JP2007247567A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To inhibit complication of a structure and rise of manufacturing cost, and to improve reliability by surely lubricating necessary sections in a scroll compressor. <P>SOLUTION: A fixed scroll 12 including a scroll lap 25 is fixed on a housing 11. A scroll lap 28 of a turning scroll 13 including the scroll lap 28 is supported by the housing in such a manner that revolution of the same is obstructed but that rotation of the same is possible under a condition where the same meshes with the scroll lap 25 of the fixed scroll 12. Consequently, a compression chamber 29 is defined between both of the laps. A drive shaft 14 is supported by the housing 11 in such a manner that the same can drive and rotate, and a balance bush 51 of an eccentric shaft 50 engages with the turning scroll 13. Consequently, the turning scroll can turn. A lubrication passage 64 supplying refrigerant gas containing lubricating oil mist to an engagement part with the turning scroll 13 is provided on an outer circumference surface of the balance bush 51. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention particularly relates to a scroll compressor suitable for use in an in-vehicle air conditioner or the like.

  In a general scroll compressor, a fixed scroll having a spiral wall standing on one surface of an end plate is fixed in a housing, and the wall of the fixed scroll is substantially fixed on one surface of the end plate. An orbiting scroll having a spiral wall of the same shape is supported, and each wall is combined and accommodated. The drive shaft is rotatably supported in the housing and can be driven and rotated by a motor. And the eccentric part formed in the edge part of this drive shaft is fitted in the boss part protrudingly provided by the other surface of the end plate of a turning scroll.

  Therefore, when the drive shaft is driven to rotate, the rotational force is transmitted to the orbiting scroll through the eccentric portion, and the orbiting scroll revolves while preventing rotation, so that the volume of the compression chamber formed between the wall bodies is reduced. The fluid gradually decreases and the fluid sucked into the compression chamber can be compressed and discharged as a compressed fluid.

  By the way, in this scroll compressor, since it is necessary to supply lubricating oil to the bearing portion of the drive shaft or the fitting portion between the eccentric portion and the orbiting scroll, the mist-like fluid is sucked into the housing from the suction portion. Gas containing lubricating oil is used. Therefore, the gas containing mist-like lubricating oil sucked into the suction chamber is compressed in the compression chamber and then sent to the discharge chamber, and is discharged from the discharge chamber to the outside. The lubricant is supplied to a fitting portion between the rotary scroll and the orbiting scroll, or the lubricating oil is separated from the gas by an oil separator, and the separated lubricating oil is supplied to the eccentric portion and the fitting portion.

  As such a conventional scroll compressor, there is one described in Patent Document 1 below. The scroll type fluid machine described in Patent Document 1 includes a movable scroll that meshes with a fixed scroll, and rotates a drive shaft that has an eccentric shaft portion at an end portion and an oil supply opening on an end surface of the eccentric shaft portion. The eccentric shaft portion is slidably connected to the movable scroll via a bearing portion, and the eccentric shaft portion is eccentric within a predetermined range from the eccentric direction of the eccentric shaft portion to the anti-rotation direction of the drive shaft. An oil supply notch is provided on the outer peripheral surface of the shaft so as to reach the end surface.

Japanese Patent No. 3279236

  In the conventional scroll compressor described above, the lubricating oil in the oil reservoir at the bottom of the container is pushed up in the oil supply passage formed in the drive shaft by the centrifugal pump, discharged from the oil supply opening of the eccentric shaft portion, and the movable scroll through the oil supply notch To the sliding part. However, in the conventional scroll compressor, the lubricating oil accumulated in the oil sump at the bottom of the container is pushed up in the oil supply passage in the drive shaft using a centrifugal pump and supplied to the sliding portion. And an oil supply passage must be formed in the drive shaft, which not only complicates the structure but also increases the manufacturing cost.

  The present invention solves such a problem, and provides a scroll compressor that improves the reliability by suppressing the complication of the structure and the increase in the manufacturing cost and by lubricating the necessary portions with certainty. For the purpose.

  In order to achieve the above object, a scroll compressor according to claim 1 of the present invention includes a housing having a suction portion for sucking a fluid containing mist-like lubricating oil, and a discharge portion for discharging a compressed fluid obtained by compressing the fluid. A fixed scroll having a spiral wall plate and an end plate fixed to the housing; and a spiral wall member having a spiral wall and the wall body meshing with the fixed scroll wall. A revolving scroll supported by the housing so as to be revolved while forming a compression chamber and being prevented from rotating, and a revolving scroll supported by the housing so as to be rotatable and being able to revolve by engaging with the revolving scroll A drive shaft having an eccentric portion, and a fluid formed on the outer peripheral surface of the eccentric portion and sucked into the housing from the suction portion to an engagement portion between the eccentric portion and the orbiting scroll It is characterized in that comprises a lubrication passage for feeding.

  In the scroll compressor according to a second aspect of the present invention, the oil return passage, the eccentric portion is formed in a cylindrical shape with an eccentric shaft provided at an end portion of the drive shaft, and is fitted to the outer periphery of the eccentric shaft. A balance bush, and the balance bush is fitted into a cylindrical boss provided on an end plate of the orbiting scroll via a floating bush and a bearing, and the lubricating passage is formed on the outer periphery of the balance bush. It is characterized by being formed by cutting out the part.

  In a scroll compressor according to a third aspect of the present invention, the lubrication passage is provided outside a bearing load acting range in the eccentric portion.

  In the scroll compressor according to claim 4, the bearing portion that rotatably supports the drive shaft on the housing and the engaging portion in which the eccentric portion engages with the orbiting scroll are partitioned with respect to the suction portion. And a supply passage for supplying the compressed fluid from the compression chamber to the mechanical chamber, and the compressed fluid supplied from the compression chamber to the mechanical chamber through the supply passage is provided in the lubrication passage. It is characterized by flowing.

  The scroll compressor according to a fifth aspect of the invention is characterized in that a balance weight is integrally provided in the eccentric portion.

  In the scroll compressor according to a sixth aspect of the present invention, the balance weight includes a weight portion having an arc shape, and a notch portion is formed in an inner peripheral portion of an intermediate position in the arc direction in the weight portion. Yes.

  In a scroll compressor according to a seventh aspect of the present invention, the notch portion of the balance weight is provided on the opposite side of the lubrication passage with respect to the rotation center of the drive shaft.

  A scroll compressor according to an eighth aspect of the present invention includes a housing having a suction portion for sucking fluid and a discharge portion for discharging compressed fluid obtained by compressing the fluid, a spiral wall plate, and the end plate being the housing. A fixed scroll fixed to the wall and a spiral-shaped wall body, and the wall body meshes with the wall body of the fixed scroll to form a compression chamber and to be able to revolve while being prevented from rotating. A rotating scroll supported by the housing, a drive shaft rotatably supported by the housing and having an eccentric portion that can be rotated by engaging the orbiting scroll, and an outer peripheral side of the eccentric portion. And a balance weight having a thin portion at an intermediate position in the circumferential direction.

  In the scroll compressor according to the ninth aspect of the present invention, the balance weight has a weight part having an arc shape connected to the eccentric part via a connection part, and the thin part has an arc direction in the weight part. It is characterized by being provided by forming a notch in the inner periphery of the intermediate position.

  According to the scroll compressor of the first aspect of the present invention, the housing having the suction portion for sucking the fluid containing the mist-like lubricating oil, the discharge portion for discharging the compressed fluid that has compressed the fluid, and the spiral wall A fixed scroll with a plate and an end plate fixed to the housing, and a wall with a spiral wall that engages the wall of the fixed scroll to form a compression chamber and prevent rotation The revolving scroll supported by the housing while being revolved, and a drive shaft that is rotatably supported by the housing and has an eccentric portion that can revolve the revolving scroll by engaging with the revolving scroll. A lubrication passage is provided on the outer peripheral surface of the part to supply the fluid sucked into the housing from the suction part to the engaging part between the eccentric part and the orbiting scroll.

  Accordingly, a fluid containing mist-like lubricating oil is sucked into the compression chamber from the suction portion, the orbiting scroll is swung and the volume of the compression chamber is gradually reduced, so that the fluid is compressed, and the compressed fluid is discharged from the discharge portion. At this time, the fluid sucked into the housing from the suction portion is supplied to the engagement portion between the eccentric portion and the orbiting scroll through the lubrication passage formed in the outer peripheral surface of the eccentric portion, and is contained in the fluid. When the lubricating oil is reliably supplied to the engaging portion and lubricated, the reliability can be improved, and the complexity of the structure and the increase in the manufacturing cost can be suppressed.

  According to the scroll compressor of the second aspect of the present invention, the eccentric portion is constituted by the eccentric shaft provided at the end portion of the drive shaft and the balance bush that is formed in a cylindrical shape and is fitted to the outer periphery of the eccentric shaft. The bush is fitted into a cylindrical boss provided on the end plate of the orbiting scroll via a floating bush and a bearing, and the lubrication passage is formed by cutting out the outer periphery of the balance bush. By providing the lubrication passage between them, the sliding portions of the balance bush, the floating bush, the bearing and the boss can be reliably lubricated.

  According to the scroll compressor of the invention of claim 3, since the lubrication passage is provided outside the bearing load acting range in the eccentric portion, the lubrication passage is formed in a range where the bearing load does not act on the eccentric portion from the orbiting scroll. Thus, an appropriate engagement relationship between the eccentric portion and the orbiting scroll can be maintained.

  According to the scroll compressor of the fourth aspect of the present invention, the mechanical chamber that partitions the bearing portion that rotatably supports the drive shaft on the housing and the engaging portion whose eccentric portion engages with the orbiting scroll with respect to the suction portion. And a supply passage for supplying compressed fluid from the compression chamber to the mechanical chamber is provided, and the compressed fluid supplied from the compression chamber to the mechanical chamber through the supply passage flows into the lubrication passage. Thus, the fluid can be reliably supplied from the compression chamber to the lubrication passage of the mechanical chamber through the supply passage.

  According to the scroll compressor of the invention of claim 5, since the balance weight is integrally provided in the eccentric portion, for example, the eccentric portion having the balance weight can be easily manufactured by a technique such as casting, thereby reducing the cost. Can be made possible.

  According to the scroll compressor of the invention of claim 6, since the weight portion having an arc shape is provided in the balance weight, and the notch portion is formed in the inner peripheral portion of the weight portion at the intermediate position in the arc direction. Stress acting on the balance weight can be dispersed, and durability can be improved.

  According to the scroll compressor of the seventh aspect of the invention, since the notch portion of the balance weight is provided on the opposite side of the lubrication passage with respect to the rotation center of the drive shaft, the notch portion and the lubrication passage are formed diagonally. It is possible to reduce the weight without impairing the function of the balance weight.

  According to the scroll compressor of the eighth aspect of the present invention, the housing having the suction portion for sucking the fluid and the discharge portion for discharging the compressed fluid obtained by compressing the fluid, the spiral wall plate, and the end plate A fixed scroll fixed to the housing and a spiral-shaped wall body, and the wall body meshes with the wall body of the fixed scroll to form a compression chamber and support the housing so that it can revolve while being prevented from rotating. And a drive shaft having an eccentric portion that is rotatably supported by the housing and engages with the orbiting scroll so as to be able to turn the orbiting scroll, and is connected to the outer peripheral side of the eccentric portion and is connected in the circumferential direction. Since a balance weight having a thin wall portion is provided at an intermediate position, when the orbiting scroll is turned through the eccentric portion by rotating the drive shaft, the balance weight causes the drive shaft to move to the drive shaft. The centrifugal force of the orbiting scroll to be used can be canceled out, and the stress acting on the balance weight can be dispersed by the thin-walled portion, so that the weight can be reduced and the durability can be improved. .

  According to the scroll compressor of the ninth aspect of the present invention, the weight portion having an arc shape connected to the eccentric portion via the connecting portion as the balance weight is provided, and the inner peripheral portion of the intermediate portion in the arc direction in the weight portion is provided. Since the notched portion is formed to form the thin portion, the stress acting on the balance weight can be easily dispersed with a simple configuration, and the durability can be improved.

  Embodiments of a scroll compressor according to the present invention will be described below in detail with reference to the drawings. In addition, this invention is not limited by this Example.

  FIG. 1 is a sectional view showing a scroll compressor according to an embodiment of the present invention, FIG. 2 is a front view of a balance bush in the scroll compressor of the present embodiment, and FIG. 3 is in the scroll compressor of the present embodiment. It is a perspective view of a balance bush.

  The scroll compressor of the present embodiment is mainly used for compressing a refrigerant of a vehicle air conditioner, and uses a refrigerant gas containing mist-like lubricating oil as a fluid.

  As shown in FIG. 1, the scroll compressor according to the present embodiment forms a compression chamber by being combined with a housing 11 having a hollow shape, a fixed scroll 12 fixed to the housing, and the fixed scroll 12. The orbiting scroll 13 supported by the housing, the drive shaft 14 having an eccentric portion that is rotatably supported by the housing 11 and engages with the orbiting scroll 13, and can rotate the orbiting scroll, and the drive shaft 14 is driven. It is comprised from the drive device 15 which rotates.

  The housing 11 is disposed horizontally and is configured as a sealed container having a substantially cylindrical shape that encloses the entire scroll compressor. The housing 11 includes a housing main body 21 having a substantially cylindrical shape and a lid portion 22 that closes an opening end portion of the housing main body 21. The housing body 21 has a shape in which a large-diameter portion 21a and a small-diameter portion 21b are integrally formed, and is fixed by a plurality of fastening bolts 23 in a state in which a lid portion 22 is fitted to the opening end portion of the housing body 21. Has been.

  The fixed scroll 12 has a disk-shaped disk (end plate) 24 and a spiral wrap (wall body) 25 formed on the surface of the disk 24. The fixed scroll 12 is disposed in the large-diameter portion 21 a of the main body housing 21, the back surface of the disk 24 is in close contact with the inner surface of the lid portion 22, and the outer peripheral portion is fitted to the inner peripheral surface of the lid portion 22. In this state, the lid portion 22 is fixed by fastening bolts 26. On the other hand, similarly to the fixed scroll 12, the orbiting scroll 13 has a disk-shaped disk (end plate) 27 and a spiral wrap (wall body) 28 formed on the surface of the disk 27. . The orbiting scroll 13 is disposed in the large-diameter portion 21 a of the main body housing 21, and the disc 27 is combined in such a manner that the spiral wrap 28 is engaged with the spiral wrap 25 of the fixed scroll 12. The rear surface of the housing abuts against the wall surface portion 21c of the housing main body 21, so that the movement in the axial direction is restricted. A compression chamber 29 is formed in the space between the spiral wraps 25 and 28.

  A suction chamber 30 is formed in the housing 11 on the outer peripheral side of a compression chamber 29 formed by combining the spiral scrolls 25 and 28 of the fixed scroll 12 and the orbiting scroll 13. Yes. The housing body 21 is formed with a suction port (suction part) 31 for sucking refrigerant gas containing lubricating oil in a mist form. The suction port 31 opens into the suction chamber 30.

  Further, a discharge chamber 32 defined by the fixed scroll 12 and the lid 22 is formed in the housing 11, and the compression chamber 29 and the discharge chamber 32 are communicated with each other by a discharge port 33. A discharge valve 34 for opening and closing the discharge port 33 is provided on the back surface of the disk 24 of the fixed scroll 12 on the discharge chamber 32 side. The discharge valve 34 is urged by a spring member (not shown) in close contact with the back surface of the disk 24 to close the discharge port 33. When the pressure in the compression chamber 29 exceeds a predetermined value, the compression of the compression chamber 29 is compressed. Since the gas moves the discharge valve 34 against the biasing force of the spring member, the discharge valve 34 can be separated from the back surface of the disk 24 to open the discharge port 33. The lid 22 is formed with a discharge port (discharge unit) 35 that discharges the compressed gas obtained by compressing the refrigerant gas to the outside, and the discharge port 35 opens into the discharge chamber 32.

  The drive shaft 14 is disposed in the small diameter portion 21 b of the housing 21 and is rotatably supported by a ball bearing 36 and a roller bearing 37. The small diameter portion 21b of the housing 21 is provided with a shaft seal 38 adjacent to the ball bearing 36 between the bearings 36 and 37 to prevent external leakage of the refrigerant gas in the housing 11. is doing.

  In the driving device 15, a rotating plate 39 is fixed to one end portion of the driving shaft 14 by a connecting bolt 40, and a plurality of support rings 42 are connected to the outer peripheral portion of the rotating plate 39 via a connecting ring 41. Are connected by connecting pins 43 and 44. The end surface of the driven pulley 45 is fixed to the support ring 42 and is rotatably supported on the outer peripheral portion of the small diameter portion 21b of the housing 21 via the bearing 46. An electromagnet 47 is mounted in the driven pulley 45. Thus, a magnetic clutch is configured. The driven pulley 45 is connected to a drive source (for example, an engine) via a drive belt (not shown).

Further, a boss 48 is formed on the back surface of the disk 27 in the orbiting scroll 13, so that a fitting recess 49 having the same center as the center of the orbiting scroll 13 is provided. On the other hand, a disc portion 14a supported by a roller bearing 37 is integrally formed at the other end portion of the drive shaft 14, and the disc portion 14a is eccentric by a predetermined amount d with respect to the center O ₁ of the drive shaft 14. An eccentric shaft 50 having a center O ₂ is provided. The balance bush 51 is fitted to the outer peripheral portion of the eccentric shaft 50, and the connecting shaft 52 is fitted into the disk portion 14a, so that the balance bush 51 can be rotated integrally with the eccentric portion 50. A floating bush 53 is mounted on the outer periphery of the balance bush 51. The floating bush 53 is inserted into the fitting recess 49, and a roller bearing 54 is interposed therebetween. In the present embodiment, the eccentric portion of the present invention is constituted by the eccentric shaft 50 and the balance bush 51, and the eccentric portion is fitted into the boss 48 in the orbiting scroll 13 via the floating bush 53 and the roller bearing 54. Thus, the eccentric shaft 50 and the orbiting scroll 13 can be rotated relative to each other.

  Further, a rotation restricting hole 55 is formed on the back surface of the disk 27 in the orbiting scroll 13. On the other hand, a rotation prevention pin 56 is fixed to the wall surface 21 of the housing main body 21 facing the back surface of the disk 27, and the tip of the rotation prevention pin 56 is inserted into the rotation restriction hole 55 on the back surface of the disk 27. Has been. In this embodiment, the rotation restricting hole 55 and the rotation preventing pin 56 constitute a rotation preventing mechanism for the orbiting scroll 13, and the orbiting scroll 13 can revolve in the radial direction while preventing rotation. It has become.

  The balance bush 51 is integrally provided with a balance weight 57 for canceling the unbalance amount generated in the orbiting scroll 13, and the centrifugal force of the orbiting scroll 13 acting on the drive shaft 14 by the balance weight 57. By canceling out, dynamic balance can be secured.

  By the way, in the scroll compressor described above, the refrigerant gas containing mist-like lubricating oil is sucked into the housing 11 from the suction port 31, and the refrigerant gas is compressed by the compression chamber 29 and discharged to the discharge chamber 33. By circulating the refrigerant gas through the sliding portion of the drive shaft 14, the lubricating oil is supplied to the sliding portion of the drive shaft 14, and the temperature rise due to heat generation at this sliding portion is suppressed, resulting in compression efficiency. The decrease in pressure and the increase in pressure loss are suppressed.

  That is, in the housing 11, the back surface of the disk 27 in the orbiting scroll 13 abuts on the wall surface 21 c of the housing body 21 and is supported so as to be able to pivot, so that the wall surface 21 c functions as a thrust bearing and And the drive shaft 14 side. Here, a roller bearing 37 that rotatably supports the drive shaft 14 on the housing 11 and a balance bush 51 as an eccentric portion engage with a boss 48 of the orbiting scroll 13 by the disk 27 and the shaft seal 38 in the orbiting scroll 13. A mechanical chamber 61 is provided that divides the floating bush 53 and the roller bearing 54 as engaging portions within the housing 11.

  A supply passage 62 for supplying the compressed gas in the compression chamber 29 to the mechanical chamber 61 is provided on the back surface of the disk 27 in the orbiting scroll 13 and discharge for discharging the compressed gas filled in the mechanical chamber 61 to the compression chamber 29. A passage 63 is provided. In this case, the compression chamber 29a in which the discharge passage 63 is opened is located in the vicinity of the suction chamber 30 and has substantially the same pressure as the suction chamber 30, while the orbiting scroll 13 is turned in the compression chamber 29b in which the supply passage 62 is opened. Then, the compression is started by the volume change, and the pressure is higher than that of the compression chamber 29a. Accordingly, when the orbiting scroll 13 is turned, the compressed gas in the compression chamber 29 b is supplied to the mechanical chamber 61 through the supply passage 62, and the compressed gas filled in the mechanical chamber 61 is discharged to the low-pressure compression chamber 29 a through the discharge passage 63. Is done.

  Further, in the mechanical chamber 61 partitioned in the housing 11, compared to the roller bearing 37 that supports the drive shaft 14, the engagement portion between the balance bush 51 and the boss 48, that is, the floating bush 53 and the roller bearing 54. Thus, the refrigerant gas (lubricating oil) is difficult to be supplied. Therefore, in this embodiment, a lubricating passage 64 for supplying the refrigerant gas supplied from the mechanical chamber 61 to the engaging portion (the floating bush 53 and the roller bearing 54) is formed on the outer peripheral surface of the balance bush 51.

That is, in the balance bush 51, as shown in detail in FIGS. 2 and 3, the bush main body 51a has a substantially cylindrical shape by forming a through hole 51b through which the eccentric shaft 50 penetrates in the center portion. The lubricating passage 64 described above is formed by cutting out a part of the outer peripheral portion of the main body 51a. The lubrication passage 64 is located between the bush body 51 a and the floating bush 53, and is provided so as to communicate the mechanical chamber 61 side and the back side of the fitting recess 49 in the boss 48. The lubrication passage 64 is provided outside the bearing load acting range in the balance bush 51. That is, when the drive shaft 14 rotates, the balance bush 51 performs an eccentric rotational motion together with the eccentric shaft 50, and this power is transmitted to the boss 48 via the fitting recess 49, so that the orbiting scroll 13 is prevented from rotating. While turning around. At this time, a bearing load acts on the outer peripheral surface of the balance bush 51 from the orbiting scroll 13 side with respect to the angle ranges θ ₁ and θ ₂ shown in FIG. Therefore, the lubrication passage 64 can be formed without impairing the original function of the balance bush 51 by cutting out the ranges outside the angle ranges θ ₁ and θ ₂ in the balance bush 51.

  Therefore, when the compressed gas in the compression chamber 29 b is supplied to the mechanical chamber 61 through the supply passage 62 during the turning of the orbiting scroll 13, the compressed gas containing mist-like lubricating oil is By being fully filled, the lubricating oil can be supplied to the roller bearing 37 of the drive shaft 14 and the sliding portion between the drive shaft 14 and the shaft seal 38. Further, the compressed gas containing the mist-like lubricating oil supplied to the mechanical chamber 61 flows through the lubricating passage 64 of the balance bush 51 to the back side of the fitting recess 49, so that the balance bush 51 and the boss Lubricating oil can be supplied to the floating bush 53, the roller bearing 54, and the like interposed between them.

  In this embodiment, the balance weight 57 is provided integrally with the balance bush 51 by casting, for example. In other words, the balance weight 57 has a weight portion 57a having an arc shape, and the weight portion 57a is integrally connected to the bush body 51a of the balance bush 51 via a plate-shaped connection portion 57b. Yes.

  Further, in the balance weight 57, the weight portion 57a has an arc shape having a predetermined thickness, and a notch portion 57c is formed in the inner peripheral portion at a substantially intermediate position in the arc direction, whereby a thin portion is formed here. 57d is formed. The thin portion 57 d (notch portion 57 c) of the balance weight 57 is provided on the opposite side of the lubrication passage 64 with respect to the rotation center of the drive shaft 14.

  Here, the operation of the scroll compressor of this embodiment described above will be described.

  When the drive source is driven, the drive force is transmitted to the driven pulley 45 of the drive device 15, the drive shaft 14 is driven to rotate, and the rotational force causes the balance bush 51 to rotate while rotating along with the eccentric shaft 50. Is transmitted to the orbiting scroll 15 via the boss 48. Then, the orbiting scroll 15 orbits on the revolution track while being prevented from rotating by the rotation preventing mechanism. As a result, a low-temperature refrigerant gas containing mist-like lubricating oil is sucked into the suction chamber 30 of the housing 11 from the suction port 31, and the refrigerant gas in the suction chamber 30 is sucked into the compression chamber 29.

  When the orbiting scroll 13 continues to orbit, the compression chamber 29 is gradually narrowed along with this, and the volume is reduced, so that the refrigerant gas inside flows into the central portion while being compressed, reaches the discharge port 33, and is discharged. The valve 34 opens and closes due to the differential pressure between the compression chamber 29 and the discharge chamber 32. That is, when the refrigerant gas in the compression chamber 29 is compressed and its pressure becomes higher than the pressure in the discharge chamber 32, the discharge valve 34 is pushed open, and the high-pressure refrigerant gas flows out into the discharge chamber 32. Thereafter, the high-pressure refrigerant gas is discharged from the discharge chamber 32 through the discharge port 35 to the outside.

  At this time, the refrigerant gas containing mist-like lubricating oil is sucked into the compression chamber 29, and the orbiting scroll 13 is rotated and the volume of the compression chamber 29 is gradually reduced. A part of the refrigerant gas in the chamber 29 b is supplied to the mechanical chamber 61 through the supply passage 62. Then, the refrigerant gas containing the mist-like lubricating oil supplied to the mechanical chamber 61 is filled over the entire region of the mechanical chamber 61, and the sliding between the roller bearing 37 of the drive shaft 14 and the drive shaft 14 and the shaft seal 38. Supply lubricating oil to parts. The refrigerant gas containing mist-like lubricating oil supplied to the mechanical chamber 61 flows through the lubrication passage 64 of the balance bush 51 to the back side of the fitting recess 49, and the balance bush 51 and the boss 48 are in contact with each other. Lubricating oil is supplied to the floating bush 53 and the roller bearing 54 interposed therebetween. Thereafter, the refrigerant gas filled in the mechanical chamber 61 is discharged through the discharge passage 63 to the low-pressure compression chamber 29a.

  Accordingly, by supplying the refrigerant gas in the middle of compression to the mechanical chamber 61, the lubricating oil contained in the refrigerant gas is properly supplied to the roller bearing 37 of the drive shaft 14 and the sliding portion between the drive shaft 14 and the shaft seal 38. The refrigerant gas is supplied from the lubrication passage 64 of the balance bush 51 to the floating bush 53 and the roller bearing 54 interposed between the balance bush 51 and the boss 48, so that the refrigerant gas is Even if it is difficult to enter, lubricating oil can be reliably supplied. As a result, a temperature rise due to heat generation at the sliding portion such as the drive shaft 14 is suppressed, and a decrease in compression efficiency and an increase in pressure loss due to this are suppressed.

  Further, when the drive shaft 14 is driven to rotate and the orbiting scroll 15 is revolved through the eccentric shaft 50 and the balance bush 51, the balance weight 57 rotates together with the eccentric shaft 50 and the balance bush 51. Therefore, the balance weight 57 can cancel the centrifugal force from the orbiting scroll 13 acting on the drive shaft 14, and a dynamic balance can be ensured. At this time, since the thin portion 57d is provided in the weight portion 57a of the balance weight 57, the stress (centrifugal force) acting on the balance weight is dispersed by the thin portion 57d along the arc direction of the weight portion 57a. Can improve durability.

  As described above, in the scroll compressor of this embodiment, the fixed scroll 12 having the spiral wrap 25 is fixed to the housing 11, and the spiral wrap 28 of the orbiting scroll 13 having the spiral wrap 28 is fixed to the fixed scroll 12. By supporting the housing 11 so as to be able to rotate and rotate while being in mesh with the spiral wrap 25, a compression chamber 29 is defined between them, and the drive shaft 14 can be driven to rotate in the housing 11. The balance bush 51 of the eccentric shaft 50 is supported and engaged with the orbiting scroll 13 so that the orbiting scroll can be orbited. Refrigerant gas containing mist-like lubricating oil is supplied to the outer periphery of the balance bush 51 with the orbiting scroll 13. A lubricating passage 64 is provided to be supplied to the engaging portion.

  Accordingly, the refrigerant gas containing mist-like lubricating oil is sucked into the compression chamber 29 from the suction port 31, and the volume of the compression chamber 29 is gradually reduced by turning the orbiting scroll 13, whereby the refrigerant gas is compressed, The compressed refrigerant gas is discharged into the discharge chamber 32, and at this time, the refrigerant gas compressed in the compression chamber 29 is supplied from the supply passage 32 to the mechanical chamber 61, and the balance bush 51 swivels through the lubrication passage 64 of the balance bush 51. It is supplied to the engaging portion with the scroll 13, that is, the floating bush 53 and the roller bearing 54, and the lubricating oil contained in the refrigerant gas is reliably supplied to the engaging portion and lubricated, so that the reliability of the apparatus is improved. Performance can be improved, and complexity of the structure and an increase in manufacturing cost can be suppressed.

  The eccentric shaft 50 provided at the end of the drive shaft 14 and the balance bush 51 that is cylindrical and fits on the outer periphery of the eccentric shaft 50 constitute an eccentric portion. The roller bushing 54 is fitted into the boss 48 of the orbiting scroll 13, and the lubricating passage 64 is formed by cutting out the outer peripheral portion of the balance bush 51. Therefore, by providing the lubrication passage 64 between the balance bush 51 and the floating bush 53, the sliding portion between the balance bush 51 and the floating bush 53, the bearing 54 and the fitting recess 49 of the boss 48, is reliably lubricated. can do.

  Further, the lubrication passage 64 is provided outside the bearing load acting range in the balance bush 51. Therefore, since the lubrication passage 64 is formed in a range in which the bearing load does not act on the balance bush 51 from the orbiting scroll 13, an appropriate engagement relationship between the balance bush 51 and the orbiting scroll 13 can be maintained.

  In this embodiment, the roller bearing 37 that rotatably supports the drive shaft 14 on the housing 11 and the engaging portion (the floating bush 53 and the roller bearing 54) where the balance bush 51 engages with the boss 48 of the orbiting scroll 13. And a supply passage 62 for supplying the refrigerant gas from the compression chamber 29 to the mechanical chamber 61, and lubricates the refrigerant gas supplied from the compression chamber 29 to the mechanical chamber 61 through the supply passage 62. A discharge passage 63 is provided which flows into the passage 64 and returns the refrigerant gas in the mechanical chamber 61 to the compression chamber 29. Therefore, the refrigerant gas supplied from the compression chamber 29 to the mechanical chamber 61 through the supply passage 62 can be reliably supplied to the lubrication passage 64, and the refrigerant gas in the mechanical chamber 61 can be supplied from the discharge passage 63 to the compression chamber 29. By returning, the pressure rise in the mechanical chamber 61 can be prevented.

  A balance weight 57 is provided integrally with the balance bush 51. Accordingly, when the orbiting scroll 13 is revolved through the balance bush 51 due to the rotation of the drive shaft 14, the centrifugal force of the orbiting scroll 13 acting on the drive shaft 14 can be canceled by the balance weight 57. The balance bush 51 having the balance weight 57 can be easily manufactured by a technique such as casting, and the cost can be reduced.

  In this case, the balance weight 57 is provided with a weight portion 57a having an arc shape, and a thin portion 57d is provided by forming a notch portion 57c in the inner peripheral portion of the weight portion 57a at an intermediate position in the arc direction. Therefore, the stress acting on the balance weight 57 can be dispersed by the thin portion 57d, and the durability can be improved. Further, a thin portion 57 of the balance weight is provided on the opposite side of the lubrication passage 64 with respect to the rotation center of the drive shaft 15. Therefore, by forming the thin portion 57d and the lubricating passage 64 diagonally, the weight can be reduced without impairing the function of the balance weight 57.

In the above-described embodiment, one lubrication passage 64 is provided on the outer peripheral surface of the balance bush 51 to supply refrigerant gas containing mist-like lubricating oil to the engaging portion with the orbiting scroll 13. In this case, the balance bush 51 may be provided at any position as long as it is out of the angular range θ ₁ and θ ₂ outside the bearing load acting range.

  The scroll compressor according to the present invention is designed to improve reliability by reliably supplying and lubricating a fluid containing a mist-like lubricating oil sucked into the interior at a necessary location. It is useful when applied to a compressor having a scroll.

It is sectional drawing showing the scroll compressor which concerns on one Example of this invention. It is a front view of the balance bush in the scroll compressor of a present Example. It is a perspective view of the balance bush in the scroll compressor of a present Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Housing 12 Fixed scroll 13 Orbiting scroll 14 Drive shaft 15 Drive device 23, 27 Disk (end plate)
24, 28 Spiral wrap (wall)
29, 29a, 29b Compression chamber 26, 27 Suction port 30 Suction chamber 31 Suction port (suction part)
32 Discharge chamber 33 Discharge port 35 Discharge port 37, 54 Roller bearing 38 Shaft seal 48 Boss 49 Fitting recess 50 Eccentric part (eccentric part)
51 Balance bush (eccentric part)
53 Floating bush (engagement part)
57 Balance weight (engagement part)
57b Weight portion 57c Notch portion 57d Thin portion 61 Mechanical chamber 62 Supply passage 63 Discharge passage 64 Lubrication passage

Claims (9)

  A housing having a suction portion for sucking a fluid containing mist-like lubricating oil and a discharge portion for discharging a compressed fluid obtained by compressing the fluid, and a spiral wall plate, and an end plate is fixed to the housing. The fixed scroll has a spiral wall and the wall is engaged with the wall of the fixed scroll to form a compression chamber and supported by the housing so as to be able to revolve while being prevented from rotating. And a drive shaft having an eccentric portion that is rotatably supported by the housing and engages with the orbiting scroll so that the orbiting scroll can be turned, and is formed on an outer peripheral surface of the eccentric portion. A scroll compressor comprising a lubrication passage for supplying fluid sucked into the housing from a suction portion to an engagement portion between the eccentric portion and the orbiting scroll.   2. The scroll compressor according to claim 1, wherein the eccentric portion includes an eccentric shaft provided at an end portion of the drive shaft, and a balance bush having a cylindrical shape and fitted to an outer periphery of the eccentric shaft. The balance bush is fitted into a cylindrical boss provided on an end plate of the orbiting scroll through a floating bush and a bearing, and the outer periphery of the balance bush is cut out in the lubricating passage. A scroll compressor characterized by being formed.   3. The scroll compressor according to claim 1, wherein the lubrication passage is provided outside a bearing load acting range in the eccentric portion. 4.   2. The scroll compressor according to claim 1, wherein a bearing portion that rotatably supports the drive shaft on the housing and an engaging portion in which the eccentric portion engages with the orbiting scroll are partitioned with respect to the suction portion. And a supply passage for supplying the compressed fluid from the compression chamber to the mechanical chamber, and the compressed fluid supplied from the compression chamber to the mechanical chamber through the supply passage is provided in the lubrication passage. Scroll compressor characterized by flowing into   The scroll compressor according to claim 1, wherein a balance weight is integrally provided in the eccentric portion.   6. The scroll compressor according to claim 5, wherein the balance weight has a weight portion having an arc shape, and a notch portion is formed in an inner peripheral portion of an intermediate position in the arc direction in the weight portion. Scroll compressor.   7. The scroll compressor according to claim 6, wherein the notch portion of the balance weight is provided on the opposite side of the lubrication passage with respect to the rotation center of the drive shaft.   A housing having a suction portion for sucking fluid and a discharge portion for discharging compressed fluid obtained by compressing the fluid; a fixed scroll having a spiral wall plate and an end plate fixed to the housing; and a spiral shape A revolving scroll supported by the housing so as to be able to revolve while preventing rotation and forming a compression chamber by engaging the wall with the wall of the fixed scroll. A drive shaft that is supported rotatably and engages with the orbiting scroll so that the orbiting scroll can be revolved, and a thin-walled portion that is connected to the outer peripheral side of the eccentric portion and is positioned at an intermediate position in the circumferential direction. A scroll compressor comprising a balance weight.   9. The scroll compressor according to claim 8, wherein the balance weight includes a weight part having an arc shape connected to the eccentric part via a connection part, and the thin part is formed in the arc direction in the weight part. A scroll compressor characterized in that it is provided by forming a notch in an inner periphery of an intermediate position.

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