JP2020056394A - Scroll compressor - Google Patents

Abstract

To optimize a position at which a load is applied from a support member to a movable scroll.SOLUTION: A scroll compressor includes: a fixed scroll fixed to an interior of a housing; a movable scroll which engages with the fixed scroll and revolves; a rotary shaft which causes the movable scroll to revolve; a holding member which holds the fixed scroll from the opposite side of the movable scroll; and a support member which is provided between the rotary shaft and the holding member and supports the movable scroll by a load applied to a position offset from a center of the movable scroll.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a scroll compressor.

  A fixed scroll and an orbiting scroll provided in the hermetic container at a high pressure and provided in the hermetic container, and each plate-shaped spiral tooth is meshed on a base plate so as to form a compression chamber therebetween; The oscillating scroll is driven by inserting an eccentric shaft into the boss provided on the opposite side of the scroll-shaped spiral teeth of the scroll. A compliant frame that supports a driving main shaft in a radial direction with a main shaft portion provided on the main shaft, and a guide frame that supports the compliant frame in a radial direction and is fixed to an airtight container. A scroll compressor that enables an orbiting scroll to move in the axial direction by sliding in the axial direction with respect to the scroll compressor is known (for example, Patent Document 1). Irradiation).

Japanese Patent No. 5641978

  Here, when the movable scroll is supported by a support member provided between a rotating shaft for rotating the movable scroll and a holding member for holding the fixed scroll, the movable scroll is axially moved by sliding the support member in the axial direction with respect to the holding member. If a configuration that is only movable in the direction is adopted, it is not possible to optimize the position where a load is applied to the movable scroll from the support member.

  An object of the present invention is to optimize a position where a load is applied from a support member to a movable scroll.

  With this object in mind, the present invention provides a fixed scroll fixed in a housing, a movable scroll that rotates while being engaged with the fixed scroll, a rotation axis that rotates the movable scroll, and a fixed scroll that is moved from the opposite side of the movable scroll. Provided is a scroll compressor including a holding member for holding, and a support member provided between a rotation shaft and the holding member and supporting the movable scroll by a load applied to a position shifted from the center of the movable scroll.

  Here, the support member may be provided so as to be displaceable in one direction with respect to the holding member.

  The support member may be displaceable in a direction along the rotation axis and may be displaceable in a rotation direction about a virtual axis substantially orthogonal to the rotation axis.

  Further, the support member may be displaceable in a rotational direction opposite to a moment generated in the orbiting scroll, among rotational directions about a virtual axis.

  In this case, the support member receives the reaction force from the holding member with respect to the load received by the orbiting scroll at a specific position on the orbiting scroll side from the position where the load from the rotating shaft is received. May be displaceable in opposite rotational directions. The specific position may be between the end surface of the bearing of the rotation shaft of the support member on the movable scroll side and the surface of the base plate of the movable scroll on the side meshed with the fixed scroll.

  Alternatively, the support member has a gap at a specific position where the gap between the movable scroll and the holding member is the narrowest on the same side as the movable scroll with respect to the position receiving the load from the rotating shaft. Is provided so that the gap between the holding member on the opposite side is smaller than the gap at the narrowest position, so that the movable scroll can be displaced in the rotation direction opposite to the moment generated in the movable scroll. Is also good. The specific position may be between the end surface of the bearing of the rotation shaft of the support member on the movable scroll side and the surface of the base plate of the movable scroll on the side engaged with the fixed scroll.

  Further, the support member may be displaceable in a rotation direction opposite to a moment generated in the orbiting scroll by coming into contact with a protrusion provided on the holding member.

  In addition, the portion of the support member that supports the movable scroll has a shape that exhibits elasticity when the support member is inclined and comes into contact with a surface of the base plate of the movable scroll that is not engaged with the fixed scroll. May be.

  Further, the scroll compressor further includes an Oldham ring for preventing rotation of the movable scroll, and the Oldham ring is engaged with the movable scroll and the support member, the movable scroll and the holding member, or the movable scroll and the fixed scroll. May be.

  In addition, the scroll compressor further includes a sealing mechanism that forms an internal space between at least the holding member and the support member by sealing at least a part of the gap between the holding member and the support member. , May be.

  Further, the holding member may be provided with a passage in the holding member for introducing a refrigerant derived from a compression chamber formed by turning the movable scroll into mesh with the fixed scroll and rotating into the internal space. .

  Further, the fixed scroll may be provided with a fixed scroll internal passage that guides the refrigerant out of the compression chamber and introduces the refrigerant into the holding member internal passage.

  Alternatively, the fixed scroll includes a fixed scroll passage for introducing the refrigerant derived from the compression chamber into the holding member passage, and the movable scroll includes a movable scroll for guiding the refrigerant from the compression chamber and introducing the refrigerant into the fixed scroll passage. It may have a passage. In this case, the fixed scroll inner passage may be in communication with the movable scroll inner passage in at least a part of a cycle in which the movable scroll turns. The fixed scroll passage may have an inlet on the orbit of the outlet of the movable scroll passage when the movable scroll is turned, or the movable scroll passage when the movable scroll is turned. Having an inflow port connected to a recess covering the entire orbit of the outflow port.

  According to the present invention, it is possible to optimize a position where a load is applied to the movable scroll from the support member.

1 is an axial sectional view of a scroll compressor according to a first embodiment. It is an axial section of a compression part and a rotating shaft of a 1st modification of a scroll compressor concerning a 1st embodiment. It is an axial section of a compression part and a rotating shaft of a 2nd modification of a scroll compressor concerning a 1st embodiment. It is an axial sectional view of a compression part and a rotating shaft of a 3rd modification of a scroll compressor concerning a 1st embodiment. It is an axial section of a compression part and a rotating shaft of a 4th modification of a scroll compressor concerning a 1st embodiment. It is an axial sectional view of the scroll compressor concerning a 2nd embodiment. (A) is a perspective view showing a moment received by the orbiting scroll, and (b) is a view showing a state where the orbiting scroll is inclined. It is an axial sectional view of a compression part of a scroll compressor, and a rotating shaft when a moment which acts on a subframe becomes the same direction as a moment which acts on a movable scroll. FIG. 4 is an axial cross-sectional view of a compression unit and a rotary shaft of a scroll compressor when a moment acting on a subframe is in a direction opposite to a moment acting on a movable scroll. FIG. 2 is an axial cross-sectional view of a compression unit and a rotation shaft of a first implementation example of the scroll compressor. It is an axial section of a compression part and a rotating shaft of a 2nd example of implementation of a scroll compressor. It is an axial section of a compression part and a rotating shaft of a 3rd example of implementation of a scroll compressor. It is an axial section of a compression part and a rotating shaft of a 1st modification of a scroll compressor concerning a 2nd embodiment. It is the upper surface figure which looked at the end of the end plate of the movable scroll in the compression part of the 1st modification of the scroll compressor concerning a 2nd embodiment from the upper part. It is the bottom view which looked at the cylindrical part of the fixed scroll in the compression part of the 1st modification of the scroll compressor concerning a 2nd embodiment from the lower part. It is an axial section of a compression part and a rotating shaft of a 2nd modification of a scroll compressor concerning a 2nd embodiment. It is the bottom view which looked at the cylindrical part of the fixed scroll in the compression part of the 2nd modification of the scroll compressor concerning a 2nd embodiment from the lower part.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
In the present embodiment, a fixed scroll, a movable scroll that meshes with the fixed scroll and turns, a rotating shaft that turns the movable scroll, a holding member that holds the fixed scroll from the opposite side of the movable scroll, In a scroll compressor having a support member provided between the movable scroll and the support member, the support member supports the movable scroll by a load applied to a position shifted from the center of the movable scroll. There are two possible configurations for supporting the movable scroll by a load applied to a position where the support member is shifted from the center of the movable scroll. Therefore, the two configurations will be described below in the first embodiment. This will be described as a second embodiment.

[First Embodiment]
FIG. 1 is an axial cross-sectional view of the scroll compressor 1 according to the first embodiment.
The scroll compressor 1 is a compressor widely used for an air conditioner, a refrigerator, and a heat pump. FIG. 1 is a longitudinal sectional view of a hermetic scroll compressor used in a refrigerant circuit of an air conditioner.

  The scroll compressor 1 includes a compression unit 10 that compresses a refrigerant, a drive motor 20 that drives the compression unit 10, and a casing 30 that is an example of a housing that houses the compression unit 10 and the drive motor 20. I have. The scroll compressor 1 according to the present embodiment is a vertical scroll compressor that is disposed such that an axial direction of a rotating shaft 23 of the drive motor 20 described later is the direction of gravity. Hereinafter, the axial direction of the rotating shaft 23 may be referred to as “up and down direction”, the upper side as viewed in FIG. 1 may be referred to as “upper side”, and the lower side may be referred to as “lower side”. Here, a vertical scroll compressor will be described as an example, but the present invention is also applicable to a horizontal scroll compressor.

First, the compression unit 10 will be described.
The compression unit 10 includes a fixed scroll 11 fixed in the casing 30, a movable scroll 12 that turns while being engaged with the fixed scroll 11, and a main frame 13 that is fixed to the casing 30 and holds the fixed scroll 11. A subframe 14 arranged in a space surrounded by the movable scroll 12 and the main frame 13 and supporting the movable scroll 12, and an Oldham ring 15 for rotating the movable scroll 12 without rotating. I have.

  The fixed scroll 11 includes a cylindrical portion 111, an end plate 112 that covers an upper opening of the cylindrical portion 111, and a protruding portion that protrudes radially outward from a lower end of the cylindrical portion 111. 113. Further, the fixed scroll 11 has a fixed-side spiral body 114 projecting downward from a lower end portion of the end plate 112 and formed in a spiral shape when viewed from below. The material of the fixed scroll 11 can be exemplified to be a cast iron material, for example, gray cast iron of FC250.

The cylindrical portion 111 has a radial through-hole 111a formed therein. The through hole 111a functions as a suction port for sucking refrigerant into a space surrounded by the cylindrical portion 111, the end plate 112, and the movable scroll 12.
A vertical through-hole 112a is formed at the center of the end plate 112. The through hole 112a functions as a discharge port for discharging the refrigerant from a space surrounded by the end plate 112, the fixed scroll 114, and the movable scroll 12.
The fixed scroll 11 configured as described above is fixed to the main frame 13 by a positioning means such as a bolt or a positioning pin that is passed through a vertical through hole formed in the protrusion 113.

  The orbiting scroll 12 includes a disk-shaped end plate 121, a movable-side scroll 122 projecting upward from an upper end of the end plate 121 and formed in a spiral shape when viewed from above, and an end plate. 121, a cylindrical portion 123 protruding downward from a lower end portion. The material of the movable scroll 12 can be exemplified by an FC material or an FCD material.

The movable scroll 122 is a spiral having a shape that meshes with the fixed scroll 114 of the fixed scroll 11. The movable scroll 122 and the fixed scroll 114 of the fixed scroll 11 are arranged in a space formed between the cylindrical portion 111 and the end plate 112 of the fixed scroll 11 and the end plate 121 and compressed. A chamber 16 is defined. Then, the volume of the compression chamber 16 is reduced by causing the movable-side spiral 122 to make a circular motion with respect to the fixed stationary-side spiral 114, thereby compressing the refrigerant. In other words, the internal space between the fixed-side spiral 114 and the movable-side spiral 122 contracts toward the center of rotation and compresses the refrigerant.
An eccentric shaft 232 of the rotary shaft 23 described below is fitted into the cylindrical portion 123 via a slide bearing. Thus, the cylindrical portion 123 functions as a bearing for the eccentric shaft 232.

  The main frame 13 is an example of a holding member that holds the fixed scroll 11, and protrudes downward from a radially inner side of a cylindrical first cylindrical portion 131 and a lower end of the first cylindrical portion 131. Cylindrical second cylindrical portion 132, cylindrical third cylindrical portion 133 protruding inward in the radial direction from the lower end of second cylindrical portion 132, and third cylindrical portion 133. And a cylindrical fourth cylindrical portion 134 protruding upward and downward from the inner end. The outer peripheral surface of the first cylindrical portion 131 of the main frame 13 is fixed to a later-described central casing 31 of the casing 30. A rotating shaft 23 of the drive motor 20 described below is fitted inside the fourth cylindrical portion 134 via a journal bearing. As described above, the main frame 13 also functions as a bearing that rotatably supports the rotating shaft 23.

An outer peripheral portion of the first cylindrical portion 131 is provided with a protruding portion 131a that protrudes upward from an upper end. A female screw is formed in the protruding portion 131a, and a bolt passed through a through hole formed in the protruding portion 113 of the fixed scroll 11 is tightened to the female screw so that the fixed scroll 11 is attached to the main frame 13. It is attached.
The first cylindrical portion 131 has a groove 131b extending vertically from the center to the lower portion of the outer peripheral portion.
The rotating shaft 23 is fitted to the inner periphery of the fourth cylindrical portion 134 via a journal bearing, and the fourth cylindrical portion 134 functions as a bearing that rotatably supports the rotating shaft 23.

  The sub-frame 14 is an example of a support member that supports the orbiting scroll 12, and includes a first cylindrical portion 141 having a cylindrical shape and a second cylindrical portion projecting downward from a lower end surface of the first cylindrical portion 141. And a cylindrical portion 142. The subframe 14 is provided between the outer peripheral surface of the first cylindrical portion 141 and the inner peripheral surface of the first cylindrical portion 131 of the main frame 13 and between the inner peripheral surface of the second cylindrical portion 142 and the main frame. A space is provided between the movable frame 12 and the main frame 13 such that the sub frame 14 can be displaced from the main frame 13 only in the axial direction of the rotary shaft 23 between the movable frame 12 and the main frame 13. 13 and is disposed in a space surrounded by the reference numeral 13.

  Further, the first cylindrical portion 131 and the fourth cylindrical portion 134 of the main frame 13 and the first cylindrical portion 141 of the sub-frame 14 have a first concave portion 141a which is recessed downward from the upper end surface. The second recess 141b is formed. In the radial direction, the first recess 141a is formed at the center, and the second recess 141b is formed between the first recess 141a and the protrusion 131a. Then, the cylindrical portion 123 of the movable scroll 12 is inserted into the first concave portion 141a. An Oldham ring 15 disposed between the main frame 13 and the movable scroll 12 to prevent the movable scroll 12 from rotating is disposed in the second recess 141b.

  Note that a discharge passage (not shown) for discharging the refrigerant compressed in the compression chamber 16 is formed in the compression section 10 described above. One end of the discharge passage that discharges the high-pressure refrigerant among the discharge passages is connected to the through hole 112a of the end plate 112 that discharges the refrigerant from a space including the high-pressure refrigerant surrounded by the fixed scroll 11 and the movable scroll 12, The other end is connected to a space below the main frame 13 in the casing 30, and is also connected to the rear chamber 121a. The discharge passage for discharging the intermediate-pressure refrigerant among the discharge passages has a discharge port (not shown) for discharging the refrigerant from a space including the intermediate-pressure refrigerant surrounded by the fixed scroll 11 and the movable scroll 12 at one end. , And the other end is connected to the rear chambers 121b and 142a.

Next, the drive motor 20 will be described.
The drive motor 20 is fixed to the casing 30 below the compression unit 10.
The drive motor 20 includes a stator 21 that forms a stator, a rotor 22 that forms a rotor, a rotation shaft 23 that supports the rotor 22 and rotates with respect to a casing 30, and rotatably supports the rotation shaft 23. And a support member 24.

The stator 21 has a stator main body 211 and a coil 212 wound around the stator main body 211.
The stator main body 211 is a laminated body in which many electromagnetic steel sheets are laminated, and has a substantially cylindrical shape. The diameter of the outer peripheral surface of the stator main body 211 is formed larger than the diameter of the inner peripheral surface of a later-described central casing 31 of the casing 30, and the stator main body 211 (stator 21) is fitted into the central casing 31 by fitting. It is fitted. Examples of a method of fitting the stator main body 211 to the center casing 31 include shrink fitting and press fitting.

  In addition, the stator body 211 has a plurality of teeth (not shown) in a circumferential direction at an inner portion facing the outer periphery of the rotor 22. The coil 212 is arranged in a notch (not shown) existing between adjacent teeth. In the stator 21 according to the present embodiment, it can be illustrated that the coil 212 is a concentrated winding inserted in a notch existing between a plurality of adjacent teeth.

The rotor 22 is a laminate in which a number of ring-shaped electromagnetic steel sheets are laminated, and has a cylindrical shape as a whole. The diameter of the inner peripheral surface of the rotor 22 is formed smaller than the diameter of the outer peripheral surface of the rotating shaft 23, and the rotor 22 is fitted into the rotating shaft 23 with an interference fit. The method of fitting the rotating shaft 23 into the rotor 22 can be exemplified by press fitting. Then, the rotor 22 is fixed to the rotating shaft 23 and rotates together with the rotating shaft 23. In addition, the rotor 22 can be exemplified as having a permanent magnet embedded therein.
The diameter of the outer peripheral surface of the rotor 22 is formed smaller than the diameter of the inner peripheral surface of the stator main body 211 of the stator 21, and there is a gap between the rotor 22 and the stator 21.

The rotation shaft 23 has a main shaft 231 to which the rotor 22 is fitted, and an eccentric shaft 232 provided on the main shaft 231 and having an axis eccentric from the axis of the main shaft 231.
The lower part of the main shaft 231 is rotatably supported by the support member 24, and the upper part is rotatably supported by the main frame 13 of the compression unit 10. The eccentric shaft 232 is rotatably supported by the cylindrical portion 123 of the orbiting scroll 12.

  The rotary shaft 23 has a through hole 233 that passes through the rotary shaft 23 in the axial direction. A first communication hole 234 for communicating the through hole 233 with the bearing of the support member 24; a second communication hole 235 for communicating the through hole 233 with the bearing of the main frame 13; A third communication hole 236 that communicates the through hole 233 with the bearing of the cylindrical portion 123 is formed in the radial direction.

The support member 24 includes a first cylindrical portion 241 having a cylindrical shape, and a second cylindrical portion 242 having a cylindrical shape projecting downward from a lower end of the first cylindrical portion 241. The support member 24 is fixed to the central casing 31 such that an outer peripheral surface of the first cylindrical portion 241 faces an inner peripheral surface of a later-described central casing 31 of the casing 30. The rotating shaft 23 is fitted inside the first cylindrical portion 241 and the second cylindrical portion 242 via a journal bearing. As described above, the support member 24 functions as a bearing that rotatably supports the rotation shaft 23.
Further, the first cylindrical portion 241 is formed with a hole (not shown) or a groove (not shown) for communicating a space above and below the first cylindrical portion 241.
At the lower end of the second cylindrical portion 242 of the support member 24, a pump 243 for pumping lubricating oil is mounted.

Next, the casing 30 will be described.
The casing 30 includes a cylindrical central casing 31 arranged at the center in the vertical direction, an upper casing 32 covering an upper opening in the central casing 31, and a lower casing 33 covering a lower opening in the central casing 31. And The casing 30 includes a discharge unit 34 that discharges the high-pressure refrigerant compressed by the compression unit 10 to the outside of the casing 30 and a suction unit 35 that suctions the refrigerant from outside the casing 30.

As described above, the main frame 13 of the compression unit 10, the stator 21 of the drive motor 20, and the support member 24 are fixed to the central casing 31. Further, the discharge part 34 and the suction part 35 are configured by inserting tubes into through holes formed in the central casing 31. The suction portion 35 is provided at a position corresponding to the through-hole 111 a formed in the cylindrical portion 111 of the fixed scroll 11, and is surrounded by the fixed scroll 11 and the movable scroll 12 from outside the casing 30. A refrigerant is sucked into the space.
The lower casing 33 is formed in a bowl shape, and can store lubricating oil.

Next, the operation of the scroll compressor 1 will be described.
When the drive motor 20 of the scroll compressor 1 is driven, the rotating shaft 23 rotates, and the movable scroll 12 fitted on the eccentric shaft 232 of the rotating shaft 23 turns with respect to the fixed scroll 11. When the orbiting scroll 12 orbits with respect to the fixed scroll 11, low-pressure refrigerant is sucked from the outside of the casing 30 into the space surrounded by the fixed scroll 11 and the movable scroll 12 via the suction portion 35. Then, this refrigerant is compressed as the volume of the compression chamber 16 changes. The high-pressure refrigerant compressed in the compression chamber 16 flows out below the compression unit 10.

  The high-pressure refrigerant that has flowed below the compression unit 10 is discharged to the outside of the casing 30 via a discharge unit 34 provided in the casing 30. In the process of being discharged to the outside of the casing 30, the gas flows through a gap between the rotor 22 and the stator 21 and a gap between the stator 21 and the central casing 31. Then, the high-pressure refrigerant discharged to the outside of the casing 30 is sucked again from the suction portion 35 after the respective steps of condensation, expansion, and evaporation in the refrigerant circuit.

  On the other hand, the lubricating oil accumulated in the lower casing 33 of the casing 30 is pumped up by the pump 243 and rises through the through hole 233 formed in the rotating shaft 23. The raised lubricating oil is supplied to each bearing of the rotating shaft 23 through the first communication hole 234, the second communication hole 235, and the third communication hole 236 formed in the rotating shaft 23, Or 10 sliding parts. The lubricating oil supplied to the sliding portion of the compression unit 10 and the lubricating oil supplied to the bearing of the rotating shaft 23 through the second communication hole 235 and the third communication hole 236 are supplied to the main frame 13. It returns to the lower casing 33 via the formed groove 131b, the gap between the rotor 22 and the stator 21, the axial hole formed in the support member 24, etc., and accumulates in the lower part of the casing 30. In this process and in the process in which the high-pressure refrigerant flows through the gap between the rotor 22 and the stator 21 before being discharged to the outside of the casing 30, the lubricating oil and the refrigerant cool the drive motor 20 while cooling the drive motor 20. Flows to The lubricating oil circulated with the high-pressure refrigerant is then separated from the refrigerant and accumulates in a lower portion of the casing 30.

As described above, in the scroll compressor 1 according to the present embodiment, the sub frame 14 that supports the movable scroll 12 is disposed in the space surrounded by the movable scroll 12 and the main frame 13.
In a general scroll compressor, the sub-frame 14 is not provided, and the moment load received by the movable scroll 12 from the refrigerant sucked from the suction part 35 is applied to the upper surface thrust load from the fixed scroll 11 and the back of the movable scroll 12. Cancel by pressure load. In contrast, in the scroll compressor 1 according to the present embodiment, as shown, the moment load F _M where the movable scroll 12 receives from the suction refrigerant from the suction unit 35, mainly, the upper surface thrust from fixed scroll 11 It is offset by the lower surface thrust reaction force F _L from the reaction force F _U and subframe 14.
In this case, since the distance from the point of the upper surface thrust reaction force F _U to the point of the lower surface thrust reaction force F _L becomes longer, the lower surface thrust reaction force F _L is smaller than the rear load in a typical scroll compressor I can do it. Further, it requires only a top thrust reaction force F _U is small. Thereby, the scroll compressor 1 according to the present embodiment improves the efficiency by reducing the friction loss between the fixed scroll 11 and the movable scroll 12, and slides the upper and lower surfaces of the end plate 121 of the movable scroll 12. The reliability is improved by reducing the load on the part.

Next, a modified example of the scroll compressor 1 according to the present embodiment will be described.
FIG. 2 is an axial cross-sectional view of the compression unit 10 and the rotation shaft 23 of the first modified example of the scroll compressor 1.
The compression unit 10 of the first modified example of the scroll compressor 1 includes a fixed scroll 11, a movable scroll 12, a main frame 13, a sub-frame 14, and an Oldham ring 15, as in FIG. I have. The cylindrical portion 123 of the movable scroll 12 is provided with seal members 123c and 123d for sealing a gap between the movable scroll 12 and the fourth cylindrical portion 134 of the main frame 13. In the first modified example, the inside of the rear chamber 121a is maintained at a high pressure by providing such seal members 123c and 123d. In addition, the first cylindrical portion 141 of the sub-frame 14 seals a gap between the first cylindrical portion 131 of the main frame 13 (a first gap between the sub-frame 14 and the main frame 13). Seal members 141c and 141d as an example of the first seal member are provided, and a gap between the fourth cylindrical portion 134 of the main frame 13 and the second cylindrical portion 142 of the sub-frame 14 is provided. Seal members 142c and 142d as an example of a second seal member that seals (a second gap between the main frame 13) are provided. In the first modification, the pressure in the rear chamber 142a is maintained at a specific intermediate pressure by providing the seal members 141c, 141d, 142c, and 142d.

  In the first modification, seal members 141c, 141d, 142c, 142d for sealing a gap between the sub frame 14 and the main frame 13 are provided. However, this may be broadly regarded as providing a sealing mechanism that seals a gap between the subframe 14 and at least one member facing the subframe 14.

FIG. 3 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the second modification of the scroll compressor 1.
The compression unit 10 of the second modification of the scroll compressor 1 is the same as the compression unit 10 of the first modification of the scroll compressor 1 shown in FIG. 2 except that the outer diameter of the subframe 14 is maximized. . The Oldham ring 15 is moved inward in the radial direction, and the position where the first cylindrical portion 141 of the sub-frame 14 supports the movable scroll 12 is moved outward in the radial direction. In the second modification, the distance from the point of application of the upper surface thrust reaction force to the point of application of the lower surface thrust reaction force is maximized, so that the upper surface thrust reaction force and the lower surface thrust reaction force are minimized.

FIG. 4 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the third modification of the scroll compressor 1.
The compression unit 10 of the third modification of the scroll compressor 1 is different from the compression unit 10 of the second modification of the scroll compressor 1 shown in FIG. 134g and 134h are provided. Here, rails can be exemplified as the guide members 134g and 134h. Further, wheels rolling on the rails may be provided on the subframe 14 as guide members. In the third modified example, the guide members 134g and 134h are provided on the fourth cylindrical portion 134 of the main frame 13 so that the sub-frame 14 is not inclined and is only in the axial direction of the rotation shaft 23 with respect to the main frame 13. It can be displaced.

FIG. 5 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the fourth modification of the scroll compressor 1.
The compression unit 10 of the fourth modification of the scroll compressor 1 is different from the compression unit 10 of the first modification of the scroll compressor 1 shown in FIG. Instead of providing the seal members 142 c and 142 d for sealing the gap between the fourth cylindrical portion 134 of the frame 13 and the first cylindrical portion 141 of the sub-frame 14, Seal members 141e and 141f are provided as an example of a third seal member that seals a gap between them. In the fourth modification, by providing the seal members 141c, 141d, 141e, and 141f, the refrigerant in the rear chamber 142a also flows into the rear chamber 121b, and the pressure in the rear chamber 121b is reduced to the pressure in the rear chamber 142a. The same specific intermediate pressure is maintained.

  In the fourth modification, seal members 141c and 141d for sealing a gap between the subframe 14 and the main frame 13, and seal members 141e and 141e for sealing a gap between the subframe 14 and the movable scroll 12 are provided. 141f. However, this may be broadly regarded as providing a sealing mechanism that seals a gap between the subframe 14 and at least one member facing the subframe 14.

  As described above, in the present embodiment, the movable scroll 12 is movable in the space surrounded by the movable scroll 12, the rotating shaft 23, and the main frame 13 so that the movable scroll 12 can be displaced only in the axial direction of the rotating shaft 23 relative to the main frame 13. A sub-frame 14 for supporting the scroll 12 is provided. This makes it possible to improve the efficiency and reliability of the scroll compressor 1 by reducing the thrust load for stabilizing the orbiting scroll 12 while equalizing the pressure applied to the orbiting scroll 12 from the sub-frame 14 regardless of the location. Now you can.

  In the present embodiment, the sub-frame 14 can be displaced with respect to the main frame 13 only in the direction along the rotation axis 23. However, the sub-frame 14 does not have to move at all with respect to the main frame 13 except for displacement in a direction along the rotation axis 23. In addition to the displacement in the direction along the rotation axis 23, the rotation around the rotation axis 23, the displacement in the direction along the axis perpendicular to the rotation axis 23, and the rotation around the axis perpendicular to the rotation axis 23 Among the rotations, other displacements or rotations may be enabled as long as rotation about an axis perpendicular to the rotation axis 23 is not enabled. In addition, this may be regarded as being wider, which enables the sub-frame 14 to be displaceable with respect to the main frame 13 in a direction along the rotation axis 23. Further, it may be considered that the sub-frame 14 can be displaced in one direction with respect to the main frame 13.

[Second embodiment]
FIG. 6 is an axial cross-sectional view of the scroll compressor 2 according to the second embodiment.
The scroll compressor 2 is also a compressor widely used for an air conditioner, a refrigerator, and a heat pump. FIG. 6 is a longitudinal sectional view of a hermetic scroll compressor used in a refrigerant circuit of an air conditioner.

  The scroll compressor 2 includes a compression unit 10 that compresses a refrigerant, a drive motor 20 that drives the compression unit 10, and a casing 30 that is an example of a housing that houses the compression unit 10 and the drive motor 20. I have. The scroll compressor 2 according to the present embodiment is a vertical scroll compressor that is disposed such that an axial direction of a rotation shaft 23 of the drive motor 20 described later is the direction of gravity. Hereinafter, the axial direction of the rotating shaft 23 may be referred to as “up / down direction”, the upper side as viewed in FIG. 6 may be referred to as “upper side”, and the lower side may be referred to as “lower side”. Here, a vertical scroll compressor will be described as an example, but the present invention is also applicable to a horizontal scroll compressor.

First, the compression unit 10 will be described.
The compression unit 10 includes a fixed scroll 11 fixed in the casing 30, a movable scroll 12 that turns while being engaged with the fixed scroll 11, and a main frame 13 that is fixed to the casing 30 and holds the fixed scroll 11. A subframe 14 disposed between a rotating shaft 23 and a main frame 13 to support the movable scroll 12, and an Oldham ring 15 for rotating the movable scroll 12 without rotating. .

  The fixed scroll 11 includes a cylindrical portion 111, an end plate 112 that covers an upper opening of the cylindrical portion 111, and a protruding portion that protrudes radially outward from a lower end of the cylindrical portion 111. 113. Further, the fixed scroll 11 has a fixed-side spiral body 114 projecting downward from a lower end portion of the end plate 112 and formed in a spiral shape when viewed from below. The material of the fixed scroll 11 can be exemplified to be a cast iron material, for example, gray cast iron of FC250.

The cylindrical portion 111 has a radial through-hole 111a formed therein. The through hole 111a functions as a suction port for sucking refrigerant into a space surrounded by the cylindrical portion 111, the end plate 112, and the movable scroll 12.
A vertical through-hole 112a is formed at the center of the end plate 112. The through hole 112a functions as a discharge port for discharging the refrigerant from a space surrounded by the end plate 112, the fixed scroll 114, and the movable scroll 12.
The fixed scroll 11 configured as described above is fixed to the main frame 13 by a positioning means such as a bolt or a positioning pin that is passed through a vertical through hole formed in the protrusion 113.

  The orbiting scroll 12 includes a disk-shaped end plate 121, a movable-side scroll 122 projecting upward from an upper end of the end plate 121 and formed in a spiral shape when viewed from above, and an end plate. 121, a cylindrical portion 123 protruding downward from a lower end portion. The material of the movable scroll 12 can be exemplified by an FC material or an FCD material.

The movable scroll 122 is a spiral having a shape that meshes with the fixed scroll 114 of the fixed scroll 11. The movable scroll 122 and the fixed scroll 114 of the fixed scroll 11 are arranged in a space formed between the cylindrical portion 111 and the end plate 112 of the fixed scroll 11 and the end plate 121 and compressed. A chamber 16 is defined. Then, the volume of the compression chamber 16 is reduced by causing the movable-side spiral 122 to make a circular motion with respect to the fixed stationary-side spiral 114, thereby compressing the refrigerant. In other words, the internal space between the fixed-side spiral 114 and the movable-side spiral 122 contracts toward the center of rotation and compresses the refrigerant.
An eccentric shaft 232 of the rotary shaft 23 described below is fitted into the cylindrical portion 123 via a slide bearing. Thus, the cylindrical portion 123 functions as a bearing for the eccentric shaft 232.

  The main frame 13 is an example of a holding member that holds the fixed scroll 11, and protrudes downward from a radially inner side of a cylindrical first cylindrical portion 131 and a lower end of the first cylindrical portion 131. And a third cylindrical portion 133 that projects radially inward from a lower end of the second cylindrical portion 132. The outer peripheral surface of the first cylindrical portion 131 of the main frame 13 is fixed to a later-described central casing 31 of the casing 30. Note that, in the second embodiment, unlike the first embodiment, the main frame 13 does not support a rotating shaft 23 of the drive motor 20 described later.

An outer peripheral portion of the first cylindrical portion 131 is provided with a protruding portion 131a that protrudes upward from an upper end. A female screw is formed in the protruding portion 131a, and a bolt passed through a through hole formed in the protruding portion 113 of the fixed scroll 11 is tightened to the female screw so that the fixed scroll 11 is attached to the main frame 13. It is attached.
The first cylindrical portion 131 has a groove 131b extending vertically from the center to the lower portion of the outer peripheral portion.

  The sub-frame 14 is an example of a support member that supports the orbiting scroll 12, and includes a first cylindrical portion 141 having a cylindrical shape and a second cylindrical portion projecting downward from a lower end surface of the first cylindrical portion 141. A cylindrical portion 142 and a cylindrical third cylindrical portion 143 projecting downward from an inner end of the second cylindrical portion 142 are provided. A rotating shaft 23 of the drive motor 20, which will be described later, is fitted inside the third cylindrical portion 143 via a journal bearing. As described above, the subframe 14 also functions as a bearing that rotatably supports the rotating shaft 23. The sub frame 14 is provided between the outer peripheral surface of the first cylindrical portion 141 and the inner peripheral surface of the first cylindrical portion 131 of the main frame 13, and between the outer peripheral surface of the third cylindrical portion 143 and the main frame 13. The sub-frame 14 is displaceable in the axial direction of the rotating shaft 23 with respect to the main frame 13 between the inner peripheral surface of the third cylindrical portion 133 and a virtual axis substantially orthogonal to the rotating shaft 23. The main frame 13 is disposed between the rotating shaft 23 and the main frame 13 with a gap capable of being displaced in the rotation direction about the center.

  In addition, a portion formed by the first cylindrical portion 131 of the main frame 13 and the first cylindrical portion 141 and the third cylindrical portion 143 of the sub-frame 14 has a first concave portion 141a which is recessed downward from the upper end surface. The second recess 141b is formed. In the radial direction, the first recess 141a is formed at the center, and the second recess 141b is formed between the first recess 141a and the protrusion 131a. Then, the cylindrical portion 123 of the movable scroll 12 is inserted into the first concave portion 141a. An Oldham ring 15 disposed between the main frame 13 and the movable scroll 12 to prevent the movable scroll 12 from rotating is disposed in the second recess 141b.

  Note that a discharge passage (not shown) for discharging the refrigerant compressed in the compression chamber 16 is formed in the compression section 10 described above. One end of the discharge passage that discharges the high-pressure refrigerant among the discharge passages is connected to the through hole 112a of the end plate 112 that discharges the refrigerant from a space including the high-pressure refrigerant surrounded by the fixed scroll 11 and the movable scroll 12, The other end is connected to a space below the main frame 13 in the casing 30, and is also connected to the rear chamber 121a. The discharge passage for discharging the intermediate-pressure refrigerant among the discharge passages has a discharge port (not shown) for discharging the refrigerant from a space including the intermediate-pressure refrigerant surrounded by the fixed scroll 11 and the movable scroll 12 at one end. , And the other end is connected to the rear chambers 121b and 142a.

  The drive motor 20 and the casing 30 are the same as those described in the first embodiment, and a description thereof will be omitted.

  Also, the operation of the scroll compressor 2 is the same as that described in the first embodiment, and a description thereof will be omitted.

By the way, in such a scroll compressor 2, the movable scroll 12 tends to incline under the compressive load of gas.
FIG. 7A is a perspective view illustrating a moment received by the orbiting scroll 12. As shown, the movable scroll 12 from a direction perpendicular on the eccentric direction and the horizontal plane of the eccentric shaft 232 from the main axis 231 of the rotary shaft 23 receives a compressive load F _t. Then, the movable scroll 12, the moment M _S around the clock is generated from the perspective A.
FIG. 7B is a diagram showing a state in which the orbiting scroll 12 is inclined when viewed from the viewpoint A in FIG. 7A. As shown, the movable scroll 12 generates a moment load clockwise under compressive load F _t, trying to incline.

On the other hand, the sub-frame 14 receives a lateral load from the shaft and thereby tries to move in the load direction.
FIG. 8 is an axial sectional view of the compression unit 10 and the rotating shaft 23 of the scroll compressor 2 in this case. It is assumed that the position supporting the lateral load _FMJ from the shaft is opposite to the movable scroll 12 with respect to the lateral load _FMJ , as shown in FIG. That is, for example, by the protruding portion 135 of the main frame 13 is in contact with the sub-frame 14, the reaction force R _MJ acting on the sub-frame 14, and has occurred in the position shown in FIG. Then, a moment M _F acting on the sub-frame 14, like becomes clockwise and moment M _S acting on the movable scroll 12, it is impossible to effectively suppress the inclination of the movable scroll 12.

  Therefore, in the present embodiment, a moment in a direction opposite to that of the orbiting scroll 12 is generated in the sub-frame 14 using the lateral load from the shaft, and the inclination of the orbiting scroll 12 is suppressed. This is an example of enabling the sub-frame 14 to be displaced in a direction opposite to the moment generated in the orbiting scroll 12 in a rotation direction about a virtual axis substantially orthogonal to the rotation axis 23. is there.

FIG. 9 is an axial sectional view of the compression unit 10 and the rotating shaft 23 of the scroll compressor 2 in this case. In the present embodiment, as shown in the drawing, the sub-frame 14 has a structure that supports the lateral load _FMJ from the shaft on the same side as the movable scroll 12. That is, for example, by the protrusion 136 of the main frame 13 is in contact with the sub-frame 14, to generate a reaction force R _MJ acting on the subframe 14 to the position shown in FIG. Thus, by generating a moment M _F counterclockwise to the subframe 14, effectively suppressing the inclination of the movable scroll 12. This is an example of receiving the reaction force from the holding member against the load received by the movable scroll at a specific position on the movable scroll side of the position receiving the load from the rotating shaft. Here, the position for generating a reaction force R _MJ acting on the sub-frame 14 may be a position between L1 and L2 in FIG. L1 is the position of the end surface of the third cylindrical portion 143 of the sub-frame 14 on the movable scroll 12 side. If the end face is inclined, the end face may be located at the lowermost position. L1 is an example of the position of the end surface on the movable scroll side of the bearing of the rotation shaft of the support member. L2 is the position of the surface of the end plate 121 of the movable scroll 12 on which the movable scroll 122 is formed. When this surface is inclined, the uppermost position of the surface may be set. L2 is an example of the position of the surface of the base plate of the movable scroll on the side meshed with the fixed scroll.

Further, the reaction force R _MJ acting on the subframe 14 to be generated in the position shown in FIG. 9, when the movable scroll 12 is about to incline, the first first cylindrical portion 131 and the sub-frame 14 of the main frame 13 The structure may be such that the cylindrical portion 141 comes in contact with the third cylindrical portion 133 of the main frame 13 and the third cylindrical portion 143 of the sub-frame 14. More specifically, when the thrust surface of the sub-frame 14 supporting the movable scroll 12 is substantially parallel to the thrust surface of the fixed scroll 11, the first cylindrical portion 131 of the main frame 13 and the first cylindrical portion of the sub-frame 14 The structure may be such that the shape portion 141 comes in contact with the third cylindrical portion 133 of the main frame 13 and the third cylindrical portion 143 of the subframe 14.

  For this purpose, a gap between the first cylindrical portion 131 of the main frame 13 and the first cylindrical portion 141 of the sub-frame 14 is formed by the third cylindrical portion 133 of the main frame 13 and the third cylindrical portion of the sub-frame 14. What is necessary is just to make it narrower than the clearance gap with the shape part 143. This is because the gap at the specific position where the gap between the movable scroll and the holding member is narrowest on the same side as the movable scroll with respect to the position receiving the load from the rotating shaft is set to the opposite side of the movable scroll with respect to the position receiving the load from the rotating shaft. This is an example of making the gap between the holding member and the holding member narrower than the gap at the narrowest position. Here, the position of the gap between the first cylindrical portion 131 of the main frame 13 and the first cylindrical portion 141 of the sub-frame 14 may be the position between L1 and L2 in FIG. L1 is the position of the end surface of the third cylindrical portion 143 of the sub-frame 14 on the movable scroll 12 side. If the end face is inclined, the end face may be located at the lowermost position. L1 is an example of the position of the end surface on the movable scroll side of the bearing of the rotation shaft of the support member. L2 is the position of the surface of the end plate 121 of the movable scroll 12 on which the movable scroll 122 is formed. When this surface is inclined, the uppermost position of the surface may be set. L2 is an example of the position of the surface of the base plate of the movable scroll on the side meshed with the fixed scroll.

  Further, in the present embodiment, as shown in FIG. 9, the outer peripheral side of the thrust bearing 144 of the sub-frame 14 is elastic when the movable scroll 12 is inclined and comes into contact with the surface on which the movable scroll 122 is not formed. It is good also as a shape which exerts. This disperses the thrust load and suppresses local contact. However, the shape of the thrust bearing 144 shown in FIG. 9 is merely an example, and any shape may be used as long as it can exhibit elasticity. The thrust bearing 144 is an example of a portion of the support member that supports the movable scroll. The shape of the thrust bearing 144 in FIG. 9 is such that the surface of the movable scroll that is not engaged with the fixed scroll of the base plate of the movable scroll when the movable scroll is inclined. This is an example of a shape that exerts elasticity when it comes into contact with.

Next, an example of mounting the Oldham ring 15 of the scroll compressor 2 according to the present embodiment will be described.
FIG. 10 is an axial sectional view of the compression unit 10 and the rotating shaft 23 of the first implementation example of the scroll compressor 2.
The compression unit 10 of the first implementation example of the scroll compressor 2 includes a fixed scroll 11, a movable scroll 12, a main frame 13, a sub-frame 14, and an Oldham ring 15, as in FIG. I have. In the first mounting example, the Oldham ring 15 is engaged with the movable scroll 12 and the sub-frame 14. Specifically, a pair of Oldham guide grooves 121g are formed on the lower surface of the end plate 121 of the orbiting scroll 12 in a substantially straight line. A pair of two key portions 15b formed on the upper surface of the ring portion 15a of the Oldham ring 15 are reciprocally slidably engaged with the respective Oldham guide grooves 121g. On the upper surface of the first cylindrical portion 141 of the sub-frame 14, a pair of Oldham guide grooves 141g having a phase difference of about 90 ° with the Oldham guide grooves 121g of the orbiting scroll 12 are formed substantially in a straight line. I have. A pair of two key portions 15c formed on the lower surface of the ring portion 15a of the Oldham ring 15 are respectively slidably engaged with the Oldham guide grooves 141g. With the Oldham ring 15 configured as described above, the orbiting scroll 12 can perform a turning motion without rotating.

FIG. 11 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the second implementation example of the scroll compressor 2.
The compression unit 10 of the second implementation example of the scroll compressor 2 includes a fixed scroll 11, a movable scroll 12, a main frame 13, a sub-frame 14, and an Oldham ring 15, as in FIG. I have. In the second mounting example, the Oldham ring 15 is engaged with the movable scroll 12 and the main frame 13. Specifically, a pair of Oldham guide grooves 121g are formed on the lower surface of the end plate 121 of the orbiting scroll 12 in a substantially straight line. A pair of two key portions 15b formed on the upper surface of the ring portion 15a of the Oldham ring 15 are reciprocally slidably engaged with the respective Oldham guide grooves 121g. On the upper surface of the first cylindrical portion 131 of the main frame 13, a pair of Oldham guide grooves 131 g having a phase difference of approximately 90 ° with respect to the Oldham guide grooves 121 g of the orbiting scroll 12 is formed substantially in a straight line. I have. A pair of two key portions 15d formed on the lower surface of the ring portion 15a of the Oldham ring 15 are reciprocally slidably engaged with the respective Oldham guide grooves 131g. With the Oldham ring 15 configured as described above, the orbiting scroll 12 can perform a turning motion without rotating.

FIG. 12 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the third mounting example of the scroll compressor 2.
The compression unit 10 of the third mounting example of the scroll compressor 2 includes a fixed scroll 11, a movable scroll 12, a main frame 13, a sub-frame 14, and an Oldham ring 15, as in FIG. I have. In the third example, the Oldham ring 15 is engaged with the movable scroll 12 and the fixed scroll 11. Specifically, a pair of Oldham guide grooves 121g are formed on the lower surface of the end plate 121 of the orbiting scroll 12 in a substantially straight line. A pair of two key portions 15b formed on the upper surface of the ring portion 15a of the Oldham ring 15 are reciprocally slidably engaged with the respective Oldham guide grooves 121g. On the lower surface of the end plate 112 of the fixed scroll 11, a pair of Oldham guide grooves 112g each having a phase difference of about 90 ° with the Oldham guide groove 121g of the movable scroll 12 are formed substantially in a straight line. In each Oldham guide groove 112g, a pair of two key portions 15e formed on the upper surface of the ring portion 15a of the Oldham ring 15 are reciprocally slidably engaged. With the Oldham ring 15 configured as described above, the orbiting scroll 12 can perform a turning motion without rotating.

  By the way, in the configuration in which the sub-frame 14 supporting the orbiting scroll 12 can be displaced only in the direction along the rotation axis 23, the moment acting on the sub-frame 14 is not controlled, and the state is left to the end. In this case, the lower surface thrust reaction force cannot be set at an effective position, and the effect cannot be exhibited. On the other hand, in the present embodiment, since the lower surface thrust reaction force can be set to an ideal position, the effect can be maximized.

  Also, in the second embodiment, similarly to the first embodiment, the main frame 13 and the sub-frame 14 are surrounded by the two seal members between the main frame 13 and the sub-frame 14. May be formed. Then, the sub-frame 14 may be pressed against the movable scroll 12 by introducing a specific pressure (intermediate pressure) from the compression chamber 16 during the compression stroke into the space. Since there are mainly two methods for realizing the method, they will be described below in detail as a first modified example and a second modified example.

FIG. 13 is an axial sectional view of the compression unit 10 and the rotating shaft 23 of the first modification of the scroll compressor 2.
The compression section 10 of the first modification of the scroll compressor 2 includes a fixed scroll 11, a movable scroll 12, a main frame 13, and a sub-frame 14, as in FIG. The movable scroll 12 is engaged with the fixed scroll 11 and turns to form a compression chamber 16. The compression chamber 16 draws in and compresses a low-pressure refrigerant from the radial through-hole 111a as shown by an arrow, and discharges a high-pressure refrigerant from the vertical through-hole 112a as shown by an arrow. The illustration of the Oldham ring 15 is omitted.

  The compression section 10 is provided with a seal member 171a that seals a gap between the cylindrical section 123 of the orbiting scroll 12 and the third cylindrical section 143 of the subframe 14. In the first modification, the back chamber 171 is formed by providing the seal member 171a, and the inside of the back chamber 171 is maintained at a high pressure.

  The compression section 10 is provided with a seal member 172 a for sealing a gap between the second cylindrical section 132 of the main frame 13 and the first cylindrical section 141 of the subframe 14, and the A seal member 172b that seals a gap between the three cylindrical portions 133 and the third cylindrical portion 143 of the subframe 14 is provided. These seal members 172a and 172b correspond to the above two seal members. In the first modified example, the back chamber 172 is formed by providing the seal members 172a and 172b.

  Further, the compression section 10 is provided with a first passage 181, a second passage 182, and a third passage 183 for guiding the refrigerant having a specific pressure from the compression chamber 16 to the rear chamber 172. The first passage 181 is a passage that passes through the inside of the orbiting scroll 12, and is an example of a passage in the orbiting scroll. The first passage 181 guides the refrigerant out of the compression chamber 16, circulates the refrigerant, and introduces the refrigerant into the second passage 182. The second passage 182 is a passage that passes through the inside of the fixed scroll 11, and is an example of a passage inside the fixed scroll. The second passage 182 circulates the refrigerant introduced from the first passage 181 and introduces the refrigerant into the third passage 183. The third passage 183 is a passage that passes through the inside of the main frame 13 and is an example of a passage in the holding member. The third passage 183 circulates the refrigerant introduced from the second passage 182 and introduces the refrigerant into the rear chamber 172. Thus, the pressure in the back chamber 172 is maintained at a specific intermediate pressure.

FIG. 14 is a top view of the end of the end plate 121 of the orbiting scroll 12 as viewed from above.
An inflow port 181a of the first passage 181 is provided in a region 125a (a region on the right side of the dashed arc) of the upper surface of the end plate 121 which faces the compression chamber 16, and the cylindrical portion 111 of the fixed scroll 11 has The outflow port 181b of the first passage 181 is provided in the contact area 125b (the area on the left side of the dashed arc). When the end plate 121 is viewed from above, the first passage 181 is not visible, but the first passage 181 is also shown by a broken line in the figure. Further, in the drawing, the inflow port 181a of the first passage 181 is provided in a region sandwiched between two outermost adjacent movable-side spiral bodies 122, but is not limited thereto. The position where the inflow port 181a of the first passage 181 is provided may be appropriately determined according to the magnitude of the intermediate pressure to be introduced into the back chamber 172. As a result, the desired intermediate-pressure refrigerant in the compression chamber 16 flows to the first passage 181.

FIG. 15 is a bottom view of the cylindrical portion 111 of the fixed scroll 11 as viewed from below.
An inflow port 182a of the second passage 182 is provided in a region 115a (a region on the right side of the dashed circular arc) of the lower surface of the cylindrical portion 111 which is in contact with the end plate 121 of the orbiting scroll 12, and is in contact with the main frame 13. The outflow port 182b of the second passage 182 is provided in the area 115b (the area on the left side of the broken arc). When the cylindrical portion 111 of the fixed scroll 11 is viewed from below, the second passage 182 is not visible, but the second passage 182 is shown by a broken line in the figure. In the first modification, the inflow port 182a of the second passage 182 is provided at one point on the orbit 181c of the outflow port 181b of the first passage 181 when the movable scroll 12 turns. Accordingly, a specific range of intermediate-pressure refrigerant in the compression chamber 16 facing the inflow port 181a flows from the first passage 181 to the second passage 182.

FIG. 16 is an axial cross-sectional view of the compression unit 10 and the rotating shaft 23 of the second modification of the scroll compressor 2.
The compression unit 10 according to the second modification of the scroll compressor 2 is different from the compression unit 10 according to the first modification of the scroll compressor 2 shown in FIG. 13 in that a portion between the first passage 181 and the second passage 182 is provided. A counterbore 184 is provided.

  The top view of the end of the end plate 121 of the orbiting scroll 12 as viewed from above is the same as that of the first modified example, and therefore the description is omitted.

FIG. 17 is a bottom view of the cylindrical portion 111 of the fixed scroll 11 as viewed from below.
An inflow port 182a of the second passage 182 is provided in a region 115a (a region on the right side of the dashed circular arc) of the lower surface of the cylindrical portion 111 which is in contact with the end plate 121 of the orbiting scroll 12, and is in contact with the main frame 13. The outflow port 182b of the second passage 182 is provided in the area 115b (the area on the left side of the broken arc). When the cylindrical portion 111 of the fixed scroll 11 is viewed from below, the second passage 182 is not visible, but the second passage 182 is shown by a broken line in the figure. Further, in the second modification, the inflow port 182a of the second passage 182 is provided as a seat as an example of a recessed portion that covers the entire orbit 181c of the outflow port 181b of the first passage 181 when the movable scroll 12 is turned. It is provided so as to be connected to the loop portion 184. Thus, the intermediate-pressure refrigerant in the compression chamber 16 facing the inflow port 181a always flows from the first passage 181 to the second passage 182.

  In the second modification, the inflow port 182a of the second passage 182 is connected to the counterbore portion 184 that covers the entire orbit 181c of the outflow port 181b of the first passage 181 when the orbiting scroll 12 is turned. , But not limited to this. The movable scroll 12 may be provided so as to be connected to a counterbore portion 184 that covers a part of the track 181c of the outlet 181b of the first passage 181 when the movable scroll 12 turns. That is, the inflow port 182a of the second passage 182 may communicate with the outflow port 181b of the first passage 181 in at least a part of the cycle in which the orbiting scroll 12 turns.

  In the first modification and the second modification, a first passage 181 that guides the refrigerant from the compression chamber 16 and introduces the refrigerant into the second passage 182 in the fixed scroll 11 is provided in the movable scroll 12. Although it is assumed that the second passage 182 for introducing the refrigerant introduced from the passage 181 into the third passage 183 in the main frame 13 is provided in the fixed scroll 11, the present invention is not limited to this. A configuration in which a passage for guiding the refrigerant from the compression chamber 16 and directly introducing the refrigerant to the third passage 183 in the main frame 13 may be provided in the fixed scroll 11 may be used. Assuming such a configuration, it is not necessary to control the timing of communication between the first passage 181 and the second passage 182 as described in the first and second modifications.

Further, in the first modified example and the second modified example, the gap between the main frame 13 and the sub-frame 14 is determined based on the shapes of the main frame 13 and the sub-frame 14 in FIGS. By sealing with the seal members 172a and 172b, the rear chamber 172 is formed between the main frame 13 and the subframe 14, and the intermediate pressure is guided from the compression chamber 16 to the rear chamber 172, but is not limited thereto. . For example, assuming the shapes of the main frame 13 and the sub-frame 14 in FIG. 11, the gap between the main frame 13 and the sub-frame 14 is sealed with two seal members, so that the main frame 13 and the sub-frame 14 Between the compression chamber 16 and the rear chamber.
Alternatively, assuming the shapes of the main frame 13 and the sub-frame 14 in the first embodiment, the rear chamber 142a in FIGS. 2 to 4 is changed to the rear chamber 172 in FIG. 13 or FIG. The intermediate pressure may be led to 172. Further, the space formed by the rear chamber 142a and the rear chamber 121b in FIG. 5 may be used as the rear chamber 172 in FIG. 13 or FIG. 16, and the intermediate pressure may be guided from the compression chamber 16 to the rear chamber 172.
In this sense, by sealing two places between the main frame 13 and the sub-frame 14 with the sealing members 172a and 172b, a back chamber 172 is formed between the main frame 13 and the sub-frame 14, and compressed. The introduction of the intermediate pressure from the chamber 16 to the rear chamber 172 is wider, and at least a part of the gap between the main frame 13 and the sub-frame 14 is sealed by a seal mechanism, so that at least the main frame 13 and the sub-frame 14 are sealed. Between the compression chamber 16 and the internal space.

Reference numerals 1 and 2: scroll compressor, 11: fixed scroll, 12: movable scroll, 121: end plates, 121a, 121b: rear chamber, 123: cylindrical portion, 123c, 123d: seal member, 13: main frame, 131, 132, 133, 134: cylindrical portion, 134g, 134h: guide member, 135, 136: protrusion, 14: subframe, 141, 142, 143: cylindrical portion, 141c, 141d, 141e, 141f: seal member, 142a: rear chamber, 142c, 142d: seal member, 144: thrust bearing, 15: Oldham ring, 16: compression chamber, 172: rear chamber, 172a, 172b: seal member, 181: first passage, 182: second passage , 183: Third passage, 184: Counterbore

Claims (18)

A fixed scroll fixed in the housing,
A movable scroll that rotates while being engaged with the fixed scroll;
A rotation axis for orbiting the movable scroll,
A holding member for holding the fixed scroll from the opposite side of the movable scroll,
A scroll compressor, comprising: a support member provided between the rotation shaft and the holding member, the support member supporting the movable scroll by a load applied to a position shifted from the center of the movable scroll.   The scroll compressor according to claim 1, wherein the support member is provided so as to be displaceable in one direction with respect to the holding member.   The said support member was displaceable in the direction along the said rotation axis, and was provided so that displacement was possible in the rotation direction centering on the virtual axis substantially orthogonal to the said rotation axis. 2. The scroll compressor according to 1.   4. The scroll compressor according to claim 3, wherein the support member is displaceable in a rotation direction opposite to a moment generated in the movable scroll in a rotation direction around the virtual axis. 5. Machine.   The support member receives the reaction force from the holding member with respect to the load received by the movable scroll at a specific position on the movable scroll side from a position receiving the load from the rotating shaft. The scroll compressor according to claim 4, wherein the scroll compressor is displaceable in a rotation direction opposite to the applied moment.   The specific position is located between an end face of the bearing of the rotating shaft of the support member on the movable scroll side and a face of the base plate of the movable scroll on a side meshed with the fixed scroll. The scroll compressor according to claim 5, wherein   The support member is located at a specific position where the gap between the supporting member and the holding member on the same side as the position receiving the load from the rotating shaft is the narrowest. With respect to the movable scroll, the gap between the movable scroll and the holding member is provided so as to be smaller than the gap at the narrowest position, so that the displacement in the rotation direction opposite to the moment generated in the movable scroll is provided. The scroll compressor according to claim 4, wherein the scroll compressor can be used.   The specific position is located between an end face of the bearing of the rotating shaft of the support member on the movable scroll side and a face of the base plate of the movable scroll on a side meshed with the fixed scroll. The scroll compressor according to claim 7, wherein   The scroll according to claim 4, wherein the support member is displaceable in a rotation direction opposite to a moment generated in the movable scroll by contacting a protrusion provided on the holding member. Compressor.   The portion of the support member that supports the movable scroll has a shape that exhibits elasticity when the support member is tilted and comes into contact with a surface of the base plate of the movable scroll that is not engaged with the fixed scroll. The scroll compressor according to claim 3, wherein: An Oldham ring for preventing rotation of the movable scroll is further provided,
The scroll compressor according to claim 3, wherein the Oldham ring is engaged with the movable scroll and the support member, the movable scroll and the holding member, or the movable scroll and the fixed scroll. .   A sealing mechanism that seals at least a part of a gap between the holding member and the support member to form an internal space between at least the holding member and the support member. The scroll compressor according to claim 1.   The holding member has a passage in the holding member for introducing a refrigerant derived from a compression chamber formed by the movable scroll meshing with the fixed scroll and rotating to form the internal space. The scroll compressor according to claim 12, wherein   The scroll compressor according to claim 13, wherein the fixed scroll includes a fixed scroll inner passage that guides the refrigerant from the compression chamber and introduces the refrigerant into the holding member inner passage. The fixed scroll includes a fixed scroll internal passage that introduces the refrigerant derived from the compression chamber into the holding member internal passage,
14. The scroll compressor according to claim 13, wherein the movable scroll includes a movable scroll inner passage that guides the refrigerant from the compression chamber and introduces the refrigerant into the fixed scroll inner passage.   The scroll compressor according to claim 15, wherein the fixed scroll passage communicates with the movable scroll passage in at least a part of a cycle in which the movable scroll turns.   17. The scroll compressor according to claim 16, wherein the fixed scroll passage has an inlet on an orbit of an outlet of the movable scroll passage when the movable scroll is turned.   17. The scroll according to claim 16, wherein the fixed scroll passage has an inlet connected to a recessed portion that covers the entire orbit of the outlet of the movable scroll passage when the movable scroll turns. Compressor.