Scroll compressor

Abstract

This scroll compressor has: a crank shaft having an oil passage through which a lubricating oil flows; a swing scroll attached to the crank shaft and having a disk-shaped swing substrate, a swing spiral protrusion which is provided on one surface of the swing substrate, and a boss part which has an internal space contiguous to an oil passage of the crank shaft, and which is provided on the other side of the swing substrate and fits an upper end part of the crank shaft; a fixation scroll having a disk-shaped fixation substrate which is disposed so as to face the swing substrate, and a fixation spiral protrusion which is provided on the fixation substrate and which engages with the swing spiral protrusion of the swing scroll; a mainframe to which the fixation scroll is fixed, and which has a space for accommodating the swing scroll and a thrust surface on which the other surface of the swing substrate slides; and an Oldham ring having a protrusion part for preventing rotation of the swing scroll. An Oldham groove, which accommodates the protrusion part of the Oldham ring and which has a wall surface where the protrusion part of the Oldham ring slides, is formed in the swing substrate of the swing scroll. Inside the swing substrate of the swing scroll, an internal flow path connecting the internal space of the boss part and the wall surface is formed.

Description

Scroll Compressor

[0001] The present disclosure relates to a scroll compressor, and more particularly to an oil supply structure in a scroll compressor.

[0002] In a scroll compressor, the orbiting scroll revolves around the fixed scroll, compressing the refrigerant in a compression space defined by the spiral teeth of the fixed scroll and the orbiting scroll. The orbiting scroll is housed in a main frame, and an Oldham ring is provided between the orbiting scroll and the main frame as a mechanism for preventing the orbiting scroll from rotating relative to the main frame.

[0003] A protrusion is formed on the Oldham ring, and Oldham grooves for accommodating the protrusion of the Oldham ring are formed on the opposite side of the surface of the orbiting scroll having the spiral protrusion, i.e., the wrap, and on the bottom surface of the main frame that accommodates the orbiting scroll. Two Oldham grooves are formed on the main frame at opposing positions. Two Oldham grooves are formed on the orbiting scroll at opposing positions on a line perpendicular to the line connecting the two Oldham grooves on the main frame.

[0004] Therefore, the Oldham ring can reciprocate in a predetermined direction due to the Oldham groove of the main frame. Furthermore, while the orbiting scroll reciprocates together with the Oldham ring, it can also reciprocate in a direction perpendicular to the predetermined direction in which the Oldham ring reciprocates due to the Oldham groove and the Oldham ring protrusion. In other words, by disposing the Oldham ring between the main frame and the orbiting scroll, the orbiting scroll is prevented from rotating on its axis, but is allowed to revolve.

[0005] Because the Oldham ring protrusions and the Oldham grooves of the main frame and orbiting scroll slide against each other during reciprocating motion, it is necessary to supply lubricating oil to the Oldham grooves to prevent seizure, etc. A common method of supplying lubricating oil in scroll compressors is to collect lubricating oil sucked up by an oil pump through an oil passage in the crankshaft in the space between the main frame and the orbiting scroll.

[0006] However, if operation is started without lubricating oil in the space, such as during a test run or when starting up after a long shutdown, oil cannot be supplied to the Oldham groove until the lubricating oil is stored in the space. This increases the friction coefficient, which increases the compressor's input value and reduces performance, and can lead to compressor failure due to seizure of the Oldham groove and Oldham ring protrusions. In particular, because the Oldham groove of the orbiting scroll is located at the highest position in the space where lubricating oil is stored, it takes time for lubricating oil to be supplied after operation starts.

[0007] As a means for solving this problem, Patent Document 1 discloses a method in which a boss portion of an orbiting scroll that fits onto the upper end portion of the crankshaft communicates with the Oldham groove through an oil supply hole, thereby supplying lubricating oil that has passed through the crankshaft directly to the Oldham groove.

[0008] Japanese Patent Application Laid-Open No. 2008-138572

[0009] In an Oldham groove, the location where the Oldham ring protrusion slides during operation is the wall surface portion on the side surface of the Oldham groove, and it is important to improve the lubrication of this portion. However, in the structure of Patent Document 1, lubricating oil is discharged from one end of the Oldham groove of the orbiting scroll, which is closer to the center of the base plate, so there is a possibility that sufficient lubricating oil cannot be supplied to the wall surface portion. If sufficient lubricating oil cannot be supplied to the wall surface portion, performance will decrease due to an increased friction coefficient, or the reliability of the compressor will decrease due to seizure.

[0010] An object of the present disclosure is to provide a scroll compressor that can suppress a decrease in reliability due to a shortage of lubricating oil supply.

[0011] The scroll compressor according to the present disclosure comprises: a crankshaft having an oil passage through which lubricating oil flows; an orbiting scroll attached to the crankshaft and having a disk-shaped oscillating base plate; an orbiting spiral protrusion provided on one surface of the oscillating base plate; and a boss portion provided on the other surface of the oscillating base plate, which fits with an upper end of the crankshaft and has an internal space communicating with the oil passage of the crankshaft; a disk-shaped fixed base plate disposed opposite the oscillating base plate; and a fixed spiral protrusion provided on the fixed base plate which meshes with the orbiting spiral protrusion of the orbiting scroll. and an Oldham ring having a protrusion that prevents the orbiting scroll from rotating about its axis, the orbiting base plate of the orbiting scroll having a fixed scroll having a boss portion, a space that accommodates the orbiting scroll, and a thrust surface against which the other surface of the orbiting base plate slides. An Oldham groove is formed in the orbiting base plate of the orbiting scroll, the Oldham groove having a wall surface against which the protrusion of the Oldham ring slides, and an internal flow path that connects the internal space of the boss portion and the wall surface is formed inside the orbiting base plate of the orbiting scroll.

[0012] In the scroll compressor according to the present disclosure, the internal flow path of the orbiting scroll supplies lubricating oil to the wall surface of the Oldham groove, where the Oldham ring protrusion slides, thereby suppressing performance degradation or seizure of the scroll compressor and reducing deterioration in reliability.

[0013] FIG. 1 is a schematic vertical cross-sectional view of a scroll compressor according to a first embodiment of the present disclosure. FIG. 2 is an exploded perspective view of a scroll compressor according to a first embodiment of the present disclosure. FIG. 3 is a plan view of the internal structure of an orbiting scroll according to a first embodiment of the present disclosure, viewed from the other end side. FIG. 4 is a cross-sectional view showing the internal structure of an orbiting scroll according to a first embodiment of the present disclosure. FIG. 5 is a cross-sectional view showing the internal structure of an orbiting scroll according to a first embodiment of the present disclosure. FIG. 6 is a plan view illustrating the positional relationship between an internal flow path of an orbiting scroll according to a first embodiment of the present disclosure and a second Oldham groove. FIG. 7 is a plan view of a scroll compressor according to a modified example of the first embodiment of the present disclosure. FIG. 8 is a cross-sectional view showing the structure of an orbiting scroll of a scroll compressor according to a second embodiment of the present disclosure. FIG. 9 is a plan view of an orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure, viewed from the other end side. FIG. 10 is a cross-sectional view of an orbiting scroll of a scroll compressor according to a third embodiment of the present disclosure. 13 is a plan view of an orbiting scroll according to a sixth embodiment of the present disclosure as viewed from one end side;FIG.

[0014] A scroll compressor according to an embodiment of the present disclosure will be described below with reference to the drawings. In the following drawings, components with the same reference numerals are identical or equivalent and will be common throughout the following embodiments. The configurations of components shown throughout the specification are merely examples and are not intended to be limiting. The size relationships between components in the drawings may differ from the actual size relationships. In the present embodiment, directional terms (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate to facilitate understanding, but these terms are for explanatory purposes only and do not limit the present disclosure.

[0015] Embodiment 1. Fig. 1 is a schematic vertical cross-sectional view of a scroll compressor 100 according to embodiment 1 of the present disclosure. Fig. 2 is an exploded perspective view of the scroll compressor 100 according to embodiment 1 of the present disclosure. The scroll compressor 100 is a so-called vertical compressor that is used with the central axis of a crankshaft 6 (described below) positioned substantially perpendicular to the ground. In the following description, the upper side will be referred to as one end side U, and the lower side facing the ground will be referred to as the other end side L.

[0016] The scroll compressor 100 includes a shell 1, a main frame 2, a compression mechanism 3, a drive mechanism 4, a subframe 5, a crankshaft 6, a slider 7, and a power supply unit 8. Lubricating oil 9 is stored in the scroll compressor 100.

[0017] The shell 1 is a cylindrical housing made of a conductive material such as metal and closed at both ends. The shell 1 includes a main shell 11, a lower shell 12, and an upper shell 13. The main shell 11 is cylindrical and includes a suction pipe 111 on its side wall. The suction pipe 111 is a pipe that introduces refrigerant into the shell 1 and is connected to the inside of the main shell 11.

[0018] The lower shell 12 is a substantially hemispherical bottom body, and a portion of its side wall is connected to the lower end of the main shell 11 by welding or the like, thereby closing the opening on the lower side of the main shell 11. At least a portion of the inside of the lower shell 12 is used as an oil reservoir 121 that stores the lubricating oil 9.

[0019] The upper shell 13 is a substantially hemispherical lid, and a portion of its side wall is connected to the upper end of the main shell 11 by welding or the like, thereby closing the upper opening of the main shell 11. The upper shell 13 is provided with a discharge pipe 131 at its top.

[0020] The discharge pipe 131 is a pipe that discharges the refrigerant to the outside of the shell 1 and is in communication with the internal space of the main shell 11. The shell 1 is supported by a fixing base 122 that has a plurality of screw holes. The scroll compressor 100 is configured so that it can be fixed to another member, such as the housing of an outdoor unit, by screwing screws into the plurality of screw holes.

[0021] The main frame 2 is a hollow metal support member having an opening at one end side U, and is disposed inside the shell 1. The main frame 2 includes a main body 21, a main bearing 22, and an oil return pipe 23. The main body 21 is fixedly supported to the inner peripheral surface of the one end side U of the main shell 11 by shrink fitting, welding, or the like, and an accommodation space 211 is formed inside the main body 21 along the longitudinal direction of the shell 1. The accommodation space 211 is open at the one end side U, and has a stepped interior that gradually narrows toward the other end side L. As shown in FIG. 2 , a portion of the surface of the stepped portion facing the one end side U forms a ring-shaped thrust surface 212.

[0022] The main frame 2 has a refrigerant passage 213 in a portion of the outer circumferential side of the thrust surface 212 and in an inner wall surface of the main frame 2 that is continuous with that portion. The refrigerant passage 213 is a hole that provides spatial communication between the inside and outside of the main frame 2. A pair of refrigerant passages 213 are formed on either side of the axis of the crankshaft 6, for example, the central axis of a main shaft portion 61 described below, and are arranged to be aligned in a substantially straight line.

[0023] An Oldham arrangement portion 214 is formed in a part of the step portion closer to the other end side L than the thrust surface 212. A first Oldham groove 215 is formed in the Oldham arrangement portion 214. The first Oldham groove 215 is formed such that the outer end side thereof enters into a part of the inner peripheral side of the thrust surface 212 that is cut away. A pair of first Oldham grooves 215 are formed, and they are arranged so as to be aligned substantially in a straight line with the axis of the crankshaft 6 in between.

[0024] A thrust plate 216 made of a steel-based material and having a smaller surface roughness than the machined surfaces of typical iron parts is disposed on the thrust surface 212. The thrust plate 216 is ring-shaped and disposed on the thrust surface 212, thereby covering a portion of the refrigerant passage 213 and the first Oldham groove 215. Therefore, the thrust plate 216 functions as a thrust bearing.

[0025] The main bearing portion 22 is formed continuously with the other end side L of the body portion 21, and has a shaft through-hole 221 formed therein. The shaft through-hole 221 passes through the main bearing portion 22 in the vertical direction, and one end side U communicates with the accommodation space 211. The oil return pipe 23 is a pipe for returning the lubricating oil 9 accumulated in the accommodation space 211 to the oil reservoir 121 of the lower shell 12.

[0026] The lubricating oil 9 is, for example, a refrigeration oil containing an ester-based synthetic oil. The lubricating oil 9 is stored in the oil reservoir 121 of the lower shell 12 and passes through the oil passage 63 of the crankshaft 6 to reduce wear between parts that come into mechanical contact with each other, adjust the temperature of sliding parts, or improve sealing performance. An oil having excellent lubrication properties, electrical insulation properties, stability, refrigerant solubility, or low-temperature fluidity, as well as an appropriate viscosity, is suitable for the lubricating oil 9.

[0027] The compression mechanism 3 is a compression mechanism that compresses the refrigerant and includes a fixed scroll 31 and an orbiting scroll 32.

[0028] The fixed scroll 31 is made of a metal such as aluminum or cast iron, and includes a first base plate 311 and a first spiral body 312. The first base plate 311 is disk-shaped, and its outer end is disposed in contact with the main body 21 and is fixed to the main frame 2 with screws or the like. The first spiral body 312 protrudes from the other end surface 3112 of the first base plate 311 to form a spiral wall, with its tip facing the other end side L. The first base plate 311 is an example of a fixed base plate, and the first spiral body 312 is an example of a fixed spiral protrusion.

[0029] The orbiting scroll 32 is made of a metal such as aluminum or cast iron and includes a second base plate 321, a second scroll 322, a boss portion 323, and a second Oldham groove 324. The second base plate 321 is disk-shaped and is supported by the main frame 2 so that at least a portion of the outer circumferential region of the other end surface 3212 is slidable on the thrust plate 216. The second scroll 322 protrudes from one end surface 3211 of the second base plate 321 to form a scroll-shaped wall, and its tip is provided to face the one end side U. Note that sealing members are provided at the tips of the first scroll 312 and the second scroll 322 to prevent refrigerant leakage.

[0030] Boss portion 323 is provided on other end surface 3212 of second substrate 321, and is a cylindrical boss formed to protrude from approximately the center of other end surface 3212 of second substrate 321 toward other end side L. Second substrate 321 is an example of an oscillating substrate, and second spiral body 322 is an example of an oscillating spiral protrusion.

[0031] The second Oldham groove 324 is formed on the other end surface 3212 of the second base plate 321. The second Oldham groove 324 is an oval groove. A pair of the second Oldham grooves 324 are formed on either side of the axis of the crankshaft 6, and are arranged to be aligned in a substantially straight line.

[0032] An Oldham ring 33 is provided in the Oldham arrangement portion 214 of the main frame 2. The Oldham ring 33 includes a ring portion 331, a first protrusion 332, and a second protrusion 333. The ring portion 331 is ring-shaped and is disposed in a space formed between the main frame 2 and the second base plate 321 of the orbiting scroll 32. A pair of first protrusions 332 are formed opposite each other on the surface of the other end side L of the ring portion 331. A pair of second protrusions 333 are formed opposite each other on the surface of one end side U of the ring portion 331. The pair of first protrusions 332 are received in the pair of first Oldham grooves 215, and the pair of second protrusions 333 are received in the pair of second Oldham grooves 324.

[0033] Furthermore, the first protrusion 332 of the Oldham ring 33 has a first protrusion load surface 3321 and a first protrusion counter-load surface 3322 on the reverse side thereof. The first Oldham groove 215 has a first Oldham groove load surface 2151 and a first Oldham groove counter-load surface 2152 on the wall surface in contact with the first protrusion load surface 3321 and the first protrusion counter-load surface 3322, respectively. Similarly, the second protrusion 333 has a second protrusion load surface 3331 and a second protrusion counter-load surface 3332. The second Oldham groove 324 has a second Oldham groove load surface 3241 and a second Oldham groove counter-load surface 3242 on the wall surface in contact with the second protrusion load surface 3331 and the second protrusion counter-load surface 3332, respectively.

[0034] The first protrusion-loaded surface 3321 and the second protrusion-loaded surface 3331 are surfaces along which the orbiting scroll 32 slides while receiving a force that causes the orbiting scroll 32 to rotate on its axis during operation. The first protrusion-loaded surface 3321 and the second protrusion-loaded surface 3331 are surfaces that receive a counterclockwise force that causes the orbiting scroll 32 to rotate on its axis during operation in the scroll compressor 100. The first protrusion-loaded surface 3321 and the second protrusion-loaded surface 3331 are locations at which wear or seizure is particularly likely to occur in the first protrusion 332 and the second protrusion 333 of the Oldham ring 33 and in the first Oldham groove 215 and the second Oldham groove 324.

[0035] The first scroll 312 and the second scroll 322 mesh with each other to form a compression space 34. The compression space 34 is composed of multiple spaces whose volume decreases radially inward. Refrigerant is taken in through the scrolls located at the outer end and gradually compressed as the orbiting scroll 32 revolves. The compression space 34 communicates with a discharge port 313 formed through the center of the first base plate 311 of the fixed scroll 31, and the compressed refrigerant is discharged from the discharge port 313. A discharge valve 35 and a muffler 36 are each fixed to the surface of one end side U of the fixed scroll 31 with screws or the like. The discharge valve 35 opens and closes the discharge port 313 at a predetermined opening and timing to prevent backflow of the refrigerant. The muffler 36 has an exhaust hole 361 and covers the discharge port 313 and the discharge valve 35. The dimensions of the gap between the first base plate 311 and the tip of the second scroll 322 and the dimensions of the gap between the second base plate 321 and the tip of the first scroll 312 are each adjusted to be appropriate by the thrust plate 216. The thickness of the thrust plate 216 is calculated, for example, during assembly by measuring the height of the orbiting scroll 32, the fixed scroll 31, or the main frame 2. This prevents the scroll from coming into contact with the base plate due to thermal expansion of the scroll during operation, or prevents an increase in the amount of refrigerant leaking through the gap from the compression space 34 during refrigerant compression, thereby reducing operating efficiency.

[0036] The refrigerant may be, for example, a halogenated hydrocarbon having a carbon-carbon double bond, a halogenated hydrocarbon having no carbon-carbon double bond, a hydrocarbon, or a mixture thereof. The halogenated hydrocarbon having a carbon-carbon double bond is an HFO refrigerant or a fluorocarbon-based low GWP refrigerant with a zero ozone depletion potential, and has the chemical formula C ３ H ２ F ４ Examples of halogenated hydrocarbons that do not have a carbon-carbon double bond include tetrafluoropropenes such as HFO1234yf, HFO1234ze, and HFO1243zf, which are represented by the following formula: ２ F ２Examples of suitable refrigerants include refrigerants containing R32 (difluoromethane), R41, etc. Examples of suitable hydrocarbons include natural refrigerants such as propane and propylene. Examples of suitable mixtures include refrigerant mixtures containing HFO1234yf, HFO1234ze, HFO1243zf, etc., mixed with R32, R41, etc.

[0037] The drive mechanism 4 is provided on the other end side L of the main frame 2 inside the shell 1. The drive mechanism 4 includes a stator 41 and a rotor 42. The stator 41 is a ring-shaped stator formed by winding a winding around an iron core made of, for example, multiple laminated electromagnetic steel sheets, with an insulating layer interposed between them. The stator 41 is supported by having its outer periphery fixed to the inside of the main shell 11 by shrink fitting or the like. The rotor 42 is a cylindrical rotor that incorporates a permanent magnet inside an iron core made of multiple laminated electromagnetic steel sheets and has a through-hole that passes through it in the vertical direction in the center. The rotor 42 is disposed in the internal space of the stator 41.

[0038] The subframe 5 is a metal support member. The subframe 5 is provided inside the shell 1 on the other end side L of the drive mechanism 4. The subframe 5 is fixed to and supported by the inner circumferential surface of the other end side L of the main shell 11 by shrink fitting, welding, or the like. The subframe 5 includes an auxiliary bearing 51 and an oil pump 52. The auxiliary bearing 51 is a ball bearing provided on the upper central side of the subframe 5 and has a hole penetrating vertically in the center. The oil pump 52 is provided on the lower central side of the subframe 5 and is positioned so that at least a portion of it is immersed in the lubricating oil 9 stored in the oil sump 121 of the shell 1.

[0039] The crankshaft 6 is a long, rod-shaped member made of metal and is provided inside the shell 1. The crankshaft 6 includes a main shaft portion 61, an eccentric shaft portion 62, and an oil passage 63. The main shaft portion 61 has its outer surface press-fitted into a through hole in the rotor 42 and is disposed so that its central axis coincides with the central axis of the main shell 11. The eccentric shaft portion 62 is provided at one end U of the main shaft portion 61 so that its central axis is eccentric with respect to the central axis of the main shaft portion 61. The oil passage 63 is provided to penetrate vertically through the main shaft portion 61 and the eccentric shaft portion 62. The eccentric shaft portion 62 at one end U of the crankshaft 6 is inserted and fixed inside the cylindrical boss portion 323, and the other end L is inserted and fixed in the auxiliary bearing portion 51 of the sub-frame 5. As a result, the crankshaft 6 is positioned inside the stator 41 with the main shaft portion 61 located within the main bearing portion 22 of the main frame 2 and the outer surface of the rotor 42 maintaining a predetermined gap between it and the inner surface of the stator 41.

[0040] The slider 7 is a member that connects the orbiting scroll 32 and the crankshaft 6. The slider 7 is a cylindrical member made of a metal such as iron, and is fitted into the eccentric shaft portion 62 and the boss portion 323, respectively.

[0041] The power supply unit 8 is a power supply member that supplies power to the scroll compressor 100, and is formed on the outer peripheral surface of the main shell 11 of the shell 1. The power supply unit 8 includes a cover 81, a power supply terminal 82, and wiring 83. The cover 81 is a cover member with an opening at a bottom. The power supply terminal 82 is made of a metal member, and one end is provided inside the cover 81 and the other end is provided inside the shell 1. One end of the wiring 83 is connected to the power supply terminal 82, and the other end is connected to the stator 41.

[0042] Next, the structure of the orbiting scroll 32, which is a feature of the first embodiment, will be described in more detail with reference to FIGS. 3 to 5. FIG. 3 is a plan view of the internal structure of the orbiting scroll 32 according to the first embodiment of the present disclosure, as viewed from the other end side L. FIG. 4 is a cross-sectional view showing the internal structure of the orbiting scroll 32 according to the first embodiment of the present disclosure, taken along line A-O-A in FIG. 3. FIG. 5 is a cross-sectional view showing the internal structure of the orbiting scroll 32 according to the first embodiment of the present disclosure, taken along line B-B in FIG.

[0043] 3 to 5 , the orbiting scroll 32 has an internal flow passage 325. The internal flow passage 325 is a flow passage formed in the second base plate 321, connecting the inside of the boss portion 323 and the wall surface of the second Oldham groove 324. The internal flow passage 325 is further composed of a first internal flow passage 3251 and a second internal flow passage 3252.

[0044] A thick-walled portion 3213 having a truncated cone shape whose diameter gradually decreases toward the other end L is formed within the boss portion 323 at the inner end of the first internal flow path 3251. The thick-walled portion 3213 has the effect of ensuring the strength of the center portion of the second substrate 321 where pressure increases due to compression of the refrigerant, and the effect of smoothly guiding the lubricating oil 9 sucked up by the crankshaft 6 into the first internal flow path 3251 via its inclined surface.

[0045] The first internal flow path 3251 and the second internal flow path 3252 are formed along the other end surface 3212 of the second substrate 321. "Along the other end surface 3212" means that it is optimal for them to be parallel to the other end surface 3212, but it is also acceptable for them to be inclined at about ±10° with respect to the other end surface 3212.

[0046] Plug members 326 are inserted into the flow paths constituting the internal flow path 325 at the locations where they connect to the side surface of the second substrate 321. The plug members 326 corresponding to the first internal flow path 3251 and the second internal flow path 3252 are referred to as the first plug member 3261 and the second plug member 3262, respectively. The plug members 326 are, for example, metal screws made of a material with a linear expansion coefficient close to that of the fixed scroll 31 and the orbiting scroll 32. The plug members 326 are inserted and fixed by being screwed into thread grooves formed in the internal flow path 325, sealing one end of each of the first internal flow path 3251 and the second internal flow path 3252. As a result, the internal flow path 325 functions as an oil supply path that guides the lubricating oil 9 accumulated in the boss portion 323 to the second Oldham groove 324 via the first internal flow path 3251 and the second internal flow path 3252.

[0047] Fig. 6 is a plan view illustrating the positional relationship between the internal flow passage 325 and the second Oldham groove 324 of the orbiting scroll 32 according to the first embodiment of the present disclosure. In Fig. 6, a sliding range α is a range in which the second protrusion 333 slides when the Oldham ring 33 reciprocates during operation. In Fig. 6, an angle β is the smaller of the angles formed between the central axes of the first internal flow passage 3251 and the second internal flow passage 3252. In Fig. 6, a shaded area C is a space in the internal flow passage 325 that does not function as a flow passage and in which the plug member 326 is not disposed.

[0048] 6 , the other end of the second internal flow passage 3252 is connected to the second Oldham groove load surface 3241. As described above, the second protrusion load surface 3331 is a location where wear or seizure is particularly likely to occur. The internal flow passage 325 allows the lubricating oil 9 in the boss portion 323 to be directly supplied to the second protrusion load surface 3331, thereby improving lubrication and preventing wear or seizure.

[0049] Furthermore, it is desirable that the other end of the second internal flow passage 3252 is located within the sliding range α of the second protrusion 333 of the Oldham ring 33. By arranging the other end of the second internal flow passage 3252 within the sliding range α, the lubricating oil 9 discharged from the other end of the second internal flow passage 3252 automatically spreads over the entire second Oldham groove loaded surface 3241 along with the sliding of the second protrusion 333, thereby enabling efficient lubrication. Furthermore, it is desirable that the other end of the second internal flow passage 3252 is located on the side of the sliding range α that is closer to the side surface of the orbiting scroll 32. A portion of the lubricating oil 9 discharged from the other end of the second internal flow passage 3252 is scattered from the second Oldham groove 324 to the other end surface 3212 of the second base plate 321 due to the reciprocating motion of the second protrusion 333. In this case, the closer the other end of the second internal flow path 3252 is to the side of the oscillating scroll 32, the more oil will be splashed onto the part of the other end face 3212 that comes into contact with the thrust plate 216, i.e., the sliding part, or onto the thrust plate 216, thereby efficiently improving the lubrication of the sliding part.

[0050] Furthermore, if the angle β is reduced, the pressure loss increases when the lubricating oil 9 flowing through the internal flow path 325 turns, which may result in a delay in oil supply to the second Oldham groove loaded surface 3241. Therefore, it is desirable to arrange the first internal flow path 3251 and the second internal flow path 3252 so that the angle β is as large as possible.

[0051] As described above, the hatched area C is a space in the internal flow path 325 that does not function as a flow path and in which the plug member 326 is not disposed. A portion of the lubricating oil 9 flowing through the internal flow path 325 remains in the space of the hatched area C, and the amount of retained lubricating oil 9 increases as the volume of the space increases. Therefore, if the space of the hatched area C is increased, the ratio of the amount of oil discharged from the internal flow path 325 to the second Oldham groove 324 decreases relative to the amount of oil flowing from the boss portion 323 into the internal flow path 325, and there is a possibility that the oil may not be sufficiently supplied. Therefore, it is desirable to determine the arrangement of the internal flow path 325 and the length of the plug member 326 so that the space of the hatched area C is minimized as much as possible.

[0052] Next, the operation of the scroll compressor 100 will be described. When current is applied to the power supply terminal 82 of the power supply unit 8, torque is generated in the stator 41 and the rotor 42, causing the crankshaft 6 to rotate. The rotation of the crankshaft 6 is transmitted to the orbiting scroll 32 via the eccentric shaft portion 62 and the slider 7, and the orbiting scroll 32 performs eccentric orbital motion while its rotation is suppressed by the Oldham ring 33.

[0053] Refrigerant drawn into the shell 1 through the suction pipe 111 passes through the refrigerant passage 213 of the main frame 2 and is taken into the compression space 34. The refrigerant then moves from the outer periphery toward the center as the orbiting scroll 32 revolves eccentrically, reducing its volume and compressing it. During the eccentric orbital motion of the orbiting scroll 32, the orbiting scroll 32 moves radially together with the slider 7 due to its own centrifugal force, bringing the second volute 322 and the first volute 312 into close contact. This prevents refrigerant leakage from the high-pressure side to the low-pressure side in the compression space 34, enabling efficient compression. The compressed refrigerant is discharged from the discharge port 313 of the fixed scroll 31 against the discharge valve 35 and discharged to the outside of the shell 1 via the exhaust hole 361 of the muffler 36 and the discharge pipe 131.

[0054] When the orbiting scroll 32 orbits due to the rotation of the crankshaft 6, the lubricating oil 9 stored in the oil reservoir 121 of the shell 1 is sucked up by the oil pump 52. The lubricating oil 9 passes through the oil passage 63 of the crankshaft 6 and flows into a space between the tip of the eccentric shaft portion 62 and the boss portion 323, which is called an oil lift reservoir. The lubricating oil 9 that has flowed into the oil lift reservoir is supplied to sliding portions such as the slider 7, the main bearing portion 22, and the first Oldham groove 215, and a portion of the lubricating oil passes through the inside of the boss portion 323 and flows into the internal flow path 325.

[0055] The lubricating oil 9 passes through the internal flow passage 325 and is discharged from the second Oldham groove loaded surface 3241 at a side closer to the side of the orbiting scroll 32 within the sliding range α, which is the movable range of the second protrusion 333 of the Oldham ring 33. The discharged lubricating oil 9 lubricates the second Oldham groove unloaded surface 3242 as the second protrusion 333 slides, and further lubricates the entire second Oldham groove 324. After that, the discharged lubricating oil 9 is returned to the oil reservoir 121 from the oil return pipe 23 via the accommodation space 211. Furthermore, part of the lubricating oil 9 discharged to the second Oldham groove loaded surface 3241 is scattered by the reciprocating motion of the second protrusion 333, lubricates the other end surface 3212 of the second base plate 321 or the thrust plate 216, and then is taken into the compression space 34 together with the refrigerant. The remaining part is returned to the oil reservoir 121 from the oil return pipe 23.

[0056] The lubricating oil 9 that has entered the compression space 34 lubricates the sliding parts between the fixed scroll 31 and the orbiting scroll 32 and acts as a seal to prevent refrigerant from leaking between the scroll body and the base plate, and is then discharged together with the refrigerant from the discharge pipe 131. The discharged lubricating oil 9 is separated from the refrigerant, for example, by an oil separator in the refrigeration cycle device, and then returned to the shell 1 by utilizing the flow of the refrigerant drawn in from the suction pipe 111.

[0057] By configuring the orbiting scroll 32 as described above, the lubricating oil 9 is supplied directly to the second Oldham groove loaded surface 3241. Therefore, even when the lubricating oil 9 is not stored in the oil reservoir 121, such as during a test run or when starting up after a long period of shutdown, the lubricating oil 9 is supplied to the second Oldham groove loaded surface 3241 in a short time, and wear or seizure due to an increase in the friction coefficient can be prevented.

[0058] Each component of the scroll compressor 100 may be made of metal, or alternatively, resin components may be used.

[0059] Furthermore, the thrust plate 216 is not essential, and the thrust surface 212 of the main frame 2 may be configured to slide against the orbiting scroll 32 .

[0060] Furthermore, the two first internal flow paths 3251 do not necessarily have to be arranged in a substantially straight line, and may be arranged at an angle as long as one end is connected to the side surface of the second substrate 321 and the other end is connected to the inside of the boss portion 323. The cross-sectional shapes of the first internal flow path 3251 and the second internal flow path 3252 are not limited to being perfect circles, and may be ellipses, flattened circles, or polygons.

[0061] Furthermore, the thick portion 3213 of the second substrate 321 may be omitted if the strength of the central portion of the second substrate 321 is sufficiently high and sufficient lubricating oil 9 can be supplied to the internal flow path 325 even without the thick portion 3213.

[0062] Furthermore, the plug member 326 may be omitted if there is no need to drill holes from the side surface of the orbiting scroll 32 when processing the internal flow path 325. For example, if the orbiting scroll 32 is molded from a resin material using a three-dimensional printer or the like, the plug member 326 is not necessary.

[0063] 7 is a plan view of a scroll compressor 100 according to a modification of the first embodiment of the present disclosure. As shown in FIG. 7 , the internal flow path 325 and the plug member 326 may be disposed on both the second Oldham groove loaded surface 3241 and the second Oldham groove anti-load surface 3242.

[0064] The internal flow passage 325 and the plug member 326 on the second Oldham groove anti-load surface 3242 side can have the same structure as those on the second Oldham groove loaded surface 3241 side. The internal flow passage 325 and the plug member 326 on the second Oldham groove anti-load surface 3242 side may be disposed in a position that is line-symmetrical with respect to the center line of the second Oldham groove 324 and the second Oldham groove loaded surface 3241 side, or may be disposed at a position that is not symmetrical.

[0065] The internal flow passage 325 may be arranged so as to be connected to at least the second Oldham groove load surface 3241, but by also arranging it on the second Oldham groove anti-load surface 3242, the amount of wear can be reduced.

[0066] In the scroll compressor 100 according to the first embodiment described above, the second base plate 321 of the orbiting scroll 32 has an internal flow passage 325 formed therein, which connects the boss portion 323 and the second Oldham groove loaded surface 3241, which is the wall surface of the second Oldham groove 324. The second Oldham groove loaded surface 3241 is a location where the second protrusion 333 of the Oldham ring 33 slides in the second Oldham groove 324. The internal flow passage 325 allows the lubricating oil 9 supplied from the crankshaft 6 to be directly supplied to the second Oldham groove loaded surface 3241, so that the lubricating oil 9 can be effectively supplied to the second Oldham groove loaded surface 3241, which is the sliding location.

[0067] The Oldham ring 33 is disposed, for example, between the orbiting scroll 32 and the main frame 2, and the second Oldham groove 324 is provided on the other end surface 3212 of the second base plate 321. Therefore, the first Oldham groove 215 is disposed in a position close to the accommodation space 211 in which the oil is stored, and the lubricating oil 9 can be easily supplied to the first Oldham groove 215.

[0068] Furthermore, the internal flow passage 325 allows the lubricating oil 9 to be directly supplied to the second Oldham groove loaded surface 3241, which is a surface that receives a force in a certain direction when the orbiting scroll 32 attempts to rotate. The second Oldham groove loaded surface 3241 is a location where wear or seizure is particularly likely to occur, but the provision of the internal flow passage 325 increases lubricity, making it possible to prevent wear or seizure.

[0069] Furthermore, the internal flow passage 325 is connected to a range of half of the side surface of the second base plate 321 of the second Oldham groove load surface 3241. The closer the end of the internal flow passage 325 is to the side surface of the orbiting scroll 32, the more likely the lubricating oil 9 discharged from the side surface of the second base plate 321 is to be scattered onto the sliding parts or the thrust plate 216 due to the reciprocating motion of the second protrusion 333, thereby effectively improving the lubrication of the sliding parts.

[0070] The orbiting scroll 32 also has a thick portion 3213 that protrudes from the other end surface 3212 of the second base plate 321 toward the tip of the boss portion 323. This ensures the strength of the central portion of the second base plate 321, where pressure increases due to compression of the refrigerant, and the inclined surface of the thick portion 3213 smoothly guides the lubricating oil 9 sucked up by the crankshaft 6 to the internal flow path 325.

[0071] Furthermore, a thrust plate 216 is provided between the thrust surface 212 of the main frame 2 and the other end surface 3212 of the second base plate 321 of the orbiting scroll 32, covering the area where the thrust surface 212 and the other end surface 3212 slide against each other. The thrust plate 216 covers a portion of the outer circumferential side of the thrust surface 212, as well as a portion of the refrigerant passage 213 and the first Oldham groove 215 provided on the inner wall surface of the main frame 2 that is continuous with that portion, and functions as a thrust bearing. The thrust plate 216 is sandwiched in the sliding portion between the orbiting scroll 32 and the main frame 2, thereby reducing friction during the orbiting scroll 32's revolving motion.

[0072] In addition, the orbiting scroll 32 is provided with a plug member 326 that seals the side end of the internal flow path 325, and when the plug member 326 is opened, the internal flow path 325 can function as an oil supply path that guides the lubricating oil 9 accumulated in the boss portion 323 to the second Oldham groove 324.

[0073] 8 is a cross-sectional view showing the structure of an orbiting scroll 32A of a scroll compressor 100 according to a second embodiment of the present disclosure. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be assigned the same reference numerals and description thereof will be omitted.

[0074] 8, the orbiting scroll 32A has a protrusion 3214A that protrudes toward the center on one end side U inside the boss portion 323. The protrusion 3214A acts as a resistance when the lubricating oil 9 sucked up by the crankshaft 6 flows into the internal flow path 325. In other words, the flow rate of the lubricating oil 9 flowing through the internal flow path 325 can be adjusted by the shape of the protrusion 3214A.

[0075] The lubricating oil 9 pumped up by the oil pump 52 flows through the oil passage 63 of the crankshaft 6 into the oil discharge sump, and some of the lubricating oil 9 flows into the internal flow path 325. In addition to the internal flow path 325, the oil passage 63 and the oil discharge sump are connected to passages and oil discharge pipes for supplying oil to each sliding part, and these are affected by the pressure state downstream of each passage. Therefore, the distribution of oil flowing through each passage is determined by the flow path resistance, and the flow rate is relatively higher in the direction of lower downstream pressure. If there is excess oil flowing through the internal flow path 325, the provision of the protrusion 3214A creates flow path resistance, increasing the pressure and reducing the amount of oil flowing into the internal flow path 325.

[0076] In the scroll compressor 100 according to the second embodiment described above, the boss portion 323 has a protruding portion 3214A that protrudes from the inside of the second base plate 321 toward the center of the boss portion 323. The protruding portion 3214A acts as a resistance to the lubricating oil 9 sucked up by the crankshaft 6 when it flows into the internal flow path 325, and can reduce the amount of oil flowing into the internal flow path 325. Therefore, even if the lubricating oil 9 is in excess, the amount of oil can be adjusted.

[0077] Embodiment 3. Figure 9 is a plan view of orbiting scroll 32B of scroll compressor 100 according to embodiment 3 of the present disclosure, as viewed from the other end side L. Figure 10 is a cross-sectional view of orbiting scroll 32B of scroll compressor 100 according to embodiment 3 of the present disclosure, taken along line A-O-A in Figure 9. In embodiment 3, differences from embodiment 1 or 2 will be mainly described, and the same parts as those in embodiment 1 or 2 will be assigned the same reference numerals and description thereof will be omitted.

[0078] 9 and 10 , the orbiting scroll 32B has a connecting hole 3215B in the other end surface 3212 of the second base plate 321 that is connected to the first internal flow path 3251. The connecting hole 3215B is formed so that the position where it connects to the first internal flow path 3251 is closer to the side surface than the position where the first internal flow path 3251 and the second internal flow path 3252 intersect. The connecting hole 3215B guides a portion of the lubricating oil 9 flowing through the internal flow path 325 to the other end surface 3212, thereby making it possible to supply the lubricating oil 9 not only to the second Oldham groove 324 but also between the second base plate 321 and the thrust plate 216.

[0079] The position where the connection hole 3215B and the first internal flow path 3251 connect is closer to the side than the intersection position of the first internal flow path 3251 and the second internal flow path 3252, and therefore the presence of the connection hole 3215B has little effect on the amount of oil flowing through the second internal flow path 3252. Furthermore, in order to supply sufficient lubricating oil 9 to both the connection hole 3215B and the second internal flow path 3252, the diameter of the first internal flow path 3251 may be larger than the diameters of the connection hole 3215B and the second internal flow path 3252.

[0080] The lubricity is more easily improved when the other end surface 3212 side of the connection hole 3215B is within or close to the range where the second substrate 321 and thrust plate 216 slide. Therefore, the connection hole 3215B is arranged diagonally with respect to the other end surface 3212 so that it can be accommodated within the range where the second substrate 321 and thrust plate 216 slide while avoiding interference with the attachment portion of the first plug member 3261. However, the connection hole 3215B may be arranged perpendicular to the other end surface 3212 as long as sufficient lubricity can be maintained within that range.

[0081] In the scroll compressor 100 according to the third embodiment described above, the internal flow path 325 is configured with a first internal flow path 3251 that communicates with the internal space of the boss portion 323 and a second internal flow path 3252 that communicates with the second Oldham groove loaded surface 3241. The first internal flow path 3251 has a connection hole 3215B that communicates with the other end surface 3212 of the second substrate 321, located closer to the side surface of the second substrate 321 than the intersection with the second internal flow path 3252. The connection hole 3215B guides a portion of the lubricating oil 9 flowing through the internal flow path 325 to the other end surface 3212 of the second substrate 321. Therefore, the lubricating oil 9 can be supplied not only to the second Oldham groove 324 but also between the second substrate 321 and the thrust plate 216.

[0082] Fourth Embodiment Figure 11 is a plan view of an orbiting scroll 32C of a scroll compressor 100 according to a fourth embodiment of the present disclosure, as viewed from the other end side L. Figure 12 is a cross-sectional view of an orbiting scroll 32C of a scroll compressor 100 according to a fourth embodiment of the present disclosure, taken along line A-O-A in Figure 11. In the fourth embodiment, differences from the first to third embodiments will be mainly described, and the same parts as those in the first to third embodiments will be denoted by the same reference numerals and description thereof will be omitted.

[0083] As shown in FIGS. 11 and 12 , the orbiting scroll 32C has an oil feed groove 3216C on the other end surface 3212 of the second substrate 321. The oil feed groove 3216C is a ring-shaped circumferential groove. The oil feed groove 3216C is connected to the connecting hole 3215B and is formed so as not to deviate from the range in which the second substrate 321 and the thrust plate 216 slide. The oil feed groove 3216C may be configured to surround the entire circumference or at least a portion of the range in which the second substrate 321 and the thrust plate 216 slide. The oil feed groove 3216C guides the lubricating oil 9 flowing from the connecting hole 3215B to the entire range in which the second substrate 321 and the thrust plate 216 slide, thereby further improving lubrication.

[0084] Since connection hole 3215B is machined after oil supply groove 3216C is machined, oil supply groove 3216C around connection hole 3215B is structured so that the width thereof is increased to allow the drill used to machine connection hole 3215B to be inserted obliquely. This structure may be omitted if no problems arise in machining connection hole 3215B. Although embodiment 4 requires more steps than embodiment 3, it can improve the lubrication in the sliding range between second substrate 321 and thrust plate 216 more effectively than embodiment 3.

[0085] The shape of the oil supply groove 3216C is not limited to a ring shape. Furthermore, the oil supply groove 3216C may be a groove that is interrupted midway by the second Oldham groove 324 or the like, as long as it is in a form that allows a sufficient amount of lubricating oil 9 to be supplied to the entire thrust bearing.

[0086] In scroll compressor 100 according to the fourth embodiment described above, connecting hole 3215B is connected to oil supply groove 3216C. This allows lubricating oil 9 flowing from connecting hole 3215B to be guided to the entire area where second substrate 321 and thrust plate 216 slide, further improving lubrication.

[0087] 13 is a cross-sectional view showing the structure of a first plug member 3261D of an orbiting scroll 32D according to a fifth embodiment of the present disclosure. In the fifth embodiment, differences from the first to fourth embodiments will be mainly described, and the same parts as those in the first to fourth embodiments will be assigned the same reference numerals and description thereof will be omitted.

[0088] 13 , the first plug member 3261D has a through hole 3263D in its center that connects the first internal flow path 3251 of the orbiting scroll 32D with the space outside it. The through hole 3263D discharges a portion of the lubricating oil 9 that passes from the boss portion 323 through the internal flow path 325 to the side surface of the second base plate 321. The lubricating oil 9 discharged from the through hole 3263D is further divided into oil that flows toward the other end surface 3212 and oil that rises toward the compression space 34, i.e., so-called oil rising. The lubricating oil 9 that flows toward the other end surface 3212 lubricates the area where the second base plate 321 and the thrust plate 216 slide in contact with each other as the orbiting scroll 32 revolves eccentrically.

[0089] The lubricating oil 9 that rises from the through hole 3263D toward the compression space 34 lubricates the sliding areas between the fixed scroll 31 and the orbiting scroll 32D or acts as a seal to prevent refrigerant leakage between the scroll body and the base plate. However, if too much lubricating oil 9 rises, it may migrate to the heat exchanger via the discharge pipe 131 of the shell 1 and stagnate, resulting in reduced heat exchange efficiency. On the other hand, if too little lubricating oil 9 is present, the amount of oil supplied to the sliding areas between the fixed scroll 31 and the orbiting scroll 32D decreases, resulting in insufficient lubrication or sealing. Therefore, it is desirable to adjust the diameter of the through hole 3263D to allow for adequate oil rise. The first plug member 3261D having the through hole 3263D may be applied to either one or both of the pair of first internal flow paths 3251. Furthermore, in order to supply sufficient lubricating oil 9 to both the through hole 3263D and the second internal flow path 3252, the diameter of the first internal flow path 3251 may be larger than the diameters of the through hole 3263D and the second internal flow path 3252.

[0090] In the scroll compressor 100 according to the fifth embodiment described above, the first plug member 3261D has a through hole 3263D formed therein, which connects the first internal flow path 3251 of the orbiting scroll 32D with the side surface of the second base plate 321. The through hole 3263D lubricates the sliding portions between the fixed scroll 31 and the orbiting scroll 32 and also provides a sealing function to prevent refrigerant from leaking between the first scroll body 312 and the second base plate 321, and between the second scroll body 322 and the first base plate 311.

[0091] Sixth Embodiment Figure 14 is a schematic vertical cross-sectional view of a scroll compressor 100 according to a sixth embodiment of the present disclosure. The sixth embodiment differs from the first embodiment in that the Oldham ring 33 is disposed between the fixed scroll 31E and the orbiting scroll 32E, in that the Oldham ring 33 is disposed between the orbiting scroll 32 and the main frame 2. The sixth embodiment will be described mainly with reference to the first to sixth embodiments, and the same components as those in the first to sixth embodiments will be designated by the same reference numerals and will not be described again. In other words, the basic configuration and operation of the scroll compressor 100 according to the sixth embodiment are the same as those of the scroll compressor 100 according to the first embodiment.

[0092] As shown in FIG. 14 , a pair of first Oldham grooves 215E are formed in the other end surface 3112 of the first base plate 311 of the fixed scroll 31E, and a first protrusion 332 of the Oldham ring 33 is accommodated therein. A pair of second Oldham grooves 324E are formed in one end surface 3211 of the second base plate 321 of the orbiting scroll 32E, and a second protrusion 333 of the Oldham ring 33 is accommodated therein. The ring portion 331 of the Oldham ring 33 slides between the first base plate 311 and the second base plate 321. By disposing the Oldham ring 33 between the fixed scroll 31E and the orbiting scroll 32E, the contact area between the other end surface 3212 of the second base plate 321 and the thrust surface 212 of the main frame 2 can be made larger than in the first embodiment. Furthermore, the load in the thrust direction due to the pressure of the refrigerant can be reduced. This is because the amount of carbon dioxide (CO ２ It is often used in compressors that use refrigerants with higher operating pressures than other refrigerants, such as refrigerants containing nitrous oxide (NOx).

[0093] Here, the structure of the orbiting scroll 32E, which is a feature of the sixth embodiment, will be described in more detail with reference to Fig. 15 and Fig. 16. Fig. 15 is a plan view of the orbiting scroll 32E according to the sixth embodiment of the present disclosure as viewed from one end side U. Fig. 16 is a cross-sectional view of the orbiting scroll 32E according to the sixth embodiment of the present disclosure, taken along line A-O-A in Fig. 15.

[0094] 15 and 16 , the second Oldham groove 324E is formed on one end surface 3211. Similar to the first embodiment, the second Oldham groove 324E has a second Oldham groove load surface 3241E and a second Oldham groove counter-load surface 3242E. Similarly to the first embodiment, the second Oldham groove load surface 3241E is prone to wear or seizure.

[0095] Similarly to the first embodiment, the orbiting scroll 32E includes an internal flow passage 325E connecting the boss portion 323 and the second Oldham groove loaded surface 3241E, and a plug member 326E. As a result, during operation, the lubricating oil 9 is directly supplied to the second Oldham groove loaded surface 3241E via the internal flow passage 325E. The lubricating oil 9 lubricates the entire second Oldham groove 324E as the second protrusion 333 of the Oldham ring 33 slides, and then spreads to the second base plate 321 or the side surface of the orbiting scroll 32E. The internal flow passage 325E includes a first internal flow passage 3251E and a second internal flow passage 3252E, and the plug member 326E includes a first plug member 3261E and a second plug member 3262E.

[0096] By providing the second Oldham groove 324E on the one end face 3211 of the orbiting scroll 32E, the scroll compressor 100 according to Embodiment 6 can also supply the lubricating oil 9 directly to the second Oldham groove loaded surface 3241E. Therefore, even if the lubricating oil 9 is not stored in the oil reservoir, the lubricating oil 9 is supplied to the second Oldham groove loaded surface 3241E in a short time, and wear or seizure due to an increase in the friction coefficient can be prevented.

[0097] According to the scroll compressor 100 according to the sixth embodiment described above, the Oldham ring 33 is disposed between the fixed scroll 31 and the orbiting scroll 32, and the second Oldham groove 324E is provided in one end surface 3211 of the second base plate 321. By disposing the Oldham ring 33 between the fixed scroll 31 and the orbiting scroll 32, the contact area between the other end surface 3212 of the second base plate 321 and the thrust surface 212 of the main frame 2 is increased, and the load in the thrust direction due to the pressure of the refrigerant can be reduced.

[0098] The present disclosure is not limited to the disclosure of the first to sixth embodiments, and various modifications are possible without departing from the spirit of the present disclosure. For example, in the first to sixth embodiments, the vertical low-pressure shell scroll compressor 100 has been described, but the present disclosure can also be applied to a horizontal or high-pressure shell scroll compressor 100. Furthermore, the first to sixth embodiments can be combined as appropriate.

[0099] REFERENCE SIGNS LIST 1 Shell, 2 Main frame, 3 Compression mechanism, 4 Drive mechanism, 5 Subframe, 6 Crankshaft, 7 Slider, 8 Power supply section, 9 Lubricating oil, 11 Main shell, 12 Lower shell, 13 Upper shell, 21 Main body section, 22 Main bearing section, 23 Oil return pipe, 31 Fixed scroll, 31E Fixed scroll, 32 Oscillating scroll, 32A Oscillating scroll, 32B Oscillating scroll, 32C Oscillating scroll, 32D Oscillating scroll, 32E Oscillating scroll, 33 Oldham ring, 34 Compression space, 35 Discharge valve, 36 Muffler, 41 Stator, 42 Rotor, 51 Sub-bearing section, 52 Oil pump, 61 Main shaft section, 62 Eccentric shaft section, 63 Oil passage, 81 Cover, 82 Power supply terminal, 83 Wiring, 100 Scroll compressor, 111 Suction pipe, 121 oil reservoir, 122 fixing base, 131 discharge pipe, 211 accommodation space, 212 thrust surface, 213 refrigerant passage, 214 Oldham arrangement portion, 215 first Oldham groove, 215E first Oldham groove, 216 thrust plate, 221 shaft through hole, 311 first base plate, 312 first scroll body, 313 discharge port, 321 second base plate, 322 second scroll body, 323 boss portion, 324 second Oldham groove, 324E second Oldham groove, 325 internal flow passage, 325E internal flow passage, 326 plug member, 326E plug member, 331 ring portion, 332 first protrusion portion, 333 second protrusion portion, 361 exhaust hole, 2151 first Oldham groove load surface, 2152 first Oldham groove anti-load surface, 3112 Other end surface, 3211 One end surface, 3212 Other end surface, 3213 Thick portion, 3214A Projecting portion, 3215B Connecting hole, 3216C Oil supply groove, 3241 Second Oldham groove load surface, 3241E Second Oldham groove load surface, 3242 Second Oldham groove anti-load surface, 3242E Second Oldham groove anti-load surface, 3251 First internal flow path, 3251E First internal flow path, 3252 Second internal flow path, 3252E Second internal flow path, 3261 First plug member, 3261D First plug member, 3261E First plug member, 3262 Second plug member, 3262E Second plug member, 3263D Through hole, 3321 First protrusion load surface, 3322 First protrusion anti-load surface, 3331 Second protrusion load surface, 3332 Second protrusion anti-load surface.

Claims

1. A crankshaft having an oil passage through which lubricating oil flows; an orbiting scroll attached to the crankshaft and having a disk-shaped oscillating base plate, an oscillating spiral protrusion provided on one surface of the oscillating base plate, and a boss portion provided on the other surface of the oscillating base plate, the boss portion engaging with the upper end of the crankshaft and having an internal space through which the oil passage of the crankshaft is communicated; a fixed scroll having a disk-shaped fixed base plate disposed opposite the oscillating base plate and a fixed spiral protrusion provided on the fixed base plate and meshing with the oscillating spiral protrusion of the oscillating scroll; a main frame to which the fixed scroll is fixed, the main frame having a space for accommodating the oscillating scroll and a thrust surface against which the other surface of the oscillating base plate slides; and an Oldham ring having a protrusion for preventing the oscillating scroll from rotating, wherein the protrusion of the Oldham ring is accommodated in the oscillating base plate of the oscillating scroll, and an Oldham groove having a wall surface against which the protrusion slides, an internal flow passage that connects the internal space of the boss portion and the wall surface is formed inside the orbiting base plate of the orbiting scroll.

2. The scroll compressor according to claim 1, wherein the wall surface of the Oldham groove has an Oldham groove load surface which is a surface that receives a force in a certain direction that causes the orbiting scroll to rotate, and the internal flow passage is connected to the Oldham groove load surface.

3. The scroll compressor according to claim 2, wherein the internal flow passage is connected to a half of the Oldham groove load surface on the side surface of the oscillating base plate.

4. A scroll compressor according to any one of claims 1 to 3, wherein the orbiting scroll has a thick portion protruding from the other surface of the orbiting base plate towards the tip of the boss portion.

5. A scroll compressor according to any one of claims 1 to 4, wherein the boss portion of the orbiting scroll has a protrusion that protrudes from the orbiting base plate side inside the boss portion toward the center of the boss portion.

6. A scroll compressor as claimed in any one of claims 1 to 5, wherein the internal flow path has a first internal flow path connected to the internal space of the boss portion, and a second internal flow path intersecting the first internal flow path and connected to the wall surface, and the first internal flow path has a connection hole connected to the other surface of the oscillating base plate, on the side surface side of the oscillating base plate relative to the intersection with the second internal flow path.

7. The scroll compressor according to claim 6, wherein said connection hole is connected to a range of the other surface of said oscillating base plate where said thrust surface of said main frame slides.

8. The scroll compressor according to claim 7, wherein said connecting hole is connected to an oil supply groove formed in said area and circumnavigating at least a portion of said area.

9. The scroll compressor according to claim 7 or 8, further comprising a thrust plate covering the range between the thrust surface of the main frame and the other surface of the oscillating base plate of the oscillating scroll.

10. A scroll compressor as claimed in any one of claims 1 to 9, wherein the internal flow passage penetrates a side surface of the oscillating base plate, and the oscillating scroll is provided with a plug member that seals the end of the internal flow passage on the side surface.

11. The scroll compressor according to claim 10, wherein the plug member has a through hole connecting the internal flow path and a space on the side surface of the oscillating base plate.

12. A scroll compressor as claimed in any one of claims 1 to 11, wherein the Oldham ring is disposed between the orbiting scroll and the main frame, and the Oldham groove is provided on the other surface of the orbiting base plate.

13. A scroll compressor according to any one of claims 1 to 11, wherein the Oldham ring is disposed between the fixed scroll and the orbiting scroll, and the Oldham groove is provided on one surface of the orbiting base plate.

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