shaft. A third oil guide hole is provided, and the closing member is notched downward from the contact surface with the ball bearing to form a third notch communicating with the second notch. A scroll compressor characterized by being formed.