JP5540577B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor.

  The scroll compressor disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2003-286949) is a hermetic compressor in which a motor is built in a hermetic container. The oil is lubricated to the bearing part etc. by circulating. In the scroll compressor described in Patent Document 1, the oil in the oil reservoir at the bottom of the sealed container is rotated to the upper end of the crankpin shaft through the oil supply path inside the crankpin shaft by the action of a pump built in the crankpin shaft. The movable scroll is lifted into the movable scroll boss. Thereby, the sliding parts such as the inside of the boss of the movable scroll and the upper main bearing are lubricated.

  In addition, in order to supply oil to the contact surface where the movable scroll and the fixed scroll slide, it has also been proposed to provide a supply path for supplying oil to the contact surface from the space inside the movable scroll boss through the inside of the movable scroll. ing.

  However, chipping (due to low load operation or external factors, the movable scroll moves relatively downward from the fixed scroll, and as a result, oil leaks to the outside of the compression chamber and conversely the high pressure inside the casing into the compression chamber. When gas blow occurs on the crankpin shaft due to gas flow phenomenon), high-pressure gas escapes from the high-pressure space inside the movable scroll boss and the upper main bearing to the space on the contact surface side between the movable scroll and the fixed scroll. As a result, there is a possibility that oil will not be supplied to the inside of the boss of the movable scroll and the upper main bearing. For this reason, there is a risk of damaging the inside of the bosses of these movable scrolls and bearing portions such as the upper main bearing.

  An object of the present invention is to provide a scroll compressor that can stably supply oil to a bearing portion even at the time of gas blow on a crankpin shaft and prevent damage to the bearing.

A scroll compressor according to a first aspect of the present invention includes a movable scroll, a fixed scroll, and a crankpin shaft. In the movable scroll, a spiral wrap is provided on one surface of a flat end plate, and a cylindrical boss is provided on the other surface. In the fixed scroll, a spiral wrap which forms a compression chamber in combination with a wrap of a movable scroll is provided on one surface of a flat end plate. The crankpin shaft has a crankpin that is rotatably connected to the boss of the movable scroll, and is formed with an oil supply hole penetrating in the axial direction. A lateral hole communicating with the oil supply hole is formed in the crankpin to supply oil to the sliding surface on the outer periphery of the crankpin. A first space above the crankpin shaft inside the boss and a second space outside the boss are formed. A supply path for supplying a part of the oil sucked up from the oil supply hole inside the crankpin shaft from the first space to the contact surface between the movable scroll and the fixed scroll is formed inside the movable scroll. The first space and the second space are communicated with each other by a communication path having a larger flow path diameter than a bearing gap that is a gap between the crankpin and the boss.

  Here, since the first space above the crank pin and the second space B outside the boss communicate with each other through a communication path having a flow path diameter wider than the bearing gap, even when a gas blow occurs, the crank pin and the boss Oil supply to the gap can be continued. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  A scroll compressor according to a second aspect is the scroll compressor according to the first aspect, wherein the communication path is a space surrounded by a non-circular part of the outer peripheral surface of the crankpin and a boss.

  Here, since the communication path is a space surrounded by a non-circular part of the outer peripheral surface of the crankpin and the boss, a large-diameter communication path is easily formed by machining the crankpin. It is possible.

  A scroll compressor according to a third aspect is the scroll compressor according to the second aspect, wherein the crank pin has a D-shaped cross section.

  Here, since the crankpin has a D-shaped cross section, it is possible to form a large-diameter communication path more easily by cutting the crankpin and removing a part thereof.

  A scroll compressor according to a fourth aspect is the scroll compressor according to the second aspect, wherein the crank pin has a groove extending in an axial direction of the crank pin on an outer peripheral surface thereof.

  Here, since the crankpin has a groove extending in the axial direction of the crankpin on the outer peripheral surface thereof, it is possible to easily form a large-diameter communication path, and to improve the escape of gas during gas blow. Can prevent surrounding oil shortage.

  A scroll compressor according to a fifth aspect is the scroll compressor according to the first aspect, wherein the communication path is formed inside the crankpin.

  Here, since the communication path is formed inside the crankpin, it is possible to continuously supply oil to the gap between the crankpin and the boss even when gas blow occurs. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  A scroll compressor according to a sixth aspect of the present invention is the scroll compressor according to the first aspect of the present invention, wherein the communication path is formed in the boss.

  Here, since the communication path is formed in the boss, oil supply to the gap between the crankpin and the boss can be continued even when gas blow occurs. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  A scroll compressor according to a seventh aspect is the scroll compressor according to the sixth aspect, wherein the communication path is formed so as to penetrate from the outer peripheral surface of the boss to the inner peripheral surface.

  Here, since the communication path is formed so as to penetrate from the outer peripheral surface of the boss to the inner peripheral surface, it is possible to continuously supply oil to the gap between the crankpin and the boss even when gas blow occurs. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved. Further, since the communication path is formed so as to penetrate from the outer peripheral surface of the boss to the inner peripheral surface, it is easy to form the communication path.

  The scroll compressor according to an eighth aspect of the present invention is the scroll compressor according to the sixth aspect of the present invention, wherein the communication path is formed so as to penetrate the inside of the boss along the axial direction.

  Here, since the communication passage is formed so as to penetrate the inside of the boss along the axial direction, the oil supply to the gap between the crankpin and the boss can be continued even when gas blow occurs. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  A scroll compressor according to a ninth aspect of the present invention is the scroll compressor according to the eighth aspect of the present invention, wherein the communication path is formed on the side farther from the supply path than the crankpin in the interior of the boss.

  Here, since the communication path is formed on the side farther from the supply path than the crankpin in the interior of the boss, during normal operation, the oil rising from the oil supply hole is preferentially supplied to the supply path, The surplus oil can be released to the second space outside the boss using the communication path.

  A scroll compressor according to a tenth aspect of the present invention is the scroll compressor according to the eighth aspect of the present invention, wherein the communication path is formed on the side closer to the supply path than the crankpin within the boss.

  Here, since the communication path is formed on the side closer to the supply path than the crankpin in the inside of the boss, the processing of the communication path is easy.

  A scroll compressor according to an eleventh aspect of the invention is the scroll compressor according to the eighth to tenth aspects of the invention, further comprising a bearing metal having a C-shaped cross section provided on the inner peripheral surface of the boss. The communication path is disposed apart from the joint of the bearing metal in the inside of the boss.

  Here, since the communication path is arranged apart from the joint of the bearing metal inside the boss, the influence on the roundness of the C-shaped bearing metal is small, and the wear and damage of the bearing metal is reduced. It is possible to suppress.

  A scroll compressor according to a twelfth aspect of the present invention is the scroll compressor according to any of the first to eleventh aspects of the present invention, further comprising a positive displacement pump that supplies oil to an oil supply hole of the crankpin shaft.

  Here, since the positive displacement pump is further provided, oil is sucked up by the positive displacement pump, and is supplied from the crankpin shaft to the gap between the crankpin and the boss through the oil supply hole a. In addition, oil can be evenly supplied to the compression chambers inside and outside the wrap through the first space inside the movable scroll and the supply path.

  According to the first aspect of the invention, even when gas blow occurs, it is possible to continuously supply oil to the gap between the crankpin and the boss. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  According to the second invention, a large-diameter communication path can be easily formed by processing the crankpin.

  According to the third aspect of the present invention, a large-diameter communication path can be formed more easily by cutting and partially removing the crankpin.

  According to the fourth aspect of the present invention, it is possible to easily form a large-diameter communication path, and it is possible to improve the escape of gas at the time of gas blow and to prevent oil shortage around the crankpin.

  According to the fifth aspect of the invention, even when gas blow occurs, it is possible to continuously supply oil to the gap between the crankpin and the boss. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  According to the sixth aspect of the invention, even when gas blow occurs, it is possible to continuously supply oil to the gap between the crankpin and the boss. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  According to the seventh aspect of the invention, even when gas blow occurs, it is possible to continuously supply oil to the gap between the crankpin and the boss. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved. Further, since the communication path is formed so as to penetrate from the outer peripheral surface of the boss to the inner peripheral surface, it is easy to form the communication path.

  According to the eighth aspect of the invention, even when gas blow occurs, the oil supply to the gap between the crankpin and the boss can be continued. For this reason, there is no possibility of damage to the bearing portion around the crankpin and other bearing portions around the crankpin shaft, and the reliability of the scroll compressor is improved.

  According to the ninth aspect of the invention, during normal operation, oil rising from the oil supply hole can be preferentially supplied to the supply path, and the excess oil can be released to the second space outside the boss using the communication path.

  According to the tenth aspect, the processing of the communication path is easy.

  According to the eleventh invention, the influence on the roundness of the C-shaped bearing metal is small, and wear and damage of the bearing metal can be suppressed.

  According to the twelfth aspect of the present invention, oil is sucked up by the positive displacement pump and supplied from the crankpin shaft to the gap between the crankpin and the boss through the oil supply hole a. In addition, oil can be evenly supplied to the compression chambers inside and outside the wrap through the first space inside the movable scroll and the supply path.

The longitudinal cross-sectional view of the scroll compressor concerning 1st Embodiment of this invention. Cross-sectional explanatory drawing which shows the mode of the oil supply of the crankpin axis | shaft vicinity of FIG. Cross-sectional explanatory drawing which shows the mode of the oil supply of the crankpin shaft vicinity vicinity of the scroll compressor concerning 2nd Embodiment of this invention. Cross-sectional explanatory drawing which shows the mode of the oil supply of the crankpin shaft vicinity vicinity of the scroll compressor concerning 3rd Embodiment of this invention. Cross-sectional explanatory drawing which shows the mode of the oil supply of the crankpin shaft vicinity vicinity of the scroll compressor concerning 4th Embodiment of this invention. VI-VI sectional view taken on the line of FIG. Cross-sectional explanatory drawing which shows the mode of the oil supply of the crankpin shaft vicinity vicinity of the scroll compressor concerning 5th Embodiment of this invention.

  Next, an embodiment of the scroll compressor of the present invention will be described with reference to the drawings.

[First Embodiment]
A scroll compressor 1 shown in FIG. 1 is a high and low pressure dome type scroll compressor, and constitutes a refrigerant circuit together with an evaporator, a condenser, an expansion mechanism, etc., and compresses refrigerant gas in the refrigerant circuit. Is responsible for.

  The scroll compressor 1 mainly includes a vertically long cylindrical sealed dome-shaped main body casing 10, a scroll compression mechanism 15, a crankpin shaft 17 as a drive shaft, an Oldham ring 39, a motor 16, a lower main bearing 60, and a suction pipe 19. , The discharge pipe 20, the oil return guide 71, and the oil separation plate 73. Hereinafter, the components of the scroll compressor 1 will be described in detail.

[Details of components of scroll compressor 1]
(1) Main Body Casing The main body casing 10 is a vertically long closed container, and has a substantially cylindrical body casing part 11 and a bowl-shaped upper wall part 12 that is welded to the upper end of the body part casing part 11 in an airtight manner. And a bowl-shaped bottom wall portion 13 that is welded to the lower end portion of the body casing portion 11 in an airtight manner. The main body casing 10 mainly accommodates a scroll compression mechanism 15 that compresses the refrigerant gas and a motor 16 disposed below the scroll compression mechanism 15. The scroll compression mechanism 15 and the motor 16 are connected by a crankpin shaft 17 disposed so as to extend in the vertical direction in the main body casing 10. As a result, a gap space 18 is generated between the scroll compression mechanism 15 and the motor 16.

(2) Scroll Compression Mechanism As shown in FIG. 1, the scroll compression mechanism 15 mainly includes a housing 23, a fixed scroll 24 disposed in close contact with the housing 23, and a movable meshing with the fixed scroll 24. And a scroll 26.

  Hereinafter, the components of the scroll compression mechanism 15 will be described in detail.

a) Fixed Scroll As shown in FIG. 1, the fixed scroll 24 mainly includes a flat plate 24a and a spiral (involute) wrap 24b formed on the lower surface of the plate 24a. .

  A discharge port 41 communicating with a compression chamber 40 described later is formed in the end plate 24a so as to penetrate substantially the center of the end plate 24a. The discharge port 41 is formed so as to extend in the vertical direction at the central portion of the end plate 24a.

  The discharge port 41 is formed on the upper surface of the end plate 24a. The enlarged concave portion 42 is constituted by a concave portion that is recessed in the upper surface of the end plate 24a and extends in the horizontal direction. A lid 44 is fastened and fixed to the upper surface of the fixed scroll 24 by bolts 44 a so as to close the enlarged concave portion 42. And the muffler space 45 which consists of an expansion chamber which silences the driving | running | working sound of the scroll compression mechanism 15 by covering the expansion recessed part 42 with the cover body 44 is formed. The fixed scroll 24 and the lid 44 are sealed by being brought into close contact via a packing (not shown).

b) Moveable Scroll As shown in FIG. 1, the movable scroll 26 is mainly formed on the end plate 26a, a spiral (involute) wrap 26b formed on the upper surface of the end plate 26a, and the lower surface of the end plate 26a. The boss 26c is a bearing portion and the groove portions 26d formed at both ends of the end plate 26a.

  The movable scroll 26 is an outer drive movable scroll. That is, the movable scroll 26 has a boss 26 c that is rotatably connected to the outside of the crankpin 17 b at the tip of the crankpin shaft 17.

  The movable scroll 26 is supported by the housing 23 by fitting an Oldham ring 39 into the groove 26d. A crank pin 17b at the upper end of the crank pin shaft 17 is inserted into the boss 26c. The movable scroll 26 revolves in the housing 23 without being rotated by the rotation of the crankpin shaft 17 by being incorporated in the scroll compression mechanism 15 in this way. The wrap 26b of the movable scroll 26 is meshed with the wrap 24b of the fixed scroll 24, and a compression chamber 40 is formed between the contact portions of both the wraps 24b and 26b. In the compression chamber 40, the volume between the laps 24b and 26b contracts toward the center as the movable scroll 26 revolves. In the scroll compressor 1 according to the present embodiment, the refrigerant gas is compressed in this way.

  As shown in FIGS. 1 and 2, a supply path 81 extending in the radial direction and having an inner end communicating with the inside of the boss 26 c is formed inside the end plate 26 a of the movable scroll 26. The outer end portion of the supply path 81 is sealed with a seal member 83. Further, a vertical hole 82 is formed in the end plate 26 a so as to penetrate toward the contact surface 84 of the end plate 26 a of the movable scroll 26 and the end plate 24 a of the fixed scroll 24.

  Accordingly, the oil pressurized by the positive displacement pump 85 rises through the oil supply hole 17a penetrating the inside of the crankpin shaft 17 in the axial direction, and the upper part of the crankpin shaft 17 above the boss 26c of the movable scroll 26 is described later. Once stored in one space A. The oil stored in the first space A flows into a supply path 81 formed in the radial direction inside the end plate 26 a of the movable scroll 26. Further, the oil flows from the supply path 81 to the vertical hole 82, whereby oil can be supplied to the contact surface 84 of the end plate 26 a of the movable scroll 26 and the end plate 24 a of the fixed scroll 24.

  A bearing metal 87 having a substantially C-shaped cross section is fitted on the inner peripheral surface of the boss 26 c of the movable scroll 26.

c) Housing The housing 23 is press-fitted and fixed to the body casing portion 11 over the entire outer circumferential surface in the circumferential direction. That is, the body casing part 11 and the housing 23 are in close contact with each other in an airtight manner over the entire circumference. For this reason, the inside of the main body casing 10 is partitioned into a high-pressure space 28 below the housing 23 and a low-pressure space 29 above the housing 23. The fixed scroll 24 is fastened and fixed to the housing 23 with bolts (not shown) so that the upper end surface is in close contact with the lower end surface of the fixed scroll 24. The housing 23 is formed with a crank chamber 31 that is recessed in the center of the upper surface and a bearing portion 32 that extends downward from the center of the lower surface. A bearing hole 33 penetrating in the vertical direction is formed in the bearing portion 32, and the crank pin shaft 17 is rotatably fitted in the bearing hole 33 via a bearing 34. The housing 23 is formed with an oil passage 35 that leads from the crank chamber 31 (that is, a circumferential space B described later) to the outer peripheral surface. Through the oil passage 35, the oil inside the crank chamber 31 (circumferential space B) can be returned to the oil sump P at the bottom of the main body casing 10.

  Further, a C ring 89 is provided on the upper surface of the housing 23 to prevent gas leakage from the gap between the movable scroll 26 and the end plate 26a, and to maintain the high pressure inside the crank chamber 31 (circumferential space B). It is.

d) Others Although not shown in the drawing, the scroll compression mechanism 15 allows the refrigerant gas exiting from the discharge port 41 of the fixed scroll 24 to pass through a vertically extending communication passage formed near the outer periphery of the housing 23. Then, it flows out into the gap space 18. A part of the refrigerant gas flowing out into the gap space 18 passes through the core cut portion formed on the outer peripheral surface of the stator 51 of the motor 16 and descends to the lower portion of the motor 16, and then passes through the other core cut portions. It rises through and returns to the gap space 18, and is then discharged from the discharge pipe 20 to the outside of the main body casing 10 together with another refrigerant gas that swirls the gap space 18 along the inner periphery of the body casing portion 11. .

(3) Crankpin shaft The crankpin shaft 17 is a drive shaft that transmits the driving force of the motor 16 to the scroll compression mechanism 15, and penetrates the crankpin shaft 17 in the axial direction of the crankpin shaft 17. An oil supply hole 17a is formed.

  The crankpin shaft 17 is rotatably supported inside the main body casing 10 by the bearing portion 32 and the lower main bearing 60 of the housing 23. An intermediate portion of the crankpin shaft 17 is concentrically connected to the rotor 52 of the motor 16.

  A crankpin 17 b is provided at the upper end of the crankpin shaft 17 so as to be eccentric from the intermediate portion of the crankpin shaft 17. The crank pin 17 b is inserted into the boss 26 c of the movable scroll 26. As a result, the movable scroll 26 can revolve by rotating the crankpin shaft 17 by the driving force of the motor 16.

  In addition, a lateral hole 17c that communicates with an oil supply hole 17a extending in the axial direction is formed inside the crankpin 17b of the crankpin shaft 17, so that oil can be supplied to the sliding surface on the outer periphery of the crankpin 17b. .

  Further, at the lower end of the crankpin shaft 17, a positive displacement pump 85 that sucks up oil in the oil reservoir P into the oil supply hole 17 a of the crankpin shaft 17 is provided. The positive displacement pump 85 rotates together with the crankpin shaft 17 and sucks up oil using the centrifugal force generated at that time.

  As shown in FIGS. 1 and 2, a first space A is formed above the crankpin 17b at the tip of the crankpin shaft 17 inside the boss 26c of the movable scroll 26, and a second space B outside the boss 26c is formed. ing.

  The supply passage 81 and the vertical hole described above serve as a supply passage for supplying a part of the oil sucked up from the oil supply hole 17 a inside the crankpin shaft 17 to the contact surface 84 between the movable scroll 26 and the fixed scroll 24 from the first space A. 82 is formed inside the movable scroll 26.

  Between the first space A and the second space B, a gas having a larger flow path diameter (inner diameter of about 1 to 2 mm) than a bearing gap G (usually about several tens of microns) that is a gap between the crankpin 17b and the boss 26c. The communication path 86 allows communication.

  As described above, the upper space A and the circumferential space B of the crank pin 17b communicate with each other through the gas venting gas passage 86 having a flow path diameter wider than the bearing gap G. It can be carried out.

  The gas communication path 86 in FIGS. 1 and 2 is a space surrounded by a notch portion 17d and a boss 26c in which a part of the outer peripheral surface of the crankpin 17b has a non-circular D-shaped cross section.

(4) Oldham ring The Oldham ring 39 is a member for preventing the rotational movement of the movable scroll 26 as described above, and is fitted into an Oldham groove (not shown) formed in the housing 23. The Oldham groove is an oval groove and is disposed at a position facing each other in the housing 23.

(5) Motor The motor 16 is a DC motor in the present embodiment, and mainly includes an annular stator 51 fixed to the inner wall surface of the main casing 10 and a slight gap (air gap) inside the stator 51. And a rotor 52 accommodated rotatably with a passage). The motor 16 is arranged such that the upper end of the coil end 53 formed on the upper side of the stator 51 is substantially at the same height as the lower end of the bearing portion 32 of the housing 23.

  A copper wire is wound around the teeth portion of the stator 51, and coil ends 53 are formed above and below. Further, the outer peripheral surface of the stator 51 is provided with core cut portions that are notched at a plurality of locations from the upper end surface to the lower end surface of the stator 51 and at predetermined intervals in the circumferential direction. A motor cooling passage 55 extending in the vertical direction is formed between the body casing portion 11 and the stator 51 by the core cut portion.

  Further, as shown in FIG. 1, an oil return channel 74 capable of lowering the oil is formed between the stator 51 and the main body casing 10. The oil return passage 74 is configured by a groove-shaped core cut portion 51 a formed in the outer peripheral surface of the stator 51 and extending in the vertical direction.

  The rotor 52 is drivably coupled to the movable scroll 26 of the scroll compression mechanism 15 via a crankpin shaft 17 disposed at the shaft center of the trunk casing 11 so as to extend in the vertical direction.

(6) Lower Main Bearing The lower main bearing 60 is disposed in the lower space below the motor 16. The lower main bearing 60 is fixed to the trunk casing 11 and constitutes a lower end bearing of the crankpin shaft 17 to support the crankpin shaft 17.

(7) Suction Pipe The suction pipe 19 is for guiding the refrigerant in the refrigerant circuit to the scroll compression mechanism 15 and is fitted into the upper wall portion 12 of the main casing 10 in an airtight manner. The suction pipe 19 penetrates the low pressure space 29 in the vertical direction, and an inner end portion is fitted into the fixed scroll 24.

(8) Discharge pipe The discharge pipe 20 is for discharging the refrigerant in the main body casing 10 to the outside of the main body casing 10, and is fitted in the body casing portion 11 of the main body casing 10 in an airtight manner. The discharge pipe 20 is opened at a position protruding from the inner surface of the body to the center.

(9) Oil Return Guide As shown in FIG. 1, the oil return guide 71 is a member having a flow path 71 a that communicates between the oil passage 35 of the housing 23 and the upper opening 74 a of the oil return flow path 74. . The oil return guide 71 has a flow path 71 a formed of a thin metal plate or the like, and is fixed to the inner surface of the body casing portion 11 so as to be disposed between the housing 23 and the motor 16.

(10) Oil Separation Plate As shown in FIG. 1, the oil separation plate 73 is a plate-like member that is disposed below the stator 51 in the main body casing 10 and separates oil from the descending refrigerant gas. The oil separation plate 73 is fixed to the lower surface side of the lower main bearing 60. The oil separation plate 73 is partially cut off at a portion below the lower opening 74 b of the oil return channel 74.

[Operation of scroll compressor 1]
Next, the operation of the scroll compressor 1 will be briefly described with reference to FIG. First, when the motor 16 is driven, the crankpin shaft 17 is rotated, and the revolving operation is performed without the movable scroll 26 rotating. Then, the low-pressure refrigerant gas is sucked into the compression chamber 40 from the peripheral side of the compression chamber 40 through the suction pipe 19 and is compressed along with the volume change of the compression chamber 40 to become a high-pressure refrigerant gas. The high-pressure refrigerant gas is discharged from the central portion of the compression chamber 40 through the discharge port 41 to the muffler space 45, and then flows out to the gap space 18 through a communication passage (not shown) of the housing 23. And this refrigerant gas is partly divided and flows in the circumferential direction along the inner peripheral surface of the trunk casing 11. At this time, the lubricating oil mixed in the refrigerant gas is separated. On the other hand, the other part of the divided refrigerant gas flows downward in the motor cooling passage 55, flows to the lower motor space, and then reverses to be an air gap passage between the stator 51 and the rotor 52, Alternatively, it flows in the other motor cooling passage 55 upward. Thereafter, the rising refrigerant gas merges with the other refrigerant gas in the gap space 18 and is discharged from the discharge pipe 20 to the outside of the main casing 10. The refrigerant gas discharged to the outside of the main casing 10 circulates through the refrigerant circuit, and is again sucked into the scroll compression mechanism 15 through the suction pipe 19 and compressed.

  Further, the scroll compressor 1 sucks up the oil in the oil sump P by the pumping action of the positive displacement pump 85 inside the main body casing 10, passes through the oil supply hole 17 a and the lateral hole 17 c from the crankpin shaft 17, and the boss 17 Lubricate to the gap with 26c. At the same time, the oil can be evenly supplied to the compression chambers 40 inside and outside the wrap 26b through the first space A inside the movable scroll 26, the supply path 81 and the vertical hole 82 (see the two-dot chain line arrow in FIG. 2). ).

  Although not shown, oil supply to the upper and lower bearing portions (the bearing portion 32 of the housing 23 and the lower main bearing 60) of the crankpin shaft 17 is also a horizontal hole (not shown) branched from the oil supply hole 17a inside the crankpin shaft 17. To be refueled appropriately.

  Further, since the upper space A and the circumferential space B of the crank pin 17b communicate with each other through a gas venting gas passage 86 having a flow path diameter wider than the bearing gap G, when gas blow occurs due to chipping or the like. However, the high-pressure gas inside the circumferential space B is guided to the upper space A through the gas communication path 86 and then escapes to the contact surface 84 and the compression chamber 40 via the supply path 81 and the vertical hole 82 (FIG. 2). The oil supply to the gap between the crankpin 17b and the boss 26c can be continued.

<Characteristics of First Embodiment>
(1)
In the scroll compressor 1 of the first embodiment, the upper space A and the circumferential space B of the crank pin 17b are communicated with each other by a gas communication passage 86 for venting gas having a flow path diameter wider than the bearing gap G. Accordingly, even when gas blow occurs due to chipping or the like, the high-pressure gas inside the circumferential space B passes through the gas communication path 86, the upper space A, the supply path 81, and the vertical hole 82, and the contact surface 84 and Since it can be smoothly extracted into the compression chamber 40, oil supply to the gap between the crankpin 17b and the boss 26c can be continued. For this reason, there is no risk of damage to the bearing portion around the crankpin 17b and other bearing portions around the crankpin shaft 17, and the reliability of the scroll compressor is improved.

(2)
In the scroll compressor 1 of the first embodiment, the gas communication path 86 is a space surrounded by a part of the outer peripheral surface of the crankpin 17b made noncircular and the boss 26c. By processing, a large-diameter gas communication passage 86 can be easily formed.

(3)
Furthermore, in the scroll compressor 1 according to the first embodiment, the crank pin 17b is partly non-circular so as to have a D-shaped cross section, and therefore the crank pin 17b is cut with a milling machine or the like. By removing a part, it is possible to form the gas communication passage 86 having a large diameter more easily.

(4)
Furthermore, since the scroll compressor 1 of the first embodiment includes the positive displacement pump 85 that supplies oil to the oil supply hole 17a of the crankpin shaft 17, the positive displacement pump 85 sucks up the oil in the oil reservoir P, Oil is supplied from the crankpin shaft 17 through the oil supply hole 17a and the lateral hole 17c to the gap between the crankpin 17b and the boss 26c. At the same time, the oil can be evenly supplied to the compression chambers 40 inside and outside the wrap 26b through the upper space A, the supply path 81, and the vertical hole 82 inside the movable scroll 26.

<Modification of First Embodiment>
(A)
In the scroll compressor 1 of the first embodiment, the crankpin 17b is processed so as to have a D-shaped cross section in order to make a part of the outer peripheral surface of the crankpin 17b noncircular. It is not limited. As a modification of the first embodiment, the crank pin 17b may have a groove (width of about 1 to 2 mm) extending in the axial direction of the crank pin 17b on its outer peripheral surface. It is possible to form a gas communication path, and it is possible to improve the escape of gas at the time of gas blowing and to prevent oil shortage around the crankpin 17b.

[Second Embodiment]
In the first embodiment described above, the gas communication passage 86 for venting gas having a flow path diameter wider than the bearing gap G that connects the upper space A and the circumferential space B of the crankpin 17b is provided on the outer peripheral surface of the crankpin 17b. Although a part is formed in a D shape by making it non-circular, the present invention is not limited to this, and it is possible to form a gas communication path in other paths.

  As shown in FIG. 3, the scroll compressor according to the second embodiment is different from the first embodiment in that a gas communication passage 91 is formed inside the crank pin 17b. It is common with the scroll compressor 1 of one embodiment.

  The gas communication path 91 has a flow path diameter (about 1 to 2 mm) wider than the bearing gap G (several tens of microns), its lower end opening communicates with the circumferential space B, and its intermediate part is a crank pin. 17b extends in the axial direction, and its upper end opening communicates with the upper space A.

<Features of Second Embodiment>
(1)
Also in the second embodiment, the gas communication path 91 formed inside the crankpin 17b has a flow path diameter in which the upper space A and the circumferential space B of the crankpin 17b are wider than the bearing gap G. Even when gas blow occurs due to chipping or the like, the high-pressure gas in the circumferential space B is compressed through the gas communication passage 91, the upper space A, the supply passage 81, and the vertical hole 82 and the contact surface 84. Since it can be smoothly extracted into the chamber 40, the oil supply to the gap between the crankpin 17b and the boss 26c can be continued. For this reason, there is no risk of damage to the bearing portion around the crankpin 17b and other bearing portions around the crankpin shaft 17, and the reliability of the scroll compressor is improved.

(2)
Moreover, since the gas communication path 91 is formed inside the crank pin 17b, the bearing gap G between the outer peripheral surface of the crank pin 17b and the boss 26c is constant over the entire circumference, and between the crank pin 17b and the boss 26c. The support state is stable, and the wear of the bearing portion can be further reduced.

[Third Embodiment]
In the scroll compressor of the third embodiment, as shown in FIG. 4, the gas communication path 95 is a further path of the gas communication path having a wide flow path diameter that communicates the upper space A and the circumferential space B. The boss 26c is formed so as to penetrate in the thickness direction (in other words, the radial direction). Other configurations are common to the scroll compressor 1 of the first embodiment.

<Features of Third Embodiment>
(1)
Also in the third embodiment, the gas communication passage 95 formed so as to penetrate from the outer peripheral surface of the boss 26c to the inner peripheral surface has a bearing gap G (several tens of microns) between the upper space A and the circumferential space B of the crankpin 17b. ) Wider channel diameter (about 1 to 2 mm). As a result, even when gas blow occurs due to chipping or the like, the high pressure gas in the circumferential space B passes through the gas communication path 95 and passes through the upper space A, the supply path 81 and the vertical hole 82 to contact the surface 84. And since it can be smoothly extracted to the compression chamber 40, the oil supply to the gap between the crank pin 17b and the boss 26c can be continued. For this reason, there is no risk of damage to the bearing portion around the crankpin 17b and other bearing portions around the crankpin shaft 17, and the reliability of the scroll compressor is improved.

(2)
Further, since the gas communication passage 95 is formed so as to penetrate from the outer peripheral surface of the boss 26c to the inner peripheral surface, the formation of the gas communication passage 95 is easy.

[Fourth Embodiment]
In the scroll compressor according to the fourth embodiment, as shown in FIG. 5, the gas communication path 98 is provided as another path of the gas communication path having a wide flow path diameter that communicates the upper space A and the circumferential space B. The inside of the boss 26c is formed so as to penetrate along the axial direction. Other configurations are common to the scroll compressor 1 of the first embodiment.

  Specifically, the gas communication path 98 in FIGS. 5 to 6 is the back side of the bearing metal 87 (the side not in contact with the crank pin 17b) inside the boss 26c and is supplied with the crank pin 17b interposed therebetween. It is arranged on the opposite side to the path 81.

  Further, as shown in FIG. 6, the gas communication path 98 is separated from the joint 87a which is the open portion of the C-shaped bearing metal 87 within the boss 26c (preferably the crank pin 17b is inserted). It is arranged on the opposite side of the joint 87a.

<Features of Fourth Embodiment>
(1)
Also in the fourth embodiment, the gas communication passage 98 formed through the inside of the boss 26c along the axial direction has a bearing gap G (several tens of microns) between the upper space A and the circumferential space B of the crankpin 17b. ) Wider channel diameter (about 1 to 2 mm). As a result, even when gas blow occurs due to chipping or the like, the high pressure gas in the circumferential space B passes through the gas communication path 98 through the upper space A, the supply path 81, and the vertical hole 82, and the contact surface 84 And since it can be smoothly extracted to the compression chamber 40, the oil supply to the gap between the crank pin 17b and the boss 26c can be continued. For this reason, there is no risk of damage to the bearing portion around the crankpin 17b and other bearing portions around the crankpin shaft 17, and the reliability of the scroll compressor is improved.

(2)
In the fourth embodiment, the gas communication path 98 in FIGS. 5 to 6 is located on the side farther from the supply path than the crankpin in the boss 26c, that is, opposite to the supply path 81 with the crankpin 17b interposed therebetween. Therefore, during normal operation, the oil rising from the oil supply hole 17a can be preferentially supplied to the supply passage 81, and the excess oil can be released to the circumferential space B using the gas communication passage 98. It is.

(3)
In the fourth embodiment, as shown in FIG. 6, the gas communication path 98 is disposed apart from the joint 87 a of the C-shaped bearing metal 87 in the inside of the boss 26 c. The influence on the roundness of the letter-shaped bearing metal 87 is small, and the wear and damage of the bearing metal 87 can be suppressed.

[Fifth Embodiment]
In the scroll compressor of the fifth embodiment, as shown in FIG. 7, the gas communication path 101 is a further path of the gas communication path having a wide flow path diameter that communicates the upper space A and the circumferential space B. The inside of the boss 26c is formed so as to penetrate along the axial direction, and the inside of the boss 26c is disposed on the back side of the bearing metal 87 and close to the supply path 81. Other configurations are common to the scroll compressor 1 of the first embodiment.

  Specifically, the gas communication path 101 in FIG. 7 is in the vicinity of the communication portion between the upper space A and the supply path 81 and communicates with the supply path 81 from below in a straight tube shape. Also in this case, the gas communication path 101 communicates the upper space A and the circumferential space B via a part of the supply path 81.

<Features of Fifth Embodiment>
(1)
Also in the fifth embodiment, the gas communication passage 101 formed so as to penetrate the inside of the boss 26c along the axial direction has an upper space A and a circumferential space B wider than the bearing gap G (several tens of microns). It has a channel diameter (about 1 to 2 mm). As a result, even when gas blow occurs due to chipping or the like, the high-pressure gas inside the circumferential space B passes through the gas communication path 101 or the path via the supply path 81 and the vertical hole 82 or the upper space A. Since it can be smoothly pulled out to the contact surface 84 and the compression chamber 40 through one of the paths via the path 81 and the vertical hole 82, oil supply to the gap between the crank pin 17b and the boss 26c is continuously performed. Can do. For this reason, there is no risk of damage to the bearing portion around the crankpin 17b and other bearing portions around the crankpin shaft 17, and the reliability of the scroll compressor is improved.

(2)
Further, in the fifth embodiment, the gas communication path 101 of FIG. 7 is disposed on the side close to the supply path 81 in the boss 26c, and communicates with the supply path 81 from below in a straight tube shape. The shape of the communication path is simple and the distance is short, and the processing of the gas communication path 101 is easy.

<Modification of Fifth Embodiment>
Also in the fifth embodiment, similarly to the fourth embodiment, the direction of the joint 87a of the C-shaped bearing metal 87 is adjusted as appropriate, and the joint 87a of the bearing metal 87 having the C-shaped bearing metal 87 is formed. If the arrangement is away from the bearing, the influence on the roundness of the C-shaped bearing metal 87 is small, and the wear and damage of the bearing metal 87 can be suppressed.

    The present invention can be variously applied to a scroll compressor having an oil supply hole on a crankpin shaft.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 17 Crank pin shaft 17a Oil supply hole 17b Crank pin 17c Lateral hole 17d Notch part 26 Movable scroll 26a End plate 26b Lap 26c Boss 81 Supply path 82 Vertical hole 84 Contact surface 85 Positive displacement pumps 86, 91, 95, 98, 101 Gas communication passage 87 Bearing metal 87a Joint A Upper space (first space)
B Circumferential space (second space)
G Bearing clearance

JP 2003-286949 A

Claims (12)

A movable scroll (26) in which a spiral wrap (26b) is provided on one surface of a flat end plate (26a) and a cylindrical boss (26c) is provided on the other surface;
A fixed scroll (24) provided with a spiral wrap (24b) that forms a compression chamber (40) in combination with a wrap (26b) of the movable scroll (26) on one surface of a flat end plate (24a). )When,
A crankpin shaft (17) having a crankpin (17b) rotatably connected to a boss (26c) of the movable scroll (26) and having an oil supply hole (17a) formed in the axial direction;
With
A lateral hole (17c) communicating with the oil supply hole (17a) is formed in the crankpin (17b) to supply oil to the sliding surface on the outer periphery of the crankpin (17b).
A first space (A) above the crankpin shaft (17) inside the boss (26c) and a second space (B) outside the boss (26c) are formed,
Part of the oil sucked up from the oil supply hole (17a) inside the crankpin shaft (17) is transferred from the first space (A) to the contact surface (84) between the movable scroll (26) and the fixed scroll (24). A supply path (81) for supplying is formed inside the movable scroll (26),
Between the first space (A) and the second space (B), a communication path having a larger flow path diameter than a bearing gap (G) that is a gap between the crank pin (17b) and the boss (26c) ( 86, 91, 95, 98, 101),
Scroll compressor (1). The communication path (86) is a space surrounded by a part of the outer peripheral surface of the crankpin that is made non-circular and the boss (26c).
The scroll compressor (1) according to claim 1. The crankpin has a D-shaped cross section,
The scroll compressor (1) according to claim 2. The crank pin (17b) has a groove extending in the axial direction of the crank pin (17b) on the outer peripheral surface thereof.
The scroll compressor (1) according to claim 2. The communication path (91) is formed inside the crank pin (17b).
The scroll compressor (1) according to claim 1. The communication path (95, 98, 101) is formed in the boss (26c),
The scroll compressor (1) according to claim 1. The communication path (95) is formed so as to penetrate from the outer peripheral surface of the boss (26c) to the inner peripheral surface.
The scroll compressor (1) according to claim 6. The communication path (98, 101) is formed through the inside of the boss (26c) along the axial direction.
The scroll compressor (1) according to claim 6. The communication path (98) is formed on the side farther from the supply path than the crankpin (17b) in the boss (26c).
The scroll compressor (1) according to claim 8. The communication path (101) is formed on the side closer to the supply path than the crankpin (17b) in the boss (26c).
The scroll compressor (1) according to claim 8. A bearing metal having a C-shaped cross section provided on the inner peripheral surface of the boss (26c);
The communication path (98, 101) is disposed apart from the joint (87a) of the bearing metal (87) in the boss (26c).
The scroll compressor (1) according to any one of claims 8 to 10. A positive displacement pump (85) for supplying oil to the oil supply hole (17a) of the crankpin shaft (17);
The scroll compressor (1) according to any one of claims 1 to 11.

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