Scroll compressor and refrigeration cycle device

Abstract

This scroll compressor comprises a fixed scroll in which a fixed spiral body and a fixed cylindrical portion disposed on the outer peripheral side of the fixed spiral body are provided on one surface of a fixed base plate, and an orbiting scroll that performs an orbital motion and that is provided with an orbiting spiral body on one surface of an orbiting base plate, wherein an inner peripheral surface of the fixed cylindrical portion and the fixed spiral body on an inner peripheral surface thereof form a continuous spiral shape and mesh with the orbiting spiral body, and when the orbiting scroll performs the orbital motion, a tip end surface of the fixed spiral body and a tip end surface of the fixed cylindrical portion slide over one surface of the orbiting base plate with a lubricant interposed therebetween, and wherein: an annular oil supply channel is formed in the tip end surface of the fixed cylindrical portion; the radial thickness of a cylindrical portion inner wall portion constituting the inner peripheral side of the fixed cylindrical portion, with an inner peripheral end of the oil supply channel as a boundary, is greater than the radial thickness of the fixed spiral body; and the orbiting base plate and the oil supply channel of the fixed cylindrical portion are arranged such that an outer contour of a movable range of the orbiting base plate due to the orbital motion of the orbiting scroll is positioned further toward the outer peripheral side of the oil supply channel than the inner peripheral edge of the oil supply channel, and the outer peripheral edge of the orbiting base plate is positioned further toward the inner peripheral side of the oil supply channel than the outer peripheral edge of the oil supply channel during the orbital motion of the orbiting scroll.

Description

Scroll compressor and refrigeration cycle device

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

[0002] In general, a scroll compressor compresses a refrigerant by orbiting (revolving) the oscillating scroll relative to the fixed scroll without rotating on its axis, thereby changing the volume of a compression chamber formed between a fixed scroll mounted on a fixed base plate and an oscillating scroll mounted on a oscillating base plate. Among such scroll compressors, a type in which the fixed scroll includes a cylindrical fixed cylinder portion on the outer periphery of the fixed scroll is known (see, for example, Patent Document 1). In the scroll compressor of Patent Document 1, the fixed wall portion is a cylindrical wall portion formed on the outer periphery of the end plate (fixed base plate) of the fixed scroll and extending downward. In the scroll compressor of Patent Document 1, the inner circumferential surface of the fixed cylinder portion is a spirally curved surface that smoothly connects with the inner surface of the wrap terminal end of the fixed scroll (wrap) to form a part of the compression chamber.

[0003] Japanese Patent Application Publication No. 8-232863

[0004] However, in the scroll compressor disclosed in Patent Document 1, the radial thickness of the fixed cylindrical portion is greater than the radial thickness of the fixed scroll, and the tip surface of the fixed cylindrical portion that slides against the oscillating base plate is flat, so the outer peripheral portion of the portion of the oscillating base plate that slides against the tip surface of the fixed cylindrical portion is not exposed to the compression chamber during the orbital movement of the oscillating scroll.As a result, the outer peripheral portion of the portion of the oscillating base plate that slides against the tip surface of the fixed cylindrical portion is prone to seizure due to a lack of lubricating oil during the orbital movement of the oscillating scroll.

[0005] The present disclosure has been made against the background of the above-mentioned problems, and provides a scroll compressor and a refrigeration cycle device that can suppress seizure in the outer peripheral portion by ensuring the contact area between the oscillating base plate and the fixed scroll to suppress an increase in sliding surface pressure, while also supplying lubricating oil to the outer peripheral portion of the part of the oscillating base plate that slides against the tip surface of the fixed cylindrical portion.

[0006] The scroll compressor according to the present disclosure includes a fixed scroll having a fixed scroll body and a fixed cylindrical portion disposed on the outer periphery of the fixed scroll body on one surface of a fixed base plate, and an orbiting scroll having an orbiting scroll body on one surface of an orbiting base plate, wherein the inner peripheral portion of the fixed cylindrical portion and the inner peripheral surface of the fixed scroll body form a continuous spiral shape and mesh with the orbiting scroll body, and when the orbiting scroll revolves, the tip end surface of the fixed scroll body and the tip end surface of the fixed cylindrical portion slide against the one surface of the orbiting base plate via lubricating oil, An annular oil supply groove is formed on the tip surface of the fixed cylindrical portion, and the radial thickness of the cylindrical inner wall portion that forms the inner side of the fixed cylindrical portion, with the inner end of the oil supply groove as the boundary, is configured to be thicker than the radial thickness of the fixed scroll, and the oscillating base plate and the oil supply groove of the fixed cylindrical portion are arranged so that the outer contour of the movable range of the oscillating base plate due to the orbital motion of the oscillating scroll is located outer than the inner end of the oil supply groove, and there are times during the orbital motion of the oscillating scroll when the outer end of the oscillating base plate is located inner than the outer end of the oil supply groove.

[0007] A refrigeration cycle device according to the present disclosure includes the scroll compressor according to the present disclosure, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger.

[0008] According to the present disclosure, an annular oil feed groove is formed in the tip surface of the fixed cylindrical portion, and the radial thickness of the cylindrical inner wall portion that forms the inner side of the fixed cylindrical portion, with the inner circumferential end of the oil feed groove as a boundary, is configured to be thicker than the radial thickness of the fixed scroll body, so that a certain level of contact area between the oscillating base plate and the fixed scroll can be ensured and an increase in sliding surface pressure can be suppressed, as in the conventional art. Also, an annular oil feed groove is formed in the tip surface of the fixed cylindrical portion, and the oil feed grooves of the oscillating base plate and the fixed cylindrical portion are arranged so that the outer contour of the range of movement of the oscillating base plate due to the orbital motion of the oscillating scroll is located outer circumferentially beyond the inner circumferential end of the oil feed groove, and the outer circumferential end of the oscillating base plate is sometimes located inner circumferentially beyond the outer circumferential end of the oil feed groove during the orbital motion of the oscillating scroll. Therefore, the outer circumferential side of the part of the oscillating base plate that slides against the tip surface of the fixed cylindrical portion is exposed to the oil feed groove, allowing lubricating oil to be supplied, and the oil feed groove can be opened to refill the oil feed groove. Therefore, lubricating oil can be supplied to the outer peripheral portion while suppressing an increase in the sliding surface pressure between the oscillating base plate and the fixed scroll, thereby suppressing seizure in the outer peripheral portion.

[0009] 12. A longitudinal sectional view showing a scroll compressor according to embodiment 1. A cross sectional view showing a first passage provided on the outer periphery of the guide frame of FIG. 1. A longitudinal sectional view showing a rotor of the electric motor of FIG. 1. A cross sectional view showing the rotor of the electric motor of FIG. 1. A cross sectional view showing the stator of the electric motor of FIG. 1. A refrigerant circuit diagram showing a refrigeration cycle device according to embodiment 1. A longitudinal sectional view showing a fixed scroll and an orbiting scroll according to embodiment 1. A longitudinal sectional view of the fixed scroll and the orbiting scroll, showing a state in which the orbiting scroll is positioned in a facing direction relative to FIG. 7. A view from below of the fixed scroll according to embodiment 1. A plan view showing the orbiting scroll according to embodiment 1. A view from below of the fixed scroll of a comparative example. A longitudinal sectional view of the fixed scroll and the orbiting scroll of a comparative example. A longitudinal sectional view of the fixed scroll and the orbiting scroll of a comparative example, showing a state in which the orbiting scroll is positioned in a facing direction relative to FIG. 12. A longitudinal sectional view of the fixed scroll and the orbiting scroll, showing a modification of the fixed scroll of FIG. 8. A view from below of the fixed scroll according to embodiment 2. A view from below of the fixed scroll according to embodiment 3. A view from below of the fixed scroll according to embodiment 4.

[0010] An embodiment of a scroll compressor according to the present disclosure will be described below with reference to the drawings. While the scroll compressor described here is an example of a vertically-mounted type, the present disclosure can also be applied to horizontally-mounted scroll compressors. In the following description, directional terms (e.g., "upper," "lower," "right," "left," "front," "rear," etc.) are used as appropriate to facilitate understanding. However, these terms are for explanatory purposes and do not limit the present disclosure. In the drawings, identical reference numerals denote identical or equivalent components, and this applies throughout the entire specification. The following drawings, including FIG. 1, are schematic representations, and the relative dimensional relationships or shapes of the components may differ from actual ones.

[0011] Embodiment 1. Fig. 1 is a vertical cross-sectional view showing a scroll compressor 100 according to Embodiment 1. The configuration and operation of the vertical scroll compressor 100 will be described with reference to Fig. 1. The scroll compressor 100 draws in refrigerant circulating through a refrigeration cycle, compresses it, and discharges it in a high-temperature, high-pressure state. The scroll compressor 100 is one of the components of refrigeration cycles used in various industrial machines, such as refrigerators, freezers, air conditioners, refrigeration systems, and water heaters.

[0012] 1, this scroll compressor 100 is provided with a compression mechanism 14 in a sealed container 10, which combines a fixed scroll 1 and an orbiting scroll 2 that revolves (orbits) relative to the fixed scroll 1. The scroll compressor 100 also is provided with an electric motor 5 in the sealed container 10, which connects the orbiting scroll 2 to a main shaft 6 and drives the orbiting scroll 2. In the case of a vertically mounted scroll compressor 100, for example, the compression mechanism 14 is arranged on the upper side and the electric motor 5 is arranged on the lower side within the sealed container 10.

[0013] The fixed scroll 1 has a fixed base plate 1a, a fixed spiral body 1b which is a spiral protrusion provided on one surface (the lower surface in FIG. 1; the lower surface 1fb in FIG. 7 described later) of the fixed base plate 1a, and a fixed cylindrical portion 50 which is provided on the outer periphery of one surface (the lower surface) of the fixed base plate 1a and is arranged on the outer periphery side of the fixed spiral body 1b. The orbiting scroll 2 has a oscillating base plate 2a and an oscillating spiral body 2b which is a spiral protrusion which is provided on one surface (the upper surface in FIG. 1) of the oscillating base plate 2a and has substantially the same shape as the fixed spiral body 1b.

[0014] A compression chamber 1f, the volume of which changes relatively, is formed by meshing the fixed scroll 1 with the oscillating scroll 2b of the oscillating scroll 2. The outer periphery of the fixed scroll 1b is connected to the inner periphery of the fixed cylindrical portion 50, and the inner periphery of the fixed cylindrical portion 50 is also a wall surface that forms the compression chamber 1f. The surfaces (lower surfaces) of the fixed scroll 1b and the fixed cylindrical portion 50 that face the oscillating base plate 2a are sliding surfaces with the oscillating base plate 2a.

[0015] The outer periphery of the fixed scroll 1 is fastened to the guide frame 4 with bolts (not shown). A suction pipe 13 penetrates the outer periphery of the fixed scroll 1 (specifically, the fixed cylindrical portion 50) for introducing refrigerant gas from a suction port 1e into the compression chambers 1f. A discharge port 1d is formed in the center of the fixed base plate 1a of the fixed scroll 1, through which compressed, high-pressure refrigerant gas is discharged. The sealed container 10 is provided with a discharge pipe 12 for discharging the refrigerant gas to the outside. The refrigerant gas compressed and high-pressure in the compression chambers 1f is discharged into an upper space 10a within the sealed container 10 through the discharge port 1d. The refrigerant gas discharged to the upper space 10a is guided to an oil separation mechanism through a refrigerant flow path 30, as described later, and the refrigerant gas from which the oil has been separated is discharged through the discharge pipe 12, completing the refrigeration cycle. The oil corresponds to refrigeration oil 11 in this disclosure.

[0016] The orbiting scroll 2 is prevented from rotating by an Oldham mechanism 9, which allows it to revolve (oscillate) relative to the fixed scroll 1 without rotating on its axis. A pair of Oldham guide grooves 4k are formed in a substantially straight line on the frame upper base plate 4h of the guide frame 4. A pair of fixed-side keys 9a of the Oldham mechanism 9 are engaged with the Oldham guide grooves 4k so as to be able to slide back and forth. Furthermore, a pair of Oldham guide grooves 2c, which are 90 degrees out of phase with the Oldham guide grooves 4k of the guide frame 4, are formed in a substantially straight line on the outer periphery of the orbiting base plate 2a of the orbiting scroll 2, and are engaged with a pair of orbiting-side keys 9b of the Oldham mechanism 9 so as to be able to slide back and forth.

[0017] The Oldham mechanism 9 configured as described above allows the orbiting scroll 2 to perform an orbiting motion (orbiting motion) without rotating on its axis. A hollow cylindrical boss 2d is formed in the center of the surface of the orbiting base plate 2a opposite to the surface on which the orbiting scroll 2b is formed (the lower surface in FIG. 1). An eccentric shaft 6a (orbiting shaft) provided at the upper end of the main shaft 6 is inserted into this boss 2d. A thrust surface 2f that can slide and press against the thrust bearing 3a of the compliant frame 3 is formed on the surface of the orbiting base plate 2a opposite to the surface on which the orbiting scroll 2b is formed (the lower surface in FIG. 1). The orbiting base plate 2a of the orbiting scroll 2 is provided with a bleed hole 2g that penetrates the compression chamber 1f and the thrust surface 2f, allowing refrigerant gas to be extracted and directed to the thrust surface 2f during compression.

[0018] The compliant frame 3 is housed within a guide frame 4. The compliant frame 3 has an upper cylindrical surface 3p and a lower cylindrical surface 3s on its outer periphery. The guide frame 4 has an inner periphery with an upper cylindrical surface 4c and a lower cylindrical surface 4d into which the upper cylindrical surface 3p and the lower cylindrical surface 3s of the compliant frame 3 are fitted, respectively. The compliant frame 3 is supported in the radial direction within the guide frame 4 by fitting the upper cylindrical surface 3p with the upper cylindrical surface 4c and the lower cylindrical surface 3s with the lower cylindrical surface 4d, respectively. In addition, a main bearing 3c and an auxiliary main bearing 3d are provided in the center of the lower cylindrical surface 3s of the compliant frame 3, which radially support a main shaft 6 that is rotationally driven by a rotor 5a of an electric motor 5. In addition, a communication hole 3e is provided that penetrates from within the surface of the thrust bearing 3a through the outer periphery of the compliant frame 3 in the axial direction (direction of arrow Z). A thrust bearing opening 3 t that opens at the upper end of the communication hole 3 e is disposed opposite an air bleed hole 2 g that penetrates the swing base plate 2 a of the swing scroll 2 .

[0019] Furthermore, the compliant frame 3 is provided with an intermediate pressure adjustment valve space 3n between the frame upper space 4a and the boss outer space 2n for accommodating an intermediate pressure adjustment valve 3g, an intermediate pressure adjustment valve holder 3h, and an intermediate pressure adjustment spring 3k, which adjust the pressure in the boss outer space 2n. The intermediate pressure adjustment spring 3k is accommodated while being shortened from its natural length. In the first embodiment, the compliant frame 3 and the guide frame 4 are configured as separate bodies, but this is not a limitation, and the two frames may also be configured as a single, integrated frame.

[0020] The upper frame base plate 4h of the guide frame 4 is the surface on which the Oldham mechanism annular portion 9c slides back and forth. The lower frame space 4b, defined by the inner surface of the guide frame 4 and the outer surface of the compliant frame 3, is divided into upper and lower sections by ring-shaped seals 7a and 7b. Here, two ring-shaped seal grooves for accommodating the ring-shaped seals 7a and 7b are formed on the inner circumferential surface of the guide frame 4, but these seal grooves may also be formed on the outer circumferential surface of the compliant frame 3. The lower frame space 4b communicates only with the communication hole 3e of the compliant frame 3 and is configured to seal in the refrigerant gas being compressed and supplied through the bleed hole 2g of the oscillating base plate 2a. The space on the outer circumferential side of the thrust bearing 3a, which is surrounded by the oscillating base plate 2a of the oscillating scroll 2 and the compliant frame 3 on the top and bottom, i.e., the upper frame space 4a, is a low-pressure space of the intake gas atmosphere (suction pressure).

[0021] Fig. 2 is a cross-sectional view showing a first passage 4f provided on the outer periphery of the guide frame 4 shown in Fig. 1. As shown in Fig. 2, the guide frame 4 is fixed to the sealed container 10 by shrink fitting or welding on its outer periphery. The outer periphery of the guide frame 4 and the outer periphery of the fixed scroll 1 shown in Fig. 1 (i.e., the outer periphery of the compression mechanism 14) are provided with first passages 4f formed by notches. As shown in Fig. 1, refrigerant gas discharged from the discharge port 1d into the upper space 10a of the sealed container 10 flows downward through the first passage 4f into the sealed container 10. The bottom of the sealed container 10 forms an oil reservoir 10b in which refrigerating machine oil 11 is stored.

[0022] The first passage 4f is located on the opposite side of the discharge pipe 12. The guide frame 4 is also provided with a first discharge passage 4g that runs from the center of its lower end to its side surface, and the first discharge passage 4g is connected to the discharge pipe 12. The lower end of the guide frame 4 is also provided with a discharge cover 16 that has an opening 16b that surrounds the lower cylindrical portion (the portion where the lower cylindrical surface 4d is formed). A second discharge passage 16a within the discharge cover 16 is connected to the first discharge passage 4g.

[0023] The electric motor 5 drives the main shaft 6 to rotate, and is composed of a rotor 5a fixed to the main shaft 6, a stator 5b fixed to the sealed container 10, and the main shaft 6, which is a rotating shaft. The rotor 5a is fixed to the main shaft 6 by shrink-fitting, and is driven to rotate when current is applied to the stator 5b, thereby rotating the main shaft 6. An eccentric shaft portion 6a is formed at the upper end of the main shaft 6, and is rotatably engaged with the oscillating bearing 2e of the oscillating scroll 2. A main shaft balance weight 6f is fixed to the lower side of the eccentric shaft portion 6a by shrink-fitting.

[0024] Furthermore, a main shaft portion 6b is formed below the eccentric shaft portion 6a, which rotatably engages with the main bearing 3c and auxiliary main bearing 3d of the compliant frame 3. A counter shaft portion 6c is formed at the lower end of the main shaft 6, which rotatably engages with the counter bearing 8a of the subframe 8. The subframe 8 is provided with an inlet hole 8b through which refrigerant oil 11 flows into an oil reservoir 10b. A rotor 5a of the electric motor 5 is shrink-fitted to the portion of the main shaft 6 between the counter shaft portion 6c and the main shaft portion 6b.

[0025] An oil supply passage 6d, which is a hole penetrating the main shaft 6 in the axial direction (direction of arrow Z), is provided. An oil supply port 6e at the lower end of the oil supply passage 6d is immersed in refrigerating machine oil 11 stored at the bottom of the sealed container 10. Therefore, refrigerating machine oil 11 is sucked up from the oil supply port 6e by an oil supply mechanism or pump mechanism (not shown) provided at the bottom of the main shaft 6. The upper end of the oil supply passage 6d opens into the boss portion 2d of the orbiting scroll 2, and the sucked up refrigerating machine oil 11 flows from the upper end opening of the oil supply passage 6d to the orbiting bearing 2e, lubricating the eccentric shaft portion 6a and the orbiting bearing 2e. Refrigerating machine oil 11 that flows out from the upper end opening of the oil supply passage 6d and lubricates the orbiting bearing 2e flows toward the outer periphery and lubricates the Oldham mechanism 9. Refrigerating machine oil 11 present near the Oldham mechanism 9 also flows into an oil supply groove 51, which will be described later, when the oil supply groove 51 opens.

[0026] The oil supply passage 6d is provided with an oil supply hole 6g that branches off laterally, and refrigeration oil 11 is supplied to the auxiliary main bearing 3d from this oil supply hole 6g to lubricate the auxiliary main bearing 3d and the main shaft portion 6b. Note that the oil supply hole for the main bearing 3c is not shown in Figure 1.

[0027] A first balance weight 15a is fixed to the upper end surface of the rotor 5a, and a second balance weight 15b is fixed to the lower end surface at diagonally opposite eccentric positions. In FIG. 1, the first balance weight 15a is located on the right side of the main shaft 6, and the second balance weight 15b is located on the left side. In addition, the aforementioned main shaft balance weight 6f is fixed to the main shaft 6 below the eccentric shaft portion 6a, within the outer space of the boss portion 2d. These three balance weights offset the imbalance of centrifugal force and moment force caused by the orbiting scroll 2 swinging via the eccentric shaft portion 6a of the main shaft 6, thereby achieving static and dynamic balance.

[0028] Furthermore, a first cup-shaped member 17 containing a first balance weight 15a is fixed to the upper end surface of the rotor 5a, and a second cup-shaped member 18 containing a second balance weight 15b is fixed to the lower end surface of the rotor 5a. The first cup-shaped member 17 is attached with its opening 17a facing upward so that it faces the opening 16b of the discharge cover 16. The second cup-shaped member 18 is attached with its opening facing downward.

[0029] FIG. 3 is a longitudinal cross-sectional view of the rotor 5a of the electric motor 5 of FIG. 1 . FIG. 4 is a transverse cross-sectional view of the rotor 5a of the electric motor 5 of FIG. 1 . As shown in FIGS. 3 and 4 , the rotor 5a is provided with a plurality of through-flow passages 5f penetrating in the axial direction (arrow Z direction). The through-flow passages 5f shown in FIGS. 3 and 4 are provided penetrating the bottoms of the first cup-shaped member 17 and the second cup-shaped member 18, avoiding the positions of the first balance weight 15a and the second balance weight 15b (see FIG. 1 ). The first cup-shaped member 17 and the second cup-shaped member 18 shown in FIG. 1 are preferably made of a non-magnetic material. The through-flow passages 5f may be formed penetrating the first balance weight 15a and the second balance weight 15b, or may be provided avoiding the positions of the first cup-shaped member 17 and the second cup-shaped member 18. The plurality of through-flow passages 5f are formed symmetrically or point-symmetrically with respect to the axis.

[0030] Fig. 5 is a cross-sectional view showing the stator 5b of the electric motor 5 of Fig. 1. As shown in Fig. 5, the outer peripheral surface of the stator 5b of the electric motor 5 is fixed to the sealed container 10 by shrink fitting, welding, or the like. A second passage 5g formed by a notch is provided in the outer peripheral portion of the stator 5b. As shown in Fig. 1, the first passage 4f and the second passage 5g described above constitute the refrigerant flow path 30 that guides the refrigerant gas discharged from the discharge port 1d to the bottom of the sealed container 10.

[0031] As shown in FIG. 1, a glass terminal 10c is provided on the side surface of the sealed container 10, and the glass terminal 10c and the stator 5b of the electric motor 5 are connected by a lead wire 5h.

[0032] Next, the operation of the scroll compressor 100 according to the first embodiment will be described. When the scroll compressor 100 is started up or running, refrigerant is drawn into the suction pipe 13 and enters the compression chamber 1f formed by the meshing of the fixed scroll 1's fixed scroll body 1b and fixed cylindrical portion 50 with the orbiting scroll 2's orbiting scroll body 2b. The orbiting scroll 2, driven by the electric motor 5, reduces the volume of the compression chamber 1f as it orbits eccentrically. This compression stroke increases the pressure of the drawn refrigerant. During this compression stroke, intermediate-pressure refrigerant gas is guided from the bleed hole 2g of the orbiting scroll 2 through the communication hole 3e of the compliant frame 3 to the frame lower space 4b, maintaining an intermediate-pressure atmosphere in this frame lower space 4b.

[0033] The mixed gas (more specifically, the mixed gas of the refrigerant and the refrigerating machine oil 11) discharged from the discharge port 1d of the fixed scroll 1 into the upper space 10a of the sealed container 10 after the compression stroke passes through a refrigerant flow path 30 consisting of a first passage 4f provided on the outer periphery of the compression mechanism 14 and a second passage 5g provided on the outer periphery of the stator 5b of the electric motor 5, and is guided to a space below the electric motor 5, i.e., the bottom of the sealed container 10. The mixed gas is separated during the process of being guided to the bottom of the sealed container 10. The refrigerant gas separated from the refrigerating machine oil 11 enters the interior through an opening of a second cup-shaped member 18 attached to the lower end surface of the rotor 5a of the electric motor 5 and flows into a through-flow passage 5f (see FIG. 3 ) provided in the rotor 5a. The refrigerant gas from which the refrigerating machine oil 11 has been separated rises inside a first cup-shaped member 17 attached to the upper end surface of the rotor 5a and flows into the discharge cover 16. Furthermore, the refrigerant gas from which the refrigerating machine oil 11 has been separated passes through the second discharge passage 16 a in the discharge cover 16 , the first discharge passage 4 g , and further passes through the discharge pipe 12 to be discharged outside the sealed container 10 .

[0034] FIG. 6 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 400 according to the first embodiment. Next, referring to FIG. 6 , the refrigeration cycle apparatus 400, such as an air conditioner, to which a scroll compressor 100 is connected will be described. The refrigeration cycle apparatus 400 includes a suction muffler 401 of the scroll compressor 100 connected to the suction side of the scroll compressor 100, a four-way switching valve 403 connected to the discharge side of the scroll compressor 100 for switching the flow of refrigerant from the scroll compressor 100, an outdoor heat exchanger 404, a pressure reducer 405 such as an electric expansion valve, and an indoor heat exchanger 406, which are sequentially connected via piping to form a refrigerant circuit. In general, in a refrigeration air-conditioning system, the indoor heat exchanger 406 is installed in an indoor unit (i.e., an indoor unit), and the remaining scroll compressor 100, the four-way switching valve 403, the outdoor heat exchanger 404, and the pressure reducer 405 are installed in an outdoor unit (i.e., an outdoor unit).

[0035] For example, in heating operation of the air conditioner, four-way switching valve 403 is connected to the solid line side in Figure 6. High-temperature, high-pressure refrigerant compressed by scroll compressor 100 flows to indoor heat exchanger 406, condenses, and liquefies, and is then throttled by pressure reducer 405 to become a two-phase refrigerant with low temperature and low pressure. The refrigerant then flows to outdoor heat exchanger 404, evaporates, and gasifies before returning to scroll compressor 100 through four-way switching valve 403. That is, the refrigerant circulates as shown by the solid arrows in Figure 6. Through this circulation, the refrigerant exchanges heat with outside air in outdoor heat exchanger 404, which serves as an evaporator, and the refrigerant sent to outdoor heat exchanger 404 absorbs heat. The refrigerant that has absorbed heat is then sent to indoor heat exchanger 406, which serves as a condenser, where it exchanges heat with indoor air to warm the indoor air.

[0036] In cooling operation, the four-way switching valve 403 is connected to the dashed line side in Figure 6. The high-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows to the outdoor heat exchanger 404, condenses, and liquefies. The refrigerant is then throttled by the pressure reducer 405 to a low-temperature, low-pressure, two-phase state. The refrigerant then flows to the indoor heat exchanger 406, evaporates, and gasifies. The four-way switching valve 403 then returns to the scroll compressor 100. That is, when the operation mode switches from heating to cooling, the indoor heat exchanger 406 changes from a condenser to an evaporator, and the outdoor heat exchanger 404 changes from an evaporator to a condenser. Thus, the refrigerant circulates as shown by the dashed arrows in Figure 6. Through this circulation, the indoor heat exchanger 406, which functions as an evaporator, exchanges heat with the indoor air, absorbing heat from the indoor air and cooling it. The refrigerant that has absorbed heat is then sent to the outdoor heat exchanger 404, which functions as a condenser, where it exchanges heat with the outdoor air and releases heat to the outdoor air.

[0037] Refrigerants used in refrigeration cycle devices 400 such as air conditioners include fluorine-based refrigerants or hydrocarbon-based refrigerants with low global warming potential (GWP). Examples include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixture of two or more of these refrigerants, a mixture of any of these refrigerants with other refrigerants, a mixture containing R1132(E), and a mixture containing R1123. Other examples include a mixture of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0038] FIG. 7 is a vertical cross-sectional view showing the fixed scroll 1 and the orbiting scroll 2 according to the first embodiment. FIG. 8 is a vertical cross-sectional view of the fixed scroll 1 and the orbiting scroll 2, showing a state in which the orbiting scroll 2 is positioned in a facing direction relative to FIG. 7. FIG. 9 is a view of the fixed scroll 1 according to the first embodiment as seen from below. FIG. 10 is a plan view of the orbiting scroll 2 according to the first embodiment. Based on FIGS. 7 to 10 and with reference to FIG. 1, the outer peripheral structure of the fixed scroll 1, such as the fixed cylinder portion 50, oil supply groove 51, and suction port 52, as well as the positional relationship between these outer peripheral structures of the fixed scroll 1 and the orbiting scroll 2 will be described below.

[0039] 7 to 9 show the range (hereinafter, movable range R) in which the oscillating base plate 2a moves during the orbital motion of the oscillating scroll 2. In addition, in Fig. 9, for ease of understanding, the fixed scroll 1b is shown with diagonal lines, and the surface of the fixed cylinder portion 50 that contacts the oscillating base plate 2a is shown with a diagonal grid. Here, the surface of the fixed cylinder portion 50 that contacts the oscillating base plate 2a refers to a portion that is within the range (movable range R) in which the oscillating base plate 2a moves during the orbital motion of the oscillating scroll 2, and that contacts the oscillating base plate 2a at any timing during the orbital period on the lower surface (hereinafter, also referred to as the tip surface) of the fixed cylinder portion 50.

[0040] 7 to 9, an annular oil supply groove 51 is formed in the tip end surface of the fixed cylinder portion 50 that faces the oscillating base plate 2a. Hereinafter, the fixed cylinder portion 50 will be defined as being divided into an inner peripheral side and an outer peripheral side, with the inner peripheral surface 51i of the oil supply groove 51 as the boundary (i.e., with the inner peripheral end 51ei of the oil supply groove 51 as the boundary), and the part that constitutes the inner peripheral side will be referred to as the cylinder portion inner wall portion 53, and the part that constitutes the outer peripheral side will be referred to as the cylinder portion outer wall portion 54.

[0041] 7 and 9, the outer peripheral surface of the cylindrical outer wall portion 54 is the outer peripheral surface of the fixed cylindrical portion 50 and is a substantially cylindrical surface that faces the inner peripheral surface of the sealed container 10 (see FIG. 1). As in the example of FIG. 7, a step portion 54s may be formed midway in the axial direction (direction of arrow Z) on the outer peripheral surface of the fixed cylindrical portion 50. The oil groove 51 (particularly the outer peripheral surface 51o and bottom surface 51a of the oil groove 51) is provided on the inner peripheral side of the lower part of the cylindrical outer wall portion 54. As shown in FIGS. 7 and 9, the outer peripheral surface 51o of the oil groove 51 has a cylindrical shape.

[0042] 9, the cylindrical inner wall portion 53 has a spiral shape in which a starting end 53e1 and a terminal end 53e2 are offset in the radial direction via the intake port 52. The starting end 53e1 of the cylindrical inner wall portion 53 is connected to the outer peripheral end of the fixed spiral body 1b.

[0043] The inner peripheral surface 53b of the cylindrical inner wall portion 53 is the inner peripheral surface of the fixed cylindrical portion 50 and is formed in a spiral shape. The inner peripheral surface 53b of the cylindrical inner wall portion 53 forms part of the compression chamber 1f and is the surface that slides against the oscillating scroll 2b. The outer peripheral surface 53a of the cylindrical inner wall portion 53 forms part of the oil groove 51. Specifically, the outer peripheral surface 53a of the lower part of the cylindrical inner wall portion 53 is the inner peripheral surface 51i of the oil groove 51.

[0044] As described above, the outer peripheral end of the fixed spiral body 1b is connected to the inner peripheral surface 53b of the cylindrical inner wall portion 53, and as shown in FIG. 9, the inner peripheral surface 53b of the cylindrical inner wall portion 53 and the inner surface 1bi of the fixed spiral body 1b are smoothly connected to form a continuous involute curve.

[0045] In the first embodiment, the outer peripheral surface 53a of the cylindrical inner wall portion 53 (i.e., the inner peripheral surface 51i of the oil groove 51) is also an involute curve. The outer peripheral surface 53a of the cylindrical inner wall portion 53 and the outer surface 1bo of the fixed scroll 1b are smoothly connected to form a continuous involute curve.

[0046] 9 , the radial width W1 of oil groove 51 in the tip end face of fixed cylindrical portion 50 is generally constant in the circumferential middle portion of oil groove 51 except for the vicinity of suction port 52. Furthermore, the radial width W1 of oil groove 51 is wider in a portion of oil groove 51 formed on the outer circumferential side of starting end 53e1 of cylindrical portion inner wall portion 53 than in the middle portion, and the radial width W1 of oil groove 51 is narrower in a portion of oil groove 51 formed on the outer circumferential side of terminal end 53e2 of cylindrical portion inner wall portion 53 than in the middle portion.

[0047] As shown in FIG. 10, the inner surface 2bi and the outer surface 2bo of the orbiting scroll 2 form an involute curve.

[0048] 9, the thickness T2 of the cylindrical inner wall 53 is set to be thicker than the thickness T1 of the fixed scroll 1b, which is provided radially inward of the cylindrical inner wall 53. This makes it possible to reduce the sliding surface pressure on the surface of the cylindrical inner wall 53 that comes into contact with the oscillating base plate 2a (see FIG. 7) compared to when the thickness T2 of the cylindrical inner wall 53 is set to be the same as the thickness T1 of the fixed scroll 1b.

[0049] 7 and 8, an inner peripheral portion of the surface of the oscillating base plate 2a facing the fixed cylinder portion 50 (the upper surface in FIGS. 7 and 8) is exposed to and lubricated by the compression chamber 1f, in which refrigerating machine oil 11, which serves as a lubricant, is present, as the oscillating scroll 2 revolves. Also, an outer peripheral portion of the upper surface of the oscillating base plate 2a is exposed to and lubricated by the oil supply groove 51, in which refrigerating machine oil 11 is present, as the oscillating scroll 2 revolves. As a result, compared to a conventional configuration in which the fixed cylinder portion 50 does not have the oil supply groove 51, seizure can be suppressed even in the outer peripheral portion of the upper surface of the oscillating base plate 2a.

[0050] In a specific structure, the outer peripheral end 2ao of the oscillating base plate 2a moves outward beyond the inner peripheral end 51ei of the oil feed groove 51 during the orbital motion of the oscillating scroll 2, and the oil feed groove 51 opens at least at some timing during the orbital period of the oscillating scroll 2. For example, as shown in Figures 7 and 8, the oscillating base plate 2a may be provided so that the outer shape of the oscillating base plate 2a moves within the outer shape of the oil feed groove 51. Note that the oscillating base plate 2a may be provided so that the outer shape of the oscillating base plate 2a protrudes from the outer shape of the oil feed groove 51 during the orbital motion of the oscillating scroll 2. In this case, the outer peripheral end 2ao of the oscillating base plate 2a moves inward beyond the outer peripheral end 51eo of the oil feed groove 51 at some timing during the orbital period of the oscillating scroll 2, allowing refrigeration oil 11 to flow into the oil feed groove 51 from the space below the oscillating base plate 2a.

[0051] 9, the thickness T2 of the cylindrical inner wall portion 53 is formed to be the same as or smaller than the orbital diameter 61 of the orbiting scroll 2 (see FIG. 10). Here, the orbital locus 60 of the orbiting scroll 2 and the orbital diameter 61 of the orbiting scroll 2 shown representatively in FIG. 9 are the orbital locus and the orbital diameter of the orbiting scroll 2 corresponding to the center 2h of the orbiting scroll 2b shown in FIG. 10. By configuring the thickness T2 of the cylindrical inner wall portion 53 to be the same as or smaller than the orbital diameter 61 of the orbiting scroll 2, lubricating oil can be supplied to all parts of the surface of the cylindrical inner wall portion 53 that comes into contact with the orbiting base plate 2a as the orbital motion of the orbiting scroll 2 progresses. If the thickness T2 of the cylindrical inner wall portion 53 is configured to be larger than the orbital diameter 61 of the oscillating scroll 2, during the orbital motion of the oscillating scroll 2, there will be a portion of the surface of the cylindrical inner wall portion 53 that comes into contact with the oscillating base plate 2a where lubricating oil cannot be supplied, and seizure cannot be completely prevented.

[0052] 9, a suction pipe 13 is provided through a fixed cylinder portion 50 provided on the outer periphery of the fixed scroll body 1b in the fixed scroll 1, and a suction port 52 is formed in the fixed cylinder portion 50, which communicates with the suction pipe 13 and serves as a refrigerant inlet for the compression chamber 1f. The suction port 52 also communicates between the compression chamber 1f and an oil supply groove 51 provided in the fixed cylinder portion 50. This allows refrigeration oil 11 (mixed with refrigerant gas) to be supplied from the compression chamber 1f to the oil supply groove 51, ensuring the refrigeration oil 11 in the oil supply groove 51 and enabling favorable sliding between the fixed cylinder portion 50 and the oscillating base plate 2a.

[0053] 8, the depth Dr of the oil groove 51 is smaller than the depth Df of the compression chamber 1f, based on the sliding surface of the fixed scroll 1 with the oscillating base plate 2a. That is, in the axial direction (arrow Z direction), the distance from the sliding surface to the bottom surface 51a, which is the upper end of the oil groove 51, is smaller than the distance from the sliding surface to the lower surface 1fb of the fixed base plate 1a. With this configuration, it is easier to fill the entire circumferential area of ​​the oil groove 51 with lubricating oil, compared to when the depth Dr of the oil groove 51 and the depth Df of the compression chamber 1f are the same. As a result, the sliding between the fixed cylinder portion 50 and the oscillating base plate 2a can be performed more efficiently.

[0054] Fig. 11 is a view of the fixed scroll 1x of the comparative example as seen from below. Fig. 12 is a vertical cross-sectional view of the fixed scroll 1x and the orbiting scroll 2 of the comparative example. Fig. 13 is a vertical cross-sectional view of the fixed scroll 1x and the orbiting scroll 2 of the comparative example, showing a state in which the orbiting scroll 2 is positioned in a facing direction relative to Fig. 12. Below, based on Figs. 1, 7 and 9, the actions and effects of the outer peripheral structure of the fixed scroll 1, such as the fixed cylinder portion 50, oil supply groove 51, and suction port 52, in the scroll compressor 100 of the present disclosure will be described in detail, while comparing it with the comparative example shown in Figs. 11 to 13.

[0055] 11, for ease of understanding, the fixed scroll 1b is indicated by diagonal lines, and the surface of the fixed cylinder 50x that comes into contact with the oscillating base plate 2a is indicated by a diagonal grid. Here, the surface of the fixed cylinder 50x that comes into contact with the oscillating base plate 2a refers to the range (movable range R) in which the oscillating base plate 2a moves during the orbital motion of the oscillating scroll 2, and also refers to the portion of the tip surface of the fixed cylinder 50x that comes into contact with the oscillating base plate 2a at any timing during the orbital period.

[0056] Referring to FIG. 7, the fixed scroll body 1b of the fixed scroll 1 slides on the swinging base plate 2a of the swinging scroll 2 via refrigeration oil 11 (see FIG. 1), which is a lubricating oil. Therefore, in order to prevent the sliding surfaces from seizing, it is necessary to reduce the sliding surface pressure and ensure a supply of oil to the sliding surfaces.

[0057] In the fixed scroll 1 of the present disclosure, first, with regard to the sliding surface pressure, as shown in FIG. 9 , the thickness T2 of the cylindrical inner wall portion 53 is configured to be thicker than the thickness T1 of the fixed scroll body 1b. This configuration is also the same in the comparative example. That is, as shown in FIG. 11 , the thickness T2x of the wall portion 53x forming the compression chamber 1f in the fixed cylindrical portion 50x of the comparative example is configured to be thicker than the thickness T1 of the fixed scroll body 1b. This configuration increases the contact area between the lower surface (hereinafter also referred to as the tip surface) of the cylindrical inner wall portion 53 and the oscillating base plate 2a (see FIG. 7 ) compared to when the thickness T2 of the cylindrical inner wall portion 53 is configured to be the same as the thickness T1 of the fixed scroll body 1b. As a result, in the present disclosure, the sliding surface pressure of the surface of the cylindrical inner wall portion 53 that contacts the oscillating base plate 2a can be reduced.

[0058] Next, in the fixed scroll 1 of the present disclosure, with regard to the supply of oil to the sliding surfaces, as shown in Fig. 9 , an annular oil feed groove 51 is formed in the tip end surface of the fixed cylindrical portion 50. The fixed cylindrical portion 50 and the oscillating base plate 2a are arranged so that the outer peripheral portion of the upper surface of the oscillating base plate 2a is exposed to the oil feed groove 51 as the oscillating scroll 2 revolves, and the oil feed groove 51 is open at least at any timing during the orbital period. More specifically, the movable range R of the oscillating base plate 2a and the position of the oil feed groove 51 in the fixed cylindrical portion 50 are determined so that the outer contour of the movable range R of the oscillating base plate 2a due to the orbital motion of the oscillating scroll 2 is located outer peripherally of the inner peripheral end 51ei of the oil feed groove 51, and there are times during the orbital motion of the oscillating scroll 2 that the outer peripheral end 2ao of the oscillating base plate 2a is located inner peripherally of the outer peripheral end 51eo of the oil feed groove 51. With this configuration, as the oscillating scroll 2 revolves, the inner peripheral portion of the upper surface of the oscillating base plate 2a is lubricated by the refrigerant oil 11 present in the compression chamber 1f, and the outer peripheral portion of the upper surface of the oscillating base plate 2a can be lubricated by the refrigerant oil 11 present in the oil feed groove 51. When the oil feed groove 51 opens, the refrigerant oil 11 that has lubricated the oscillating bearing 2e and the like flows into the oil feed groove 51 from below the oscillating base plate 2a, thereby replenishing the oil feed groove 51 with the refrigerant oil 11. Thus, in the present disclosure, the supply of oil to the sliding surfaces can be ensured.

[0059] 11 to 13, the oil supply groove 51 (see FIGS. 7 and 9) is not provided on the tip surface of the fixed cylinder 50x, so the outer peripheral portion of the upper surface of the oscillating plate 2a cannot be lubricated. Therefore, in the comparative example, seizure may occur between the outer peripheral portion of the upper surface of the oscillating plate 2a and the outer peripheral portion of the wall portion 53x that forms the compression chamber 1f in the fixed cylinder 50x.

[0060] 9 , in the fixed scroll 1 of the present disclosure, the outer peripheral surface 53a of the cylindrical portion inner wall portion 53 (i.e., the inner peripheral surface 51i of the oil groove 51) forms the oil groove 51 that communicates with the suction port 52. With this configuration, the oil groove 51 and the compression chamber 1f communicate with each other via the suction port 52, so that refrigerant oil 11 mixed with refrigerant can be supplied from the compression chamber 1f to the oil groove 51. Therefore, the amount of refrigerant oil 11 in the oil groove 51 is increased by supplying the refrigerant oil 11 into the oil groove 51 not only from below the oscillating base plate 2a but also from the compression chamber 1f. This allows the outer peripheral portion of the upper surface of the oscillating base plate 2a to be lubricated with a sufficient amount of refrigerant oil 11, thereby more effectively sliding between the tip end surface (i.e., the lower surface) of the fixed cylindrical portion 50 and the upper surface of the oscillating base plate 2a.

[0061] Fig. 14 is a vertical cross-sectional view of a fixed scroll 501 and an orbiting scroll 2, illustrating a modification of the fixed scroll 1 of Fig. 8. As shown in Fig. 14, the oil supply groove 551 in the fixed cylinder portion 550 may be configured by cutting out the outer circumferential edge portion of the tip surface of the fixed cylinder portion 550. That is, the oil supply groove 551 may have an inner circumferential surface 551i and a bottom surface 551a but may not have the outer circumferential surface 51o shown in Fig. 8. In Fig. 14, the outer circumferential surface of the fixed cylinder portion 550, i.e., the outer circumferential surface of the cylinder portion outer wall portion 554, is a substantially cylindrical surface that faces the inner circumferential surface of the sealed container 10 (see Fig. 1).

[0062] As described above, the scroll compressor 100 according to the first embodiment includes the fixed scroll 1, which has the fixed scroll 1b and the fixed cylindrical portion 50 disposed on one surface (lower surface 1fb) of the fixed base plate 1a, and the orbiting scroll 2, which has the orbiting scroll 2b disposed on one surface (upper surface) of the orbiting base plate 2a. In the scroll compressor 100, the inner peripheral portion of the fixed cylindrical portion 50 and the fixed scroll 1b have inner peripheral surfaces (the inner peripheral surface 53b of the cylindrical portion inner wall portion 53 and the inner surface 1bi of the fixed scroll 1b) that form a continuous spiral shape and mesh with the orbiting scroll 2b. When the orbiting scroll 2 revolves, the tip surfaces of the fixed scroll 1b, the tip surfaces of the fixed cylindrical portion 50, and one surface of the orbiting base plate 2a slide against each other via lubricating oil. An annular oil supply groove 51 is formed in the tip surface of the fixed cylindrical portion 50. Furthermore, the radial thickness T2 of the cylindrical inner wall portion 53 that forms the inner peripheral side of the fixed cylindrical portion 50, with the inner peripheral end 51ei of the oil supply groove 51 as a boundary, is configured to be thicker than the radial thickness T1 of the fixed scroll 1b. The oscillating base plate 2a and the oil supply groove 51 of the fixed cylindrical portion 50 are arranged so that the outer contour of the movable range R of the oscillating base plate 2a due to the orbital motion of the oscillating scroll 2 is located outer peripherally of the inner peripheral end 51ei of the oil supply groove 51, and so that during the orbital motion of the oscillating scroll 2, the outer peripheral end 2ao of the oscillating base plate 2a is sometimes located inner peripherally of the outer peripheral end 51eo of the oil supply groove 51.

[0063] In this way, an annular oil supply groove 51 is formed on the tip surface of the fixed cylindrical portion 50, and the radial thickness T2 of the cylindrical portion inner wall portion 53 that forms the inner side of the fixed cylindrical portion 50, with the inner end 51ei of the oil supply groove 51 as the boundary, is configured to be thicker than the radial thickness T1 of the fixed scroll body 1b.As a result, as in the conventional case, the contact area between the oscillating base plate 2a and the fixed scroll 1 can be ensured to be greater than a certain level, thereby suppressing an increase in sliding surface pressure. Furthermore, an annular oil feed groove 51 is formed in the tip end surface of the fixed cylinder 50, and the oil feed groove 51 of the oscillating base plate 2a and the fixed cylinder 50 is arranged so that the outer contour of the movable range R of the oscillating base plate 2a due to the orbital motion of the oscillating scroll 2 is located outer peripherally of the inner peripheral end 51ei of the oil feed groove 51, and the outer peripheral end 2ao of the oscillating base plate 2a is sometimes located inner peripherally of the outer peripheral end 51eo of the oil feed groove 51 during the orbital motion of the oscillating scroll 2. Therefore, the outer peripheral portion of the part of the oscillating base plate 2a that slides against the tip end surface of the fixed cylinder 50 is exposed to the oil feed groove 51 to supply lubricating oil, and the oil feed groove 51 can be opened to replenish oil into the oil feed groove 51. Therefore, lubricating oil can be supplied to the outer peripheral portion while suppressing an increase in the sliding surface pressure between the oscillating base plate 2a and the fixed scroll 1, and seizure in the outer peripheral portion can be suppressed.

[0064] Furthermore, the radial thickness T2 of the cylindrical inner wall portion 53 is configured to be the same as or smaller than the orbital diameter 61 of the orbiting scroll 2. This allows the entire portion of the oscillating base plate 2a that slides against the tip end surface of the fixed cylindrical portion 50 as the orbiting scroll 2 revolves to be lubricated by the oil (refrigerant oil 11) in the compression chamber 1f or the oil supply groove 51, more reliably preventing seizure.

[0065] The outer peripheral surface 53a of the cylindrical inner wall portion 53 forms an involute curve, which allows the shape of the outer peripheral surface 53a of the cylindrical inner wall portion 53 to be simplified.

[0066] A compression chamber 1f, the volume of which changes with the orbital motion of the orbiting scroll 2, is formed between the inner peripheral surface of the fixed cylindrical portion 50 (i.e., the cylindrical portion inner wall portion 53) and the fixed scroll 1b, which forms a continuous spiral shape, and the orbiting scroll 2b. A suction port 52 is formed in the fixed cylindrical portion 50 to draw refrigerant into the compression chamber 1f, and the compression chamber 1f and the oil supply groove 51 are connected to each other via the suction port 52.

[0067] This allows the lubricating oil (refrigerant oil 11) mixed with the refrigerant to be supplied from the compression chamber 1f to the oil supply groove 51, ensuring that the refrigerant oil 11 is secured in the oil supply groove 51, allowing for smooth sliding between the fixed cylinder portion 50 and the oscillating base plate 2a.

[0068] Furthermore, the bottom surface 51a of the oil groove 51 is positioned closer to one surface (upper surface) of the oscillating bed plate 2a than to one surface (lower surface 1fb) of the fixed bed plate 1a. This makes it easier to fill the entire circumferential direction of the oil groove 51 with lubricating oil, compared to when the bottom surface 51a of the oil groove 51 and the lower surface 1fb of the oscillating bed plate 2a are positioned at the same position relative to the upper surface of the oscillating bed plate 2a in the axial direction (arrow Z direction). As a result, sliding between the fixed cylinder portion 50 and the oscillating bed plate 2a can be performed more efficiently.

[0069] The refrigeration cycle apparatus 400 according to the first embodiment includes the above-described scroll compressor 100, an outdoor heat exchanger 404, a pressure reducer 405, and an indoor heat exchanger 406. The refrigeration cycle apparatus 400 includes the above-described scroll compressor 100 that can suppress seizure, and therefore has improved reliability compared to conventional refrigeration cycle apparatuses.

[0070] Second Embodiment Fig. 15 is a view of the fixed scroll 101 according to the second embodiment as viewed from below. The configuration of the fixed scroll 101 according to the second embodiment will be described with reference to Fig. 15. In the second embodiment, the shape of the outer peripheral surface 153a of the cylindrical inner wall portion 153 of the fixed scroll 101 is different from that in the first embodiment. Note that in the second embodiment, components having the same functions and actions as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

[0071] 15 , in the fixed cylinder 150 of the fixed scroll 101 according to the second embodiment, as in the first embodiment, the outer peripheral surface 153a of the cylinder inner wall 153 forms part of the oil groove 151 (particularly the inner peripheral surface 151i of the oil groove 151), and the inner peripheral surface 53b of the cylinder inner wall 153 forms part of the compression chamber 1f. The inner peripheral surface 53b of the cylinder inner wall 153 is connected to the outer peripheral end of the fixed scroll 1b, and the inner peripheral surface 53b of the cylinder inner wall 153 and the inner surface 1bi of the fixed scroll 1b are smoothly connected to form a continuous involute curve. The outer peripheral surface 151o of the oil groove 151 has a cylindrical shape.

[0072] In the second embodiment, the outer peripheral surface 153a of the cylindrical inner wall portion 153 is configured with a plurality of curves 153a1 to 153a4. In the example of Fig. 15, the outer peripheral surface 153a of the cylindrical inner wall portion 153 is configured with four different arc-shaped curves 153a1, 153a2, 153a3, and 153a4, which are connected to form a substantially spiral shape. Here, the concept of a curve includes an involute shape.

[0073] In the example of Figure 15, outer peripheral surface 153a of cylindrical inner wall portion 153, i.e., inner peripheral surface 151i of oil groove 151, is composed of multiple curves 153a1, 153a2, 153a3, and 153a4, so that the radial width W2 of oil groove 151 changes in the intermediate portion between starting end 153e1 and terminal end 153e2 of oil groove 151.

[0074] 15 , the radial width W2 of the intermediate portion of oil groove 151 is greatest at the portion farthest from suction port 52, i.e., the portion located on the outer periphery of curved line 153a2. The radial width W2 of oil groove 151 is greater than the maximum width at the intermediate portion in a portion of oil groove 151 formed on the outer periphery of starting end 153e1 of cylindrical inner wall portion 153, and is narrower than the minimum width at the intermediate portion in a portion of oil groove 151 formed on the outer periphery of terminal end 153e2 of cylindrical inner wall portion 153. This configuration allows refrigeration oil 11 from compression chamber 1f to reach the portion of oil groove 151 farthest from suction port 52, thereby more uniformly lubricating the sliding surfaces in the circumferential direction.

[0075] As in the case of embodiment 1, the scroll compressor 100 of embodiment 2 can also supply lubricating oil to the outer peripheral portion while suppressing an increase in the sliding surface pressure between the oscillating base plate 2a and the fixed scroll 101, thereby achieving the effect of suppressing seizure in the outer peripheral portion.

[0076] In scroll compressor 100 according to the second embodiment, outer peripheral surface 153a of cylindrical inner wall portion 153 is formed by a plurality of curves 153a1 to 153a4. In the second embodiment, the degree of freedom in the shape of outer peripheral surface 153a of cylindrical inner wall portion 153 is increased compared to the first embodiment.

[0077] Embodiment 3 Fig. 16 is a view of the fixed scroll 201 according to embodiment 3 as viewed from below. The configuration of the fixed scroll 201 according to embodiment 3 will be described using Fig. 16. In embodiment 3, the shape of the outer peripheral surface 253a of the cylindrical inner wall portion 253 in the fixed scroll 201 is different from that in embodiments 1 and 2. Note that in embodiment 3, components having the same functions and actions as those in embodiment 1 are denoted by the same reference numerals, and description thereof will be omitted.

[0078] 16 , in the fixed cylinder 250 of the fixed scroll 201 according to the third embodiment, as in the first embodiment, the outer peripheral surface 253a of the cylinder inner wall 253 forms part of the oil groove 251 (particularly the inner peripheral surface 251i of the oil groove 251), and the inner peripheral surface 53b of the cylinder inner wall 253 forms part of the compression chamber 1f. The inner peripheral surface 53b of the cylinder inner wall 253 is connected to the outer peripheral end of the fixed scroll 1b, and the inner peripheral surface 53b of the cylinder inner wall 253 and the inner surface 1bi of the fixed scroll 1b are smoothly connected to form a continuous involute curve. The outer peripheral surface 251o of the oil groove 251 has a cylindrical shape.

[0079] In the third embodiment, outer peripheral surface 253a of cylindrical inner wall portion 253 is configured with a plurality of straight lines 253a1 to 253a11 in a plan view. In the example of Fig. 16, outer peripheral surface 253a of cylindrical inner wall portion 253 is configured with eleven straight lines 253a1, 253a2, 253a3, 253a4, 253a5, 253a6, 253a7, 253a8, 253a9, 253a10, and 253a11, which are connected to form a substantially spiral shape.

[0080] In the example of Figure 16, outer peripheral surface 253a of cylindrical inner wall portion 253, i.e., inner peripheral surface 251i of oil groove 251, is composed of multiple straight lines 253a1 to 253a11, so that the radial width W3 of oil groove 251 changes in the intermediate portion between starting end 253e1 and terminal end 253e2 of oil groove 251.

[0081] 16 , the radial width W3 of the intermediate portion of oil groove 251 is narrower at the connection position between the straight lines constituting outer circumferential surface 253a of cylindrical inner wall portion 253 than at the intermediate positions of the straight lines. The radial width W3 of oil groove 251 is wider than the maximum width at the intermediate portion in a portion of oil groove 251 formed on the outer circumferential side of starting end 253e1 of cylindrical inner wall portion 253, and is narrower than the minimum width at the intermediate portion in a portion of oil groove 251 formed on the outer circumferential side of terminal end 253e2 of cylindrical inner wall portion 253. By repeatedly increasing and decreasing the radial width W3 of oil groove 251 in the circumferential direction of the intermediate portion of oil groove 251 in this manner, the sliding surfaces can be more uniformly lubricated in the circumferential direction than in the first embodiment, in which the radial width W1 is constant in the circumferential direction of the intermediate portion of oil groove 251.

[0082] As in the case of embodiment 1, the scroll compressor 100 of embodiment 3 can also supply lubricating oil to the outer peripheral portion while suppressing an increase in the sliding surface pressure between the oscillating base plate 2a and the fixed scroll 201, thereby achieving the effect of suppressing seizure in the outer peripheral portion.

[0083] In scroll compressor 100 according to the third embodiment, outer peripheral surface 253a of cylindrical inner wall portion 253 is formed of a plurality of straight lines 253a1 to 253a11. In the third embodiment, the degree of freedom in the shape of outer peripheral surface 253a of cylindrical inner wall portion 253 is increased compared to the first embodiment.

[0084] Fourth Embodiment Fig. 17 is a view of a fixed scroll 301 according to a fourth embodiment, viewed from below. The configuration of the fixed scroll 301 according to the fourth embodiment will be described with reference to Fig. 17. In the fourth embodiment, the shape of the outer peripheral surface 353a of the cylindrical inner wall portion 353 in the fixed scroll 301 differs from that in the first to third embodiments. Note that in the fourth embodiment, components having the same functions and actions as those in the first embodiment are denoted by the same reference numerals, and description thereof will be omitted.

[0085] 17 , in the fixed cylinder 350 of the fixed scroll 301 according to the fourth embodiment, as in the first embodiment, the outer peripheral surface 353a of the cylinder inner wall 353 forms part of the oil groove 351 (particularly the inner peripheral surface 351i of the oil groove 351), and the inner peripheral surface 53b of the cylinder inner wall 353 forms part of the compression chamber 1f. The inner peripheral surface 53b of the cylinder inner wall 353 is connected to the outer peripheral end of the fixed scroll 1b, and the inner peripheral surface 53b of the cylinder inner wall 353 and the inner surface 1bi of the fixed scroll 1b are smoothly connected to form a continuous involute curve. The outer peripheral surface 351o of the oil groove 351 has a cylindrical shape.

[0086] In the fourth embodiment, the outer peripheral surface 353a of the cylindrical inner wall portion 353 is configured with a plurality of curves 353a1 to 353a6 and a plurality of straight lines 353a7 to 353a11 in a plan view. The example in Fig. 17 shows an example in which the outer peripheral surface 353a of the cylindrical inner wall portion 353 is configured with six different arc-shaped curves 353a1, 353a2, 353a4, 353a5, and 353a6 and five straight lines 353a7, 353a8, 353a9, 353a10, and 353a11, which are connected to form a substantially spiral shape. Here, the term "curve" is a concept that also includes an involute shape.

[0087] 17 , outer peripheral surface 353a of cylindrical inner wall portion 353, i.e., inner peripheral surface 351i of oil groove 351, is configured to include a plurality of curves 353a1 to 353a6 and a plurality of straight lines 353a7 to 353a11, so that radial width W4 of oil groove 351 changes in the intermediate portion between starting end 353e1 and terminal end 353e2 of oil groove 351. It should be noted that outer peripheral surface 353a of cylindrical inner wall portion 353 may be formed by combining one or more curves and one or more straight lines.

[0088] 17 , outer peripheral surface 353a of cylindrical inner wall portion 353 is configured with straight lines and curved lines alternately connected in the circumferential direction, and radial width W4 is wider in the portion of oil groove 351 where straight lines 353a7 to 353a11 are arranged than in the portion of oil groove 351 where curved lines 353a1 to 353a6 are arranged. Radial width W4 of oil groove 351 is wider than the maximum width in the intermediate portion at a portion of oil groove 351 formed on the outer periphery of starting end 353e1 of cylindrical inner wall portion 353, and is narrower than the minimum width in the intermediate portion at a portion of oil groove 351 formed on the outer periphery of terminal end 353e2 of cylindrical inner wall portion 353. In this way, by configuring the radial width W4 of oil groove 251 to repeatedly expand and contract in the circumferential direction of the middle part of oil groove 351, the sliding surface can be lubricated more uniformly in the circumferential direction compared to the configuration in which the radial width W1 of oil groove 51 is constant in the circumferential direction of the middle part as in embodiment 1.

[0089] As in the case of embodiment 1, the scroll compressor 100 of embodiment 4 can also supply lubricating oil to the outer peripheral portion while suppressing an increase in the sliding surface pressure between the oscillating base plate 2a and the fixed scroll 301, thereby achieving the effect of suppressing seizure in the outer peripheral portion.

[0090] Furthermore, in scroll compressor 100 of embodiment 4, outer peripheral surface 353a of cylindrical portion inner wall portion 353 is formed by combining one or more curves (e.g., curves 353a1 to 353a6) and one or more straight lines (e.g., 353a7 to 353a11). In embodiment 4, the degree of freedom in the shape of outer peripheral surface 353a of cylindrical portion inner wall portion 353 is increased compared to embodiment 1.

[0091] 1 Fixed scroll, 1a Fixed base plate, 1b Fixed scroll, 1bi Inner surface, 1bo Outer surface, 1d Discharge port, 1e Intake port, 1f Compression chamber, 1fb Lower surface, 1x Fixed scroll, 2 Oscillating scroll, 2a Oscillating base plate, 2ao Outer peripheral end, 2b Oscillating scroll, 2bi Inner surface, 2bo Outer surface, 2c Oldham guide groove, 2d Boss portion, 2e Oscillating bearing, 2f Thrust surface, 2g Bleed hole, 2h Center, 2n Boss outer space, 3 Compliant frame, 3a Thrust bearing, 3c Main bearing, 3d Auxiliary main bearing, 3e Communication hole, 3g Intermediate pressure adjustment valve, 3h Intermediate pressure adjustment valve holder, 3k Intermediate pressure adjustment spring, 3n Intermediate pressure adjustment valve space, 3p Upper cylindrical surface, 3s Lower cylindrical surface, 3t Thrust bearing opening, 4 Guide frame, 4a frame upper space, 4b frame lower space, 4c upper cylindrical surface, 4d lower cylindrical surface, 4f first passage, 4g first discharge passage, 4h frame upper base plate, 4k Oldham guide groove, 5 electric motor, 5a rotor, 5b stator, 5f through passage, 5g second passage, 5h lead wire, 6 main shaft, 6a eccentric shaft portion, 6b main shaft portion, 6c counter shaft portion, 6d oil supply passage, 6e oil supply port, 6f main shaft balance weight, 6g oil supply hole, 7a ring-shaped seal material, 7b ring-shaped seal material, 8 subframe, 8a counter bearing, 8b inlet hole, 9 Oldham mechanism, 9a fixed side key, 9b swing side key, 9c Oldham mechanism annular portion, 10 sealed container, 10a upper space, 10b oil reservoir portion, 10c glass terminal, 11 Refrigerant oil, 12 discharge pipe, 13 suction pipe, 14 compression mechanism, 15a first balance weight, 15b second balance weight, 16 discharge cover, 16a second discharge passage, 16b opening, 17 first cup-shaped member, 17a opening, 18 second cup-shaped member, 30 refrigerant flow path, 50 fixed cylinder portion, 50x fixed cylinder portion, 51 oil supply groove, 51a bottom surface, 51ei inner peripheral end, 51eo outer peripheral end, 51i inner peripheral surface, 51o outer peripheral surface, 52 suction port, 53 cylinder inner wall portion, 53a outer peripheral surface, 53b inner peripheral surface, 54s step portion, 53e1 starting end, 53e2 terminal end, 53x wall portion, 54 cylinder outer wall portion, 60 revolution locus, 61 revolution diameter, 100 scroll compressor, 101 Fixed scroll, 150 fixed cylindrical portion, 151 oil supply groove, 151i inner peripheral surface, 151o outer peripheral surface, 153 cylindrical portion inner wall portion,153a outer peripheral surface, 153a1 to 153a4 curved line, 153e1 starting end, 153e2 terminal end, 201 fixed scroll, 250 fixed cylindrical portion, 251 oil supply groove, 251i inner peripheral surface, 251o outer peripheral surface, 253 cylindrical portion inner wall portion, 253a outer peripheral surface, 253a1 to 253a11 straight line, 253e1 starting end, 253e2 terminal end, 301 fixed scroll, 350 fixed cylindrical portion, 351 oil supply groove, 351i inner peripheral surface, 351o outer peripheral surface, 353 cylindrical portion inner wall portion, 353a outer peripheral surface, 353a1 to 353a6 curved line, 353a7 to 353a11 straight line, 353e1 starting end, 353e2 terminal end, 400 Refrigeration cycle device, 401 suction muffler, 403 four-way switching valve, 404 outdoor heat exchanger, 405 pressure reducer, 406 indoor heat exchanger, 501 fixed scroll, 550 fixed cylindrical portion, 551 oil supply groove, 551i inner peripheral surface, 551a bottom surface, 554 cylindrical outer wall portion, Df depth, Dr depth, R movable range, T1 thickness, T2 thickness, T2x thickness, W1 to W4 width.

Claims

1. A scroll compressor comprising: a fixed scroll having a fixed scroll body and a fixed cylinder portion arranged on the outer periphery of the fixed scroll body on one surface of a fixed base plate; and an oscillating scroll which revolves and has an oscillating scroll body on one surface of an oscillating base plate, the inner peripheral portion of the fixed cylinder portion and the fixed scroll body having an inner peripheral surface which forms a continuous spiral shape and meshes with the oscillating scroll body, and when the oscillating scroll revolves, the tip surface of the fixed scroll body and the tip surface of the fixed cylinder portion slide against the one surface of the oscillating base plate via lubricating oil, wherein an annular oil supply groove is formed in the tip surface of the fixed cylinder portion, and the radial thickness of the cylinder portion inner wall portion constituting the inner peripheral side of the fixed cylinder portion with the inner peripheral end of the oil supply groove as a boundary is configured to be thicker than the radial thickness of the fixed scroll body, the oscillating base plate and the oil supply groove of the fixed cylinder portion are arranged such that an outer contour of a movable range of the oscillating base plate due to the orbital motion of the oscillating scroll is located outer circumferentially further than the inner circumferential end of the oil supply groove, and the outer circumferential end of the oscillating base plate is sometimes located inner circumferentially further than the outer circumferential end of the oil supply groove during the orbital motion of the oscillating scroll.

2. The scroll compressor according to claim 1, wherein the radial thickness of the cylindrical inner wall portion is configured to be equal to or smaller than the orbital diameter of the orbiting scroll.

3. A scroll compressor as claimed in claim 1 or 2, wherein the outer peripheral surface of the inner wall of the cylindrical portion forms an involute curve.

4. A scroll compressor as claimed in claim 1 or 2, wherein the outer peripheral surface of the inner wall of the cylindrical portion is formed by a plurality of curved lines or a plurality of straight lines.

5. A scroll compressor as claimed in claim 1 or 2, wherein the outer peripheral surface of the inner wall portion of the cylindrical portion is formed by combining one or more curves and one or more straight lines.

6. A scroll compressor as claimed in any one of claims 1 to 5, wherein a compression chamber whose volume changes with the orbital motion of the oscillating scroll is formed between the oscillating scroll and the inner peripheral surface of the fixed cylinder and the fixed scroll forming the continuous spiral shape, and a suction port is formed in the fixed cylinder for drawing refrigerant into the compression chamber, and the compression chamber and the oil supply groove are connected by the suction port.

7. A scroll compressor according to any one of claims 1 to 6, wherein a bottom surface of the oil groove is located closer to said one surface of the oscillating base plate than to said one surface of the fixed base plate.

8. A refrigeration cycle device comprising the scroll compressor according to any one of claims 1 to 7, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger.

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