JP2018135820A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a scroll compressor which enables reduction of a local load received by a bearing from a crank shaft while reducing a diameter of a seal ring.SOLUTION: A scroll compressor 101 includes: a crank shaft 17; a motor 16; a compression mechanism 15; and a housing 23. The housing 23 supports the crank shaft 17 between the motor 16 and a movable scroll 26 of the compression mechanism 15. The housing 23 includes: a housing body 36; an upper bearing 32; and an elastic member 34. The housing body 36 has a housing through hole 31 through which the crank shaft 17 penetrates. The upper bearing 32 rotatably supports the crank shaft 17 and is installed at the inner side of the housing through hole 31. The elastic member 34 is installed between the housing body 36 and the upper bearing 32. A radial young's modulus of the elastic member 34 is smaller than a radial young's modulus of the upper bearing 32.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a scroll compressor used in a refrigeration apparatus or the like.

  A scroll compressor used for a refrigeration apparatus or the like includes a crankshaft, a motor, a compression mechanism, and a housing. The motor rotates the crankshaft around the rotation axis. The compression mechanism includes a movable scroll into which an end of the crankshaft is fitted, and a fixed scroll that meshes with the movable scroll. The housing supports the crankshaft between the motor and the movable scroll. The housing has a bearing that supports an upper portion of the crankshaft. A crankshaft that rotates at high speed tends to bend in a radial direction orthogonal to the rotation axis, whereby the bearing receives a radial load from the crankshaft. This load is locally generated in the vicinity of the upper end of the bearing and causes a decrease in the reliability of the bearing.

  Conventionally, in order to reduce the local load that the bearing receives from the rotating crankshaft, as disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2003-206873), an annular groove is formed radially outside the upper portion of the bearing. A housing in which is formed is used. In this housing, the upper part of the bearing can be bent and elastically deformed in the radial direction by the annular groove. For this reason, the upper part of the bearing is deflected in the radial direction in accordance with the radial deflection of the rotating crankshaft, so that it is avoided that the bearing locally receives a radial load from the crankshaft near the upper end of the bearing. The

  However, when the annular groove is formed on the radially outer side of the upper part of the bearing, the housing needs to have a hole having a diameter larger than that of the bearing above the bearing. This is because, when the housing is viewed from above along the rotation axis of the crankshaft, the annular groove needs to be formed radially outside the bearing. Therefore, when the annular groove is formed in the housing, it is necessary to increase the diameter of the seal ring installed between the housing and the movable scroll.

  The seal ring is fitted into a groove formed on the upper surface of the housing, and defines a back space of the movable scroll. In the back space of the movable scroll, the space inside the seal ring has a higher pressure than the space outside the seal ring. The movable scroll is pressed against the fixed scroll by the pressure in the space inside the seal ring. Therefore, as the seal ring diameter increases, the force with which the movable scroll presses the fixed scroll increases, the performance of the compressor deteriorates due to loss of power of the movable scroll, and the sliding surface between the movable scroll and the fixed scroll increases. There is a risk of lowering reliability. Therefore, in the scroll compressor, it is preferable that the diameter of the seal ring is small.

  The objective of this invention is providing the scroll compressor which can reduce the local load which a bearing receives from a crankshaft, suppressing the diameter of a seal ring.

  A scroll compressor according to a first aspect of the present invention includes a crankshaft, a motor, a compression mechanism, and a housing. The motor rotates the crankshaft around the rotation axis. The compression mechanism includes a movable scroll into which an end of the crankshaft is fitted, and a fixed scroll that meshes with the movable scroll. The housing supports the crankshaft between the motor and the movable scroll. The housing includes a main body, a plain bearing, and an elastic member. The main body has a through hole through which the crankshaft passes. The slide bearing rotatably supports the crankshaft and is installed inside the through hole. The elastic member is installed between the main body and the slide bearing in the radial direction orthogonal to the rotation axis. The Young's modulus in the radial direction of the elastic member is smaller than the Young's modulus in the radial direction of the slide bearing.

  A scroll compressor according to a first aspect includes a housing to which an elastic member is attached. The elastic member is attached to the radially outer side of the slide bearing that supports the crankshaft. The elastic member is elastically deformed by a radial load received from the crankshaft. Therefore, even if the crankshaft is bent and deformed during high load operation of the compressor, the elastic member can be easily deformed according to the shape of the crankshaft. Thereby, the fall of the reliability of a slide bearing by receiving a local load from the crankshaft which deform | transformed and deform | transformed is suppressed. Further, by attaching the elastic member, it is not necessary to provide a structure for reducing the local load that the sliding bearing receives from the crankshaft on the radially outer side of the sliding bearing. Therefore, the diameter of the seal ring installed between the housing and the movable scroll is not restricted due to the structure. Therefore, the scroll compressor which concerns on a 1st viewpoint can reduce the local load which a slide bearing receives from a crankshaft, suppressing the diameter of a seal ring.

  The scroll compressor which concerns on the 2nd viewpoint of this invention is a scroll compressor which concerns on a 1st viewpoint, Comprising: The dimension of the radial direction of an elastic member is larger than the dimension of the radial direction of a slide bearing.

  In the scroll compressor according to the second aspect, the elastic member has a larger radial dimension than the sliding bearing. For this reason, the elastic member is more easily deformed by a radial load received from the crankshaft than the plain bearing. Therefore, the scroll compressor which concerns on a 2nd viewpoint can suppress effectively the fall of the reliability of a slide bearing.

  A scroll compressor according to a third aspect of the present invention is the scroll compressor according to the first aspect or the second aspect, wherein the elastic member has a radial dimension from the motor side toward the movable scroll side. growing.

  In the scroll compressor according to the third aspect, the radial dimension of the elastic member gradually or gradually increases from the lower end toward the upper end in the rotation axis direction. For this reason, the upper end portion of the elastic member is more easily deformed by a radial load received from the crankshaft than the other portions. When the elastic member is not present, the radial load that the sliding bearing receives from the crankshaft becomes maximum at the upper end of the sliding bearing. Therefore, by making it easy to deform the upper end portion of the elastic member, the sliding bearing is effectively suppressed from receiving a local load from the bent and deformed crankshaft. Therefore, the scroll compressor which concerns on a 3rd viewpoint can suppress the fall of the reliability of a slide bearing effectively.

  The scroll compressor which concerns on the 4th viewpoint of this invention is a scroll compressor which concerns on any one of the 1st thru | or 3rd viewpoint, Comprising: An elastic member is resin.

  In the scroll compressor according to the fourth aspect, the elastic member is formed of a resin excellent in workability. Therefore, the shape of the elastic member can be easily processed into a shape suitable for being attached to the housing. Therefore, the scroll compressor according to the fourth aspect can achieve easy attachment of the elastic member and cost reduction.

  The scroll compressor which concerns on the 5th viewpoint of this invention is a scroll compressor which concerns on a 4th viewpoint, Comprising: The Young's modulus of an elastic member is 400 MPa-4000 MPa.

  In the scroll compressor according to the fifth aspect, the elastic member has a Young's modulus that can be appropriately deformed by a radial load received from the crankshaft. If the Young's modulus of the elastic member is too high, the elastic member cannot be sufficiently deformed by a radial load received from the crankshaft, and the sliding bearing is likely to receive a local load from the bent and deformed crankshaft. On the other hand, if the Young's modulus of the elastic member is too low, the sliding bearing will be excessively deformed by the radial load received from the crankshaft, and the mechanical strength of the sliding bearing will gradually decrease due to the long-term use of the compressor. There is a risk. Therefore, the scroll compressor according to the fifth aspect can effectively suppress a decrease in the reliability of the slide bearing.

  A scroll compressor according to a sixth aspect of the present invention is the scroll compressor according to any one of the first to fifth aspects, wherein an average pressure received by the inner peripheral surface of the slide bearing from the crankshaft is 7. When it is 8 MPa, the amount of deformation of the elastic member in the radial direction is 45 μm to 55 μm.

  In the scroll compressor according to the sixth aspect, when a predetermined amount of radial load is received from the crankshaft, the elastic member is deformed in the radial direction by a dimension within a predetermined range. If the amount of deformation in the radial direction of the elastic member is too small, the elastic member cannot be sufficiently deformed by the radial load received from the crankshaft, and the slide bearing is likely to receive a local load from the bent crankshaft. On the other hand, if the amount of deformation in the radial direction of the elastic member is too large, the slide bearing will be excessively deformed by the radial load received from the crankshaft, and the mechanical strength of the slide bearing will increase due to long-term use of the compressor. May decrease gradually. Therefore, the scroll compressor according to the sixth aspect can effectively suppress a decrease in the reliability of the slide bearing.

  The scroll compressor which concerns on the 1st viewpoint of this invention can reduce the local load which a slide bearing receives from a crankshaft, suppressing the diameter of a seal ring.

  The scroll compressor which concerns on the 2nd viewpoint of this invention can suppress effectively the fall of the reliability of a slide bearing.

  The scroll compressor which concerns on the 3rd viewpoint of this invention can suppress effectively the fall of the reliability of a slide bearing.

  The scroll compressor according to the fourth aspect of the present invention can achieve easy attachment of the elastic member and cost reduction.

  The scroll compressor which concerns on the 5th viewpoint of this invention can suppress effectively the fall of the reliability of a slide bearing.

  The scroll compressor which concerns on the 6th viewpoint of this invention can suppress the fall of the reliability of a slide bearing effectively.

It is a longitudinal cross-sectional view of the scroll compressor 101 which concerns on 1st Embodiment. 4 is a bottom view of the fixed scroll 24. FIG. 3 is a top view of the movable scroll 26. FIG. It is a bottom view of the fixed scroll 24 in which the second wrap 26b of the movable scroll 26 and the compression chamber 40 are shown. It is an expanded sectional view of the housing 23 shown by FIG. 4 is a perspective view of an upper bearing 32. FIG. 4 is a cross-sectional view of the upper bearing 32. FIG. 4 is a perspective view of an elastic member 34. FIG. FIG. 6 is a sectional view of only the housing body 36 shown in FIG. 5. FIG. 4 is a view showing a part of a cross section of the housing 23 in a state where the upper bearing 32 is not receiving a radial load from the crankshaft 17. FIG. 4 is a view showing a part of a cross section of the housing 23 in a state where the upper bearing 32 receives a radial load from the crankshaft 17. It is a reference view for comparison, and is a cross-sectional view of the housing 23 having an annular groove 38 instead of the elastic member 34. It is sectional drawing of the housing 123 which concerns on 2nd Embodiment. It is sectional drawing of the housing 223 which concerns on 3rd Embodiment. 14 is a cross-sectional view of a housing 323 according to Modification A. FIG. FIG. 14 is a cross-sectional view of the housing 123 shown in FIG. 13 according to Modification B, showing another embodiment of the elastic member 134. FIG. 16 is a cross-sectional view of the housing 223 shown in FIG. 14 according to Modification B, showing another embodiment of the elastic member 234.

<First Embodiment>
A scroll compressor 101 according to a first embodiment of the present invention will be described with reference to the drawings. The scroll compressor 101 is used in a refrigeration apparatus such as an air conditioner. The scroll compressor 101 compresses the refrigerant circulating in the refrigerant circuit of the refrigeration apparatus.

(1) Configuration of Scroll Compressor FIG. 1 is a longitudinal sectional view of the scroll compressor 101. In FIG. 1, an arrow U indicates a vertically upward direction. An arrow U indicating a vertically upward direction is also shown in FIGS. The scroll compressor 101 mainly includes a casing 10, a compression mechanism 15, a housing 23, an Oldham joint 39, a motor 16, a lower bearing 60, a crankshaft 17, a suction pipe 19, and a discharge pipe 20. Composed. Next, each component of the scroll compressor 101 will be described.

(1-1) Casing The casing 10 includes a cylindrical trunk casing portion 11, a bowl-shaped upper wall section 12, and a bowl-shaped bottom wall section 13. The upper wall portion 12 is welded to the upper end portion of the trunk portion casing portion 11 in an airtight manner. The bottom wall portion 13 is welded to the lower end portion of the body casing portion 11 in an airtight manner.

  The casing 10 is formed of a rigid member that is unlikely to be deformed or damaged when pressure and temperature change inside and outside the casing 10. The casing 10 is installed such that the cylindrical axial direction of the body casing portion 11 is along the vertical direction.

  The casing 10 mainly accommodates the compression mechanism 15, the housing 23, the Oldham coupling 39, the motor 16, the lower bearing 60, and the crankshaft 17. A suction pipe 19 and a discharge pipe 20 are welded to the casing 10 in an airtight manner.

  An oil reservoir space 10 a in which lubricating oil is stored is formed at the bottom of the internal space of the casing 10. The lubricating oil is a refrigerating machine oil that is used to keep the lubricity of the sliding portion of the compression mechanism 15 or the like during the operation of the scroll compressor 101.

(1-2) Compression Mechanism The compression mechanism 15 sucks and compresses low-temperature and low-pressure refrigerant gas, and discharges high-temperature and high-pressure refrigerant gas (hereinafter referred to as “compressed refrigerant”). The compression mechanism 15 is mainly composed of a fixed scroll 24 and a movable scroll 26. The fixed scroll 24 is fixed with respect to the casing 10. The movable scroll 26 performs a revolving motion with respect to the fixed scroll 24. FIG. 2 is a bottom view of the fixed scroll 24 viewed along the vertical direction. FIG. 3 is a top view of the movable scroll 26 viewed along the vertical direction.

(1-2-1) Fixed Scroll The fixed scroll 24 includes a first end plate 24a and a first wrap 24b. The first wrap 24b stands upright from the lower surface of the first end plate 24a. The first wrap 24b has a spiral shape when viewed along the vertical direction. As shown in FIG. 2, a C-shaped oil groove 24e is formed on the lower surface of the first end plate 24a.

  A main suction hole 24c is formed in the first end plate 24a. The main suction hole 24c is a space that connects the suction pipe 19 and a compression chamber 40 described later. The main suction hole 24 c is a space for introducing a low-temperature and low-pressure refrigerant gas from the suction pipe 19 into the compression chamber 40.

  As shown in FIG. 1, an enlarged recess 42, which is a cylindrical recess, is formed on the upper surface of the first end plate 24a. A discharge hole 41 is formed on the bottom surface of the enlarged recess 42. The discharge hole 41 communicates with the compression chamber 40.

  A first compressed refrigerant channel 46 is formed in the first end plate 24a. The first compressed refrigerant channel 46 opens to the enlarged recess 42 and the lower surface of the fixed scroll 24.

  A cover member 44 is fastened to the fixed scroll 24 by bolts 49. The bolt 49 penetrates the cover member 44 and is fixed to the first end plate 24a. The cover member 44 closes the enlarged recess 42 of the fixed scroll 24. The fixed scroll 24 and the cover member 44 are sealed via a gasket (not shown).

  By covering the enlarged recess 42 with the cover member 44, a muffler space 45 that silences the operation sound of the compression mechanism 15 is formed. The first compressed refrigerant channel 46 communicates with the muffler space 45.

(1-2-2) Movable Scroll The movable scroll 26 includes a second end plate 26a, a second wrap 26b, and an upper end bearing 26c. The second wrap 26b stands upright from the upper surface of the second end plate 26a. The second wrap 26b has a spiral shape when viewed along the vertical direction. The upper end bearing 26c stands upright from the center of the lower surface of the second end plate 26a. The upper end bearing 26c has a cylindrical shape.

  Oil supply pores 63 are formed in the second end plate 26a. The oil supply hole 63 communicates the space above the outer peripheral portion of the second end plate 26a and the space inside the upper end bearing 26c.

  The fixed scroll 24 and the movable scroll 26 are surrounded by the first end plate 24a, the first wrap 24b, the second end plate 26a, and the second wrap 26b when the first wrap 24b and the second wrap 26b are engaged with each other. A compression chamber 40 that is a space is formed. The volume of the compression chamber 40 is periodically changed by the revolving motion of the movable scroll 26. During the revolution of the movable scroll 26, the lower surfaces of the first end plate 24 a and the first wrap 24 b of the fixed scroll 24 slide with the upper surfaces of the second end plate 26 a and the second wrap 26 b of the movable scroll 26. Hereinafter, the surface of the first end plate 24a that slides with the movable scroll 26 is referred to as a thrust sliding surface 24d.

  FIG. 4 is a bottom view of the fixed scroll 24 in which the second wrap 26b of the movable scroll 26 and the compression chamber 40 are shown. In FIG. 4, the hatched area represents the thrust sliding surface 24d. As shown in FIG. 4, the oil groove 24e of the fixed scroll 24 is formed on the lower surface of the first end plate 24a so as to fit in the thrust sliding surface 24d.

(1-3) Housing The housing 23 is disposed below the compression mechanism 15 and above the motor 16. The outer peripheral surface of the housing 23 is joined to the inner peripheral surface of the body casing portion 11 in an airtight manner. Thereby, the internal space of the casing 10 is partitioned into a high-pressure space S <b> 1 below the housing 23 and an upper space S <b> 2 above the housing 23. The housing 23 mounts a fixed scroll 24 and sandwiches a movable scroll 26 together with the fixed scroll 24. A second compressed refrigerant channel 48 is formed on the outer periphery of the housing 23. The second compressed refrigerant channel 48 is a hole that penetrates the housing 23 in the vertical direction. The second compressed refrigerant channel 48 communicates with the first compressed refrigerant channel 46 on the upper surface of the housing 23, and communicates with the high-pressure space S <b> 1 on the lower surface of the housing 23.

  A housing through hole 31 is formed in the housing 23. The housing through hole 31 is a hole that penetrates the housing 23 in the vertical direction from the central portion of the upper surface of the housing 23 to the central portion of the lower surface of the housing 23.

  The housing 23 has an upper bearing 32 and an elastic member 34. The upper bearing 32 and the elastic member 34 are attached to the inside of the housing through hole 31. The upper bearing 32 rotatably supports the crankshaft 17. A detailed configuration of the housing 23 including the upper bearing 32 and the elastic member 34 will be described later.

(1-4) Oldham Joint The Oldham Joint 39 is a member for preventing the revolving movable scroll 26 from rotating. The Oldham coupling 39 is disposed between the movable scroll 26 and the housing 23.

(1-5) Motor The motor 16 is a brushless DC motor disposed below the housing 23. The motor 16 mainly has a stator 51 and a rotor 52.

  The stator 51 mainly includes a stator core 51a and a plurality of coils 51b. The stator core 51 a is a cylindrical member that is fixed to the inner peripheral surface of the casing 10. Stator core 51a has a plurality of teeth (not shown). A coil 51b is formed by winding a winding around the teeth.

  A plurality of core cuts are formed on the outer peripheral surface of the stator core 51a. The core cut is a groove formed in the vertical direction from the upper end surface to the lower end surface of the stator core 51a. The core cuts are formed at predetermined intervals along the circumferential direction of the stator core 51a. The core cut forms a core cut passage 55 that extends in the vertical direction between the body casing portion 11 and the stator core 51a.

  The rotor 52 is a columnar member disposed inside the stator core 51a. An air gap is formed between the inner peripheral surface of the stator core 51 a and the outer peripheral surface of the rotor 52. The rotor 52 is connected to the crankshaft 17. The rotor 52 is connected to the compression mechanism 15 via the crankshaft 17. The rotor 52 rotates the crankshaft 17 around the rotation shaft 16a. The rotation shaft 16 a passes through the central axis of the rotor 52.

(1-6) Lower Bearing The lower bearing 60 is disposed below the motor 16. The outer peripheral surface of the lower bearing 60 is joined to the inner peripheral surface of the casing 10. The lower bearing 60 rotatably supports the crankshaft 17. An oil separation plate 62 is attached to the lower bearing 60. The oil separation plate 62 is a plate-like member that is accommodated inside the casing 10. The oil separation plate 62 is fixed to the upper end surface of the lower bearing 60.

(1-7) Crankshaft The crankshaft 17 is disposed such that its axial direction is along the vertical direction. The shaft center of the upper end portion of the crankshaft 17 is eccentric with respect to the shaft center of the portion excluding the upper end portion. The crankshaft 17 has a balance weight 18. The balance weight 18 is fixed in close contact with the crankshaft 17 at a height position below the housing 23 and above the motor 16.

  The crankshaft 17 passes through the center of rotation of the rotor 52 in the vertical direction and is connected to the rotor 52. The upper end portion of the crankshaft 17 is fitted into the upper end bearing 26 c of the movable scroll 26. Thereby, the crankshaft 17 is connected to the movable scroll 26. The crankshaft 17 is rotatably supported by the upper bearing 32 and the lower bearing 60.

  A main oil supply passage 61 is formed inside the crankshaft 17. The main oil supply passage 61 extends along the axial direction of the crankshaft 17. The upper end of the main oil supply passage 61 communicates with an oil chamber 83 that is a space between the upper end surface of the crankshaft 17 and the lower surface of the second end plate 26a. The oil chamber 83 communicates with the thrust sliding surface 24d and the oil groove 24e via the oil supply hole 63 of the second end plate 26a, and finally communicates with the low pressure space S2 via the compression chamber 40. The lower end of the main oil supply passage 61 communicates with the oil sump space 10a.

  The crankshaft 17 has a first sub oil supply path 61 a, a second sub oil supply path 61 b, and a third sub oil supply path 61 c that branch from the main oil supply path 61. The first sub oil supply path 61a, the second sub oil supply path 61b, and the third sub oil supply path 61c extend in the horizontal direction. The first sub oil supply passage 61 a opens at a sliding portion between the crankshaft 17 and the upper end bearing 26 c of the movable scroll 26. The second sub oil supply passage 61 b opens at a sliding portion between the crankshaft 17 and the upper bearing 32 of the housing 23. The third sub oil supply passage 61 c opens at a sliding portion between the crankshaft 17 and the lower bearing 60.

(1-8) Suction Pipe The suction pipe 19 is a pipe for introducing the refrigerant of the refrigerant circuit from the outside of the casing 10 to the compression mechanism 15. The suction pipe 19 passes through the upper wall portion 12 of the casing 10. The suction pipe 19 penetrates the upper space S2 in the vertical direction. Inside the casing 10, the end of the suction pipe 19 is fitted into the main suction hole 24 c of the fixed scroll 24.

(1-9) Discharge Pipe The discharge pipe 20 is a pipe for discharging the compressed refrigerant from the high-pressure space S1 to the outside of the casing 10. The discharge pipe 20 penetrates the trunk casing portion 11 of the casing 10. The discharge pipe 20 penetrates the high-pressure space S1 in the horizontal direction. Inside the casing 10, the end of the discharge pipe 20 is at a height position between the housing 23 and the motor 16.

(2) Detailed Configuration of Housing FIG. 5 is an enlarged cross-sectional view of the housing 23 shown in FIG. The housing 23 mainly includes an upper bearing 32, an elastic member 34, and a housing body 36. The housing 23 is a member in which an upper bearing 32 and an elastic member 34 are attached to a housing main body 36.

(2-1) Upper Bearing The upper bearing 32 is a cylindrical bearing that rotatably supports the crankshaft 17 that passes through the housing through hole 31. The upper bearing 32 is a slide bearing that supports the upper portion of the crankshaft 17. The central axis of the cylindrical hole penetrating the upper bearing 32 in the vertical direction is located on the rotating shaft 16a. The upper bearing 32 has a bearing upper end 33a that is an upper end in the vertical direction and a bearing lower end 33b that is a lower end in the vertical direction.

  FIG. 6 is a perspective view of the upper bearing 32. FIG. 7 is a cross-sectional view of the upper bearing 32. As shown in FIG. 7, the upper bearing 32 is mainly composed of a resin layer 32a and a back metal layer 32b. The resin layer 32a is a cylindrical portion formed of resin. The back metal layer 32b is a cylindrical portion formed of a metal such as steel. The back metal layer 32b covers the outer peripheral surface of the resin layer 32a so as to be in close contact with the outer peripheral surface of the resin layer 32a. The inner peripheral surface of the resin layer 32a is a surface that slides with the outer peripheral surface of the crankshaft 17 that rotates around the rotation shaft 16a. During operation of the scroll compressor 101, the inner peripheral surface of the resin layer 32 a is heated by sliding with the outer peripheral surface of the crankshaft 17. Therefore, it is preferable that the resin layer 32a is formed of an engineering plastic having heat resistance. Moreover, it is preferable that the resin used for the resin layer 32a is blended with a lubricant or the like for improving the slidability with the crankshaft 17.

  The dimension of the resin layer 32a in the radial direction is, for example, greater than 0.0 mm and 0.3 mm or less. The dimension in the radial direction of the back metal layer 32b is, for example, 1.0 mm to 2.0 mm. In this case, the thickness of the upper bearing 32 is 2.3 mm at the maximum. The radial direction is a direction orthogonal to the rotation shaft 16a. In the case of a cylindrical member such as the upper bearing 32, the thickness is a radial distance between the outer peripheral surface and the inner peripheral surface.

(2-2) Elastic Member The elastic member 34 is a cylindrical member disposed between the upper bearing 32 and the housing body 36. The outer peripheral surface of the elastic member 34 is in contact with the inner peripheral surface of the housing through hole 31. The inner peripheral surface of the elastic member 34 is in contact with the outer peripheral surface of the upper bearing 32. FIG. 8 is a perspective view of the elastic member 34.

  The elastic member 34 is made of resin. Resins used for the elastic member 34 are, for example, ABS resin, PTFE (polytetrafluoroethylene), and PET (polyethylene terephthalate). The Young's modulus of the resin used for the elastic member 34 is 400 MPa to 4000 MPa, and preferably 500 MPa to 3500 MPa. For example, the Young's modulus of ABS resin is 2940 MPa, the Young's modulus of PTFE is 520 MPa, and the Young's modulus of PET is 3500 MPa.

  As shown in FIG. 5, the radial dimension of the elastic member 34 is larger than the radial dimension of the upper bearing 32. Further, the smaller the Young's modulus of the resin used for the elastic member 34, the shorter the radial dimension of the elastic member 34 may be. For example, the radial dimension of the elastic member 34 made of ABS resin is 20 mm, the radial dimension of the elastic member 34 made of PTFE is 3.5 mm, and the radial dimension of the elastic member 34 made of PET. May be 22 mm. The vertical dimension of the elastic member 34 is equal to the vertical dimension of the upper bearing 32.

  The Young's modulus in the radial direction of the elastic member 34 is smaller than the Young's modulus in the radial direction of the upper bearing 32. That is, when the same radial load is applied to each of the upper bearing 32 and the elastic member 34, the radial deformation amount of the elastic member 34 is larger than the radial deformation amount of the upper bearing 32. That is, the elastic member 34 is more easily deformed than the upper bearing 32 in the radial direction. When a predetermined amount of radial load is received from the crankshaft 17, the elastic member 34 is deformed in the radial direction by a dimension within a predetermined range.

(2-3) Housing Body The housing body 36 is a metal member that occupies most of the housing 23 excluding the upper bearing 32 and the elastic member 34. The housing body 36 includes a housing through hole 31 and a second compressed refrigerant channel 48. FIG. 9 is a sectional view of only the housing body 36 shown in FIG.

  The housing body 36 has a through hole step portion 31 a formed on the inner peripheral surface of the housing through hole 31. As shown in FIG. 9, the through-hole step portion 31 a is a portion in which the inner diameter of the housing through-hole 31 becomes discontinuously small on the way from the lower end in the vertical direction toward the upper end. The upper bearing 32 and the elastic member 34 are attached below the through hole step portion 31a. Specifically, the elastic member 34 is attached to the housing body 36 so that the outer peripheral surface of the elastic member 34 is in close contact with the inner peripheral surface of the housing through hole 31 below the through hole step portion 31a. Further, the upper bearing 32 is attached to the elastic member 34 such that the outer peripheral surface of the upper bearing 32 is in close contact with the inner peripheral surface of the elastic member 34. As shown in FIG. 5, the upper end surface of the elastic member 34 is in close contact with the horizontal surface of the through-hole step portion 31a. The horizontal plane in the through-hole step portion 31a is a step surface indicated by the arrow 31a in FIG. The lower end surfaces of the upper bearing 32 and the elastic member 34 are at the same position as the lower end surface of the housing body 36 in the vertical direction.

  In the state where the upper bearing 32 and the elastic member 34 are attached to the housing main body 36, the inner diameter of the elastic member 34 is equal to the inner diameter of the housing through hole 31 above the through hole step portion 31a. Therefore, the inner diameter of the upper bearing 32 is shorter than the inner diameter of the housing through hole 31 above the through hole step portion 31a. That is, when the housing through hole 31 is viewed from above along the rotation shaft 16 a, the upper bearing 32 appears to protrude from the inner peripheral surface of the housing through hole 31.

  A seal ring groove 36 a is formed on the upper surface of the housing body 36. The seal ring groove 36 a is an annular groove formed around the opening on the upper side in the vertical direction of the housing through hole 31. The seal ring groove 36a is a groove into which a seal ring (not shown) is fitted. The seal ring is an annular elastic member. The seal ring fitted in the seal ring groove 36 a contacts the lower surface of the second end plate 26 a of the movable scroll 26. The seal ring defines a back space of the movable scroll 26. The back space of the movable scroll 26 is a space between the movable scroll 26 and the housing 23. In the back space of the movable scroll 26, the space inside the seal ring communicates with the high-pressure space S1, and therefore has a higher pressure than the space outside the seal ring. The movable scroll 26 is pressed against the fixed scroll 24 by the pressure in the space inside the seal ring.

(3) Operation of Scroll Compressor First, the flow of refrigerant in the scroll compressor 101 will be described. Next, the flow of the lubricating oil inside the scroll compressor 101 will be described.

(3-1) Flow of refrigerant When the motor 16 is driven and the rotor 52 starts to rotate, the crankshaft 17 connected to the rotor 52 starts to rotate. The axial rotation movement of the crankshaft 17 is transmitted to the movable scroll 26 via the upper end bearing 26c. The axis of the upper end portion of the crankshaft 17 is eccentric with respect to the rotation axis of the crankshaft 17. Therefore, the movable scroll 26 performs a revolving motion with respect to the fixed scroll 24 by the rotational motion of the crankshaft 17. The movable scroll 26 is engaged with the housing 23 via an Oldham joint 39. Therefore, the rotation of the movable scroll 26 is prevented while the movable scroll 26 is revolving.

  The low-temperature and low-pressure refrigerant before being compressed is supplied from the suction pipe 19 to the compression chamber 40 of the compression mechanism 15 via the main suction hole 24c. By the revolving motion of the movable scroll 26, the compression chamber 40 moves from the outer peripheral portion of the fixed scroll 24 toward the center portion while gradually reducing the volume. As a result, the refrigerant in the compression chamber 40 is compressed to become a compressed refrigerant. The compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45 and then discharged to the high-pressure space S <b> 1 above the motor 16 via the first compressed refrigerant channel 46 and the second compressed refrigerant channel 48. Thereafter, the compressed refrigerant flows downward in a part of the core cut passage 55 and reaches the high-pressure space S <b> 1 below the motor 16. Thereafter, the compressed refrigerant reverses the flow direction, flows upward through the other core cut passages 55 and the air gap of the motor 16, and reaches the high-pressure space S <b> 1 above the motor 16. Thereafter, the compressed refrigerant is discharged from the discharge pipe 20 to the outside of the scroll compressor 101.

(3-2) Flow of lubricating oil When the motor 16 is driven and the rotor 52 starts to rotate, the crankshaft 17 connected to the rotor 52 starts to rotate. When the compression mechanism 15 compresses the refrigerant by the rotational movement of the crankshaft 17 and the compressed refrigerant is supplied to the high-pressure space S1, the pressure in the high-pressure space S1 increases. The lower end of the main oil supply passage 61 of the crankshaft 17 communicates with the oil sump space 10a at the bottom of the high pressure space S1. The upper end of the main oil supply passage 61 communicates with the low pressure space S <b> 2 through the oil chamber 83 and the oil supply pores 63. Thereby, a differential pressure is generated between the upper end and the lower end of the main oil supply passage 61. As a result, the lubricating oil stored in the oil reservoir space 10 a is sucked from the lower end of the main oil supply passage 61 due to the differential pressure, and rises in the main oil supply passage 61 toward the oil chamber 83.

  Most of the lubricating oil that moves up the main oil supply passage 61 is sequentially divided into the third sub oil supply passage 61c, the second sub oil supply passage 61b, and the first sub oil supply passage 61a. The lubricating oil flowing through the third sub oil supply passage 61c lubricates the sliding portion between the crankshaft 17 and the lower bearing 60, and then flows into the high pressure space S1 and returns to the oil pool space 10a. The lubricating oil flowing through the second sub oil supply passage 61b lubricates the sliding part between the crankshaft 17 and the upper bearing 32 of the housing 23, and then the housing through hole above the high pressure space S1 and the upper bearing 32. 31 flows into. The lubricating oil that has flowed into the high-pressure space S1 returns to the oil reservoir space 10a. The lubricating oil that has flowed into the housing through hole 31 above the upper bearing 32 flows into the high-pressure space S1 via an oil discharge passage (not shown) formed in the housing 23, and returns to the oil pool space 10a. The lubricating oil flowing through the first auxiliary oil supply passage 61 a lubricates the sliding portion between the crankshaft 17 and the upper end bearing 26 c of the movable scroll 26 and then flows into the housing through hole 31 above the upper bearing 32. Then, it flows into the high pressure space S1 via the oil discharge passage of the housing 23 and returns to the oil sump space 10a.

  The lubricating oil that has moved up to the upper end of the main oil supply passage 61 and reached the oil chamber 83 flows through the oil supply holes 63 and is supplied to the oil groove 24e due to the differential pressure. Part of the lubricating oil supplied to the oil groove 24e leaks into the low pressure space S2 and the compression chamber 40 while sealing the thrust sliding surface 24d. At this time, the leaked high-temperature lubricating oil heats the low-temperature refrigerant gas existing in the low-pressure space S2 and the compression chamber 40. Further, the lubricating oil leaking into the compression chamber 40 is mixed into the compressed refrigerant in the form of minute oil droplets. The lubricating oil mixed in the compressed refrigerant flows from the compression chamber 40 into the high-pressure space S1 through the same path as the compressed refrigerant. Thereafter, the lubricant oil collides with the oil separation plate 62 after descending the core cut passage 55 together with the compressed refrigerant. The lubricating oil adhering to the oil separation plate 62 falls in the high pressure space S1 and returns to the oil reservoir space 10a.

(4) Features of scroll compressor (4-1)
The scroll compressor 101 includes a housing 23 to which an elastic member 34 is attached. The elastic member 34 is disposed between the upper bearing 32 that supports the upper portion of the crankshaft 17 and the housing main body 36 of the housing 23.

  The crankshaft 17 is connected to the rotor 52 of the motor 16 disposed below the housing 23. The upper end portion of the crankshaft 17 is fitted into the upper end bearing 26c of the movable scroll 26 disposed above the housing 23, and is not connected to any member. Therefore, the upper part of the crankshaft 17 that rotates at high speed around the rotation shaft 16a is easily shaken in the radial direction and bent. When the upper part of the crankshaft 17 is bent and inclined, the inner peripheral surface of the upper bearing 32 is pressed from the outer peripheral surface of the crankshaft 17. Thereby, the upper bearing 32 receives a radial load from the crankshaft 17.

  The amount of bending in the radial direction of the rotating crankshaft 17 increases as it approaches the upper end of the crankshaft 17. Therefore, since the bearing upper end 33a of the upper bearing 32 is closer to the upper end of the crankshaft 17 than the bearing lower end 33b of the upper bearing 32, it is easy to receive a larger radial load from the crankshaft 17 that is bent while rotating. .

  However, in the scroll compressor 101, the radial load received by the upper bearing 32 from the crankshaft 17 is transmitted to the elastic member 34 located on the radially outer side of the upper bearing 32. The elastic member 34 is elastically deformed by a radial load received from the crankshaft 17. Specifically, even if the crankshaft 17 is bent and deformed, the elastic member 34 can be easily deformed together with the upper bearing 32 in accordance with the shape of the crankshaft 17. In this manner, the upper bearing 32 receiving a local load from the bent crankshaft 17 is suppressed by the deformation of the elastic member 34.

  The above operation will be described with reference to the drawings. FIG. 10 is a view showing a part of a cross section of the housing 23 in a state where the upper bearing 32 is not receiving a radial load from the crankshaft 17. FIG. 11 is a diagram illustrating a part of a cross section of the housing 23 in a state where the upper bearing 32 receives a radial load from the crankshaft 17. In FIG. 10, since the crankshaft 17 is not bent, the upper bearing 32 and the elastic member 34 are not deformed. On the other hand, in FIG. 11, the crankshaft 17 is bent, and the upper bearing 32 receives a radial load from the crankshaft 17. However, in FIG. 11, the elastic member 34 also receives a radial load from the crankshaft 17, whereby the elastic member 34 is elastically deformed. As a result, the elastic member 34 is deformed in accordance with the shape of the crankshaft 17 together with the upper bearing 32, so that the upper bearing 32 is restrained from receiving a local load from the bent and deformed crankshaft 17. . That is, the pressure that the inner peripheral surface of the upper bearing 32 receives from the outer peripheral surface of the crankshaft 17 is uniform on the inner peripheral surface of the upper bearing 32.

  Here, a case where the housing 23 does not include the elastic member 34 will be described as a comparative example. In this case, when the crankshaft 17 is bent and deformed, the vicinity of the bearing upper end 33 a of the upper bearing 32 receives a local load from the crankshaft 17. Accordingly, the inner peripheral surface of the resin layer 32a in the vicinity of the bearing upper end 33a of the upper bearing 32 slides with the outer peripheral surface of the crankshaft 17 in a state of being pressed against the outer peripheral surface of the rotating crankshaft 17, so that the resin layer 32a May overheat, and the reliability of the upper bearing 32 may be reduced.

  Thus, in the scroll compressor 101 of this embodiment, the local load that the upper bearing 32 receives from the crankshaft 17 is reduced by the elastic deformation of the elastic member 34. Therefore, the scroll compressor 101 reduces the local load in the radial direction received by the upper bearing 32 from the rotating crankshaft 17 by the elastic member 34 attached to the outer peripheral side of the upper bearing 32, and the reliability of the upper bearing 32 is reduced. Deterioration can be suppressed.

(4-2)
In the scroll compressor 101, by attaching the elastic member 34 to the housing 23, it is not necessary to provide a structure for reducing the local load that the upper bearing 32 receives from the crankshaft 17 on the radially outer side of the upper bearing 32. . Therefore, the diameter of the seal ring installed between the housing 23 and the movable scroll 26 is not restricted due to the structure.

  FIG. 12 is a reference view for comparison for explaining the above-described operation, and is a cross-sectional view of the housing 23 having an annular groove 38 instead of the elastic member 34. The annular groove 38 is a structure for reducing a local load that the upper bearing 32 receives from the crankshaft 17. 12, for the sake of convenience, the same reference numerals are used for the same components as those in FIG. 5 showing the embodiment.

  In FIG. 12, the housing main body 36 has a through hole step portion 31 a formed on the inner peripheral surface of the housing through hole 31. The through-hole step portion 31a is a portion in which the inner diameter of the housing through-hole 31 increases discontinuously on the way from the lower end in the vertical direction toward the upper end. A through hole step portion 31 a of the housing through hole 31 is formed at the same height as the bearing upper end 33 a of the upper bearing 32.

  In FIG. 12, the annular groove 38 is formed in the horizontal plane of the through hole step portion 31a. Due to the annular groove 38, the portion radially inward of the housing main body 36 in the vicinity of the bearing upper end 33 a of the upper bearing 32 can be easily bent by a radial load received from the crankshaft 17. Therefore, since the upper bearing 32 can be deformed in accordance with the shape of the crankshaft 17, it is possible to suppress the upper bearing 32 from receiving a local load from the bent and deformed crankshaft 17.

  As shown in FIG. 12, in order to form the annular groove 38, the inner diameter of the housing through hole 31 needs to be increased on the way from the lower end in the vertical direction to the upper end. Therefore, the inner diameter of the seal ring groove 36 a formed on the upper surface of the housing body 36 needs to be larger than the inner diameter of the opening on the upper side in the vertical direction of the housing through hole 31. Therefore, when the annular groove 38 is formed in the housing 23, the inner diameter of the seal ring groove 36a tends to be large.

  On the other hand, in the scroll compressor 101 of the embodiment, since it is not necessary to form the annular groove 38 shown in FIG. 12 in the housing 23, it is necessary to increase the inner diameter of the housing through hole 31 on the way from the lower end in the vertical direction to the upper end. There is no. Therefore, as can be seen from a comparison between FIGS. 5 and 12, in the housing 23 of the embodiment having the elastic member 34, the inner diameter of the seal ring fitted in the seal ring groove 36a can be suppressed.

  Here, the larger the inner diameter of the seal ring, the greater the force with which the movable scroll 26 presses the fixed scroll 24, the performance degradation of the scroll compressor 101 due to the power loss of the movable scroll 26, and the movable scroll 26 and the fixed scroll 24. There is a risk that the reliability of the sliding surface between the two will decrease. Therefore, in the scroll compressor 101, it is preferable that the inner diameter of the seal ring is small.

  As described above, in the scroll compressor 101, the housing 23 includes the elastic member 34 disposed on the outer side in the radial direction of the upper bearing 32. Therefore, it is not necessary to form the annular groove 38 as shown in FIG. Therefore, since the scroll compressor 101 can suppress the inner diameter of the seal ring groove 36a of the housing 23, the performance and reliability of the scroll compressor 101 can be suppressed.

(4-3)
In the scroll compressor 101, the elastic member 34 has a larger radial dimension than the upper bearing 32. The elastic member 34 is formed of a resin that is more easily elastically deformed than the upper bearing 32. Therefore, the elastic member 34 is more easily deformed by the radial load received from the crankshaft 17 than the upper bearing 32. As described above, the local load that the upper bearing 32 receives from the crankshaft 17 is reduced by the elastic deformation of the elastic member 34. Therefore, the scroll compressor 101 can effectively suppress a decrease in reliability of the upper bearing 32 by the elastic member 34 having a larger dimension in the radial direction than the upper bearing 32.

(4-4)
In the scroll compressor 101, the elastic member 34 is formed of a resin having excellent workability. Therefore, the shape of the elastic member 34 can be easily processed into a shape suitable for being attached to the housing body 36. For example, the shape of the elastic member 34 can be processed according to the dimension of the through hole step portion 31 a of the housing body 36. Accordingly, the scroll compressor 101 can achieve easy attachment of the elastic member 34 and cost reduction associated with processing of the elastic member 34.

(4-5)
In the scroll compressor 101, the Young's modulus of the elastic member 34 is 400 MPa to 4000 MPa, and preferably 500 MPa to 3500 MPa. Accordingly, the elastic member 34 has a Young's modulus that can be appropriately deformed by a radial load received from the crankshaft 17. If the Young's modulus of the elastic member 34 is too high, the elastic member 34 cannot be sufficiently deformed by the radial load received from the crankshaft 17, and the upper bearing 32 is likely to receive a local load from the bent crankshaft 17. Become. On the other hand, if the Young's modulus of the elastic member 34 is too low, the elastic member 34 is easily deformed excessively by the radial load received from the crankshaft 17. Since the upper bearing 32 is deformed in accordance with the elastic member 34, the mechanical strength of the upper bearing 32 may be gradually lowered by long-term use of the scroll compressor 101. Therefore, the scroll compressor 101 can effectively suppress a decrease in the reliability of the upper bearing 32 by the elastic member 34 having an appropriate Young's modulus.

(4-6)
In the scroll compressor 101, when a predetermined amount of radial load is received from the crankshaft 17, the elastic member 34 is deformed in the radial direction by a dimension within a predetermined range. If the amount of deformation in the radial direction of the elastic member 34 is too small, the elastic member 34 cannot be sufficiently deformed by the radial load received from the crankshaft 17, and the upper bearing 32 is locally loaded from the deformed crankshaft 17. It becomes easy to receive. On the other hand, if the amount of deformation in the radial direction of the elastic member 34 is too large, the elastic member 34 is easily deformed excessively by the radial load received from the crankshaft 17. Since the upper bearing 32 is deformed in accordance with the elastic member 34, the mechanical strength of the upper bearing 32 may be gradually lowered by long-term use of the scroll compressor 101. Therefore, the scroll compressor 101 effectively suppresses the lowering of the reliability of the upper bearing 32 by the elastic member 34 having an appropriate amount of deformation when receiving a predetermined amount of radial load from the crankshaft 17. can do.

  As an example, when the radial load that the upper bearing 32 receives from the crankshaft 17 is the maximum, the average pressure that the inner peripheral surface of the upper bearing 32 receives from the crankshaft 17 is 7.8 MPa. In this case, the amount of deformation of the elastic member 34 in the radial direction is preferably 45 μm to 55 μm. Thereby, the amount of deformation of the upper bearing 32 in the radial direction due to the radial load received from the crankshaft 17 is about 50 μm at the maximum.

  For example, when the radial dimension of the elastic member 34 made of ABS resin having a Young's modulus of 2940 MPa is 20 mm, the amount of deformation in the radial direction of the elastic member 34 is about 53.3 μm under the above pressure conditions. . Similarly, when the radial dimension of the elastic member 34 made of PTFE having a Young's modulus of 520 MPa is 3.5 mm, the amount of deformation in the radial direction of the elastic member 34 is about 52.8 μm under the above pressure conditions. It is. Similarly, when the radial dimension of the elastic member 34 made of PET having a Young's modulus of 3500 MPa is 22 mm, the deformation amount in the radial direction of the elastic member 34 is about 49.3 μm under the above pressure conditions. .

Second Embodiment
A scroll compressor according to a second embodiment of the present invention will be described. Since the basic configuration, operation, and features of this embodiment are the same as those of the scroll compressor 101 according to the first embodiment, differences from the first embodiment will be mainly described.

  The scroll compressor of this embodiment includes a housing 123 that is different from the housing 23 of the first embodiment. The components other than the housing 123 are the same as those in the first embodiment. FIG. 13 is a cross-sectional view of the housing 123.

  The housing 123 is mainly composed of an upper bearing 132, an elastic member 134, and a housing body 136. The upper bearing 132 is the same as the upper bearing 32 of the first embodiment. The upper bearing 132 has a bearing upper end 133a and a bearing lower end 133b. The shapes of the elastic member 134 and the housing body 136 are different from the shapes of the elastic member 34 and the housing body 36 of the first embodiment.

  The elastic member 134 is a cylindrical member having a cylindrical hole. The elastic member 134 is attached to the housing through hole 131 of the housing body 136. The elastic member 134 has a shape in which the radial dimension gradually increases from the lower end in the vertical direction toward the upper end. That is, the inner diameter of the outer peripheral surface of the elastic member 134 gradually increases from the lower end in the vertical direction toward the upper end. On the other hand, the inner diameter of the inner peripheral surface of the elastic member 134 is constant along the vertical direction as in the embodiment. Therefore, as shown in FIG. 13, the thickness of the elastic member 134 gradually increases from the lower end in the vertical direction toward the upper end. Here, the thickness of the elastic member 134 is a radial distance between the outer peripheral surface and the inner peripheral surface of the elastic member 134. The vertical dimension of the elastic member 134 is the same as the vertical dimension of the upper bearing 132.

  The housing body 136 has a shape that matches the shape of the elastic member 134. Specifically, as shown in FIG. 13, the housing main body 136 has a shape such that the inner diameter of the inner peripheral surface of the elastic member 134 is the same as the inner diameter of the housing through hole 131 above the elastic member 134. doing.

  In the present embodiment, the thickness of the upper end portion of the elastic member 134 is larger than the thickness of the lower end portion of the elastic member 134. In the elastic member 134, the greater the thickness, the greater the amount of deformation caused by the radial load received from the crankshaft 17. Therefore, the elastic member 134 is easily deformed in the radial direction at the position of the bearing upper end 133a rather than the bearing lower end 133b of the upper bearing 132. Further, similarly to the first embodiment, the bearing upper end 133a of the upper bearing 132 is closer to the upper end of the crankshaft 17 than the bearing lower end 133b of the upper bearing 132. Easy to receive large radial loads. Therefore, by making the upper end portion of the elastic member 134 thick and easily deforming in the radial direction, the upper bearing 132 is suppressed from receiving a local load from the bent and deformed crankshaft 17.

  Therefore, the scroll compressor according to the present embodiment can effectively suppress the lowering of the reliability of the upper bearing 132 by the elastic member 134.

<Third Embodiment>
A scroll compressor according to a third embodiment of the present invention will be described. Since the basic configuration, operation, and features of this embodiment are the same as those of the scroll compressor 101 according to the first embodiment, differences from the first embodiment will be mainly described.

  The scroll compressor of this embodiment includes a housing 223 that is different from the housing 23 of the first embodiment. The components other than the housing 223 are the same as those in the first embodiment. FIG. 14 is a cross-sectional view of the housing 223.

  The housing 223 is mainly composed of an upper bearing 232, an elastic member 234, and a housing body 236. The upper bearing 232 is the same as the upper bearing 32 of the first embodiment. The upper bearing 232 has a bearing upper end 233a and a bearing lower end 233b. The shapes of the elastic member 234 and the housing body 236 are different from the shapes of the elastic member 34 and the housing body 36 of the first embodiment.

  The elastic member 234 is a cylindrical member having a cylindrical hole. The elastic member 234 is attached to the housing through hole 231 of the housing body 236. The elastic member 234 has a shape in which the radial dimension increases stepwise from the lower end in the vertical direction toward the upper end. Specifically, the elastic member 234 has one elastic member step 234a. The inner diameter of the outer peripheral surface of the elastic member 234 increases at the elastic member step portion 234a from the lower end in the vertical direction toward the upper end. On the other hand, the inner diameter of the inner peripheral surface of the elastic member 234 is constant along the vertical direction as in the embodiment. Accordingly, as shown in FIG. 14, the thickness of the elastic member 234 increases discontinuously at the elastic member step portion 234a from the lower end in the vertical direction toward the upper end. Here, the thickness of the elastic member 234 is a radial distance between the outer peripheral surface and the inner peripheral surface of the elastic member 234. The vertical dimension of the elastic member 234 is the same as the vertical dimension of the upper bearing 232.

  The housing body 236 has a shape that matches the shape of the elastic member 234. Specifically, as shown in FIG. 14, the housing main body 236 has a shape such that the inner diameter of the inner peripheral surface of the elastic member 234 is the same as the inner diameter of the housing through hole 231 above the elastic member 234. doing.

  In the present embodiment, the thickness of the upper end portion of the elastic member 234 is larger than the thickness of the lower end portion of the elastic member 234. In the elastic member 234, the greater the thickness, the greater the amount of deformation caused by the radial load received from the crankshaft 17. Therefore, the elastic member 234 is easily deformed in the radial direction at the position of the bearing upper end 233a rather than the bearing lower end 233b of the upper bearing 232. Similarly to the first embodiment, the bearing upper end 233a of the upper bearing 232 is closer to the upper end of the crankshaft 17 than the bearing lower end 233b of the upper bearing 232. Easy to receive large radial loads. Therefore, by thickening the upper end portion of the elastic member 234 so as to be easily deformed in the radial direction, the upper bearing 232 is restrained from receiving a local load from the bent crankshaft 17.

  Therefore, the scroll compressor according to the present embodiment can effectively suppress a decrease in the reliability of the upper bearing 232 by the elastic member 234.

<Modification>
A modification applicable to the embodiment of the present invention will be described.

(1) Modification A
In the first embodiment, the vertical dimension of the elastic member 34 is equal to the vertical dimension of the upper bearing 32. However, the vertical dimension of the elastic member 34 may be different from the vertical dimension of the upper bearing 32. This modification is also applicable to the second embodiment and the third embodiment.

  FIG. 15 is a cross-sectional view of the housing 323 of this modification. The housing 323 is mainly composed of an upper bearing 332, an elastic member 334, and a housing body 336. The upper bearing 332 is the same as the upper bearing 32 of the first embodiment. The shapes of the elastic member 334 and the housing body 336 are different from the shapes of the elastic member 34 and the housing body 36 of the first embodiment.

  In FIG. 15, the vertical dimension of the elastic member 334 is larger than the vertical dimension of the upper bearing 332. Therefore, since the elastic member 334 is easily deformed in the vicinity of the upper end of the upper bearing 332, the elastic member 334 effectively suppresses a decrease in the reliability of the upper bearing 332.

(2) Modification B
In the second embodiment, the elastic member 134 has a shape in which the radial dimension gradually increases from the lower end in the vertical direction toward the upper end. However, the elastic member 134 may have other shapes as long as the thickness does not decrease from the vertical lower end toward the upper end. FIG. 16 is a cross-sectional view of the housing 123 shown in FIG. 13, and shows another embodiment of the elastic member 134. In FIG. 16, the thickness of the elastic member 134 is constant at the upper end and the lower end in the vertical direction, and gradually increases from the lower end in the vertical direction toward the upper end between the upper end and the lower end in the vertical direction. Yes.

  In the third embodiment, the elastic member 234 has a shape in which the dimension in the radial direction increases stepwise from the lower end in the vertical direction toward the upper end. Specifically, the elastic member 234 has one elastic member step 234a. However, the elastic member 234 may have other shapes as long as the thickness does not decrease from the lower end in the vertical direction toward the upper end. FIG. 17 is a cross-sectional view of the housing 223 shown in FIG. 14 and shows another embodiment of the elastic member 234. In FIG. 17, the elastic member 234 has two elastic member step portions 234a. The thickness of the elastic member 234 increases stepwise from the lower end in the vertical direction toward the upper end at the position of the two elastic member step portions 234a.

  The elastic member of the housing 23 of the scroll compressor 101 may have a shape that combines the second embodiment and the third embodiment. That is, the elastic member may have both a portion where the radial dimension gradually increases from the vertical lower end toward the upper end and a portion where the radial dimension gradually increases.

  The scroll compressor which concerns on this invention can reduce the local load which a bearing receives from a crankshaft, suppressing the diameter of a seal ring.

DESCRIPTION OF SYMBOLS 15 Compression mechanism 16 Motor 16a Rotating shaft 17 Crankshaft 23 Housing 24 Fixed scroll 26 Movable scroll 31 Housing through-hole (through-hole)
32 Upper bearing (slide bearing)
34 Elastic member 36 Housing body (main body)
101 scroll compressor

JP 2003-206873 A

Claims (6)

A crankshaft (17);
A motor (16) for rotating the crankshaft around a rotation axis (16a);
A movable scroll (26) into which an end of the crankshaft is fitted, and a compression mechanism (15) having a fixed scroll (24) meshing with the movable scroll;
A housing (23) for supporting the crankshaft between the motor and the movable scroll;
With
The housing is
A body (36) having a through hole (31) through which the crankshaft passes;
A sliding bearing (32) that rotatably supports the crankshaft and is installed inside the through hole;
An elastic member (34) installed between the main body and the plain bearing in a radial direction perpendicular to the rotation axis;
With
The Young's modulus in the radial direction of the elastic member is smaller than the Young's modulus in the radial direction of the sliding bearing,
Scroll compressor (101). The radial dimension of the elastic member is larger than the radial dimension of the sliding bearing,
The scroll compressor according to claim 1. The elastic member has a larger dimension in the radial direction from the motor side toward the movable scroll.
The scroll compressor according to claim 1 or 2. The elastic member is made of resin.
The scroll compressor according to any one of claims 1 to 3. The Young's modulus of the elastic member is 400 MPa to 4000 MPa.
The scroll compressor according to claim 4. When the average pressure that the inner peripheral surface of the plain bearing receives from the crankshaft is 7.8 MPa, the amount of deformation in the radial direction of the elastic member is 45 μm to 55 μm.
The scroll compressor according to any one of claims 1 to 5.

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