JP2006104958A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide superior reliability by exhibiting sufficient bearing yield strength, even when a rotary shaft is deformed, with a simple and inexpensive structure, in a scroll compressor. <P>SOLUTION: This scroll compressor is constituted by storing a compression mechanism part, the rotary shaft and an electric motor in a sealed vessel; and has a revolving scroll 200 having a sliding bearing 210 and the rotary shaft having a crank pin eccentrically arranged in an upper end part. The rotary shaft is connected to the compression mechanism part by inserting the crank pin of the upper end part into the sliding bearing 210. A high pressure refrigerant such as R 410A is used as fluid compressed by the compression mechanism part, and a tapered part 210b expansively opening to the tip side is arranged on the whole periphery of an end part inner surface on one side of the sliding bearing 210. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a scroll compressor having a sliding bearing in an orbiting scroll bearing portion, and is particularly suitable for a scroll compressor for refrigeration and air conditioning using a high-pressure refrigerant such as R410A.

  A conventional fluid compressor is disclosed in Japanese Patent Laid-Open No. 7-233790 (Patent Document 1).

  A scroll compressor according to Patent Document 1 includes a compression mechanism unit that compresses a fluid, a rotating shaft (crankshaft) coupled to the compression mechanism unit, an electric motor that drives the rotating shaft, and a sealed container that stores them. It is configured with.

  And in the scroll compressor of patent document 1, the two slide bearings which support the principal-axis part of a rotating shaft on the one side of an electric motor are fixed to the flame | frame, and are provided. Moreover, the compression mechanism part is comprised by meshing the turning scroll and fixed scroll which each have a base plate (end plate) and scroll wrap (spiral wrap). A orbiting scroll bearing portion projects from the back side of the base plate of the orbiting scroll, and a sliding bearing that supports a crank pin (crank portion) of the rotating shaft is provided in the orbiting scroll bearing portion.

  Furthermore, in the scroll compressor of Patent Document 1, both ends of the thin sliding bearing fixed to the orbiting scroll bearing are not in contact with both ends of the thin sliding bearing so that the orbiting scroll bearing facing the back of the thin sliding bearing does not contact. A deformable projecting portion is formed so that both end portions of the bearing follow the inclination of the rotating shaft due to the gas compression action and deform.

  Furthermore, in the scroll compressor of Patent Document 1, a balance weight is provided between the slide bearing that supports the main shaft portion and the crank pin (in other words, close to the crank pin).

  Moreover, as a conventional fluid compressor, there exists a thing shown by Unexamined-Japanese-Patent No. 2002-147377 (patent document 2).

  The scroll compressor according to Patent Document 2 includes a compression mechanism unit that compresses a fluid, a rotating shaft (main shaft) coupled to the compression mechanism unit, an electric motor that drives the rotating shaft, and a sealed container that stores these. It is prepared for.

  And in the scroll compressor of patent document 2, the slide bearing which supports the principal-axis part of a rotating shaft on the one side of an electric motor adheres to the flame | frame, and is provided. Moreover, the compression mechanism part is comprised by meshing the turning scroll and the fixed scroll. An orbiting scroll bearing portion (boss portion) protrudes from one side of the orbiting scroll, and a slide bearing that supports a crank pin (eccentric shaft portion) of the rotating shaft is provided in the orbiting scroll bearing portion.

  Furthermore, in the scroll compressor of patent document 2, the annular groove is formed in the edge part of the slide bearing fixed to the turning scroll bearing part, and the rigidity of an edge part is reduced. As a result, when a moment is applied to the crank pin of the rotating shaft and the rotating shaft is inclined in the sliding bearing, and the load distribution becomes large at the end of the sliding bearing, the end of the sliding bearing is deformed. The contact stress between the rotating shaft and the end of the slide bearing is reduced.

JP 7-233790 A JP 2002-147377 A

  In Patent Document 1 described above, there has been a problem that the reliability of the sliding bearing itself fixed to the orbiting scroll bearing portion is lowered and the cost is increased. In other words, since the slide bearing must be manufactured to be thin so as to be deformed following the inclination of the rotating shaft, it is difficult to obtain a thickness capable of obtaining the necessary strength for the slide bearing, and it is thin and sufficient. In order to obtain a sufficient strength, it was necessary to use a slide bearing made of an expensive material. It should be noted that the deformation and restoration of the overhanging portion of the slide bearing may be repeated during operation, which may cause fatigue damage to the overhanging portion. From this point of view, the reliability of the slide bearing was lowered. .

  This Patent Document 1 does not mention the type of fluid to be used, but it is important to use a high-pressure refrigerant such as R410A that has little influence on the global environment. When such a high-pressure refrigerant is used, the gas force due to the compression action of the high-pressure refrigerant is greatly increased, and the load applied to the slide shaft fixed to the orbiting scroll bearing is extremely increased, further improving the reliability. It is desirable to do.

  In Patent Document 1 described above, the balance weight is provided on the crankpin side with respect to the main shaft bearing that supports the main shaft portion of the rotating shaft, so that the eccentric pressure that is increased by using the high-pressure refrigerant is balanced. There was a problem that it was difficult to cope with the weight sufficiently. In other words, there is a problem that it is difficult to secure a space for installing a large balance weight between the main shaft bearing and the crankpin. Therefore, it is conceivable to provide a balance weight on the main shaft portion located on the side opposite to the crank pin of the main shaft bearing. In this case, however, it becomes difficult to achieve a balance by the amount of the balance weight away from the crank pin. Since the pressure applied to the sliding bearing that supports the bearing tends to increase, it is necessary to improve the reliability of the sliding bearing also in this respect.

  On the other hand, in Patent Document 2 described above, the above-described configuration is adopted from the viewpoint of compensating for the deterioration of the wear resistance and seizure resistance characteristics of the refrigerating machine oil due to the use of the high-pressure refrigerant, but the slide bearing fixed to the orbiting scroll bearing portion. There was a problem that the reliability of the device itself was reduced and the cost was increased. That is, when the annular groove is formed at the end of the slide bearing and the rotation shaft has a large inclination, the end of the slide bearing is deformed. Therefore, it is necessary for the inner part of the annular groove of the slide bearing. It is difficult to obtain a thickness capable of obtaining strength, and it is necessary to use a slide bearing made of an expensive material in order to obtain sufficient strength in the inner portion. It should be noted that the deformation and restoration of the inner portion of the annular groove of the slide bearing may be repeated during operation, which may cause fatigue damage to the inner portion of the annular groove. This also causes a decrease in the reliability of the slide bearing. It was a thing.

  Further, in Patent Documents 1 and 2 described above, since the main shaft portion of the rotating shaft is supported on one side of the electric motor, the main shaft portion of the rotating shaft is easily tilted. In order to prevent this inclination, the frame is provided long in the axial direction. In this case, however, there arises a problem that the power loss due to the slide bearing increases and the capacity of the frame decreases. Therefore, it is conceivable to provide rolling bearings that support the main shaft portion of the rotating shaft on both sides of the electric motor. However, when a high-pressure refrigerant is used, two rolling bearings are provided by increasing the gas pressure applied to the crankpin. As a fulcrum, the rotating shaft is easily deformed so as to be curved, and the sliding bearing installed in the orbiting scroll bearing portion is likely to come into contact with one another, resulting in a decrease in reliability.

  An object of the present invention is to obtain a scroll compressor having a simple and inexpensive structure, exhibiting sufficient bearing strength even when a rotating shaft is deformed, and having excellent reliability.

  In order to achieve the above object, a first feature of the present invention is that a compression mechanism unit that compresses fluid, a rotary shaft that is coupled to the compression mechanism unit, an electric motor that drives the rotary shaft, and the compression mechanism A revolving scroll that includes a base plate and a scroll wrap, each having a main shaft bearing that supports a main shaft portion of the rotating shaft on at least one side of the motor. And the fixed scroll are meshed to form the compression mechanism portion, and the orbiting scroll bearing portion projects from the back side of the base plate of the orbiting scroll, and the crank pin of the rotating shaft is supported in the orbiting scroll bearing portion. In the scroll compressor provided with the slide bearing, a high-pressure refrigerant such as R410A is used as the fluid compressed by the compression mechanism, and one side of the slide bearing In providing the tapered portion expanding distally the entire circumference end inner surface.

  A second feature of the present invention is that a compression mechanism unit that compresses fluid, a rotating shaft coupled to the compression mechanism unit, an electric motor that drives the rotating shaft, the compression mechanism unit, the rotating shaft, and the electric motor An airtight container, and a rolling bearing that supports the main shaft portion of the rotating shaft on both sides of the electric motor, and the orbiting scroll having a base plate and a scroll wrap and a fixed scroll are meshed with each other, and the compression mechanism A scroll compressor provided with a sliding scroll bearing portion protruding from the back side of the base plate of the orbiting scroll, and a sliding bearing for supporting a crankpin of the rotary shaft in the orbiting scroll bearing portion, A high-pressure refrigerant such as R410A is used as a fluid to be compressed by the compression mechanism, and the main shaft portion is located on the anti-crank pin side of the rolling bearing. The balance weight is provided, in that the structure in which a tapered portion for expanding the distal end side to the entire circumference end inner surface of one side of the sliding bearing.

  According to a third aspect of the present invention, there is provided a compression mechanism unit that compresses fluid, a rotating shaft coupled to the compression mechanism unit, an electric motor that drives the rotating shaft, the compression mechanism unit, the rotating shaft, and the electric motor. An airtight container, and a rolling bearing that supports the main shaft portion of the rotating shaft on both sides of the electric motor, and the orbiting scroll having a base plate and a scroll wrap and a fixed scroll are meshed with each other, and the compression mechanism A rotating scroll bearing portion protruding from the back side of the orbiting scroll base plate, a sliding bearing for supporting the crank pin of the rotary shaft in the orbiting scroll bearing portion, and a bottom portion in the sealed container Is supplied to the sliding bearing from the back side of the sliding bearing through the oil passage of the rotating shaft, and the rolling oil is further rolled from the opening side of the sliding bearing. In the scroll compressor having an oil supply path that is supplied to the bearing and then returned to the bottom of the sealed container, a high-pressure refrigerant such as R410A is used as a fluid to be compressed by the compression mechanism, and an end of the sliding bearing on the opening side The taper part which spreads to the front end side is provided on the entire inner surface of the part.

  According to a fourth aspect of the present invention, there is provided a compression mechanism section that compresses a fluid, a rotating shaft coupled to the compression mechanism section, an electric motor that drives the rotating shaft, the compression mechanism section, the rotating shaft, and the electric motor. A sealed container that houses a main shaft bearing that supports the main shaft portion of the rotating shaft on at least one side of the electric motor, and meshes the orbiting scroll and the fixed scroll each having a base plate and a scroll wrap. A scroll compressor that constitutes the compression mechanism section and that is provided with a orbiting scroll bearing portion protruding from the back side of the base plate of the orbiting scroll, and a sliding bearing that supports a crank pin of the rotary shaft in the orbiting scroll bearing portion. In the above, a high-pressure refrigerant such as R410A is used as the fluid compressed by the compression mechanism, and the slide bearing is softer than the crank pin. It has an end inner surface all around the stepped portion of one side of and the sliding bearing formed of quality in the provision of the widened cylindrical portion expanded.

  According to the scroll compressor of the present invention, it is possible to obtain sufficient bearing strength by reducing the local surface pressure increase generated in the plain bearing when the rotating shaft is inclined with a simple structure, and it is inexpensive and reliable. Can be excellent.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.

  A scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 and 2. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, FIG. 2 is a sectional view of an orbiting scroll and a sliding bearing of the scroll compressor of FIG. 1, and FIG. 2B is an enlarged view of a portion A of FIG. .

  The scroll compressor 1 is configured by storing a compression mechanism unit 2, a drive unit 3, and a rotary shaft 300 in a sealed container 700. In this embodiment, the compression mechanism unit 2, the drive unit 3, and the oil reservoir 730 are arranged in this order from the top, and the vertical scroll compression in which the compression mechanism unit 2 and the drive unit 3 are connected via the rotating shaft 300. Machine.

  The compression mechanism unit 2 includes a fixed scroll 100, a turning scroll 200, and a frame 400 as basic elements. The frame 400 is fixed to the hermetic container 700 and constitutes a member for disposing the rolling bearing 401. The fixed scroll 100 includes a base plate 101, a scroll wrap 102, a suction port 103, and a discharge port 104 as basic components, and is fixed to the frame 400 with bolts 405. The scroll wrap 102 is erected vertically on one side of the base plate 101. The orbiting scroll 200 includes a base plate 201, a scroll wrap 202, an orbiting scroll bearing portion 203, a slide bearing 210 disposed in the orbiting scroll bearing portion 203, and a back pressure hole as basic components. The scroll wrap 202 is erected vertically on one side of the base plate 201. The orbiting scroll bearing portion 203 is formed so as to protrude perpendicularly to the other side (the opposite lap side) of the base plate 201. The orbiting scroll 200 is formed by processing each component from a casting made of cast iron, aluminum, or the like.

  The compression chamber 130 configured by meshing the fixed scroll 100 and the orbiting scroll 200 is subjected to a compression operation in which the volume thereof decreases as the orbiting scroll 200 orbits. In this compression operation, the working fluid is sucked into the compression chamber 130 through the suction pipe 711 and the suction port 103 in accordance with the turning motion of the turning scroll 200, and the sucked working fluid passes through the compression stroke and is fixed to the fixed scroll 100. The gas is discharged from the discharge port 104 into the sealed container 700 and further discharged from the sealed container 700 via the discharge pipe 701. Thereby, the space in the sealed container 700 is kept at the discharge pressure. A high-pressure refrigerant such as R410A that is friendly to the global environment is used as the working fluid that is compressed by the compression mechanism.

  The sealed container 700 has an upper cap 710 and a lower cap 720. The upper cap 710 and the lower cap 720 are fitted so as to cover the center tube portion of the sealed container, and the fitting end portions are heated and welded obliquely from below and obliquely upward by a welding torch. A leg portion 721 is attached to the bottom surface of the sealed container 700. A magnet 722 is attached to the inside of the lower cap 720 and plays a role of collecting dust in the compressor.

  A hermetic terminal 702 and a terminal cover 703 are provided on the side surface of the hermetic container 700 so that electric power can be supplied to the electric motor 600. The hermetic terminal 702 is provided through the hermetic container 700, and is positioned between the end coil of the stator 601 and the frame 400, and faces the maximum outer diameter portion 407 a of the balance weight 407.

  A discharge pipe 701 is provided on the side surface of the sealed container 700 opposite to the hermetic terminal 702 so as to penetrate the sealed container 700, and is positioned between the end coil of the stator 601 and the frame 400. It faces the maximum outer diameter portion 407a.

  The drive unit 3 that orbits the orbiting scroll 200 includes an electric motor 600 including a stator 601 and a rotor 602, a rotating shaft 300, a pump joint 310 that transmits rotation of the rotating shaft 300 to the pump unit 900, and rotation of the orbiting scroll 200. The Oldham coupling 500, which is a main part of the prevention mechanism, the frame 400, the rolling bearings 401 and 803, the orbiting scroll bearing portion 203, and the sliding bearing 210 disposed in the orbiting scroll bearing portion 203 are configured as basic elements. ing.

  The rotating shaft 300 includes a main shaft portion 302, a crankpin 301, and a sub bearing support portion 303 that are integrally provided. The main shaft portion 302 and the auxiliary bearing support portion 303 are formed on the same shaft center, and constitute a main shaft portion. Further, a pump joint 310 is press-fitted into the lower end portion of the rotating shaft 300. The rolling bearings 401 and 803 constitute a rotating shaft support portion that rotatably engages the main shaft portion 302 and the auxiliary bearing support portion 303 of the rotating shaft 300. The orbiting scroll bearing portion 203 is provided in the orbiting scroll 200 so that the sliding bearing 210 is press-fitted into the inner diameter of the orbiting scroll bearing portion 203 so that the crank pin 301 of the rotating shaft 300 can be moved and rotated in the thrust direction that is the rotating shaft direction. It has been.

  The rolling bearing 401 is arranged on the upper side of the electric motor 600, and the rolling bearing (sub bearing) 803 constituting the main part of the auxiliary bearing portion 800 is arranged on the lower side of the electric motor 600. Rolling bearings 401 and 803 constitute main shaft bearings that support main shaft portions on both sides of electric motor 600. In this embodiment, since the main shaft portion is supported by the rolling bearings 401 and 803 on both sides of the electric motor 600, the main shaft portion of the rotating shaft can be prevented from being tilted while suppressing power loss of the main shaft bearing. .

  The rolling bearing 803 constitutes a main part of the auxiliary bearing unit 800. A housing 802 is fixed to the lower frame 801 fixed to the hermetic container 700 via bolts 805. A rolling bearing 803 is inserted into the housing 802 from above, and a housing cover 804 is further attached from above.

  The pump unit 900 is fixed to the lower end of the housing 802 via a bolt 806. The lower end portion of the pump joint 310 disposed at the lower end portion of the rotating shaft 300 is inserted into the trochoid pump 900. The pump mechanism section includes a trochoidal tooth-type inner rotor 901 and an outer rotor 902, and the inner rotor 901 is fitted to the rotary shaft 300 via the pump joint 310, and the rotation of the rotary shaft 300 is transmitted to the inner rotor 901. By engaging the inner rotor 901 and the outer rotor 902, the oil stored in the oil reservoir 730 at the bottom of the sealed container 700 is sucked from the lower end of the pump unit, and the pressure is increased to supply the oil to the oil passage 311 formed in the rotary shaft 300. It has a structure.

  The Oldham joint 500 is disposed on the back surface of the base plate 201 of the orbiting scroll 200. One set of two orthogonal key portions formed on the Oldham joint 500 slides on a key groove which is a receiving portion of the Oldham joint 500 formed on the frame 400, and the other set is configured on the back side of the orbiting scroll wrap 202. Slide the keyway. As a result, the orbiting scroll 200 orbits within the plane perpendicular to the axial direction, which is the direction in which the scroll wrap 202 stands, without rotating with respect to the fixed scroll 100.

  When the crankpin 301 rotates eccentrically due to the rotation of the rotary shaft 300 connected to the electric motor 600, the compression mechanism unit 2 performs a turning motion without rotating with respect to the fixed scroll 100 by the rotation preventing mechanism of the Oldham joint 500. The gas is sucked into the compression chamber 130 formed by the scroll wraps 102 and 202 through the suction pipe 711 and the suction port 103. Due to the orbiting motion of the orbiting scroll 200, the compression chamber 130 decreases in volume while moving to the central portion, compresses the gas, and discharges the compressed gas from the discharge port 104 to the discharge chamber. The gas discharged into the discharge chamber circulates around the compression mechanism unit 3 and the electric motor 600 and is then discharged from the discharge pipe 701 to the outside of the compressor.

  The base plate 201 of the orbiting scroll 200 is provided with a back pressure hole (not shown) that allows the compression chamber 130 and the back pressure chamber 411 on the orbiting back surface to communicate with each other. The pressure is maintained at an intermediate discharge pressure (intermediate pressure). The back pressure chamber 411 configured on the back side of the orbiting scroll 200 is a space formed by being surrounded by the orbiting scroll 200, the frame 400, and the fixed scroll 100. Therefore, the frame 400 also serves as a member that forms the back pressure chamber 411.

  A seal ring 410 provided in the groove of the frame 400 prevents discharge gas from flowing into the back pressure chamber 411. The orbiting scroll 200 is pressed against the fixed scroll 100 by the resultant force of the intermediate pressure in the back pressure chamber 411 and the discharge pressure acting inside the seal ring 410.

  Here, the inner diameter of the seal ring 410 is smaller than the outer diameter of the rolling bearing 401. In order to be able to adopt such a configuration, in this embodiment, the rolling bearing 401 is inserted into the frame 400 from the rotation driving means side of the frame 400, and the inserted rolling bearing 401 is fixed by the frame cover 403. It has become. A thrust bearing 402 is provided on the frame cover 403. The frame cover 403 is formed separately from the frame 400. The frame cover 403 is fixed to the frame 400 with bolts 406. By fixing the bolts in this manner, the gap between the frame cover 403 and the frame 400 can be accurately sealed, so that oil leakage from the oil supply path can be suppressed. The frame cover 403 includes a portion that is inserted inside the frame 400 and presses the rolling bearing 401, and a portion that contacts and is fixed to the end surface of the frame 400 on the side of the rotation driving means.

  The balance weight 407 is provided on the rotating shaft 300 so as to be positioned on the electric motor side (counter crank pin side) with respect to the rolling bearing 401 that is a main shaft bearing. According to this configuration, it is possible to easily install the balance weight 407 having an appropriate size as compared with the structure in which the balance weight 407 is located closer to the crankpin than the main shaft bearing. In this embodiment, the balance weight 407 is formed separately from the rotary shaft 300 and is press-fitted and fixed to the rotary shaft 300. However, the balance weight 407 is provided integrally with the rotary shaft 300. May be. The maximum outer diameter portion 407a of the balance weight 407 is provided so as to protrude from the end face side of the coil end of the stator 601, and has a larger diameter than the inner diameter of the coil end.

  The metal balance weight cover 404 is formed in a cylindrical shape including a bottom wall and a side wall, and is provided so as to cover the outer periphery of the maximum outer diameter portion 407 a of the balance weight 407. The balance weight cover 404 is fixed to the frame 400 with bolts 406 by fastening the frame cover 403 together. The side wall of the balance weight cover 404 is provided between the discharge pipe 701 and the maximum outer diameter portion 407a of the balance weight 407, and is provided between the hermetic terminal 702 and the maximum outer diameter portion 407a of the balance weight 407. Become.

  In this way, the balance weight cover 404 closes the space between the frame 400 and the end face of the end coil of the stator 601. That is, the outer space of the maximum outer diameter portion 407 a of the balance weight 407 is substantially closed by the balance weight cover 404.

  Next, the oil supply path will be described. When the rotating shaft 300 is rotated, the oil in the oil reservoir 730 is boosted and supplied to the oil passage 311 in the rotating shaft by the pump unit 900. Part of the oil sent to the oil passage 311 flows through the lateral hole 312 to the auxiliary bearing 803 that is a rolling bearing, and then returns to the oil reservoir 730. The oil that reaches the upper portion of the crankpin 301 through the oil passage 311 passes through the slide bearing 210 and further flows into the rolling bearing 401. Most of the oil that has lubricated the rolling bearing 401 passes through the oil drain pipe 408 and returns to the oil sump 730. A part of the oil that lubricates the rolling bearing 401 passes through the gap between the frame cover 403 and the rotating shaft 300 and reaches the balance weight 407 and is scattered by the balance weight 407, but the inner surface of the side wall of the balance weight cover 404 The oil is collected by being attached to the oil and returned to the oil sump 730 by flowing down to the electric motor 600 or the like.

  Further, an oil supply pocket 205 is provided on the end face of the orbiting scroll bearing portion 203 of the orbiting scroll 200, and the orbiting scroll 200 reciprocates between the outer side and the inner side of the seal ring 410 by orbiting. Part of the oil between the bearing 210 and the bearing 401 is conveyed to the back pressure chamber 411. The conveyed oil is supplied to the Oldham coupling 500 and then supplied to the end face 105 of the fixed scroll and the sliding face of the base plate 201 of the orbiting scroll 200.

  The oil conveyed to the back pressure chamber 411 flows into the compression chamber 130 through the back pressure hole or through a minute gap on the sliding surface of the end plate. The oil that has flowed into the compression chamber 130 is discharged from the discharge port 104 together with the compressed refrigerant gas, is separated from the refrigerant gas in the sealed container 700, and returns to the oil reservoir 730.

  The rotating shaft 300 includes a main shaft portion 302 fixed to the rotor 602 of the electric motor 600, a crank pin 301 provided eccentrically at the upper end portion of the main shaft portion 302 and connected to the compression mechanism portion 2, and a lower end of the main shaft portion 302. And a small-diameter sub-bearing support portion 303 supported by the sub-bearing 803, so that the sub-bearing support portion 303 is secured by the sub-bearing 803 while ensuring the necessary strength for the rotary shaft 300. It can be supported with high accuracy.

  Next, the sliding bearing 210 of the present embodiment will be described with reference to FIG. FIG. 2 is an explanatory view of the sliding bearing portion of the scroll compressor of the present embodiment, FIG. 2A is a sectional view of the orbiting scroll, and FIG. 2B is an enlarged view of a portion A in FIG. 2A.

  The slide bearing 210 is disposed in the orbiting scroll bearing portion 203 of the orbiting scroll 200. The outer peripheral surface of the slide bearing 210 is in close contact with the inner peripheral surface of the orbiting scroll bearing portion 203. Further, the sliding bearing 210 is formed with a thickness that can ensure the necessary strength.

  A crankpin 301 provided eccentrically at the upper end of the rotary shaft 300 is connected to and supported by a slide bearing 210 disposed in the orbiting scroll bearing 203. The crankpin 301 is slightly inclined due to the centrifugal force of the orbiting scroll 200 due to rotation and the axial radial load received through the slide bearing 210 when the orbiting scroll 200 compresses gas. In particular, high pressure refrigerant such as R410A is used, the balance weight 407 is provided on the rank pin side, and the main shaft portion of the rotary shaft 300 is supported by the rolling bearings 401 and 803 on both sides of the electric motor 600. As a result, the crank pin 301 is likely to be inclined.

  Therefore, in the present embodiment, a tapered portion 210b that expands from the cylindrical inner surface portion 210a to the distal end side is provided on the entire inner surface of the end portion inner surface on the opening side of the slide bearing 210. The tapered portion 210b of the plain bearing 210 is formed with a gentle taper angle with the axial dimension being in the order of mm and the radial dimension being in the order of 10 μm. Even when the crankpin 301 is slightly inclined, the root of the crankpin 301 does not come into contact with the lower end of the slide bearing 210 and is smooth to some extent by the simple structure in which the tapered portion 210b is provided at the lower end of the slide bearing 210. It is possible to make contact with the surface, and it is possible to alleviate the increase in the surface pressure at the lower end portion of the slide bearing due to the contact of the base portion of the crankpin 301, and the reliability of the slide bearing can be improved.

  Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 3 is an explanatory view of a sliding bearing portion of a scroll compressor according to a second embodiment of the present invention, FIG. 3A is a sectional view of the orbiting scroll, and FIG. 3B is an enlarged view of portion B of FIG. 3A. The second embodiment is different from the first embodiment in the following points, and is basically the same as the first embodiment in other points.

  In the second embodiment, the portion from the cylindrical inner surface portion 210a to the tapered portion 210b of the slide bearing 210 is formed with a smooth curve. In this way, the cylindrical inner surface portion and the tapered portion of the slide bearing 210 are formed with a smooth curve, so that when the crankpin 301 is slightly inclined, the root of the crankpin 301 is in contact with the lower end portion of the slide bearing 210. Therefore, it is possible to make contact with the surface more smoothly than that with only taper machining, and to further reduce the increase in surface pressure at the lower end of the slide bearing due to the contact of the base portion of the crankpin 301, the reliability of the slide bearing The sex can be further enhanced.

  Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 4 is an explanatory view of a sliding bearing portion of a scroll compressor according to a third embodiment of the present invention, FIG. 4A is a sectional view of the orbiting scroll, and FIG. 4B is an enlarged view of a portion C of FIG. The third embodiment is different from the first embodiment in the following points, and is basically the same as the first embodiment in other points.

  In the third embodiment, the slide bearing 210 is made of a material softer than the crank pin 301, and an expanded cylindrical portion 210c is provided that expands with a stepped portion around the inner surface of one end of the slide bearing 210. ing. That is, the lower end portion of the slide bearing 210 is processed into a one-step rectangular shape when viewed in cross section to form a pseudo taper portion.

  Since the plain bearing 210 is made of a soft material with respect to the crank pin 301, the stepped portion is crushed when a load is applied, and is practically equivalent to a tapered shape. By processing the lower end portion of the slide bearing 210 with one step, even when the crankpin 301 is slightly inclined, the root contact of the crankpin 301 can be reduced at the lower end portion of the slide bearing 210. The increase in the surface pressure at the lower end of the slide bearing due to the contact of the base portion of the crankpin 301 can be mitigated. The stepping process of the slide bearing 210 is advantageous from the viewpoint of workability and quality control as compared with the taper process, and the reliability of the slide bearing 210 can be improved.

It is a longitudinal cross-sectional view of the scroll compressor of 1st Example of this invention. It is a longitudinal cross-section of the turning scroll used for the scroll compressor of a present Example. It is the A section enlarged view of FIG. 2A. It is a longitudinal cross-section of the turning scroll used for the scroll compressor of 2nd Example of this invention. It is the B section enlarged view of Drawing 3A. It is a longitudinal cross-section of the turning scroll used for the scroll compressor of 3rd Example of this invention. It is the C section enlarged view of FIG. 4A.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Scroll compressor, 2 ... Compression mechanism part, 3 ... Drive part, 100 ... Fixed scroll, 101 ... Base plate, 102 ... Wrap, 103 ... Inlet port, 104 ... Discharge port, 105 ... End plate surface, 130 ... Compression chamber , 200 ... orbiting scroll, 201 ... base plate, 202 ... lap, 203 ... orbiting scroll bearing, 205 ... oil supply pocket, 210 ... sliding bearing, 210a ... cylindrical inner surface part, 210b ... taper part, 300 ... rotating shaft, 301 ... crank Pin 302 302 Main shaft 303 Sub bearing support 310 310 Pump passage 311 Oil passage 312 Side hole 400 Frame 401 Rolling bearing 402 Thrust bearing 403 Frame cover 404 Balance Weight cover, 405 ... bolt, 406 ... bolt, 407 ... balance weight, 407a ... maximum outer diameter part, 408 ... exhaust Pipe, 410 ... Seal ring, 411 ... Back pressure chamber, 500 ... Oldham joint, 600 ... Electric motor, 601 ... Stator, 602 ... Rotor, 700 ... Sealed container, 701 ... Discharge pipe, 702 ... Herme terminal, 703 ... Terminal cover, 710 ... Upper cap, 711 ... Suction pipe, 720 ... Lower cap, 721 ... Leg, 722 ... Magnet, 730 ... Oil sump, 800 ... Sub-bearing portion, 801 ... Lower frame, 802 ... Housing, 803 ... Rolling bearing (sub-bearing) Bearings), 804 ... Housing cover, 805 ... Bolt, 806 ... Bolt, 900 ... Pump part, Inner rotor ... 901, 902 ... Outer rotor.

Claims (7)

A compression mechanism for compressing fluid;
A rotating shaft coupled to the compression mechanism,
An electric motor for driving the rotating shaft;
A hermetic container containing the compression mechanism, the rotating shaft, and the electric motor,
A main shaft bearing for supporting a main shaft portion of the rotating shaft on at least one side of the electric motor;
The compression mechanism part is configured by meshing a turning scroll and a fixed scroll each having a base plate and a scroll wrap,
A projecting scroll bearing portion is provided on the back side of the orbiting scroll base plate,
In the scroll compressor provided with a sliding bearing for supporting a crankpin of the rotary shaft in the orbiting scroll bearing portion,
While using a high-pressure refrigerant such as R410A as the fluid compressed by the compression mechanism,
A scroll compressor characterized in that a taper portion that widens toward the tip side is provided on the entire inner surface of the end portion on one side of the slide bearing. A compression mechanism for compressing fluid;
A rotating shaft coupled to the compression mechanism,
An electric motor for driving the rotating shaft;
A hermetic container containing the compression mechanism, the rotating shaft, and the electric motor,
A rolling bearing is provided to support the main shaft portion of the rotating shaft on both sides of the electric motor,
The compression mechanism portion is configured by meshing a turning scroll and a fixed scroll each having a base plate and a scroll wrap,
A projecting scroll bearing portion is provided on the back side of the orbiting scroll base plate,
In the scroll compressor provided with a sliding bearing for supporting a crankpin of the rotary shaft in the orbiting scroll bearing portion,
While using a high-pressure refrigerant such as R410A as the fluid compressed by the compression mechanism,
A balance weight is provided on the main shaft portion located on the anti-crank pin side of the rolling bearing,
A scroll compressor characterized in that a taper portion that widens toward the tip side is provided on the entire inner surface of the end portion on one side of the slide bearing. A compression mechanism for compressing fluid;
A rotating shaft coupled to the compression mechanism,
An electric motor for driving the rotating shaft;
A hermetic container containing the compression mechanism, the rotating shaft, and the electric motor,
A rolling bearing is provided to support the main shaft portion of the rotating shaft on both sides of the electric motor,
The compression mechanism portion is configured by meshing a turning scroll and a fixed scroll each having a base plate and a scroll wrap,
A projecting scroll bearing portion is provided on the back side of the orbiting scroll base plate,
A sliding bearing that supports a crankpin of the rotary shaft is provided in the orbiting scroll bearing portion,
Lubricating oil stored in the bottom of the sealed container is supplied to the sliding bearing from the back side of the sliding bearing through the oil passage of the rotating shaft, and further supplied to the rolling bearing from the opening side of the sliding bearing. In the scroll compressor having an oil supply path for returning to the bottom in the sealed container,
While using a high-pressure refrigerant such as R410A as the fluid compressed by the compression mechanism,
A scroll compressor characterized in that a taper portion that widens toward the tip side is provided on the entire inner circumference of the end portion on the opening side of the sliding bearing.   4. The scroll compressor according to claim 3, wherein a pump portion is provided at the end of the rotary shaft on the side opposite to the crankpin to pressurize and supply the lubricating oil stored in the bottom of the sealed container to the oil supply path. Scroll compressor characterized by.   5. The scroll compressor according to claim 4, wherein the taper portion of the slide bearing is formed with a gentle taper angle with an axial dimension of the order of mm and a radial dimension of the order of 10 μm. Scroll compressor.   6. The scroll compressor according to claim 1, wherein the scroll compressor is connected from the cylindrical inner surface portion of the sliding bearing to the tapered portion with a smooth curve. A compression mechanism for compressing fluid;
A rotating shaft coupled to the compression mechanism,
An electric motor for driving the rotating shaft;
A hermetic container containing the compression mechanism, the rotating shaft, and the electric motor,
A main shaft bearing for supporting a main shaft portion of the rotating shaft on at least one side of the electric motor;
The compression mechanism portion is configured by meshing a turning scroll and a fixed scroll each having a base plate and a scroll wrap,
A projecting scroll bearing portion is provided on the back side of the orbiting scroll base plate,
In the scroll compressor provided with a sliding bearing for supporting a crankpin of the rotary shaft in the orbiting scroll bearing portion,
While using a high-pressure refrigerant such as R410A as the fluid compressed by the compression mechanism,
Scroll compression characterized in that the sliding bearing is formed of a material softer than the crank pin and provided with an expanding cylindrical portion that expands with a stepped portion around the inner surface of one end of the sliding bearing. Machine.

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