JP6444535B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor that compresses working gas.

  Patent Document 1 describes a swing link of a scroll type fluid machine. The swing link includes a bush portion and a weight portion that are separately formed. The bush portion has an insertion hole to be inserted into the drive pin of the drive shaft, and is fitted into the cylindrical boss portion of the movable scroll via a journal bearing. A bush part is a straight cylinder in which the insertion hole was formed in the eccentric position. The bush portion and the weight portion are coupled via a flat plate. The bush portion is press-fitted into an insertion hole formed in the flat plate. The weight portion is coupled to the flat plate via a plurality of connecting pins.

Japanese Patent Laid-Open No. 3-74588

  However, in the swing link described in Patent Document 1, the centrifugal force generated by the rotation of the weight portion acts on the connecting pin. Thereby, there exists a possibility that a connection pin may be damaged. Further, in the swing link described in Patent Document 1, a moment to roll over is generated on the flat plate due to the centrifugal force of the weight portion. Thereby, there exists a possibility that a shift | offset | difference may generate | occur | produce between a flat plate and a bush part. Therefore, the scroll type fluid machine described in Patent Document 1 has a problem that the reliability of the swing link is low.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide a highly reliable scroll compressor.

  A scroll compressor according to the present invention is provided at a fixed scroll, a swing scroll that swings with respect to the fixed scroll, a main shaft that transmits a rotational driving force to the swing scroll, and one end of the main shaft, An eccentric shaft portion eccentric in a predetermined eccentric direction with respect to the central axis of the main shaft, a slider having a slide groove into which the eccentric shaft portion is slidably fitted, and the swing scroll are provided. A swinging bearing that rotatably supports the slider, the slider being supported by the swinging bearing, and a member separate from the slider member and fixed to the slider member. A balancer member that counteracts the centrifugal force acting on the orbiting scroll, and the balancer member is rotating while the slider is rotating when the opposite direction of the eccentric direction is the anti-eccentric direction. And a support portion for supporting the slider member from the eccentric direction side, and the slider member abuts on the support portion. An anti-eccentric load supporting surface that supports the load of the balancer member in the anti-eccentric direction, and is provided on the eccentric direction side of the anti-eccentric load supporting surface and is parallel to the central axis. A first axial load support surface that supports the load of the balancer member in a direction, and the balancer member that is provided closer to the anti-eccentric direction side than the anti-eccentric load support surface and in a direction opposite to the one direction And a second axial load support surface for supporting the load.

  According to the present invention, the load of the balancer member in the anti-eccentric direction generated by the centrifugal force of the balancer member is supported by the anti-eccentric load supporting surface of the slider member. The load of the balancer member in the central axis direction caused by the moment around the anti-eccentric load support surface is supported by the first axial load support surface and the second axial load support surface of the slider member. As a result, the force acting between the slider member and the balancer member due to the centrifugal force of the balancer member passes through the anti-eccentric load support surface, the first axial load support surface, and the second axial load support surface. It balances with the pressed load. Therefore, since the slider member and the balancer member are more firmly fixed by the centrifugal force of the balancer member, the reliability of the scroll compressor can be improved.

It is a schematic diagram which shows the general | schematic axial cross section of the scroll compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the structure of the slider 30 of the scroll compressor which concerns on Embodiment 1 of this invention. It is a bottom view which shows the structure of the slider 30 of the scroll compressor which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the axial direction cross section of the slider 30 of the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the centrifugal force which acts on the balancer member during the driving | operation of the scroll compressor which concerns on Embodiment 1 of this invention, and the load which acts on the slider member from the balancer member by this centrifugal force. It is sectional drawing which shows each axial cross section of the slider member 40 and the balancer member 50 of the scroll compressor which concerns on Embodiment 1 of this invention. It is a figure which shows the structure of the slider 30 of the scroll compressor which concerns on Embodiment 2 of this invention.

Embodiment 1 FIG.
A scroll compressor according to Embodiment 1 of the present invention will be described. FIG. 1 is a schematic diagram showing a schematic axial section of a scroll compressor according to the present embodiment. A scroll compressor becomes one of the components of the refrigerating cycle apparatus used for a refrigerator, a freezer, a vending machine, an air conditioning apparatus, a refrigerator, a hot water supply apparatus etc., for example. In this embodiment, as a scroll compressor, a vertical type scroll compressor in which a main shaft is arranged along a vertical direction is illustrated. In the following drawings including FIG. 1, the dimensional relationship and shape of each component may differ from the actual ones. Moreover, the positional relationship (for example, up-and-down relationship) between each structural member in the following description is a thing when installing a scroll compressor in the state which can be used in principle.

  The scroll compressor sucks and compresses a refrigerant (an example of a working gas) circulating in the refrigerant circuit of the refrigeration cycle apparatus, and discharges it in a high-temperature and high-pressure state. As shown in FIG. 1, the scroll compressor includes a compression mechanism unit 20 that compresses refrigerant, an electric motor unit 21 that drives the compression mechanism unit 20, a sealed container 1 that houses the compression mechanism unit 20 and the electric motor unit 21, and have. The compression mechanism unit 20 is disposed in the upper part of the sealed container 1. The electric motor unit 21 is disposed below the compression mechanism unit 20 in the sealed container 1.

  The sealed container 1 has a cylindrical body 1a, a lid 1b disposed at the upper end of the body 1a, and a bottom 1c disposed at the lower end of the body 1a. Between the trunk | drum 1a and the cover part 1b, and between the trunk | drum 1a and the bottom part 1c are mutually airtightly joined by welding etc.

  The compression mechanism unit 20 includes a fixed scroll 3 fixed to the hermetic container 1 via the frame 2 and a swing scroll 4 that swings (that is, revolves) with respect to the fixed scroll 3. Yes. The fixed scroll 3 has a base plate 3a and a spiral wrap portion 3b provided on one surface of the base plate 3a. The swing scroll 4 has a base plate 4a and a spiral wrap portion 4b provided on one surface of the base plate 4a. The fixed scroll 3 and the orbiting scroll 4 are combined so that the respective wrap portions 3b and 4b are engaged with each other. A compression chamber in which the refrigerant is compressed is formed between the wrap portion 3b and the wrap portion 4b.

  At the center of the base plate 3a of the fixed scroll 3, a discharge port 22 for discharging the compressed refrigerant from the compression chamber is formed through the base plate 3a. A discharge chamber 23 is provided on the outlet side of the discharge port 22. A discharge valve 24 having a reed valve structure is provided at the discharge port of the discharge chamber 23.

  A cylindrical boss 4c is formed at the center of the surface of the base plate 4a of the orbiting scroll 4 opposite to the surface on which the lap portion 4b is formed. A rocking bearing 14 (journal bearing) that rotatably supports a cylindrical portion 41 of a slider 30 described later is provided on the inner peripheral side of the boss portion 4c. The central axis of the rocking bearing 14 is parallel to the central axis of the main shaft 7.

  An Oldham ring 12 is provided between the swing scroll 4 and the frame 2. The Oldham ring 12 includes a ring portion, a pair of Oldham keys formed on the upper surface of the ring portion, and a pair of Oldham keys formed on the lower surface of the ring portion. The Oldham key on the upper surface is inserted into a key groove formed in the swing scroll 4 and is slidable in one direction. The Oldham key on the lower surface is inserted into a key groove formed in the frame 2 and is slidable in a direction crossing the one direction. With this configuration, the orbiting scroll 4 revolves without rotating.

  The electric motor unit 21 includes a stator 5 fixed to the inner periphery of the sealed container 1, a rotor 6 disposed on the inner periphery side of the stator 5, and a main shaft 7 fixed to the rotor 6. When the stator 5 is energized, the rotor 6 rotates together with the main shaft 7. The upper portion of the main shaft 7 is rotatably supported by the frame 2 via the main bearing portion 16. A lower portion of the main shaft 7 is rotatably supported by a sub frame 18 via a sub bearing portion 17 (for example, a ball bearing). Hereinafter, the direction parallel to the central axis of the main shaft 7 may be simply referred to as “axial direction”.

  An eccentric shaft portion 7 a is provided at the upper end portion of the main shaft 7. The eccentric shaft portion 7 a is arranged eccentrically in a predetermined eccentric direction with respect to the central axis of the main shaft 7. The eccentric shaft portion 7a is slidably fitted in a slide groove 43 of the slider 30 described later.

  An oil sump 8 for storing lubricating oil is provided at the bottom of the sealed container 1. An oil pump 9 that sucks up the lubricating oil in the oil sump 8 is provided at the lower end of the main shaft 7. An oil hole 13 extending in the axial direction of the main shaft 7 is formed inside the main shaft 7. The lubricating oil sucked up from the oil reservoir 8 by the oil pump 9 is supplied to each sliding portion including the rocking bearing 14 through the oil hole 13. The frame 2 is connected to an oil drain pipe 15 for returning the lubricating oil in the frame 2 to the oil sump 8.

  A first balancer 19 a that cancels an unbalance due to the swing of the swing scroll 4 is provided on the upper portion of the main shaft 7. A second balancer 19 b that cancels the unbalance caused by the swing of the swing scroll 4 is provided at the lower portion of the rotor 6.

  In addition, the sealed container 1 is provided with a suction pipe 10 that sucks low-pressure gas refrigerant from the outside, and a discharge pipe 11 that discharges compressed high-pressure gas refrigerant to the outside.

  Here, the overall operation of the scroll compressor will be briefly described. When the stator 5 is energized, the rotor 6 rotates. The rotational driving force of the rotor 6 is transmitted to the orbiting scroll 4 through the main shaft 7, the eccentric shaft portion 7 a and the slider 30. The orbiting scroll 4 to which the rotational driving force is transmitted is restricted from rotating by the Oldham ring 12 and performs an orbiting motion with respect to the fixed scroll 3.

  Along with the swinging motion of the swing scroll 4, the low-pressure gas refrigerant sucked into the sealed container 1 from the suction pipe 10 is taken into the compression chamber through a suction port (not shown) formed in the frame 2 and compressed. Compressed indoors. The compressed high-pressure gas refrigerant is discharged into the discharge chamber 23 through the discharge port 22. The high-pressure gas refrigerant in the discharge chamber 23 pushes up the discharge valve 24 and is discharged into the high-pressure space between the fixed scroll 3 and the sealed container 1, and then is discharged from the discharge pipe 11 to the outside of the scroll compressor.

  FIG. 2 is a top view showing the configuration of the slider 30 of the scroll compressor according to the present embodiment. FIG. 3 is a bottom view showing the configuration of the slider 30 of the scroll compressor according to the present embodiment. 2 and 3, the eccentric direction of the orbiting scroll 4 (that is, the eccentric direction of the eccentric shaft portion 7a with respect to the central axis of the main shaft 7) is indicated by a white thick arrow. 2 and 3, in a plane orthogonal to the central axis of the main shaft 7, the rotation center O of the slider 30 is the origin, the X axis is parallel to the eccentric direction of the orbiting scroll 4, and the X axis The Y axis is taken in the orthogonal direction. In the X axis, the direction opposite to the eccentric direction of the orbiting scroll 4 (the anti-eccentric direction) is positive. That is, the + X direction coincides with the anti-eccentric direction of the orbiting scroll 4, and the −X direction coincides with the eccentric direction of the orbiting scroll 4. The intersection of the X axis and the Y axis is the rotation center O. The rotation center O is located on the central axis of the main shaft 7.

  The slider 30 constitutes a variable crank mechanism that changes the revolution radius of the orbiting scroll 4 along the side surface shape of the lap portion 3 b of the fixed scroll 3. As shown in FIGS. 2 and 3, the slider 30 includes a slider member 40 that is rotatably supported by the rocking bearing 14, and a balancer member 50 that cancels at least part of the centrifugal force acting on the rocking scroll 4. ,have. The slider member 40 and the balancer member 50 are separate members formed separately from each other, and are formed of different materials, for example. Each of the slider member 40 and the balancer member 50 has an integral structure. The slider member 40 and the balancer member 50 are fixed to each other using a fastening member 70 (for example, a bolt, a rivet, a pin, etc.). 2 and 3, dot balance is given to the balancer member 50 in order to easily grasp the shapes of the slider member 40 and the balancer member 50.

  The slider member 40 includes a cylindrical portion 41 that is rotatably supported by the rocking bearing 14, and a flat plate portion 42 that projects from the vicinity of the lower end portion of the cylindrical portion 41 to the outer peripheral side. The slider member 40 including the cylindrical portion 41 and the flat plate portion 42 has an integral structure. The cylindrical portion 41 includes a cylindrical outer peripheral surface that is a sliding surface with respect to the rocking bearing 14. On the inner peripheral side of the cylindrical portion 41, an elongated hole-shaped slide groove 43 is formed for fitting the eccentric shaft portion 7a so as to be slidable in one direction. In this example, the sliding direction of the eccentric shaft portion 7 a and the slide groove 43 is inclined with respect to the eccentric direction of the orbiting scroll 4. The flat plate portion 42 is formed to be biased toward the + X side with respect to the cylindrical portion 41. The flat plate portion 42 constitutes a part of an annular flange 72 (see FIG. 4) formed on the outer periphery of the lower end portion of the cylindrical portion 41.

  The balancer member 50 includes a main weight portion 51 provided on the + X side from the rotation center O, and a support portion 52 that supports the lower end portion of the slider member 40 from the −X side and prevents the slider 30 from overturning. doing. The balancer member 50 including the main weight portion 51 and the support portion 52 has an integral structure. In the following description, the support portion 52 may be referred to as a rollover prevention weight portion. Most of the support part 52 is formed on the −X side with respect to the rotation center O, and a part of the support part 52 is formed on the + X side with respect to the rotation center O. The support portion 52 is disposed substantially in the same plane as the flat plate portion 42 of the slider member 40 and has a U-shaped planar shape surrounding the flat plate portion 42 from three directions of the + Y direction, the −X direction, and the −Y direction. . The support part 52 constitutes the other part of the annular flange 72 (see FIG. 4) formed on the outer periphery of the lower end part of the cylindrical part 41. That is, when the support portion 52 and the flat plate portion 42 are combined, an annular flange 72 that is coaxial with the cylindrical portion 41 is formed on the outer periphery of the lower end portion of the cylindrical portion 41. The annular collar 72 is positioned below the boss 4 c of the swing scroll 4 and the swing bearing 14.

  The balancer member 50 as a whole is provided eccentric to the + X side from the rotation center O in order to cancel out the centrifugal force of the orbiting scroll 4. Since the centrifugal force of the swing scroll 4 is canceled by the centrifugal force of the balancer member 50, the radial load acting on the wrap portion 4b of the swing scroll 4 is reduced. For this reason, the reliability of the orbiting scroll 4 can be improved, and the sliding loss between the wrap portion 4b of the orbiting scroll 4 and the wrap portion 3b of the fixed scroll 3 can be reduced.

  Here, the shape and function required for the slider member 40 and the balancer member 50 will be described. Since the cylindrical portion 41 of the slider member 40 slides with the rocking bearing 14, high accuracy roundness, cylindricity and surface roughness are required. On the other hand, the balancer member 50 is required to be formed of a high-density material in order to generate a large centrifugal force.

  In addition, in order to prevent the rocking bearing 14 from coming into contact with each other, it is necessary to match the position of the centrifugal force acting center of the slider 30 with the center position of the rocking bearing 14 in the axial direction. When the position of the center of centrifugal force action of the slider 30 and the center position of the rocking bearing 14 are shifted, the slider 30 tries to overturn, and a single contact occurs between the cylindrical portion 41 of the slider member 40 and the rocking bearing 14. . Therefore, in addition to the main weight portion 51 for canceling the centrifugal force of the orbiting scroll 4, the slider 30 needs to be provided with a rollover prevention weight portion that is eccentric in the opposite direction to the main weight portion 51.

  Next, problems in manufacturing the slider 30 will be described. As described above, the outer peripheral surface of the cylindrical portion 41 that slides with the rocking bearing 14 requires high-precision finishing. However, when the slider portion and the balancer portion of the slider 30 are integrally formed, the balancer portion becomes an obstacle, and it is difficult to perform a finishing process such as rotational polishing on the outer peripheral surface of the cylindrical portion 41. Further, originally, the slider portion is required to have sliding characteristics (including seizure resistance, wear resistance, etc.), and the balancer portion is required to have high density and high strength. When the slider part and the balancer part are integrally formed, it is necessary to form the slider part and the balancer part from the same material, so that both the characteristics required for the slider part and the characteristics required for the balancer part are achieved. Is difficult. On the other hand, when the slider 30 is divided into the slider member 40 and the balancer member 50 as in the present embodiment, the finishing of the cylindrical portion 41 is facilitated. The accuracy of roundness, cylindricity and surface roughness can be improved. Further, when the slider 30 is divided, the slider member 40 can be formed of a material having excellent sliding characteristics, and the balancer member 50 can be formed of a high density material or a high strength material. For this reason, the characteristic calculated | required by the slider member 40 and the characteristic calculated | required by the balancer member 50 can be made compatible.

  The support portion 52 of the balancer member 50 includes planar rotation stop surfaces 52 a and 52 b that prevent the slider member 40 from slipping. The rotation stop surfaces 52a and 52b are, for example, flat surfaces perpendicular to the Y axis, and are opposed to each other with the flat plate portion 42 of the slider member 40 interposed therebetween. The rotation stop surfaces 52a and 52b are in contact with planar end surfaces 42a and 42b formed on the flat plate portion 42, respectively. Thereby, since the idler of the balancer member 50 with respect to the slider member 40 can be prevented, a phase shift between the slider member 40 and the balancer member 50 can be prevented.

  FIG. 4 is a cross-sectional view showing an axial cross section of the slider 30 of the scroll compressor according to the present embodiment. In FIG. 4, the right direction represents the + X direction, and the left direction represents the -X direction. As shown in FIG. 4, a substantially complementary step structure 60 is formed at the contact portion between the support portion 52 and the slider member 40 on the −X side from the rotation center O. The step structure 60 includes an upper step portion 60a and a lower step portion 60b that are adjacent to each other in the axial direction.

  A protruding portion 44 that protrudes in the −X direction is formed as a part of the flat plate portion 42 on the upper step portion 60 a on the slider member 40 side. A tip end surface 44 a that faces generally in the −X direction is formed at the tip of the protruding portion 44. At least a part of the distal end surface 44a is a plane perpendicular to the X axis. A facing surface 52c facing substantially the + X direction is formed on the upper step portion 60a on the support portion 52 side. The facing surface 52c faces the tip surface 44a through the gap 61. At least a part of the facing surface 52c is a plane perpendicular to the X axis.

  A flat horizontal load support surface 44b is formed on the lower step portion 60b on the slider member 40 side. The horizontal load support surface 44b is formed perpendicular to the X axis and faces the -X direction. The horizontal load support surface 44b is located on the + X side with respect to the front end surface 44a. A flat contact surface 52d is formed on the lower step portion 60b on the support portion 52 side. The contact surface 52d is formed perpendicular to the X axis and faces the + X direction. The contact surface 52d is located on the + X side with respect to the facing surface 52c. The contact surface 52d is in contact (for example, surface contact) with the horizontal load support surface 44b.

  In the slider member 40, a first vertical load support surface 44c is formed between the lower surface of the protruding portion 44, that is, between the front end surface 44a and the horizontal load support surface 44b. The first vertical load support surface 44c is formed horizontally so as to be perpendicular to the axial direction and is directed downward. The first vertical load support surface 44c is located closer to the −X side than the horizontal load support surface 44b.

  In the support portion 52, a contact surface 52e is formed between the facing surface 52c and the contact surface 52d. The contact surface 52e is formed horizontally so as to be perpendicular to the axial direction, and faces upward. The contact surface 52e is located on the −X side with respect to the contact surface 52d. The contact surface 52e is in contact (for example, surface contact) with the first vertical load support surface 44c.

  The main weight portion 51 has a substantially partial cylindrical shape. The main weight portion 51 is provided on the outer peripheral side of the cylindrical portion 41 and on the portion that is closer to the + X side than the rotation center O. The main weight portion 51 is formed along the cylindrical portion 41 via a gap 71 in which the rocking bearing 14 and the boss portion 4 c of the rocking scroll 4 are disposed. Note that the main weight portion 51 of this example is provided only in a portion that is on the + X side from the rotation center O, but a part of the main weight portion 51 is provided in a portion that is on the −X side from the rotation center O. It may be.

  A part of the main weight portion 51 is disposed on the flat plate portion 42. A portion of the upper surface of the flat plate portion 42 that comes into contact with the main weight portion 51 is a second vertical load support surface 42c. The second vertical load support surface 42c is formed horizontally so as to be perpendicular to the axial direction and is directed upward. The second vertical load support surface is located on the + X side with respect to the horizontal load support surface 44b. A contact surface 51 a that is a part of the lower surface of the main weight portion 51 is in contact with the second vertical load support surface 42 c. The contact surface 51a is formed horizontally so as to be perpendicular to the axial direction, and faces downward. The second vertical load support surface 42 c and the contact surface 51 a also serve as a fastening surface between the slider member 40 and the balancer member 50. That is, the slider member 40 and the balancer member 50 are fastened by a fastening member 70 (for example, a bolt, a rivet, a pin, or the like) via the second vertical load support surface 42c and the contact surface 51a that are in contact with each other. .

  FIG. 5 is a diagram illustrating a centrifugal force that acts on the balancer member 50 during the operation of the scroll compressor according to the present embodiment, and a load that acts on the slider member 40 from the balancer member 50 by the centrifugal force. FIG. 5 shows the same cross section as FIG. In FIG. 5, some of the reference numerals in FIG. 4 are omitted.

  As shown in FIG. 5, during the operation of the scroll compressor, the slider 30 rotates about the rotation center O, so that the centrifugal force Fc in the + X direction acts on the balancer member 50 that is a part of the slider 30. . Due to the centrifugal force Fc, the horizontal load Fh in the + X direction from the balancer member 50 acts on the horizontal load support surface 44b of the slider member 40. The balancer member 50 receives a reaction force in the −X direction from the horizontal load support surface 44b. This reaction force has the same magnitude in the opposite direction to the centrifugal force Fc in the + X direction acting on the balancer member 50.

  Here, the centrifugal force acting center C <b> 1 of the balancer member 50 is located at substantially the same height as the axial center of the rocking bearing 14. On the other hand, the horizontal load support surface 44b is positioned below the rocking bearing 14. That is, the position of the centrifugal force acting center C1 is shifted upward from the position of the horizontal load support surface 44b. Therefore, a rollover moment in the clockwise direction in FIG. 5 is generated in the balancer member 50 around the horizontal load support surface 44b.

  Due to this overturning moment, an upward vertical load Fv1 acts on the balancer member 50 on the −X side of the horizontal load support surface 44b, and a downward vertical load Fv2 on the + X side of the horizontal load support surface 44b. Works. The upward vertical load Fv1 is supported by the first vertical load support surface 44c of the slider member 40, and the downward vertical load Fv2 is supported by the second vertical load support surface 42c of the slider member 40.

  As described above, the force acting between the slider member 40 and the balancer member 50 is pressed through the horizontal load support surface 44b, the first vertical load support surface 44c, and the second vertical load support surface 42c. Balance by load. Thereby, since it can prevent that loads, such as a shear load and a tensile load, act on the fastening member 70, the reliability of the fastening member 70 can be improved.

  The support 52 applies a horizontal load Fh in the + X direction to the slider member 40 and receives a reaction force in the −X direction from the slider member 40. Since the support portion 52 has a large radial width in terms of a function as a balance weight, the support portion 52 has high strength and rigidity in the radial direction. Therefore, high reliability is obtained by supporting the reaction force in the −X direction from the slider member 40 with the support portion 52.

  In particular, in the present embodiment, a contact surface 52 d that contacts the horizontal load support surface 44 b of the slider member 40 is provided on the lower step portion 60 b of the support portion 52. Since the lower step portion 60b of the support portion 52 has a larger radial width than the upper step portion 60a of the support portion 52, the lower step portion 60b has higher strength and rigidity than the upper step portion 60a. Therefore, higher reliability can be obtained with the configuration of the present embodiment.

  In the present embodiment, the first vertical load support surface 44 c is in contact with the contact surface 52 e of the support portion 52, and the second vertical load support surface 42 c is in contact with the contact surface 51 a of the main weight portion 51. It is in contact. Since the distance between the first vertical load support surface 44c and the second vertical load support surface 42c is sufficiently long, the rollover moment generated in the balancer member 50 can be supported with a long arm length. Therefore, the load acting on each of the first vertical load support surface 44c and the second vertical load support surface 42c can be kept small.

  In the present embodiment, the slider 30 is divided into a slider member 40 and a balancer member 50. Therefore, since the finishing process of the cylindrical part 41 becomes easy, the accuracy of the roundness, the cylindricity and the surface roughness of the cylindrical part 41 can be improved. Furthermore, in this embodiment, the slider member 40 and the balancer member 50 can be assembled without using press-fitting or shrink fitting. Therefore, it is possible to prevent the roundness and cylindricity of the cylindrical portion 41 from being deteriorated in the assembly process of the slider 30.

  In the present embodiment, since both the horizontal load support surface 44b and the contact surface 52d are planar, the contact area between the horizontal load support surface 44b and the contact surface 52d can be easily adjusted.

  FIG. 6 is a cross-sectional view showing axial sections of the slider member 40 and the balancer member 50 of the scroll compressor according to the present embodiment. As shown in FIG. 6, in the balancer member 50, the contact surface 52e facing upward is located below the contact surface 51a facing downward. An axial distance between the contact surface 52e and the contact surface 51a is h1.

  Further, in the slider member 40, the first vertical load support surface 44c facing downward is located below the second vertical load support surface 42c facing upward. An axial distance between the first vertical load support surface 44c and the second vertical load support surface 42c is h2.

  In the present embodiment, the axial distance h2 between the first vertical load support surface 44c and the second vertical load support surface 42c is the axial distance h1 between the contact surface 52e and the contact surface 51a. (H2> h1). Further, the difference between the axial distance h2 and the axial distance h1 is smaller than 0.5 mm. That is, the axial distances h1 and h2 satisfy the relationship of 0.5 [mm]> (h2−h1)> 0 [mm].

  Thus, when the slider member 40 and the balancer member 50 are fixed, the balancer member 50 is slightly inclined with respect to the slider member 40, and between the first vertical load support surface 44c and the contact surface 52e, And both the 2nd vertical direction load support surface 42c and the contact surface 51a can be made to contact reliably. At this time, since the inclination angle of the balancer member 50 with respect to the slider member 40 is very small, the deviation of the centrifugal force from the design value can be ignored.

  On the other hand, if the axial distance h2 is smaller than the axial distance h1, the first vertical load when the second vertical load support surface 42c and the contact surface 51a are fastened. The support surface 44c and the contact surface 52e are separated. Thereby, since the overturning moment of the balancer member 50 acts on the fastening member 70 during operation of the scroll compressor, the fastening member 70 may be damaged.

Embodiment 2. FIG.
A scroll compressor according to Embodiment 2 of the present invention will be described. FIG. 7 is a diagram showing a configuration of the slider 30 of the scroll compressor according to the present embodiment. In FIG. 7, a top view (a) of the slider 30 and an axial sectional view (b) are shown together. In addition, about the component which has the function and effect | action same as Embodiment 1, the same code | symbol is attached | subjected and the description is abbreviate | omitted. As shown in FIG. 7, in the present embodiment, the horizontal load support surface 44b is formed in a convex arc shape (partial cylindrical shape), and the contact surface 52d that contacts the horizontal load support surface 44b is provided. It is formed in a concave arc shape (partial cylindrical shape). The radius of curvature of the horizontal load support surface 44b is the same as or smaller than the radius of curvature of the contact surface 52d. Also in the present embodiment, the same effect as in the first embodiment can be obtained.

Embodiment 3 FIG.
A scroll compressor according to Embodiment 3 of the present invention will be described. As described in the first embodiment, during the operation of the scroll compressor, the force acting between the slider member 40 and the balancer member 50 is the horizontal load support surface 44b, the first vertical load support surface 44c, and It balances with the pressing load through each of the 2nd vertical direction load support surfaces 42c. For this reason, the fastening member 70 should just have the function of temporary fix | stop for the slider member 40 and the balancer member 50 not to isolate | separate during the stop of a scroll compressor. Accordingly, only the adhesive can be used for fixing the slider member 40 and the balancer member 50 without using the fastening member 70. According to this configuration, since the manufacturing process of the slider 30 can be simplified and the number of parts of the slider 30 can be reduced, the manufacturing cost of the scroll compressor can be reduced.

  As described above, the scroll compressor according to the first to third embodiments transmits the rotational driving force to the fixed scroll 3, the swing scroll 4 that swings with respect to the fixed scroll 3, and the swing scroll 4. A main shaft 7, an eccentric shaft portion 7a that is provided at one end of the main shaft 7 and is eccentric in a predetermined eccentric direction with respect to the central axis of the main shaft 7, and a slide that slidably fits the eccentric shaft portion 7a The slider 30 in which the groove 43 is formed and the swing bearing 14 provided on the swing scroll 4 and rotatably supporting the slider 30 are provided. The slider 30 is supported by the rocking bearing 14, and a balancer member 50 that is separate from the slider member 40 and is fixed to the slider member 40 and cancels centrifugal force acting on the rocking scroll 4. And have. The balancer member 50 has a main weight portion 51 provided on the anti-eccentric direction side of the rotation center O of the slider 30 when the opposite direction of the eccentric direction (−X direction) is the anti-eccentric direction (+ X direction). And a support portion 52 that is formed integrally with the main weight portion 51 and supports the slider member 40 from the eccentric direction side. The slider member 40 abuts on the support portion 52 and supports a load on the balancer member 50 in the anti-eccentric direction, a horizontal load support surface 44b (an example of the anti-eccentric load support surface), and a horizontal load support surface 44b. A first vertical load support surface 44c (an example of a first axial load support surface) that is provided closer to the eccentric direction and supports the load of the balancer member 50 in one direction parallel to the central axis of the main shaft 7. The second vertical load support surface 42c (the second axial load support surface of the second axial load support surface) is provided on the side opposite to the eccentric direction from the horizontal load support surface 44b and supports the load of the balancer member 50 in the direction opposite to the one direction. An example).

  According to this configuration, the load of the balancer member 50 in the anti-eccentric direction generated by the centrifugal force of the balancer member 50 is supported by the horizontal load support surface 44 b of the slider member 40. The load of the balancer member 50 in the central axis direction generated by the moment around the horizontal load support surface 44b is supported by the first vertical load support surface 44c and the second vertical load support surface 42c of the slider member 40. Accordingly, the force acting between the slider member 40 and the balancer member 50 due to the centrifugal force of the balancer member 50 causes the horizontal load support surface 44b, the first vertical load support surface 44c, and the second vertical load support surface 42c. It balances with the pressing load through each of the. Therefore, since the slider member 40 and the balancer member 50 are brought into close contact with each other by the centrifugal force of the balancer member 50 and are more firmly fixed, the reliability of the slider 30 and the scroll compressor can be improved.

  In the scroll compressor according to the above embodiment, the first vertical load support surface 44 c is in contact with the support portion 52, and the second vertical load support surface 42 c is in contact with the main weight portion 51. May be. According to this configuration, the moment around the horizontal load support surface 44b generated in the balancer member 50 can be supported with a long arm length. Therefore, the load acting on each of the first vertical load support surface 44c and the second vertical load support surface 42c can be kept small.

  In the scroll compressor according to the above embodiment, the horizontal load support surface 44b may be formed in a flat shape. According to this configuration, the contact area between the slider member 40 and the balancer member 50 via the horizontal load support surface 44b can be easily adjusted.

  In the scroll compressor according to the above embodiment, the horizontal load support surface 44b may be formed in an arc shape.

  Further, in the scroll compressor according to the above-described embodiment, the balancer member 50 may be fixed to the slider member 40 only by an adhesive without using the fastening member 70. According to this configuration, since the manufacturing process of the slider 30 can be simplified and the number of parts of the slider 30 can be reduced, the manufacturing cost of the scroll compressor can be reduced.

  In the scroll compressor according to the embodiment, the balancer member 50 includes the contact surface 52e that contacts the first vertical load support surface 44c and the contact surface 51a that contacts the second vertical load support surface 42c. And an axial distance h1 between the contact surface 52e and the contact surface 51a, and an axial direction between the first vertical load support surface 44c and the second vertical load support surface 42c. The distance h2 may satisfy the relationship of 0.5 [mm]> (h2−h1)> 0 [mm]. According to this configuration, when the slider member 40 and the balancer member 50 are fixed, the first vertical load support surface 44c and the contact surface 52e are in a state where the balancer member 50 is slightly inclined with respect to the slider member 40. And between the second vertical load support surface 42c and the contact surface 51a can be reliably brought into contact with each other.

Other embodiments.
The present invention is not limited to the above embodiment, and various modifications can be made.
For example, in the above-described embodiment, a vertical scroll compressor in which the central axis of the main shaft 7 is arranged along the vertical direction is taken as an example. The present invention can also be applied to a horizontal scroll compressor that is inclined at an angle.

  Further, the above embodiments can be implemented in combination with each other.

  DESCRIPTION OF SYMBOLS 1 Airtight container, 1a trunk | drum, 1b cover part, 1c bottom part, 2 frame, 3 fixed scroll, 3a base plate, 3b wrap part, 4 rocking scroll, 4a base plate, 4b wrap part, 4c boss part, 5 stator, 6 Rotor, 7 Main shaft, 7a Eccentric shaft, 8 Oil sump, 9 Oil pump, 10 Suction pipe, 11 Discharge pipe, 12 Oldham ring, 13 Oil hole, 14 Swing bearing, 15 Oil drain pipe, 16 Main bearing , 17 Sub bearing portion, 18 sub frame, 19a 1st balancer, 19b 2nd balancer, 20 compression mechanism portion, 21 motor portion, 22 discharge port, 23 discharge chamber, 24 discharge valve, 30 slider, 40 slider member, 41 cylinder Part, 42 flat plate part, 42a, 42b end face, 42c second vertical direction load support surface, 43 slide groove, 44 projecting part, 44a End surface, 44b Horizontal load support surface, 44c First vertical load support surface, 50 Balancer member, 51 Main weight portion, 51a Abutting surface, 52 Support portion, 52a, 52b Anti-rotation surface, 52c Opposing surface, 52d, 52e Contact surface, 60 step structure, 60a upper step, 60b lower step, 61 gap, 70 fastening member, 71 gap, 72 toroidal collar.

Claims (6)

With fixed scrolling,
A swing scroll that swings relative to the fixed scroll;
A main shaft for transmitting rotational driving force to the orbiting scroll;
An eccentric shaft portion provided at one end of the main shaft and decentered in a predetermined eccentric direction with respect to a central axis of the main shaft;
A slider in which a slide groove for slidably fitting the eccentric shaft portion is formed;
An oscillating bearing provided on the oscillating scroll and rotatably supporting the slider;
The slider is
A slider member supported by the rocking bearing;
A balancer member that is a separate member from the slider member, is fixed to the slider member, and cancels centrifugal force acting on the orbiting scroll;
The balancer member is
When the opposite direction of the eccentric direction is the anti-eccentric direction,
A main weight portion provided on the side opposite to the eccentric direction from the rotation center of the slider;
A support portion for supporting the slider member from the eccentric direction side,
The slider member is
An anti-eccentric load supporting surface that abuts the support and supports the load of the balancer member in the anti-eccentric direction;
A first axial load support surface that is provided closer to the eccentric direction than the anti-eccentric load support surface and supports the load of the balancer member in one direction parallel to the central axis;
A second axial load support surface that is provided on the anti-eccentric direction side of the anti-eccentric load support surface and supports the load of the balancer member in a direction opposite to the one direction. Scroll compressor. The first axial load support surface is in contact with the support portion;
The scroll compressor according to claim 1, wherein the second axial load support surface is in contact with the main weight portion.   The scroll compressor according to claim 1 or 2, wherein the anti-eccentric load supporting surface is formed in a flat shape.   The scroll compressor according to claim 1 or 2, wherein the anti-eccentric load supporting surface is formed in an arc shape.   The scroll compressor according to any one of claims 1 to 4, wherein the balancer member is fixed to the slider member only by an adhesive. The balancer member has a first contact surface that contacts the first axial load support surface, and a second contact surface that contacts the second axial load support surface,
The distance h1 in the central axis direction between the first contact surface and the second contact surface, and the central axis between the first axial load support surface and the second axial load support surface The scroll compressor according to any one of claims 1 to 5, wherein the distance h2 in the direction satisfies a relationship of 0.5 [mm]>(h2-h1)> 0 [mm].

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