Scroll compressor and refrigeration cycle system

Abstract

The present invention provides a scroll compressor and refrigeration cycle device that can improve the positioning accuracy of the thrust plate relative to the oscillating scroll and suppress variations in oil leakage. [Solution] The scroll compressor includes a plate-shaped thrust plate provided between a frame that supports the orbiting scroll in the axial direction of the drive shaft and the orbiting scroll, the thrust plate includes a positioning projection that protrudes outward in the planar direction, the frame has a wall portion that faces the thrust plate in the radial direction of the drive shaft, the wall portion has a positioning recess formed therein that the positioning projection is fitted into to position the thrust plate, the surface of the frame has a rough surface and a smooth surface with a surface roughness less than the rough surface, and the contact surface of the inner surface of the positioning recess that abuts the end face of the positioning projection in the circumferential direction of the drive shaft is made of a smooth surface.

Description

Technical Field

[0001] The present disclosure relates to a scroll compressor provided with a thrust plate and a refrigeration cycle device.

Background Art

[0002] A scroll compressor has an oscillating scroll and a fixed scroll that form a compression chamber, and the oscillating scroll and the fixed scroll are housed in a frame provided with an intake port for sucking refrigerant. The scroll compressor compresses the refrigerant sucked from the intake port in the compression chamber by the oscillating scroll performing an oscillating motion within the frame. The oscillating scroll oscillates while sliding on a thrust bearing surface, and a thrust plate is disposed between the oscillating scroll and the frame in order to improve the sliding property of the oscillating scroll.

[0003] In such a scroll compressor, lubricating oil is supplied to the inside of the compression chamber in order to improve the sliding property between the oscillating scroll and the fixed scroll and the sealing property of the compression chamber (see, for example, Patent Document 1). Patent Document 1 discloses a scroll compressor in which an oil supply hole, which is an oil outflow portion, is provided in the thrust bearing surface of the oscillating scroll and an oil supply hole is provided in the thrust plate. In the scroll compressor of Patent Document 1, the lubricating oil is supplied to the compression chamber from the oil supply hole through the oil supply hole by the oil supply hole intermittently communicating with the oil supply hole.

[0004] Also, in a scroll compressor provided with a thrust plate, a structure is required to prevent the thrust plate from rotating following the oscillating motion of the oscillating scroll. In the scroll compressor of Patent Document 1, the rotation of the thrust plate is prevented by locking of a convex portion and a concave portion to position the thrust plate.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

[0006] Incidentally, if the thrust plate positioning accuracy is poor and there is play in the thrust plate's position, the variation in the communication time between the oil supply hole and the oil injection hole will increase. As a result of this variation in communication time, the amount of oil discharged to the outside along with the refrigerant will also increase. Patent Document 1 does not mention anything about the thrust plate positioning accuracy, and there was room for improvement regarding both the thrust plate positioning accuracy and the variation in the amount of oil discharged.

[0007] This disclosure aims to solve the above problems and to provide a scroll compressor and refrigeration cycle device that can improve the positioning accuracy of the thrust plate relative to the oscillating scroll and suppress variations in the amount of oil rising. [Means for solving the problem]

[0008] The scroll compressor according to this disclosure comprises a fixed scroll, an orbiting scroll that orbits relative to the fixed scroll, a drive shaft that drives the orbiting scroll, a frame that supports the orbiting scroll in the axial direction of the drive shaft, and a plate-shaped thrust plate provided between the frame and the orbiting scroll. The thrust plate includes a positioning projection that protrudes outward in the planar direction, the frame has a wall portion that faces the thrust plate in the radial direction of the drive shaft, and the wall portion has a positioning recess into which the positioning projection is fitted to position the thrust plate, the surface of the frame has a rough surface and a smooth surface with a surface roughness less than the rough surface, and the contact surface of the inner surface of the positioning recess that abuts the end face of the positioning projection in the circumferential direction of the drive shaft is made of the smooth surface.

[0009] The refrigeration cycle device according to this disclosure comprises the scroll compressor, condenser, expansion valve, and evaporator described above. [Effects of the Invention]

[0010] According to the scroll compressor and refrigeration cycle device described herein, the positioning accuracy of the thrust plate relative to the oscillating scroll can be improved, and variations in the amount of oil rising can be suppressed. [Brief explanation of the drawing]

[0011] [Figure 1] This is a longitudinal cross-sectional view showing an example of the cross-sectional configuration of a scroll compressor according to Embodiment 1. [Figure 2] This is a schematic plan view of the frame in the scroll compressor according to Embodiment 1. [Figure 3] This is a plan view showing an example of a thrust plate in a scroll compressor according to Embodiment 1. [Figure 4] This is an enlarged cross-sectional view of the positioning portion of the thrust plate in a scroll compressor according to Embodiment 1. [Figure 5] This is a plan view showing an example of the sliding surface of the oscillating scroll in a scroll compressor according to Embodiment 1. [Figure 6] This is a schematic diagram showing the positional relationship between the oil supply hole and the intermittent supply hole when the oscillating scroll rotates in the scroll compressor according to Embodiment 1. [Figure 7] This is an enlarged schematic diagram of Figure 6 from θ=225° to θ=270°. [Figure 8] This is an enlarged cross-sectional view showing the state in which the lubrication hole is exposed from the oscillating scroll in a scroll compressor according to Embodiment 1. [Figure 9] This is a schematic cross-sectional view of section AA in Figure 4. [Figure 10] This is a schematic cross-sectional view of the scroll compressor according to Embodiment 2, at portion AA in Figure 4. [Figure 11] This is an enlarged cross-sectional view of the positioning portion of the thrust plate in a scroll compressor according to Embodiment 3. [Figure 12] This is a schematic cross-sectional view of section AA in Figure 11. [Figure 13] It is a schematic cross-sectional view at the A-A portion of FIG. 11 in the modification of Embodiment 3. [Figure 14] It is a refrigerant circuit diagram showing a refrigeration cycle apparatus to which a scroll compressor according to Embodiment 4 is applied.

Embodiments for Carrying Out the Invention

[0012] Hereinafter, embodiments will be described based on the drawings. In each figure, those denoted by the same reference numerals are the same or corresponding ones, which is common throughout the entire specification. Furthermore, the forms of the constituent elements shown throughout the entire specification are merely examples and are not limited to these descriptions.

[0013] Embodiment 1. FIG. 1 is a longitudinal sectional view showing a cross-sectional configuration example of a scroll compressor 100 according to Embodiment 1. FIG. 2 is a schematic plan view of a frame 2 in the scroll compressor 100 according to Embodiment 1. The scroll compressor 100 includes a shell 1, a fixed scroll 31, a swing scroll 32, a frame 2, a thrust plate 24, an O-ring 33, a drive shaft 6, and the like. Further, the scroll compressor 100 includes a drive mechanism portion 4 composed of a motor or the like housed in the shell 1. The scroll compressor 100 exemplifies a so-called vertical scroll compressor in which the fixed scroll 31 and the swing scroll 32 are arranged on the upper side and the drive mechanism portion 4 is arranged on the lower side within the shell 1. In the following description, unless otherwise specified, the direction in which the drive shaft 6 extends is referred to as the axial direction, the direction perpendicular to the axial direction is referred to as the radial direction, and the direction around the drive shaft is referred to as the circumferential direction. Also, in the following description, the radially inner side refers to the direction approaching the drive shaft 6 when viewed in the axial direction, and the radially outer side refers to the direction away from the drive shaft 6 when viewed in the axial direction.

[0014] The shell 1 forms a sealed space inside, and has a main shell 11, an upper shell 12 provided on the upper part of the main shell 11, and a lower shell 13 provided on the lower part of the main shell 11. An intake pipe 14 for sucking refrigerant is connected to the main shell 11. A discharge pipe 15 for discharging the compressed refrigerant is connected to the upper shell 12. A frame 2 is fixed to the upper side of the main shell 11, and a sub-frame 5 for holding the main shaft portion 61 is fixed to the lower side of the main shell 11. The inside of the main shell 11 is a low-pressure chamber 11a, and the inside of the upper shell 12 is a high-pressure chamber 12a. The low-pressure chamber 11a and the high-pressure chamber 12a are partitioned by the fixed scroll 31 and the frame 2, and airtightness is maintained. The lower shell 13 is an oil sump for storing lubricating oil.

[0015] The fixed scroll 31 includes a first substrate 311 and a first scroll 312 as a fixed-side scroll body which is a spiral protrusion provided on one surface of the first substrate 311. The first substrate 311 is fixed to the upper side of the frame 2 by bolts or the like, and a discharge hole 313 for discharging the compressed refrigerant at high pressure is formed at the central portion of the first substrate 311. Further, a discharge valve 36 for preventing the refrigerant from flowing back from the high-pressure chamber 12a to the discharge hole 313 side is provided above the discharge hole 313.

[0016] The oscillating scroll 32 includes a second substrate 321 and a second scroll 322 as an oscillating-side scroll body which is a spiral protrusion provided on one surface of the second substrate 321. The second substrate 321 is supported swingably within the frame 2. That is, the other surface of the oscillating scroll 32 acts as a sliding surface 3211 which is a thrust bearing surface that slides on the frame 2 via the plate-like thrust plate 24, and the load generated during operation is supported by the frame 2 via the sliding surface 3211.

[0017] The second spiral body 322 has substantially the same shape as the first spiral body 312 and is combined with the first spiral body 312. The second spiral body 322 and the first spiral body 312 are housed in the frame 2 in their combined state. The oscillating scroll 32 has a hollow cylindrical portion 323 at the center of the sliding surface 3211, which is the other side of the scroll. The eccentric shaft portion 62, which is provided at the upper end of the main shaft portion 61, is inserted into the cylindrical portion 323. The oscillating scroll 32 then performs an oscillating motion as an orbital motion relative to the fixed scroll 31 when the main shaft portion 61 rotates.

[0018] When the fixed scroll 31 and the orbiting scroll 32 are combined, the winding directions of the first spiral body 312 and the second spiral body 322 are opposite to each other. A compression chamber 34 is formed between the second spiral body 322 and the first spiral body 312. In addition, to reduce refrigerant leakage from the tip surfaces of the first spiral body 312 and the second spiral body 322, seals 316 and 325 are provided on the tip surfaces of the first spiral body 312 and the second spiral body 322, respectively.

[0019] Frame 2 houses the orbiting scroll 32 and the stationary scroll 31 and is fixed to the upper part of the shell 1. Frame 2 has a cylindrical wall portion 2a that extends in the axial direction of the drive shaft 6 so as to cover the outer circumference of the orbiting scroll 32. The outer surface of the wall portion 2a of frame 2 is fixedly supported to the shell 1 by shrink fitting or welding. Frame 2 also has a main bearing portion 22 that rotatably supports the upper part of the main shaft portion 61.

[0020] Inside the frame 2, a housing space is formed along the longitudinal direction of the shell 1, and the orbiting scroll 32 is arranged in this housing space. The frame 2 supports the orbiting scroll 32, which is arranged in the housing space, so that it can rotate in the axial direction. Inside the frame 2, there is also an intake chamber 26 that communicates with the compression chamber 34, and an oil reservoir space 25 in which lubricating oil that has flowed out from the oil passage 63 accumulates. The intake chamber 26 is formed by the first spiral body 312 of the fixed scroll 31, the second spiral body 322 of the orbiting scroll 32, and the wall portion 2a of the frame 2. The oil reservoir space 25 is formed by the outer circumference of the cylindrical portion 323 of the orbiting scroll 32 and the lower part of the frame 2.

[0021] Frame 2 has an intake port 211 that guides the refrigerant drawn in from the intake pipe 14 to the compression chamber 34 via the intake chamber 26. The intake port 211 is provided in the wall portion 2a. One end of the intake port 211 opens to the lower end surface of frame 2, and the other end opens to the intake chamber 26. A positioning recess 212 is also formed in the wall portion 2a. The positioning recess 212 is formed by recessing radially outward from the inner surface 2a1 (see Figure 4) of the wall portion 2a. The positioning recess 212 is composed of the intake port 211.

[0022] The thrust plate 24 is provided between the frame 2 and the sliding surface 3211 of the orbiting scroll 32. The thrust plate 24 is annular in shape and has an opening in the center into which a cylindrical portion 323 is inserted (see Figure 3). This opening connects to an oil reservoir space 25 formed below and inside the thrust plate 24. The thrust plate 24 improves the sliding properties of the sliding surface 3211 when the orbiting scroll 32 revolves around the frame 2, and the orbiting scroll 32 is axially supported by the frame 2 via the thrust plate 24. In other words, the thrust plate 24 pivotably supports the lower surface of the orbiting scroll. The thrust plate 24 also has a positioning projection 24b that protrudes toward a positioning recess 212 formed in the wall portion 2a of the frame 2. The positioning projection 24b will be explained in more detail later.

[0023] The Oldham ring 33 is positioned between the orbiting scroll 32 and the frame 2, and transmits the rotational force of the main shaft 61 to the orbiting scroll 32 while restricting the rotational motion of the orbiting scroll 32. The Oldham ring 33 has a first key portion 332, which is a pair of Oldham keys protruding from the side facing the frame 2, and a second key portion 333, which is a pair of Oldham keys protruding from the side facing the orbiting scroll 32. The second key portion 333 is fitted to the orbiting scroll 32 side, and the first key portion 332 is fitted to the frame 2 side.

[0024] Specifically, the sliding surface 3211 of the orbiting scroll 32 is provided with a second Oldham keyway 324 extending radially for inserting the second key portion 333, as shown in Figure 5. A pair of second Oldham keyways 324 are provided symmetrically with respect to a predetermined radius of the orbiting scroll 32. On the frame 2 side, a first Oldham keyway 213 extending radially for inserting the first key portion 332 is formed, as shown in Figure 2. The second Oldham keyway 324 and the first Oldham keyway 213 are formed radially, for example, at positions shifted by 90° in phase.

[0025] Similarly, the second key portion 333 and the first key portion 332 are positioned, for example, with a phase difference of 90°. The second key portion 333 is fitted radially movably into the second Oldham keyway 324, and the first key portion 332 is fitted radially movably into the first Oldham keyway 213. As a result, the second key portion 333 and the first key portion 332 move back and forth within the second Oldham keyway 324 and the first Oldham keyway 213, respectively, transmitting the rotational force of the drive mechanism 4 to the revolving orbiting scroll 32 while restricting the rotational motion of the orbiting scroll 32.

[0026] The drive shaft 6 has a main shaft portion 61 and an eccentric shaft portion 62. Within the shell 1, the upper part of the main shaft portion 61 is rotatably supported by a main bearing portion 22 provided on the frame 2, and the lower part of the main shaft portion 61 is rotatably supported by a sub-bearing portion 51. The sub-bearing portion 51 is press-fitted and fixed into a bearing housing formed in the center of a subframe 5 provided in the lower part of the shell 1. The eccentric shaft portion 62 is attached to the upper end of the main shaft portion 61 in an eccentric state relative to the main shaft portion 61, and the cylindrical portion 323 of the oscillating scroll 32 is provided on the eccentric shaft portion 62 so as to be able to revolve.

[0027] Furthermore, the subframe 5 is equipped with a positive displacement oil pump 52. The oil pump 52 draws lubricating oil stored in the lower shell 13 and sends it to each sliding part through an oil passage 63 formed inside the main shaft 61. The lubricating oil that has passed through the oil passage 63 is supplied to an oil reservoir space 25. The oil reservoir space 25 is connected to the second Oldham keyway 324 of the oscillating scroll 32, and the lubricating oil in the oil reservoir space 25 is supplied to the second Oldham keyway 324.

[0028] Furthermore, the main shaft portion 61 is provided with a first balance weight 64 and a second balance weight 65 to counteract the imbalance caused by the oscillation of the oscillating scroll 32. The first balance weight 64 is fixed to the upper part of the main shaft portion 61 by shrink fitting, and the second balance weight 65 is fixed integrally with the rotor 42 to the lower part of the main shaft portion 61.

[0029] The drive mechanism 4 is composed of, for example, a motor and includes a stator 41 fixed to the shell 1 and a rotor 42 fixed to the main shaft 61. The stator 41 and rotor 42 are located, for example, below the first balance weight 64. The stator 41 is, for example, made of wound coils and is shrink-fitted to the main shell 11. Power is supplied to the stator 41 via a power supply terminal 82 provided on the main shell 11. The rotor 42 is, for example, made of permanent magnets and is shrink-fitted to the main shaft 61. When power is supplied to the stator 41, the rotor 42 and the main shaft 61 rotate.

[0030] Next, the operation of the scroll compressor 100 will be described with reference to Figure 1. When power is supplied to the power supply terminal 82 from an external source, current flows through the coils of the stator 41, generating a magnetic field. This magnetic field acts to rotate the rotor 42, generating torque in the rotor 42, and causing the rotor 42 and the main shaft 61 to rotate. When the main shaft 61 rotates, rotational force is transmitted from the eccentric shaft 62 to the orbiting scroll 32, and the orbiting scroll 32 performs orbital motion while its rotational motion is restricted by the Oldham ring 33. When the rotor 42 rotates, the first balance weight 64 and the second balance weight 65 maintain balance against the eccentric orbital motion of the orbiting scroll 32.

[0031] Meanwhile, the refrigerant flows into the shell 1 via the suction pipe 14. A portion of this refrigerant flows into the compression chamber 34, initiating the compression process. During this process, the orbital motion of the oscillating scroll 32 causes the compression chamber 34 to move towards the center of the oscillating scroll 32, reducing its volume, and the refrigerant gas drawn into the compression chamber 34 is compressed. The compressed refrigerant passes through the discharge hole 313 of the fixed scroll 31, pushing open the discharge valve 36 and flowing into the high-pressure chamber 12a. The refrigerant that has flowed into the high-pressure chamber 12a is discharged from the shell 1 via the discharge pipe 15. The remaining portion of the refrigerant cools the drive mechanism 4 and the lubricating oil by passing through a notch (not shown) in the steel plate of the stator 41.

[0032] During the operation of the scroll compressor 100, the frame 2 is subjected to a load on the sliding surface 3211 of the oscillating scroll 32, which is generated by the pressure of the refrigerant gas in the compression chamber 34. In addition, the centrifugal force generated on the first balance weight 64 and the second balance weight 65, as well as the load from the refrigerant, are supported by the main bearing section 22 and the sub-bearing section 51.

[0033] Furthermore, when the scroll compressor 100 is operating, lubricating oil is supplied to the sliding parts where the components slide against each other. Specifically, the lubricating oil stored in the lower shell 13 is supplied by the oil pump 52 through the oil passage 63 from the lower to the upper side of the main shaft 61, and is supplied from the upper end of the main shaft 61 between the main shaft 61 and the cylindrical portion 323 of the orbiting scroll 32. The lubricating oil then flows into the oil reservoir space 25 located on the outer circumference of the cylindrical portion 323, while lubricating the sliding portion between the main shaft 61 and the cylindrical portion 323 of the orbiting scroll 32. Some of the lubricating oil in the oil reservoir space 25 is supplied to the second Oldham keyway 324. The remaining portion of the lubricating oil passes through an oil drain hole (not shown) and is discharged to the outside of the frame 2 and returned to the lower shell 13.

[0034] The lubricating oil that flows into the compression chamber 34 mixes with the refrigerant in the compression chamber 34. The lubricating oil mixed with the refrigerant in the compression chamber 34 then adheres to the sliding parts of the first spiral body 312 and the second spiral body 322, improving the airtightness of the compression chamber 34 and suppressing wear.

[0035] In this manner, lubricating oil flows into the compression chamber 34 via the thrust plate 24 and the orbiting scroll 32 to lubricate the lubrication points of the fixed scroll 31 and the orbiting scroll 32. If the amount of lubricating oil supplied into the compression chamber 34 is insufficient, malfunctions such as wear will occur, and if the amount of lubricating oil supplied is excessive, it will lead to a decrease in the performance of the scroll compressor 100. Therefore, the scroll compressor 100 has a structure that supplies an appropriate amount of lubricating oil to the compression chamber 34.

[0036] Figure 3 is a plan view showing an example of a thrust plate 24 in a scroll compressor 100 according to Embodiment 1. Figure 4 is an enlarged cross-sectional view of the positioning portion of the thrust plate 24 in the scroll compressor 100 according to Embodiment 1. As shown in Figure 3, the thrust plate 24 includes a positioning projection 24b that protrudes outward in the planar direction. The positioning projection 24b is composed of a pair of projections 24b1 spaced apart in the circumferential direction. The positioning projection 24b is fitted into a positioning recess 212 provided in the wall portion 2a of the frame 2, thereby preventing the rotation of the thrust plate 24 due to the oscillating motion of the oscillating scroll 32 and positioning the thrust plate 24 in the circumferential direction. Note that the positioning projection 24b is not limited to being composed of a pair of projections 24b1, but may be composed of a single projection in which the pair of projections are connected in the circumferential direction without being spaced apart in the circumferential direction.

[0037] As described above, the positioning recess 212 is formed by recessing radially outward from the inner surface 2a1 of the wall portion 2a, and the inner surface of the positioning recess 212 has a contact surface 20 that abuts against the end surface 24b2 of the circumferential positioning projection 24b. The contact surface 20 includes a pair of opposing surfaces 20a that face each other in the circumferential direction on the inner surface of the positioning recess 212. The thrust plate 24 is positioned in the circumferential direction by the end surface 24b2 of the positioning projection 24b abutting against the contact surface 20.

[0038] Furthermore, the thrust plate 24 has an oil supply hole 24a. The oil supply hole 24a is connected to the compression chamber 34 (see Figure 1). The oil supply hole 24a is formed near one of the pair of second Oldham keyways 324. Therefore, when the orbiting scroll 32 revolves, the second Oldham keyway 324 communicates with the oil supply hole 24a, and lubricating oil accumulated in the second Oldham keyway 324 is supplied to the oil supply hole 24a. The oil supply hole 24a is provided on the outer circumference of the thrust plate 24 and is exposed from the orbiting scroll 32 for a predetermined rotation period when the orbiting scroll 32 revolves. During this exposure period, lubricating oil is supplied from the oil supply hole 24a to the compression chamber 34. The position of the oil supply hole 24a can be set as needed.

[0039] Figure 5 is a plan view showing an example of the sliding surface 3211 of the orbiting scroll 32 in the scroll compressor 100 according to Embodiment 1. The arrow in Figure 5 indicates the rotation direction R of the orbiting scroll 32. As shown in Figure 5, the orbiting scroll 32 has an intermittent supply hole 90 formed recessed upward from the sliding surface 3211. The intermittent supply hole 90 is the part into which lubricating oil flows and communicates with one of a pair of second Oldham keyways 324 on the orbiting scroll 32 side. When the orbiting scroll 32 revolves and the intermittent supply hole 90 communicates with the oil supply hole 24a, the intermittent supply hole 90 supplies lubricating oil accumulated in the second Oldham keyway 324 to the oil supply hole 24a.

[0040] Figure 6 is a schematic diagram showing the positional relationship between the oil supply hole 24a and the intermittent supply hole 90 when the orbiting scroll 32 rotates in the scroll compressor 100 according to Embodiment 1. Figure 7 is an enlarged schematic diagram of Figure 6 from θ=225° to θ=270°. In Figure 7, the white arrows indicate the direction of movement of the orbiting scroll 32. Figure 8 is an enlarged cross-sectional view showing the state in which the oil supply hole 24a is exposed from the orbiting scroll 32 in the scroll compressor 100 according to Embodiment 1. Note that in Figure 6, a predetermined rotational position of the orbiting scroll 32 is represented by the rotation period θ, and the diagram shows the state in which the orbiting scroll 32 rotates by 45° increments during one rotation from θ 0° to 360°.

[0041] During the rotation period θ = approximately 0° to 90°, the oil supply hole 24a is exposed from the outer circumference of the oscillating scroll 32 and is connected to the compression chamber 34. Therefore, if lubricating oil is accumulated in the oil supply hole 24a, the lubricating oil accumulated in the oil supply hole 24a is supplied to the compression chamber 34.

[0042] During the rotation period θ = approximately 90° to 225°, the oil supply hole 24a is blocked by the outer circumference of the oscillating scroll 32, and the supply of lubricating oil from the oil supply hole 24a to the compression chamber 34 is stopped.

[0043] During the rotation period θ = approximately 225° to 315°, the lubrication hole 24a is exposed from the outer circumference of the oscillating scroll 32, and the lubricating oil accumulated in the second Oldham keyway 324 is supplied to the lubrication hole 24a via the intermittent supply hole 90.

[0044] The operation during the rotation period θ = approximately 225° to 270° will be described below with reference to Figure 7. In Figure 7, A is the area of ​​the communication portion between the lubrication hole 24a and the intermittent supply hole 90 when viewed in the axial direction. B is the area of ​​the exposed portion of the lubrication hole 24a from the oscillating scroll 32 when viewed in the axial direction.

[0045] In Figure 7(a), the lubrication hole 24a is in communication with the intermittent supply hole 90. Furthermore, the lubrication hole 24a is located radially inward from the outer peripheral edge 321a of the orbiting scroll 32, and the lubrication hole 24a is blocked by the outer peripheral portion of the orbiting scroll 32. That is, A>0 and B=0. In this state, the lubricating oil accumulated in the second Oldham keyway 324 is supplied to the lubrication hole 24a via the intermittent supply hole 90. The dotted line along the inner surface 2a1 of the wall portion 2a indicates the outer peripheral edge 241 of the thrust plate 24.

[0046] In Figure 7(b), as the orbiting scroll 32 moves in the direction of the white arrow from the state in Figure 7(a), the area A decreases, and the outer edge 321a of the orbiting scroll 32 comes into contact with the edge 24a1 of the lubrication hole 24a when viewed in the axial direction. In other words, as in Figure 7(a), A>0 and B=0. In this state, as in Figure 7(a), the lubricating oil accumulated in the second Oldham keyway 324 is supplied to the lubrication hole 24a via the intermittent supply hole 90.

[0047] In Figure 7(c), the orbiting scroll 32 moves further in the direction of the white arrow from the state in Figure 7(b), causing the area A to shrink further, while a portion of the oil supply hole 24a is located outside the outer peripheral edge 321a of the orbiting scroll 32, exposing the oil supply hole 24a from the orbiting scroll 32. In other words, A>0 and B>0. In this state, as shown in Figure 8, the intermittent supply hole 90 communicates with the intake chamber 26 via the oil supply hole 24a. Therefore, as shown by the arrow 70 in Figures 7(c) and 8, the lubricating oil accumulated in the second Oldham keyway 324 is supplied to the oil supply hole 24a via the intermittent supply hole 90, and the lubricating oil supplied to the oil supply hole 24a is supplied to the intake chamber 26. The lubricating oil supplied to the intake chamber 26 is supplied to the compression chamber 34.

[0048] Thus, when the oil supply hole 24a and the intermittent supply hole 90 are in communication and the oil supply hole 24a is exposed from the oscillating scroll 32, the following lubricating oil flow is formed in the scroll compressor 100. That is, in the scroll compressor 100, the lubricating oil accumulated in the second Oldham keyway 324 is supplied to the oil supply hole 24a via the intermittent supply hole 90, and the lubricating oil supplied to the oil supply hole 24a is supplied to the compression chamber 34 via the intake chamber 26, forming a flow.

[0049] In Figure 7(d), the oscillating scroll 32 moves further in the direction of the white arrow from the state in Figure 7(c), so that the edge 90a of the intermittent supply hole 90 comes into contact with the edge 24a1 of the oil supply hole 24a when viewed in the axial direction. As a result, area A becomes 0, while area B expands. That is, A=0 and B>0. In this state, the supply of lubricating oil from the intermittent supply hole 90 to the oil supply hole 24a is stopped.

[0050] As described above, as shown in Figure 7(b), the supply of lubricating oil to the compression chamber 34 begins at the first timing when the intermittent supply hole 90 and the oil supply hole 24a are in communication and the outer peripheral edge 321a of the oscillating scroll 32 contacts the edge 24a1 of the oil supply hole 24a when viewed in the axial direction. Then, as shown in Figure 7(d), the supply of lubricating oil to the compression chamber 34 ends at the second timing when the communication between the intermittent supply hole 90 and the oil supply hole 24a ends. The communication time, which is the time from the first timing to the second timing, occurs once during one rotation of the drive shaft 6, so while the drive shaft 6 is rotating, lubrication to the compression chamber 34 is performed intermittently using the intermittent supply hole 90.

[0051] Figure 9 is a schematic cross-sectional view of section AA in Figure 4. The contact surface 20 of the positioning recess 212 is a machined surface whose surface roughness has been reduced by machining. In Embodiment 1, both of the pair of opposing surfaces 20a of the contact surface 20 are machined surfaces. The frame 2 is made of casting, and the surface of the frame 2 is the cast surface and is rough. However, the contact surface 20 of the surface of the frame 2 is the machined surface described above, and is a smooth surface Ss with a lower surface roughness than the cast surface. The surface roughness of the machined surface is, for example, Rzjis 6.3 to Rzjis 25, and the surface roughness of the cast surface is, for example, Rzjis 50 to Rzjis 100.

[0052] The contact surface 20 is the surface that the positioning projection 24b contacts to position the thrust plate 24. If this contact surface 20 is rough, play will occur in the positioning projection 24b, reducing the positioning accuracy of the thrust plate 24. When the positioning accuracy of the thrust plate 24 decreases, variations occur in the positional relationship between the intermittent supply holes 90 of the oscillating scroll 32 and the oil supply holes 24a of the thrust plate 24, and these variations cause variations in the communication time. In other words, if the contact surface 20 is rough, variations occur in the communication time, and as a result, variations occur in the amount of oil discharged to the outside of the scroll compressor 100 along with the refrigerant. The variation in the amount of oil discharge increases as the variations in the positioning of the thrust plate 24 and the variations in the communication time increase.

[0053] The scroll compressor 100 has a smooth contact surface 20 Ss. Therefore, the scroll compressor 100 can improve the positioning accuracy of the thrust plate 24 compared to the case where the contact surface 20 is made of a rough surface. By improving the positioning accuracy of the thrust plate 24, the scroll compressor 100 can suppress variations in communication time and oil leakage amount.

[0054] As described above, the scroll compressor 100 of Embodiment 1 comprises a fixed scroll 31, an orbiting scroll 32 that orbits relative to the fixed scroll 31, and a drive shaft 6 that drives the orbiting scroll 32. The scroll compressor 100 comprises a frame 2 that supports the orbiting scroll 32 in the axial direction of the drive shaft 6, and a plate-shaped thrust plate 24 provided between the frame 2 and the orbiting scroll 32. The thrust plate 24 includes a positioning projection 24b that protrudes outward in the planar direction. The frame 2 has a wall portion 2a that faces the thrust plate 24 in the radial direction of the drive shaft 6, and a positioning recess 212 is formed in the wall portion 2a, into which the positioning projection 24b is fitted to position the thrust plate 24. The surface of the frame 2 has a rough surface and a smooth surface with a surface roughness less than that of the rough surface. Of the inner surface 2a1 of the positioning recess 212, the contact surface 20 that abuts against the end face 24b2 of the circumferential positioning projection 24b of the drive shaft 6 is made of a smooth surface Ss.

[0055] With the above configuration, the scroll compressor 100 can improve the positioning accuracy of the thrust plate 24 compared to the case where the contact surface 20 is made of a rough surface. By improving the positioning accuracy of the thrust plate 24, the scroll compressor 100 can suppress variations in communication time and oil leakage amount.

[0056] Furthermore, the scroll compressor 100 improves the positional accuracy of the thrust plate 24, thereby reducing play in the thrust plate 24 and suppressing displacement of the thrust plate 24 during operation. By suppressing displacement of the thrust plate 24, the scroll compressor 100 can reduce sliding loss between the thrust plate 24 and the frame 2 and improve the reliability of the thrust plate. Regarding the concern about increased processing costs in this configuration, this can be mitigated by minimizing the processing steps and processed surfaces.

[0057] Frame 2 is made of casting, with the rough surface of Frame 2 being the cast surface and the smooth surface being the machined surface.

[0058] With the above configuration, the scroll compressor 100 does not require any processing on parts of the frame 2 other than the machined surface, and can have the cast surface as it was formed during casting.

[0059] Frame 2 has an intake port 211 that guides refrigerant into a compression chamber 34 composed of a fixed scroll 31 and an orbiting scroll 32, and the positioning recess 212 is formed by the intake port 211.

[0060] With the above configuration, the scroll compressor 100 can maintain the strength of the frame 2 and reduce processing costs compared to a case where the positioning recess 212 is configured on the frame 2 separately from the intake port 211.

[0061] Embodiment 2. Embodiment 2 differs from Embodiment 1 in the inner surface of the positioning recess 212. Other configurations are the same as or equivalent to those of Embodiment 1. The following description will focus on the configurations in Embodiment 2 that differ from those of Embodiment 1, and configurations not described in Embodiment 2 are the same as those in Embodiment 1.

[0062] Figure 10 is a schematic cross-sectional view of the scroll compressor 100 according to Embodiment 2, at portion AA in Figure 4. In the scroll compressor 100 of Embodiment 2, the area 21 of the contact surface 20 on the inner surface of the positioning recess 212, corresponding to the axial thickness of the positioning protrusion 24b, is made of a smooth surface Ss. The remaining area of ​​the contact surface 20 on the inner surface of the positioning recess 212 is made of a rough surface Sr.

[0063] The scroll compressor 100 of Embodiment 2 provides the same effects as Embodiment 1, as well as the following effects. In the scroll compressor 100 of Embodiment 2, a region 21 of the contact surface 20 corresponding to the axial thickness of the positioning projection 24b is composed of a smooth surface Ss, so only region 21 needs to be machined. For this reason, the scroll compressor 100 of Embodiment 2 can reduce machining time and thus reduce machining costs compared to the case where the entire contact surface 20 is machined.

[0064] Embodiment 3. Embodiment 3 differs from Embodiments 1 and 2 in the inner surface of the positioning recess 212. Other configurations are the same as or equivalent to those of Embodiments 1 and 2. The following description will focus on the configurations that differentiate Embodiment 3 from Embodiments 1 and 2, while configurations not described in Embodiment 3 are the same as those in Embodiments 1 and 2.

[0065] Figure 11 is an enlarged cross-sectional view of the positioning portion of the thrust plate 24 in the scroll compressor 100 according to Embodiment 3. Figure 12 is a schematic cross-sectional view of portion AA in Figure 11. Figure 13 is a schematic cross-sectional view of portion AA in Figure 11 in a modified example of Embodiment 3.

[0066] In the scroll compressor 100 of Embodiment 3, as shown in Figures 11 and 12, of the pair of opposing surfaces 20a constituting the contact surface 20, the opposing surface 20a1 on the forward side in the rotational direction R of the orbiting scroll 32 is made of a smooth surface Ss. The opposing surface 20a2 on the rear side in the rotational direction R of the orbiting scroll 32 is made of a rough surface Sr. In addition, in the scroll compressor 100 of Embodiment 3, as shown in Figure 13, only the region 21 corresponding to the axial thickness of the positioning projection 24b of the opposing surface 20a1 on the forward side in the rotational direction of the orbiting scroll 32 may be made of a smooth surface Ss.

[0067] The scroll compressor 100 of Embodiment 3 provides the same effects as Embodiments 1 and 2, as well as the following effects. In Embodiment 3, since only the opposing surface 20a1 is composed of a smooth surface Ss, it is possible to reduce processing time and thus reduce processing costs compared to the case where both of the pair of opposing surfaces 20a1 and 20a2 are smooth surfaces Ss. Furthermore, in Embodiment 3, since only the region 21 corresponding to the axial thickness of the positioning projection 24b of the opposing surface 20a1 is composed of a smooth surface, it is possible to further reduce processing time and thus reduce processing costs.

[0068] Embodiment 4. [Refrigeration cycle device 101] Figure 14 is a refrigerant circuit diagram showing a refrigeration cycle device 101 to which the scroll compressor 100 according to Embodiment 4 is applied. As shown in Figure 14, the refrigeration cycle device 101 comprises a scroll compressor 100, a condenser 102, an expansion valve 103, and an evaporator 104. These scroll compressor 100, condenser 102, expansion valve 103, and evaporator 104 are connected by refrigerant piping to form a refrigeration cycle circuit. The refrigerant flowing out from the evaporator 104 is drawn into the scroll compressor 100 and becomes high temperature and high pressure. The high temperature and high pressure refrigerant is condensed into a liquid in the condenser 102. The liquid refrigerant is then depressurized and expanded in the expansion valve 103 to become a low temperature, low pressure gas-liquid two-phase refrigerant, and heat exchange takes place between the gas-liquid two-phase refrigerant in the evaporator 104.

[0069] The scroll compressors 100 of Embodiments 1 to 3 can be applied to such refrigeration cycle devices 101. Examples of refrigeration cycle devices 101 include air conditioners, refrigeration systems, or water heaters.

[0070] The various aspects of this disclosure are summarized below as an appendix. (Note 1) Fixed scrolling and, A swinging scroll that swings relative to the fixed scroll, A drive shaft that drives the aforementioned oscillating scroll, A frame that supports the oscillating scroll in the axial direction of the drive shaft, A plate-shaped thrust plate is provided between the frame and the oscillating scroll, Equipped with, The thrust plate includes a positioning projection that protrudes outward in the planar direction, The frame has a wall portion facing the thrust plate in the radial direction of the drive shaft, and the wall portion has a positioning recess formed therein, into which the positioning projection is fitted to position the thrust plate. The surface of the frame has a rough surface and a smooth surface with a surface roughness less than that of the rough surface. A scroll compressor in which the contact surface of the inner surface of the positioning recess that abuts the end face of the positioning protrusion in the circumferential direction of the drive shaft is configured as the smooth surface. (Note 2) The scroll compressor according to Appendix 1, wherein the region of the contact surface that corresponds to the axial thickness of the positioning projection is configured as the smooth surface. (Note 3) The contact surface includes a pair of opposing surfaces that face each other in the circumferential direction, The scroll compressor according to Appendix 1 or Appendix 2, wherein the opposing surface on the forward side in the rotational direction of the oscillating scroll, of the pair of opposing surfaces, is configured as the smooth surface. (Note 4) The aforementioned frame is made of cast metal. A scroll compressor according to any one of the appendices 1 to 3, wherein the rough surface of the frame is a cast surface and the smooth surface is a machined surface. (Note 5) The frame has an intake port for guiding a refrigerant into a compression chamber composed of the fixed scroll and the oscillating scroll. The scroll compressor according to any one of the appendices 1 to 4, wherein the positioning recess is formed by the intake port. (Note 6) A refrigeration cycle system comprising a scroll compressor, a condenser, an expansion valve, and an evaporator, as described in any one of the appendices 1 to 5. [Explanation of Symbols]

[0071] 1 Shell, 2 Frame, 2a Wall section, 2a1 Inner surface, 4 Drive mechanism section, 5 Subframe, 6 Drive shaft, 11 Main shell, 11a Low-pressure chamber, 12 Upper shell, 12a High-pressure chamber, 13 Lower shell, 14 Intake pipe, 15 Discharge pipe, 20 Contact surface, 20a Opposing surface, 20a1 Opposing surface, 20a2 Opposing surface, 21 Area, 22 Main bearing section, 24 Thrust plate, 24a Oil supply hole, 24a1 Edge, 24b Positioning protrusion, 24b1 Protrusion, 24b2 End face, 25 Oil reservoir space, 26 Intake chamber, 31 Fixed scroll, 32 Oscillating scroll, 33 Oldham ring, 34 Compression chamber, 36 Discharge valve, 38 Discharge hole, 41 Stator, 42 Rotor, 51 Sub-bearing section, 52 Oil pump, 61 main shaft section, 62 eccentric shaft section, 63 oil passage, 64 first balance weight, 65 second balance weight, 70 arrow, 82 power supply terminal, 90 intermittent supply hole, 90a edge, 100 scroll compressor, 101 refrigeration cycle device, 102 condenser, 103 expansion valve, 104 evaporator, 211 intake port, 212 positioning recess, 213 first Oldham keyway, 241 outer edge, 311 first substrate, 312 first spiral body, 313 discharge hole, 316 seal, 321 second substrate, 321a outer edge, 322 second spiral body, 323 cylindrical section, 324 second Oldham keyway, 325 seal, 332 first key section, 333 second key section, 3211 sliding surface, A Area of ​​the communication portion between the lubrication hole and the intermittent supply hole when viewed in the axial direction, B Area of ​​the exposed portion of the lubrication hole from the oscillating scroll when viewed in the axial direction, R Rotation direction, Sr Rough surface, Ss Smooth surface.

Claims

1. Fixed scrolling and, A swinging scroll that swings relative to the fixed scroll, A drive shaft that drives the aforementioned oscillating scroll, A frame that supports the oscillating scroll in the axial direction of the drive shaft, A plate-shaped thrust plate is provided between the frame and the oscillating scroll, Equipped with, The thrust plate includes a positioning projection that protrudes outward in the planar direction, The frame has a wall portion facing the thrust plate in the radial direction of the drive shaft, and the wall portion has a positioning recess formed therein, into which the positioning projection is fitted to position the thrust plate. The surface of the frame has a rough surface and a smooth surface with a surface roughness less than that of the rough surface. A scroll compressor in which the contact surface of the inner surface of the positioning recess that abuts the end face of the positioning protrusion in the circumferential direction of the drive shaft is configured as the smooth surface.

2. The scroll compressor according to claim 1, wherein the region of the contact surface that corresponds to the axial thickness of the positioning projection is configured as the smooth surface.

3. The contact surface includes a pair of opposing surfaces that face each other in the circumferential direction, The scroll compressor according to claim 1 or claim 2, wherein of the pair of opposing surfaces, the opposing surface on the side facing the rotational direction of the oscillating scroll is configured as the smooth surface.

4. The aforementioned frame is made of cast metal. The scroll compressor according to claim 1 or claim 2, wherein the rough surface of the frame is a cast surface and the smooth surface is a machined surface.

5. The frame has an intake port for guiding a refrigerant into a compression chamber composed of the fixed scroll and the oscillating scroll. The scroll compressor according to claim 1 or 2, wherein the positioning recess is configured by the intake port.

6. A refrigeration cycle apparatus comprising a scroll compressor according to claim 1 or claim 2, a condenser, an expansion valve, and an evaporator.

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