JP3952307B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor used in, for example, an air conditioner or a refrigeration apparatus.

  FIG. 16 is a cross-sectional view of a conventional scroll compressor, in which 1 is a fixed scroll and 2 is a swing scroll, each of which includes a base plate and spiral protrusions protruding from the base plate. The compression chamber is formed by combining the spiral protrusions of each other. Reference numeral 3 denotes a frame that fixedly supports the fixed scroll 1 and slidably supports the orbiting scroll 2 on the thrust bearing 17. Reference numeral 4 denotes a motor rotor 5 that is externally fitted in the middle portion, and the main bearing 6 of the frame 3 near the upper end. The main shaft 4a is slidably fitted into the rocking bearing 7 of the rocking scroll 2 while being pivotally supported by the shaft 4, and an oil supply hole formed through the main shaft 4 in the axial direction. , 8 is an electric motor stator that is provided around the electric motor rotor 5, 9 is a sub-bearing that is formed on the subframe 10 and pivotally supports the lower end portion of the main shaft 4, and 11 is a positive displacement pump attached to the subframe 10. A pump case 13 for accommodating 19 is a hermetically sealed container having an oil sump 12 for accommodating lubricating oil at the bottom while accommodating all of the above-described components (see, for example, Patent Document 1).

  FIG. 17 is an enlarged cross-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 auxiliary bearing 9, in which 14a is an inner ring of the ball bearing 14, 14b is an outer ring of the ball bearing 14, 11a Is a through hole formed in the pump case 11 through which the main shaft 4 is inserted, 15 is a gap between the inner peripheral surface of the through hole 11a and the main shaft 4, 16 is a recess formed in the upper surface of the pump case 11, and 10a is in the subframe 10. It is a formed oil drainage passage.

  Next, the operation of this scroll compressor will be described. The main shaft 4 is rotationally 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 an auxiliary 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 stationary scroll 1 and the low-temperature and low-pressure gas refrigerant is sucked into the sealed container 13. It becomes a high-temperature and high-pressure gas refrigerant and is sent out of the sealed container 13. Further, part of the gas refrigerant sucked into the sealed container 13 circulates in the space above and below the motor to cool the motor.

Further, as the main shaft 4 rotates, the pump 19 connected to the main shaft 4 is rotated, whereby the lubricating oil in the oil sump 12 is sucked and supplied to the upper end portion of the main shaft 4 through the oil supply hole 4a. After lubricating the bearing 6, the rocking bearing 7, the thrust bearing 17, and the like, the oil flows down through the sealed container 13 and returns to the oil sump 12. Further, as indicated by arrows 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 concave portion 16, and after lubricating it, the oil sump passes through the oil drain passage 10a. Return to 12.
Japanese Utility Model Publication No. 5-66292 (first page, second page, FIG. 1)

  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 11a and the main shaft 4. Therefore, in order to obtain a predetermined oil supply amount, it is necessary to process the through-hole 11a and the main shaft 4 with high accuracy. However, such high-accuracy processing is actually difficult, so that In some cases, the ball bearing 14 may be abnormally worn, seized, or generate abnormal noise.

  The present invention has been made to solve such problems, and it is easy to set the oil supply amount to the ball bearing pivotally supporting the lower end portion of the main shaft to a predetermined oil supply amount. An object of the present invention is to obtain a scroll compressor capable of preventing the wear and seizure of a ball bearing due to an insufficient amount.

In order to achieve the above object, a scroll compressor according to the present invention includes a sealed container having an oil sump at the bottom, and a fixed scroll and a swing that are arranged in the upper part of the sealed container to form a compression chamber by combining the spiral protrusions of each other. A subframe that pivotally supports the main shaft through a 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 fits the lower end of the main shaft. And an oil supply hole formed through the main shaft in the axial direction and supplying at least lubricating oil in an oil sump to the sliding portion of the orbiting scroll. A second oil introduction hole formed in the peripheral surface of the main shaft at a position where the other end opening is inserted into the ball bearing, and the main shaft is cut out in the radial direction from the peripheral surface to A space and the second oil guide hole forming the first cutouts communicating, by notch depth of the first cut-out portion, sets a fuel supply amount to the ball bearings to a predetermined quantity of oil Is.

In addition, the main shaft is provided with a second oil guide hole formed on the peripheral surface of the main shaft with one end opening formed in the oil supply hole and the other end opening inserted into the ball bearing. A first notch is provided at a position that does not directly communicate with the hole in the circumferential direction of the main shaft, and the second oil guide hole and the first notch are formed on the peripheral surface of the main shaft at a position where it is fitted into the ball bearing. An annular groove that communicates is formed, and the amount of oil supplied to the ball bearing is determined by the depth of the annular groove.

  Also, a second oil guiding ring body is provided surrounding the vicinity of the peripheral surface position of the main shaft corresponding to the upper end position of the first notch, and guides the lubricating oil released from the first notch to the ball bearing. Is formed integrally with the subframe.

  Further, a second oil that is 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 the inner ring and the outer ring of the ball bearing. The oil drain passage is formed at least in the subframe.

According to the scroll compressor according to the present invention, the second oil guide hole is formed in the main shaft on the peripheral surface of the main shaft in which the one end opening is formed in the oil supply hole and the other end opening is inserted into the ball bearing. provided with a, to form a first cutouts for communicating the upper space of the ball bearing and the second oil guide hole by cutting the main axis from the peripheral surface in the radial direction, cutting the first cut-out portion The oil supply amount to the ball bearing is set to a predetermined oil supply amount according to the notch depth, so that when a part of the lubricating oil rising up the oil supply hole reaches one end opening of the second oil introduction hole, the spindle rotates. Branching out into the second oil guide hole due to the centrifugal force accompanying, and entering the first notch from the second oil guide hole, and further discharged from the first notch and supplied to the ball bearing. predetermined but the notch depth of the first cut-out portion, the oil supply amount to the ball bearings Since setting the oil supply amount, it is easy to set to a predetermined amount of oil can be prevented wear and seizure of the ball bearing due to insufficient lubrication amount.

In addition, the main shaft is provided with a second oil guide hole formed on the peripheral surface of the main shaft with one end opening formed in the oil supply hole and the other end opening inserted into the ball bearing. A first notch is provided at a position that does not directly communicate with the hole in the circumferential direction of the main shaft, and the second oil guide hole and the first notch are formed on the peripheral surface of the main shaft at a position where it is fitted into the ball bearing. Since the annular groove that communicates is formed and the amount of oil supplied to the ball bearing is determined by the depth of the annular groove, the lubricating oil branched and led out to the second oil guide hole passes through the annular groove and the first notched portion . Although it is supplied to the bearing, the amount of oil supplied to the ball bearing is determined by the depth of the annular groove, so it becomes even easier to set the specified amount of oil and wear and seizure of the ball bearing due to insufficient oil supply. Can be prevented.

  Also, a second oil guiding ring body is provided surrounding the vicinity of the peripheral surface position of the main shaft corresponding to the upper end position of the first notch, and guides the lubricating oil released from the first notch to the ball bearing. However, since the lubricating oil discharged from the first cutout portion collides with the inner peripheral wall of the second oil guide ring body, it flows down along the inner peripheral wall. Thus, since the ball bearing is guided to the ball bearing, the lubrication of the ball bearing can be performed more reliably, and the second oil guide ring body is formed integrally with the subframe, so that the number of parts does not increase.

  Further, a second oil that is 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 the inner ring and the outer ring of the ball bearing. Since the oil drainage passage is formed at least in the sub-frame, the lubricating oil supplied to the upper end side of the ball bearing flows down the gap formed between the inner ring and the outer ring of the ball bearing, and the lower end of this gap Since the oil is discharged into the space below the subframe through the opening and the second oil discharge passage and returned to the oil sump, the lubricating oil is smoothly circulated and the ball bearing can be lubricated more reliably.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

Embodiment 1 FIG.
FIG. 1 is a cross-sectional view of a scroll compressor according to the first embodiment, and FIG. 2 is an enlarged cross-sectional view of a main part of the scroll compressor according to the first embodiment. The same reference numerals are given and description thereof is omitted. In the example of the present embodiment, the main shaft 4 is provided with a first oil introduction hole 4b in which one end opening is formed in the oil supply hole 4a and the other end opening is formed in the peripheral surface of the main shaft 4 above the ball bearing 14. . As shown in FIG. 2, the first oil guide hole 4 b is formed in a direction perpendicular to the axis of the main shaft 4, and communicates the oil supply hole 4 a with the space above 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, whereby the lubricating oil in the oil sump 12 is sucked and supplied to the upper end portion of the main shaft 4 through the oil supply hole 4a. After lubricating the dynamic bearing 7 and the thrust bearing 17, the oil flows down through the sealed container 13 and returns to the oil sump 12. Further, as indicated by an arrow in FIG. 2, when a part of the lubricating oil that rises through the oil supply hole 4 a reaches one end opening of the first oil guide hole 4 b, the first is caused by the centrifugal force accompanying the rotation of the main shaft 4. Branching out into the oil guide hole 4 b, discharged from the other end opening of the first oil guide hole 4 b, and 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, and therefore processing for setting the predetermined amount of oil is easy. In addition, 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, a necessary and sufficient amount of lubricating oil can be supplied to the ball bearing 14, and the ball bearing 14 can be a highly reliable scroll compressor that is less likely to be worn or seized.

  Note that if the first oil guide hole 4b is formed obliquely as shown in FIG. 3, the oil supply to the ball bearing 14 can be more reliably performed as compared to the case where it is formed horizontally as shown in FIG. . 2 and 3 show the case where the pump 19 is a positive displacement type, the pump may be a centrifugal type or other type.

Embodiment 2. FIG.
FIG. 4 is an enlarged cross-sectional view of a main part of the scroll compressor according to the second embodiment. In FIG. In the present embodiment, a first oil guide ring body 21 surrounding the vicinity of the peripheral surface position of the main shaft 4 corresponding to the opening position of the first oil guide hole 4b is provided. The first oil guide ring body 21 is formed in a substantially cylindrical shape, and has an inward flange portion 22 formed integrally at its upper end, and the electric motor with the flange portion 22 facing upward. Attached to the lower end of the rotor 5. The first oil guide ring body 21 is formed in such a size that the lower end thereof faces through a slight gap without contacting the upper end of the subframe 10.

  Since it is configured in this way, as shown by an arrow in FIG. 4, when the lubricating oil released from the first oil guide hole 4 b hits the inner peripheral wall of the first oil guide ring body 21, It flows down along the peripheral wall and is guided to the ball bearing 14. Therefore, for example, when the scroll compressor that is controlled at a variable speed using an inverter is operated on the high speed side, the lubricant discharged from the first oil guide hole 4b is scattered outside the ball bearing 14. Further, it is possible to avoid such a situation that the oil is circulated by the gas refrigerant flowing in the sealed container 13 and is sucked into the compression chamber to cause the oil to rise, and the ball bearing 14 is more reliably lubricated.

  The first oil guide ring body 21 may have any shape and attachment method as long as it guides the lubricating oil discharged from the first oil guide hole 4b to the ball bearing 14. For example, as shown in FIG. In addition, the first oil guide ring body 21 may be attached to the upper end of the subframe 10.

Embodiment 3 FIG.
FIG. 6 is an enlarged cross-sectional view of a main part of the scroll compressor according to the third embodiment. In FIG. 6, the same components as those of the second embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, the cylindrical portion 10b of the subframe 10 that supports 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 oil guide ring body 21 is formed. Thus, even if the first oil guide ring body 21 is formed integrally with the subframe 10, the same effect as that of the above embodiment can be obtained, and the first oil guide as in the above embodiment. Compared to the case where the ring body 21 is formed of a member independent of the subframe 10, the number of parts can be reduced.

Embodiment 4 FIG.
FIG. 7 is an enlarged cross-sectional view of a main part of the scroll compressor according to the fourth embodiment. In FIG. 7, the same components as those of the third embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, the pump case 11 that contacts the lower end surface of the ball bearing 14 is notched downward from its upper surface, and from a position facing the gap 14 c formed between the inner ring 14 a and the outer ring 14 b of the ball bearing 14. A cutout portion 11 b reaching the outer peripheral end of the pump case 11 is formed. Further, the subframe 10 is cut out in the radial direction from the inner peripheral surface of the portion accommodating the pump case 11, and a cutout portion 10c is formed from the position facing the cutout portion 11b to the lower end portion of the subframe 10. Yes. And the 1st drainage passage 23 which connects the lower end opening of the space | gap 14c and the space under the sub-frame 10 is comprised from the notch part 11b and the notch part 10c.

  Since it is configured in this way, as indicated by an 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 flows down the gap 14c. The oil is discharged into the space below the subframe 10 through the lower end opening of 14 c and the first oil discharge passage 23, and returned to the oil sump 12. Therefore, as in the case where the lower end opening of the gap 14c is closed, the lubricating oil supplied to the ball bearing 14 overflows from the gap 14c, scatters outside the first oil guide ring body 21, and is sealed. It is no longer possible for the oil to rise due to the gas refrigerant circulating in 13 and to be sucked into the compression chamber. Further, since the lubricating oil is smoothly circulated, the ball bearing 14 is more reliably lubricated.

  The first oil discharge passage 23 can be formed in any part of the subframe 10 as long as the lubricant can be taken out from the lower end opening of the gap 14c and discharged into the space below the subframe 10. I do not care.

Embodiment 5 FIG.
FIG. 8 is an enlarged cross-sectional view of a main part of the scroll compressor according to the fifth embodiment. In FIG. 8, the same components as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted. In the present embodiment, an 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 the pin 25 is positioned in the up-down direction by abutting the upper end of the ring-shaped member 24 on the main shaft 4. Used to be fixed to the main shaft 4.

  When the oil supply amount to the ball bearing 14 is set by the hole diameter of the first oil guide hole 4b, a thin drill blade is used when the set oil amount is small and the hole diameter of the first oil guide hole 4b is made small. However, in this case, since the thin drill blade is inferior in durability, the tool cost is high. If the hole diameter is extremely small, the drill may not be able to open the first oil guide hole 4b. However, in this embodiment, the amount of oil supplied to the ball bearing 14 is set by the opening area of the first oil introduction hole 4b limited by the opening area limiting means 24. Therefore, even when the set amount of oil is small, the first oil supply amount is set. Since the hole diameter of the oil guide hole 4b can be increased to a certain extent and a thick drill blade having high durability can be used, the cost for drilling the first oil guide hole 4b can be reduced.

  In this embodiment, the opening area limiting means 24 is a ring-shaped member. However, the opening area limiting means can be any one that can limit the opening area on the circumferential surface side of the main shaft 4 of the first oil guide hole 4b. For example, a small plate-like member may be fixed to the peripheral surface of the main shaft 4 to limit the opening area of the first oil introduction hole 4b.

Embodiment 6 FIG.
9 is an enlarged cross-sectional view of the main part of the scroll compressor according to Embodiment 6, and FIG. 10 is a cross-sectional view of the main part cut along the line AA of FIG. Are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, the main shaft 4 is provided with a second oil introduction hole 4e in which one end opening is formed in the oil supply hole 4a and the other end opening is formed in the circumferential surface of the ball bearing insertion portion 4d of the main shaft 4. In addition, a ball bearing insertion portion 4d of the main shaft 4 is cut out in the radial direction from the peripheral surface, and a first cutout portion 4f that communicates the space above the ball bearing 14 and the second oil guide hole 4e is formed. Is formed.

  Since it is configured in this way, as shown by the arrow in FIG. 9, when a part of the lubricating oil that rises in the oil supply hole 4a reaches the one end opening of the second oil introduction hole 4e, the rotation of the main shaft 4 rotates. Is branched into the second oil guide hole 4e by the centrifugal force accompanying the first, and enters the first cutout portion 4f through the second oil guide hole 4e. And it discharge | releases from the upper end part of the 1st notch part 4f, and is supplied to the ball bearing 14. FIG.

  In the present embodiment, since 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 4f, processing for setting a predetermined amount of oil 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 diameter of the second oil guide hole 4e can be increased to a certain extent, and a thick drill blade with high durability can be used. The shape of the first notch 4f is arbitrary without being limited to the present embodiment.

Embodiment 7 FIG.
11 is an enlarged cross-sectional view of the main part of the scroll compressor according to the seventh embodiment, and FIG. 12 is a cross-sectional view of the main part cut along the line BB of FIG. Are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, the second oil guide hole 4e and the first cutout portion 4f are formed at positions that differ 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.

  Since it is configured in this way, as shown by the arrows in FIGS. 11 and 12, when a part of the lubricating oil rising up the oil supply hole 4a 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 annular groove 4g through the second oil guide hole 4e. Then, it flows in the annular groove 4g and enters the first notch 4f, is discharged from the upper end of the first notch 4f, and is supplied to the ball bearing 14.

  In the present embodiment, since the amount of oil supplied to the ball bearing 14 is determined by the depth L of the annular groove 4g, the processing for setting the predetermined amount of oil becomes even easier. In this embodiment, in order to increase the resistance when the lubricating oil flows through the annular groove 4g by increasing the distance from the second oil guide hole 4e to the first notch 4f, the second The oil guide hole 4e and the first cutout portion 4f are formed at positions that are 180 ° different from each other in the circumferential direction. However, in the circumferential direction of the formation position of the second oil guide hole 4e and the first cutout portion 4f, The deviation may be any number of times.

Embodiment 8 FIG.
FIG. 13 is an enlarged cross-sectional view of a main part of the scroll compressor according to the eighth embodiment. In FIG. 13, the same components as those of the seventh embodiment are denoted by the same reference numerals, and the description thereof is omitted. In the present embodiment, the cylindrical portion 10b of the subframe 10 that 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 A second oil guide ring body 26 is formed.

  Since it is configured in this way, as shown by an arrow in FIG. 13, when the lubricating oil released from the upper end of the first cutout portion 4 f hits the inner peripheral wall of the second oil guide ring body 26, Since it flows down along this inner peripheral wall and is guided to the ball bearing 14, the lubrication of the ball bearing 14 becomes more reliable. Further, since the second oil guide ring body 26 is formed integrally with the subframe 10, the number of parts does not increase because the second oil guide ring body 26 is provided.

Embodiment 9 FIG.
FIG. 14 is an enlarged cross-sectional view of a main part of the scroll compressor according to the ninth embodiment. In FIG. In the present embodiment, the pump case 11 that contacts the lower end surface of the ball bearing 14 is notched downward from its upper surface, and from a position facing the gap 14c formed between the inner ring 14a and the outer ring 14b of the ball bearing 14. A cutout portion 11 b reaching the outer peripheral end of the pump case 11 is formed. Further, a communication hole 10 d is formed in the subframe 10 so as to communicate with the cutout portion 11 b at the upper end and open at the bottom of the subframe 10 at the lower end. And the 2nd oil drainage passage 27 which connects the lower end opening of the space | gap 14c and the space under the sub-frame 10 is comprised from the notch part 11b and the communicating hole 10d.

  Since it is configured in this way, as indicated by an arrow in FIG. 14, the lubricating oil supplied to the upper end side of the ball bearing 14 flows down the gap 14c, and the lower end opening of the gap 14c and the second oil drain passage 27 is discharged to the space below the subframe 10 and returned to the oil sump 12. Accordingly, the lubricating oil is smoothly circulated, and the ball bearing 14 can be more reliably lubricated.

  The second oil drain passage 27 may be formed in any part of the subframe 10 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.

Embodiment 10 FIG.
FIG. 15 is an enlarged cross-sectional view of a main part of the scroll compressor according to the tenth embodiment. In FIG. In the present embodiment, the second notch 4 h is formed along the peripheral surface of the main shaft 4 by chamfering the step portion formed at the position corresponding to the lower end position of the ball bearing 14 of the main shaft 4. It is formed in an annular shape. The main shaft 4 is provided with a third oil introduction hole 28 having one end opening formed in the oil supply hole 4a and the other end opening formed in the second notch 4h. Further, a pump case 11c (blocking member) that is in contact with the lower end surface of the ball bearing 14 and closes the lower end opening of the gap 14c formed between the inner ring 14a and the outer ring 14b is notched downward from the upper surface. A third notch portion 11c that communicates the second notch portion 4h and the gap 14c is formed.

  With this configuration, when a part of the lubricating oil rising through the oil supply hole 4a reaches the one end opening of the third oil guide hole 28, the third guide is caused by the centrifugal force accompanying the rotation of the main shaft 4. A branch is led out to the oil hole 28. Then, it passes through the third oil guide hole 28 and enters the second cutout portion 4h, flows in the second cutout portion 4h in the circumferential direction, and enters the third cutout portion 11c. It is supplied to the lower end opening of the gap 14c through the cut portion 11c. Then, while lubricating the ball bearing 14, the gap 14c is raised and discharged from the upper end opening.

  In the present embodiment, since the amount of oil supplied to the ball bearing 14 is determined by the chamfer dimension of the second notched portion 4h, the processing for setting the predetermined amount of oil is extremely easy. Further, since the lubricating oil supplied to the lower end opening of the gap 14c is discharged from the upper end opening of the gap 14c, the lubricating oil is circulated smoothly, and the lubricating oil is supplied from the upper end side of the ball bearing 14. It is not necessary to form an oil drain passage.

  In the present embodiment, the case where the closing member that closes the lower end opening of the gap 14c is the pump case 11 is shown. However, the closing member is not limited to the pump case 11, and any closing member is used. Even if it exists, it is possible to form the 3rd notch 11c. The second notch 4h is not limited to chamfering, and may be formed by cutting the main shaft into a groove shape.

It is sectional drawing of the scroll compressor which concerns on Embodiment 1 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 1 of this invention. It is a principal part expanded sectional view of the scroll compressor which shows another structure of a 1st oil guide hole. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 2 of this invention. It is a principal part expanded sectional view of the scroll compressor which shows another structure of a 1st oil guide ring body. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 3 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 4 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 5 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 6 of this invention. FIG. 10 is a cross-sectional view taken along line AA in FIG. 9. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 7 of this invention. FIG. 12 is a sectional view taken along the line BB in FIG. 11. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 8 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 9 of this invention. It is a principal part expanded sectional view of the scroll compressor which concerns on Embodiment 10 of this invention. It is sectional drawing of the scroll compressor which concerns on a prior art example. It is a principal part expanded sectional view of the scroll compressor which concerns on a prior art example.

Explanation of symbols

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

Claims (4)

A closed container having an oil sump at the bottom, a fixed scroll and an orbiting scroll which are arranged in the upper part of the closed container to form a compression chamber by combining the spiral protrusions of each other; A main shaft that is slidably connected to the dynamic scroll, a sub-frame that pivotally supports the main shaft via a ball bearing that is fitted into a lower end of the main shaft, and a shaft that penetrates the main shaft in the axial direction. A scroll compressor provided with an oil supply hole formed at least for supplying lubricating oil in the oil sump to the sliding portion of the orbiting scroll;
The main shaft is provided with a second oil introduction hole formed in the peripheral surface of the main shaft, with one end opening formed in the oil supply hole and the other end opening inserted into the ball bearing. an upper space and the second oil guide hole of the ball bearing to form a first cutouts communicating by notching from the circumferential surface radially notch depth of the first cut-out portion A scroll compressor characterized in that the oil supply amount to the ball bearing is set to a predetermined oil supply amount. A closed container having an oil sump at the bottom, a fixed scroll and an orbiting scroll which are arranged in the upper part of the closed container to form a compression chamber by combining the spiral protrusions of each other; A main shaft that is slidably connected to the dynamic scroll, a sub-frame that pivotally supports the main shaft via a ball bearing that is fitted into a lower end of the main shaft, and a shaft that penetrates the main shaft in the axial direction. A scroll compressor provided with an oil supply hole formed at least for supplying lubricating oil in the oil sump to the sliding portion of the orbiting scroll;
The main shaft is provided with a second oil introduction hole formed in the circumferential surface of the main shaft at one end opening formed in the oil supply hole and the other end opening inserted into the ball bearing . A first notch is provided at a position that does not directly communicate with the oil guide hole in the circumferential direction of the main shaft, and the second oil guide hole and the second are provided on a peripheral surface of the main shaft at a position where the main shaft is inserted into a ball bearing. 1 of the cutout forms an annular groove which communicates, features and be away crawling compressor that determines the amount of oil to the ball bearing by the depth of the annular groove.   A second oil guiding ring provided surrounding the vicinity of the peripheral surface position of the main shaft corresponding to the upper end position of the first notch, and guiding the lubricant discharged from the first notch to the ball bearing; The scroll compressor according to claim 1 or 2, wherein a body is formed integrally with the subframe.   A lubricating oil discharged from the first cutout and supplied to the ball bearing is discharged into 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. 4. The scroll compressor according to claim 1, wherein at least two oil discharge passages are formed in the sub-frame. 5.

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