Scroll compressor and air conditioner

Abstract

To provide a highly reliable scroll compressor or the like. 【Solution means】The scroll compressor includes a sealed container, a frame, a fixed scroll, a swivel scroll 22, a crankshaft 7, a main bearing 11 that rotatably supports an eccentric portion 7b with respect to the frame, and a swivel bearing 12 that rotatably supports a swivel shaft 22c with respect to the circumferential surface of an eccentric hole 71b. When the crankshaft 7 floats, the crankshaft 7 and the swivel scroll 22 are in contact with each other. An oil groove G2 or G3 is provided on one or both of a first contact surface that is a contact surface on the crankshaft 7 side and a second contact surface that is a contact surface on the swivel scroll 22 side. The oil grooves G2 and G3 are grooves that guide oil flowing out into the eccentric hole 71b through a through hole 7c of the crankshaft 7 toward the upper end of the main bearing 11.

Description

Technical Field

[0001] The present disclosure relates to a scroll compressor and an air conditioner.

Background Art

[0002] Regarding the structure of a scroll compressor, for example, the technology described in Patent Document 1 is known. That is, Patent Document 1 describes a scroll compressor having a double bearing structure in which an upper bearing installed on a bracket and a swing bearing installed in an eccentric hole overlap in the radial direction.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In Patent Document 1, as described above, a scroll compressor having a double bearing structure is described, but insufficient lubrication of the bearing when the crankshaft floats is not particularly considered, and there is room for improving reliability.

[0005] Therefore, an object of the present disclosure is to provide a highly reliable scroll compressor and the like.

Means for Solving the Problems

[0006] To solve the above problems, the scroll compressor according to the present disclosure includes a sealed container, a frame installed inside the sealed container, a fixed scroll having a spiral fixed wrap and fixed to the frame, and a spiral orbiting wrap that forms a compression chamber between the fixed wrap and has an orbiting shaft provided on the opposite side of the orbiting wrap with respect to the mirror plate. An orbiting scroll, a crankshaft having an eccentric portion provided with an eccentric hole fitted to the orbiting shaft, a first bearing that rotatably supports the eccentric portion with respect to the frame, and a second bearing that rotatably supports the orbiting shaft with respect to the peripheral surface of the eccentric hole. When the crankshaft floats, the crankshaft and the orbiting scroll are in contact with each other. An oil groove is provided on one or both of a first contact surface that is a contact surface on the crankshaft side and a second contact surface that is a contact surface on the orbiting scroll side. The oil groove is a groove that guides oil flowing out of the through hole of the crankshaft to the upper end of the first bearing through the eccentric hole. Further, the depth dimension of the eccentric hole is longer than the axial length of the turning axis. The first contact surface is the upper surface of the eccentric portion, the second contact surface is the portion of the lower surface of the platen that faces the eccentric portion, the oil groove is a radial groove that is recessed downward from the upper surface of the eccentric portion, the radially inner end of the oil groove is located at the edge of the eccentric hole, and the radially outer end of the oil groove is located at the outer peripheral edge of the upper surface of the eccentric portion. It was decided as follows. Other details will be described in the embodiments.

Effect of the Invention

[0007] According to the present disclosure, a highly reliable scroll compressor or the like can be provided.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14A

Figure 14B

Mode for Carrying Out the Invention

[0009] ≪First Embodiment≫ <Configuration of Scroll Compressor> FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to the first embodiment. The scroll compressor 100 is a device that compresses gaseous refrigerant. As shown in FIG. 1, the scroll compressor 100 includes a sealed container 1, a compression mechanism section 2, a frame 3, a thrust receiving section 4, a first resin ring 5, and a second resin ring 6. In addition to the above-described configuration, the scroll compressor 100 further includes a crankshaft 7, an oldham ring 8, balance weights 9, 10, a main bearing 11 (first bearing), a swivel bearing 12 (second bearing), a sub bearing 13, and a thrust bearing 14. Furthermore, the scroll compressor 100 includes an electric motor 15, an oil return pipe 16, a centrifugal pump 17, and legs 18.

[0010] The sealed container 1 is a metal container that houses members such as the compression mechanism section 2, the crankshaft 7, and the electric motor 15, and is substantially sealed. Oil for lubricating each sliding portion is enclosed in the sealed container 1 and stored as an oil sump R1 at the bottom of the sealed container 1. The sealed container 1 includes a cylindrical tube chamber 1a, a lid chamber 1b that closes the upper side of the tube chamber 1a, and a bottom chamber 1c that closes the lower side of the tube chamber 1a.

[0011] As shown in FIG. 1, the suction pipe P1 is fixed in a state of being inserted into the lid chamber 1b of the sealed container 1. The suction pipe P1 is a pipe that guides refrigerant to the suction chamber (not shown) of the compression mechanism section 2. Also, the discharge pipe P2 is fixed in a state of being inserted into the tube chamber 1a of the sealed container 1. The discharge pipe P2 is a pipe that guides the refrigerant compressed by the compression mechanism section 2 to the outside of the scroll compressor 100.

[0012] The compression mechanism section 2 is a mechanism that compresses the refrigerant as the crankshaft 7 rotates. The compression mechanism section 2 includes a fixed scroll 21 and a revolving scroll 22, and is disposed in the upper space within the sealed container 1. The fixed scroll 21 is a member that forms the compression chamber C1 together with the revolving scroll 22, and is fixed to the frame 3. More specifically, the fixed scroll 21 is fixed to the upper side of the main frame 31 with a plurality of bolts. As shown in FIG. 1, the fixed scroll 21 includes a base plate 21a, a support portion 21b, and a fixed wrap 21c, which are integrally formed.

[0013] The base plate 21a is a thick portion having a circular shape in plan view. The support portion 21b is a cylindrical portion that supports the base plate 21a, and extends downward from the peripheral edge of the base plate 21a. Note that the annular lower surface of the support portion 21b is a mirror surface that slides with the revolving scroll 22. The height position of this mirror surface is substantially equal to the height position of the tooth tip of the fixed wrap 21c. The fixed wrap 21c has a spiral shape and extends downward from the base plate 21a.

[0014] The revolving scroll 22 is a member that revolves as the crankshaft 7 rotates, and is disposed between the fixed scroll 21 and the frame plate 32. Also, the revolving scroll 22 is disposed so as to face the fixed scroll 21 in a state where its central axis is eccentric from the central axis of the fixed scroll 21 by a predetermined distance.

[0015] As shown in FIG. 1, the revolving scroll 22 includes a mirror plate 22a, a revolving wrap 22b, and a revolving shaft 22c, which are integrally formed. The mirror plate 22a is a portion that slides with the fixed scroll 21 and has a disk shape. The revolving wrap 22b has a spiral shape and extends upward from the mirror plate 22a. The revolving shaft 22c has a columnar shape and extends downward from the central portion of the back surface of the mirror plate 22a. That is, the revolving shaft 22c is provided on the side opposite to the revolving wrap 22b with respect to the mirror plate 22a. This revolving shaft 22c is fitted into the eccentric hole 71b of the crankshaft 7.

[0016] And a compression chamber C1 is formed between the spiral fixed wrap 21c and the spiral revolving wrap 22b. The compression chamber C1 is a space for compressing gaseous refrigerant, and is formed on each of the inner circumferential side and the outer circumferential side of the revolving wrap 22b. Near the center of the base plate 21a of the fixed scroll 21, a discharge port K1 is provided for guiding the refrigerant compressed in the compression chamber C1 to the discharge space C2 above the compression mechanism portion 2. The refrigerant discharged into the discharge space C2 through the discharge port K1 is guided to the motor chamber C3 below the compression mechanism portion 2 through a predetermined gap between the sealed container 1 and the compression mechanism portion 2.

[0017] The frame 3 is a metal member installed inside the sealed container 1, and is composed of a main frame 31 and a frame plate 32. The main frame 31 is a member for supporting the fixed scroll 21 and fixing the sub-bearing 13, and is fixed to the inner circumferential surface of the cylinder chamber 1a by welding or the like. The main frame 31 generally has a rotationally symmetric shape, and the diameters of the inner circumferential surface and the outer circumferential surface gradually decrease toward its lower end. Note that the lower part of the main frame 31 (the part including the installation location of the sub-bearing 13) is close to the intermediate part 71a of the crankshaft 7. An insertion hole 3a for inserting the crankshaft 7 is provided in the main frame 31. Further, an oil return hole 3b is provided in the main frame 31 in the lateral direction. An oil return pipe 16 is inserted into the oil return hole 3b.

[0018] The frame plate 32 is an annular member fitted inside the main frame 31. By providing such a frame plate 32, it becomes possible to arrange the balance weight 9 in the space between the main frame 31 and the frame plate 32 (the balance weight space A2 in FIG. 1).

[0019] As shown in Fig. 1, a thrust receiving portion 4 is provided at the lower end of the main frame 31. The thrust receiving portion 4 is a portion that receives an axial (thrust direction) force from the stepped surface 73a of the crankshaft 7 via the thrust bearing 14, and has an annular shape in plan view. The diameter of the inner peripheral edge of the thrust receiving portion 4 is shorter than the diameter of the intermediate portion 71a of the crankshaft 7. Further, the inner peripheral edge of the thrust receiving portion 4 is radially close to the peripheral surface of the small diameter portion 72a of the crankshaft 7. In the example of Fig. 1, the thrust receiving portion 4 is a separate member from the main frame 31, but it may be integrally formed with the main frame 31.

[0020] The first resin ring 5 is an annular resin member for sealing between the frame plate 32 and the mirror plate 22a of the turning scroll 22. The first resin ring 5 is installed in an annular groove V1 (see Fig. 4) provided on the upper end surface of the frame plate 32. Note that a leaf spring N1 (not shown in Fig. 1, see Fig. 4) for pushing up the first resin ring 5 upward (toward the turning scroll 22 side) is installed at the bottom of the groove V1. The second resin ring 6 is an annular resin member for sealing between the main frame 31 and the frame plate 32. The second resin ring 6 is installed in an annular groove V2 (see Fig. 4) provided on the outer peripheral surface of the frame plate 32.

[0021] The crankshaft 7 is a shaft member that rotates integrally with the rotor 152 of the electric motor 15 and extends in the vertical direction. As shown in Fig. 1, the crankshaft 7 includes a main shaft portion 7a and an eccentric portion 7b. The main shaft portion 7a is a portion that is coaxially fixed to the rotor 152 of the electric motor 15, and includes an intermediate portion 71a, a small diameter portion 72a, and a stepped surface 73a.

[0022] The intermediate portion 71a is continuous with the lower side of the eccentric portion 7b, and its periphery is surrounded by the main frame 31. The small-diameter portion 72a is a portion having a diameter shorter than that of the intermediate portion 71a, and is continuous with the lower side of the intermediate portion 71a via a stepped surface 73a. Most of the small-diameter portion 72a exists outside the main frame 31 in the radial direction. Also, the vicinity of the upper end of the small-diameter portion 72a overlaps with the thrust receiving portion 4 in the radial direction.

[0023] The stepped surface 73a is an annular surface that forms the boundary between the intermediate portion 71a and the small-diameter portion 72a. As shown in FIG. 1, the stepped surface 73a is in contact with the upper surface of the thrust bearing 14. The surface direction of the stepped surface 73a is substantially perpendicular to the axial direction of the crankshaft 7.

[0024] The eccentric portion 7b has a bottomed cylindrical shape that opens upward and extends upward from the main shaft portion 7a. An eccentric hole 71b is provided in the eccentric portion 7b. The eccentric hole 71b is a hole that fits into the columnar pivot shaft 22c and opens upward. Also, the internal space of the eccentric hole 71b communicates with the through hole 7c of the main shaft portion 7a. The eccentric hole 71b has a circular shape in plan view, and its central axis is eccentric by a predetermined amount with respect to the central axis of the main shaft portion 7a. Then, with the driving of the electric motor 15, the pivot shaft 22c moves while being eccentric with respect to the main shaft portion 7a. As a result, the swivel scroll 22 performs a swivel motion while being eccentric with respect to the fixed scroll 21.

[0025] As shown in FIG. 1, a through hole 7c through which oil flows is provided in the axial direction inside the crankshaft 7. Also, a radial lateral hole 7d is provided in the crankshaft 7 so as to communicate with the through hole 7c. And a part of the oil flowing through the through hole 7c is guided to the sub-bearing 13 through the lateral hole 7d.

[0026] The Oldham ring 8 is an annular member that swivels the swivel scroll 22 without causing it to rotate, and is interposed between the swivel scroll 22 and the frame plate 32. The balance weight 9 is a member for suppressing the vibration of the scroll compressor 100 and is installed on the crankshaft 7. More specifically, the balance weight 9 is installed directly below the eccentric portion 7b at the intermediate portion 71a of the crankshaft 7. By installing the balance weight 9 near the upper end of the crankshaft 7 in this way, the deflection of the crankshaft 7 caused by the centrifugal force of the balance weight 9 can be suppressed. As shown in FIG. 1, the balance weight 9 is provided in the balance weight space A2 between the main frame 31 and the frame plate 32. And, as the motor 15 is driven, the crankshaft 7 and the balance weight 9 rotate integrally.

[0027] The other balance weight 10 is installed below the rotor 152 of the motor 15. And the rotor 152 and the balance weight 10 rotate integrally. The balance weights 9 and 10 are arranged such that the positions of their centers of gravity are on opposite sides of each other with the crankshaft 7 in between. Thereby, the vibration of the scroll compressor 100 can be effectively suppressed. Note that the number and installation location of the balance weights can be changed as appropriate.

[0028] The main bearing 11 (first bearing) shown in FIG. 1 rotatably supports the eccentric portion 7b with respect to the frame plate 32 (frame) and is fixed to the inner peripheral surface of the frame plate 32 by press-fitting or the like. As such a main bearing 11, for example, a cylindrical sliding bearing is used. The swivel bearing 12 (second bearing) rotatably supports the swivel shaft 22c with respect to the peripheral surface of the eccentric hole 71b and is arranged radially inside the main bearing 11 (first bearing). As such a swivel bearing 12, for example, a cylindrical sliding bearing is used. The swivel bearing 12 is fixed to the peripheral surface of the swivel shaft 22c by press-fitting or the like.

[0029] In the example of FIG. 1, the axial installation regions of the main bearing 11 and the slewing bearing 12 are substantially the same, but it is not limited thereto. That is, it is only necessary that the axial installation regions of the main bearing 11 and the slewing bearing 12 overlap at least partially. Such a configuration is referred to as a "double bearing structure".

[0030] By adopting the double bearing structure, when a radial force associated with a gas load acts from the slewing shaft 22c, the axial height positions of the acting point on the slewing bearing 12 and the acting point on the main bearing 11 become substantially equal. Therefore, the generation of a moment that tilts the crankshaft 7 can be suppressed, and thus, the jamming of the crankshaft 7 can be suppressed. Further, since the deflection of the crankshaft 7 is suppressed even during high-speed operation, the reliability of the scroll compressor 100 is enhanced. Also, compared with a configuration (not shown) in which the slewing bearing is arranged above the main bearing, the double bearing structure shortens the vertical dimension of the scroll compressor 100, so that the scroll compressor 100 can be miniaturized.

[0031] The auxiliary bearing 13 rotatably supports the intermediate portion 71a of the crankshaft 7 with respect to the main frame 31. The auxiliary bearing 73 is fixed to the peripheral surface of the insertion hole 3a of the main frame 31 by press-fitting or the like. Note that the height position of the auxiliary bearing 13 is lower than those of the main bearing 11 and the slewing bearing 12, while being higher than the height position of the electric motor 15. As such an auxiliary bearing 13, for example, a cylindrical sliding bearing is used.

[0032] The thrust bearing 14 is a bearing that receives an axial (thrust direction) load from the crankshaft 7 and has an annular shape of a thin plate. As shown in FIG. 1, the thrust bearing 14 is placed on the thrust receiving portion 4. And the stepped surface 73a of the crankshaft 7 abuts against the upper surface of the thrust bearing 14. The thrust bearing 14 is arranged below the auxiliary bearing 13 in a state slightly separated from the auxiliary bearing 13 in the vertical direction.

[0033] The electric motor 15 is a drive source for rotating the crankshaft 7. As such an electric motor 15, for example, a permanent magnet synchronous motor is used, but other types of motors may be used. The electric motor 15 includes a stator 151 and a rotor 152, and is disposed below the compression mechanism portion 2.

[0034] The stator 151 has a stator core 151a and windings 151b, and is fixed to the inner peripheral surface of the cylinder chamber 1a. The stator core 151a is a cylindrical member made of a magnetic material. The windings 151b are wound around the stator core 151a in a predetermined manner.

[0035] The rotor 152 rotates around the central axis of the crankshaft 7 and is disposed radially inside the stator 151. The rotor 152 has, for example, a configuration in which a plurality of permanent magnets (not shown) are embedded in a cylindrical iron core formed by laminating electromagnetic steel sheets. The plurality of electromagnetic steel sheets described above are fixed by rivets T1. Then, when a predetermined current flows through the windings 151b, a magnetic attractive force and repulsive force are generated between the stator 151 and the rotor 152, causing the rotor 152 to rotate.

[0036] The oil return pipe 16 is a pipe for returning the oil that has lubricated the main bearing 11, the swivel bearing 12, and the sub-bearing 13 to the oil sump R1. The oil return pipe 16 has an inverted L shape in side view and is inserted into the oil return hole 3b of the main frame 31 as described above. As shown in FIG. 1, the upstream end of the oil return pipe 16 faces the balance weight space A2.

[0037] The centrifugal pump 17 is a pump for sucking up oil from the oil sump R1 at the bottom of the sealed container 1, and is installed near the lower end of the crankshaft 7. The plurality of legs 18 are members for supporting the sealed container 1 and are installed in the bottom chamber 1c.

[0038] FIG. 2 is an explanatory diagram showing the flow of oil in the scroll compressor 100. Note that the configuration of the scroll compressor 100 shown in FIG. 2 is the same as that in FIG. 1. Also, the dashed arrows in FIG. 2 indicate the flow of oil. The oil sucked up by the centrifugal pump 17 as the motor 15 is driven rises through the through-hole 7c of the crankshaft 7, and a part of it is guided to the auxiliary bearing 13 through the lateral hole 7d. The oil that has lubricated the auxiliary bearing 13 is returned to the oil sump R1 sequentially through the balance weight space A2 and the oil return pipe 16.

[0039] Also, a part of the oil flowing through the through-hole 7c rises along the swivel bearing 12. That is, the oil rises through the first groove G1 (see FIG. 3) provided on the peripheral surface of the eccentric hole 71b to lubricate the swivel bearing 12. The oil that has lubricated the swivel bearing 12 and reached the upper end of the eccentric portion 7b heads radially outward through the gap between the eccentric portion 7b and the mirror plate 22a of the orbiting scroll 22 to lubricate the main bearing 11. The oil that has lubricated the main bearing 11 is returned to the oil sump R1 sequentially through the balance weight space A2 and the oil return pipe 16. In this way, the swivel bearing 12 and the main bearing 11 are sequentially lubricated with oil.

[0040] Also, a part of the oil that has risen through the through-hole 7c is guided to the oil supply groove (not shown) on the mirror plate surface of the fixed scroll 21 through the oil supply passage (not shown) inside the orbiting scroll 22. The oil guided to the oil supply groove (not shown) is used for sealing and lubricating the compression chamber C1 and then guided to the back pressure chamber A1.

[0041] <Regarding the floating of the crankshaft> During the drive of the scroll compressor 100, a downward force acts on the crankshaft 7 due to gravity and the magnetic force of the motor 15. Therefore, normally, the stepped surface 73a of the crankshaft 7 is in contact with the thrust bearing 14. In this state, the eccentric portion 7b of the crankshaft 7 is separated from the mirror plate 22a of the orbiting scroll 22 by a predetermined distance in the vertical direction.

[0042] However, when so-called "flooded start-up" occurs or in other cases, the crankshaft 7 may float upward in the axial direction (towards the side of the orbiting scroll 22). Here, "flooded start-up" refers to a phenomenon in which, when the scroll compressor 100 is started, the liquid refrigerant dissolved in the oil rapidly vaporizes and foams due to decompression (decompression of the liquid refrigerant due to suction through the through-hole 7c). Especially in a low-temperature environment, a large amount of refrigerant liquefies and dissolves in the oil, making flooded start-up more likely to occur. When flooded start-up occurs, the pressure in the motor chamber C3 becomes relatively higher than the pressure in the through-hole 7c of the crankshaft 7, so the crankshaft 7 may float and contact the orbiting scroll 22.

[0043] In this way, the scroll compressor 100 has a structure in which the crankshaft 7 and the orbiting scroll 22 come into contact when the crankshaft 7 floats. Specifically, when the crankshaft 7 floats, the upper surface of the eccentric portion 7b abuts against the lower surface of the mirror plate 22a of the orbiting scroll 22. In order to prevent the oil flow path from being blocked even in such a state, in the first embodiment, radial oil grooves G2, G3 (see FIG. 3) are provided on the upper surface S1 (see FIG. 3) of the eccentric portion 7b.

[0044] FIG. 3 is a perspective view of the crankshaft 7. The first groove G1 shown in FIG. 3 is a groove that guides the oil flowing out from the through-hole 7c (see FIG. 2) of the crankshaft 7 to the upper end of the eccentric portion 7b. In the example of FIG. 3, the first groove G1, which is recessed radially outward from the peripheral surface of the eccentric hole 71b, is provided in the axial direction (the axial direction of the crankshaft 7). More specifically, the first groove G1 with an arcuate cross-section is provided in the axial direction from the bottom to the upper end of the eccentric hole 71b.

[0045] Note that a radially outward load acts on the outer peripheral surface of the eccentric portion 7b from the swivel shaft 22c (see FIG. 2) on the side where the eccentric hole 71b is eccentric (the side where the oil groove G3 is provided). Therefore, the first groove G1 is provided on the side opposite to the side where the eccentric hole 71b is eccentric. As a result, an oil film is likely to be formed on the swivel bearing 12 (see FIG. 2) by the oil flowing through the first groove G1. Incidentally, there is no particular need to provide an axial groove like the first groove G1 at the location on the peripheral surface of the eccentric hole 71b that faces the first groove G1 (the side of the oil groove G3), but an axial groove may be provided at this location.

[0046] The oil grooves G2 and G3 shown in FIG. 3 are grooves that guide the oil flowing out of the eccentric hole 71b through the through-hole 7c (see FIG. 2) of the crankshaft 7 toward the upper end of the main bearing 11 (the first bearing: see FIG. 2). Specifically, radially inward grooves recessed downward from the upper surface S1 of the eccentric portion 7b are provided as the oil grooves G2 and G3. Note that the radially inner ends of the oil grooves G2 and G3 are located at the edge of the eccentric hole 71b. Also, the radially outer ends of the oil grooves G2 and G3 are located at the outer peripheral edge of the upper surface S1 of the eccentric portion 7b. One oil groove G2 is continuous with the upper end of the first groove G1 described above. The other oil groove G3 is provided on the side opposite to the oil groove G2 with the eccentric hole 71b interposed therebetween and is continuous with the upper end of the second groove G4.

[0047] The second groove G4 is a groove that guides oil downward along the inner peripheral surface of the main bearing 11 (see FIG. 2). In the example of FIG. 3, the second groove G4 recessed radially inward from the outer peripheral surface of the eccentric portion 7b is provided in the axial direction (the axial direction of the crankshaft 7). More specifically, the second groove G4 is provided in the axial direction from the upper end to the lower end of the eccentric portion 7b.

[0048] On the outer peripheral surface of the eccentric portion 7b, a second groove G4 is provided on the side opposite to the side where the radial inward reaction force acts from the main bearing 11 (see FIG. 2) (the side where the eccentric portion 7b is eccentric). As a result, an oil film is likely to be formed on the main bearing 11 (see FIG. 2) by the oil flowing through the second groove G4. Incidentally, on the outer peripheral surface of the eccentric portion 7b, on the side opposite to the second groove G4, there is no particular need to provide an axial groove like the second groove G4, but an axial groove may be provided at this location.

[0049] FIG. 4 is a partial longitudinal sectional view when the crankshaft 7 of the scroll compressor 100 floats. In FIG. 4, the orbiting scroll 22, the frame plate 32, the oldham ring 8, the first resin ring 5, the main bearing 11, the orbiting bearing 12, a part of the crankshaft 7, and the balance weight 9 are illustrated (the illustration of the remaining members is omitted).

[0050] In the example of FIG. 4, the depth dimension L1 (the depth dimension in the axial direction of the crankshaft 7) of the eccentric hole 71b of the crankshaft 7 is longer than the axial length L2 of the orbiting shaft 22c (L1 > L2). In such a configuration, when the crankshaft 7 floats due to the above-described bedding-in start-up or the like, the upper surface S1 of the eccentric portion 7b (see also FIG. 3) contacts the portion S2 of the lower surface of the mirror plate 22a that faces the eccentric portion 7b. On the other hand, a predetermined gap is formed between the lower surface of the orbiting shaft 22c and the bottom surface of the eccentric hole 71b.

[0051] In the configuration as shown in FIG. 4 (the dimensional relationship of L1 > L2), the "first contact surface", which is the contact surface on the crankshaft 7 side, is the upper surface S1 of the eccentric portion 7b. Oil grooves G2 and G3 are provided on the upper surface S1 of this eccentric portion 7b (that is, the first contact surface). Also, the "second contact surface", which is the contact surface on the orbiting scroll 22 side, is the portion S2 of the lower surface of the mirror plate 22a that faces the eccentric portion 7b.

[0052] In the example of FIG. 4, the height positions of the bottoms of the oil grooves G2 and G3 are substantially equal to the height positions of the main bearing 11 and the swivel bearing 12, but it is not limited thereto. That is, the height positions of the bottoms of the oil grooves G2 and G3 may be lower than the height positions of the main bearing 11 and the swivel bearing 12, may be higher, or may be either.

[0053] As shown in FIG. 4, even when the crankshaft 7 floats and the upper surface S1 of the eccentric portion 7b abuts against the lower surface (portion S2 facing the eccentric portion 7b) of the mirror plate 22a, the oil lubricating the swivel bearing 12 is guided to the vicinity of the upper end of the main bearing 11 through each of the oil grooves G2 and G3. More specifically, a part of the oil that has reached the upper end of the eccentric portion 7b through the first groove G1 (see FIG. 3) described above is guided radially outward through the oil groove G2, and further flows through a minute gap between the main bearing 11 and the eccentric portion 7b. Also, a part of the oil existing above the eccentric portion 7b is guided radially outward through the oil groove G3, and further descends through the second groove G4 (see FIG. 3) described above. Therefore, even when the crankshaft 7 floats due to lying-in start or the like, the oil flow path is not particularly blocked, and the main bearing 11 and the swivel bearing 12 can be appropriately lubricated.

[0054] <Effect> According to the first embodiment, since the main bearing 11 and the swivel bearing 12 have a double bearing structure that overlaps in the radial direction, the generation of a moment that causes the crankshaft 7 to tilt can be suppressed. Therefore, the deflection and jamming of the crankshaft 7 can be suppressed even during high-speed operation. Also, by adopting the double bearing structure, the vertical length of the scroll compressor 100 can be shortened, and its miniaturization can be achieved.

[0055] In addition, radial oil grooves G2 and G3 are provided on the contact surface (the upper surface S1 of the eccentric portion 7b, the first contact surface) with the orbiting scroll 22 when the crankshaft 7 floats (see FIG. 3). Therefore, for example, even when the crankshaft 7 floats due to a seizure start, oil is supplied from the orbiting bearing 12 to the main bearing 11 through each of the oil grooves G2 and G3. As a result, wear and seizure of the main bearing 11 and the orbiting bearing 12 can be suppressed, and thus the reliability of the scroll compressor 100 can be enhanced. Further, since the oil grooves G2 and G3 can be easily formed with a cutting tool such as an end mill, an increase in manufacturing cost can be suppressed.

[0056] ≪Second Embodiment≫ The second embodiment is different from the first embodiment in that oil grooves G6 and G7 (see FIG. 5) are provided on the lower surface of the mirror plate 22a instead of the upper surface of the eccentric portion 7b. Otherwise, it is the same as the first embodiment. Therefore, the parts different from the first embodiment will be described, and the description of the overlapping parts will be omitted. It is assumed that the first groove G1 (see FIG. 3) and the second groove G4 (see FIG. 3) described in the first embodiment are provided in the eccentric portion 7b of the crankshaft 7, but it is not particularly necessary to provide the oil grooves G2 and G3 (see FIG. 3).

[0057] FIG. 5 is a bottom view of the orbiting scroll 22A provided in the scroll compressor according to the second embodiment. Note that the circle D1 shown by the broken line in FIG. 5 indicates a projection of the outer peripheral edge of the eccentric portion 7b (see FIG. 6) onto the mirror plate 22a. Incidentally, as the orbiting scroll 22A orbits, the positional relationship between the outer peripheral edge of the eccentric portion 7b (that is, the circle D1 in FIG. 5) and the mirror plate 22a also changes in a predetermined manner.

[0058] As shown in FIG. 5, a pair of key grooves 22d are provided on the lower surface of the mirror plate 22a of the orbiting scroll 22A. These key grooves 22d are radial grooves recessed upward from the lower surface of the mirror plate 22a and have a function of guiding a key (not shown) of the O-ring 8 in the radial direction. The pair of key grooves 22d are provided on opposite sides of each other with the orbiting shaft 22c interposed therebetween.

[0059] The oil grooves G6 and G7 shown in Fig. 5 are radial grooves that are recessed upward from the lower surface of the mirror plate 22a. These oil grooves G6 and G7 have a function of guiding the oil flowing out from the eccentric hole 71b (see Fig. 6) through the through-hole 7c (see Fig. 6) of the crankshaft 7 toward the upper end of the main bearing 11 (first bearing: see Fig. 6). The oil grooves G6 and G7 are provided radially over a predetermined length from the peripheral edge at the base of the swivel shaft 22c. In the example of Fig. 5, the oil grooves G6 and G7 are provided at positions on opposite sides with the swivel shaft 22c interposed therebetween. And, as the crankshaft 7 (see Fig. 6) rotates, the oil grooves G6 and G7 communicate alternately and intermittently with the first groove G1 (see Fig. 3) and the second groove G4 (see Fig. 3) provided on the peripheral surface of the eccentric hole 71b (see Fig. 6).

[0060] Incidentally, the radially inner ends of the oil grooves G6 and G7 are located near the peripheral edge at the base of the swivel shaft 22c (see Fig. 6). Explaining from another perspective, the radially inner ends of the oil grooves G6 and G7 are located radially inward of the outer peripheral surface of the swivel bearing 12 (see Fig. 6). Also, the radially outer ends of the oil grooves G6 and G7 are provided at positions where this end intermittently projects radially outward from the eccentric portion 7b in plan view (that is, intermittently projects outside the circle D1 in Fig. 5). Explaining from another perspective, the radially outer ends of the oil grooves G6 and G7 are provided at positions where this end intermittently projects radially outward of the inner peripheral surface of the main bearing 11 (see Fig. 6) in plan view.

[0061] Fig. 6 is a partial longitudinal sectional view when the crankshaft 7 of the scroll compressor floats. As shown in Fig. 6, the depth dimension L1 of the eccentric hole 71b of the crankshaft 7 is longer than the axial length L2 of the swivel shaft 22c (L1 > L2). When the crankshaft 7 floats in such a configuration, the upper surface S1 of the eccentric portion 7b contacts the portion S2 on the lower surface of the mirror plate 22a that faces the eccentric portion 7b. Incidentally, the "first contact surface" which is the contact surface on the crankshaft 7 side is the upper surface S1 of the eccentric portion 7b. Also, the "second contact surface" which is the contact surface on the swivel scroll 22 side is the portion S2 (also see Fig. 5) on the lower surface of the mirror plate 22a that faces the eccentric portion 7b.

[0062] As shown in Fig. 6, even when the crankshaft 7 floats and the upper surface of the eccentric portion 7b abuts against the lower surface of the mirror plate 22a, the space above the swing bearing 12 and the space above the main bearing 11 communicate with each other alternately and intermittently via the oil grooves G6 and G7. As a result, even when the crankshaft 7 floats during a bed-in start or the like, the main bearing 11 and the swing bearing 12 can be properly lubricated.

[0063] <Effect> According to the second embodiment, radial oil grooves G6 and G7 are provided on the lower surface of the mirror plate 22a of the swing scroll 22 (see Fig. 5). Therefore, even when the crankshaft 7 floats, oil is intermittently supplied from the swing bearing 12 to the main bearing 11 via the oil grooves G6 and G7, so that the reliability of the scroll compressor can be improved.

[0064] ≪Modification of the Second Embodiment≫ In the second embodiment, the case where the radial oil grooves G6 and G7 (see Fig. 5) are provided on the lower surface of the mirror plate 22a has been described, but the present invention is not limited to this. For example, an annular oil groove G8 (see Fig. 7) may be provided so as to surround the swing shaft 22c.

[0065] Fig. 7 is a bottom view of a swing scroll 22B provided in a scroll compressor according to a modification of the second embodiment. Note that a circle D1 shown by a broken line in Fig. 7 shows a projection of the outer peripheral edge of the eccentric portion 7b (see Fig. 6) on the mirror plate 22a, similar to Fig. 5. The oil groove G8 shown in Fig. 7 is an annular groove recessed upward from the lower surface of the mirror plate 22a. The inner peripheral edge of the oil groove G8 is located near the peripheral edge at the base of the swing shaft 22c. Further, the outer peripheral edge of the oil groove G8 is provided at a position where a part of this outer peripheral edge extends radially outward from the eccentric portion 7b (see Fig. 6) in a plan view (that is, outside the circle D1 in Fig. 7).

[0066] According to such a configuration, the oil lubricating the swing bearing 12 (see Fig. 6) is constantly supplied to the main bearing 11 (see Fig. 6) via the oil groove G8. Therefore, compared with the second embodiment (see Fig. 5), the amount of oil supplied per unit time to the main bearing 11 and the swing bearing 12 can be increased.

[0067] <<Third Embodiment>> In the third embodiment, the depth dimension of the eccentric hole 71b (see FIG. 8) of the crankshaft 7C (see FIG. 8) is shorter than the axial length of the turning shaft 22c (see FIG. 8), which is different from the first embodiment. Also, in the third embodiment, an oil groove G9 (see FIG. 8) is provided on the bottom surface of the eccentric hole 71b, which is different from the first embodiment. Note that other aspects are the same as those of the first embodiment. Therefore, the parts different from the first embodiment will be described, and the description of overlapping parts will be omitted.

[0068] FIG. 8 is a partial longitudinal sectional view when the crankshaft 7C of the scroll compressor according to the third embodiment floats. As shown in FIG. 8, the depth dimension L1 of the eccentric hole 71b of the crankshaft 7C is shorter than the axial length L2 of the turning shaft 22c (L1 < L2). When the crankshaft 7C floats in such a configuration, the lower surface S4 of the turning shaft 22c abuts against the bottom surface S3 of the eccentric portion 7b. On the other hand, the upper surface of the eccentric portion 7b is in a state of being separated from the lower surface of the mirror plate 22a by a predetermined distance in the vertical direction. In this case, the "first contact surface", which is the contact surface on the crankshaft 7C side, is the bottom surface S3 of the eccentric hole 71b. Also, the "second contact surface", which is the contact surface on the turning scroll 22 side, is the lower surface S4 of the turning shaft 22c.

[0069] The oil groove G9 shown in FIG. 8 is a radial groove recessed downward from the bottom surface S3 of the eccentric hole 71b. The radially inner end of the oil groove G9 is connected to the upper end of the through hole 7c. Also, the radially outer end of the oil groove G9 is located near the periphery of the bottom surface of the eccentric hole 71b (directly below the turning bearing 12). This oil groove G9 has a function of guiding the oil flowing out into the eccentric hole 71b through the through hole 7c of the crankshaft 7C toward the upper end of the main bearing 11 (first bearing).

[0070] FIG. 9 is a plan view of the crankshaft 7C. In the example of Fig. 9, a radial oil groove G9 is provided on the side of the crankshaft 7C where the eccentric hole 71b is eccentric. More specifically, a radial oil groove G9 is provided from the upper end of the through hole 7c to the vicinity of the periphery of the bottom surface of the eccentric hole 71b. Since a centrifugal force acts on the side where the eccentric hole 71b is eccentric, the oil flowing out from the through hole 7c moves radially outward by the centrifugal force and is guided to the peripheral surface of the eccentric hole 71b through the oil groove G9.

[0071] In the example of Fig. 9, since it is assumed that the oil groove G9 is formed by cutting with a cutting tool such as an end mill, the outer end of the oil groove G9 in the radial direction is rounded, but it is not limited thereto. For example, the outer end of the oil groove G9 in the radial direction may be along the periphery of the bottom surface of the eccentric hole 71b.

[0072] The oil flowing through the oil groove G9 rises through the gap of an axial groove (not shown) provided in the eccentric hole 71b and is guided to the upper end of the eccentric hole 71b. The above-mentioned axial groove may be provided at a position corresponding to the oil groove G9 on the peripheral surface of the eccentric hole 71b, or may be provided at a position on the side opposite to the oil groove G9 (that is, the position of the first groove G1 in Fig. 3), and either is acceptable. When an axial groove is provided at a position on the peripheral surface of the eccentric hole 71b opposite to the oil groove G9, an arc-shaped or annular groove (not shown) for guiding oil from the oil groove G9 to this groove may be provided on the bottom surface of the eccentric hole 71b.

[0073] <Effect> According to the third embodiment, a radial oil groove G9 (see Fig. 9) is provided on the bottom surface of the eccentric hole 71b of the crankshaft 7C. Therefore, even when the crankshaft 7C floats and the swing shaft 22c abuts against the bottom surface of the eccentric hole 71b, oil is supplied to the swing bearing 12 and the like through the oil groove G9, so that the reliability of the scroll compressor can be improved.

[0074] <<Fourth Embodiment>> In the fourth embodiment, oil grooves G10 and G11 (see FIG. 10) are provided on the lower surface of the swivel shaft 22c of the swivel scroll 22D (see FIG. 10) instead of on the bottom surface of the eccentric portion 7b of the crankshaft 7 (see FIG. 10), which is different from the first embodiment. Otherwise, it is the same as the first embodiment. Therefore, the parts different from the first embodiment will be described, and the description of the overlapping parts will be omitted.

[0075] FIG. 10 is a partial longitudinal sectional view when the crankshaft 7 of the scroll compressor according to the fourth embodiment floats. As shown in FIG. 10, the depth dimension L1 of the eccentric hole 71b of the crankshaft 7 is shorter than the axial length L2 of the swivel shaft 22c (L1 < L2). When the crankshaft 7 floats in such a configuration, the lower surface S4 of the swivel shaft 22c contacts the bottom surface S3 of the eccentric portion 7b. In this case, the "first contact surface" which is the contact surface on the crankshaft 7 side is the bottom surface S3 of the eccentric hole 71b. Also, the "second contact surface" which is the contact surface on the swivel scroll 22D side is the lower surface S4 of the swivel shaft 22c.

[0076] The oil grooves G10 and G11 shown in FIG. 10 are radial grooves recessed upward from the lower surface S4 of the swivel shaft 22c. These oil grooves G10 and G11 have the function of guiding the oil flowing out into the eccentric hole 71b through the through hole 7c of the crankshaft 7 toward the upper end of the main bearing 11 (first bearing).

[0077] FIG. 11 is a bottom view of the swivel scroll 22D. As shown in FIG. 11, a pair of oil grooves G10 and G11 recessed upward from the lower surface are provided in the radial direction on the swivel shaft 22c of the swivel scroll 22D. The radially inner end of the oil groove G10 is provided at a position where the oil groove G10 intermittently communicates with the through hole 7c (see FIG. 10) (the same applies to the other oil groove G11). That is, as the crankshaft 7 (see FIG. 10) rotates, the oil grooves G10 and G11 alternately and intermittently communicate with the through hole 7c (see FIG. 10).

[0078] Also, the outer ends of the oil grooves G10 and G11 in the radial direction are located at the periphery of the lower surface of the swivel shaft 22c (see FIG. 10). In the example of FIG. 11, a pair of oil grooves G10 and G11 are provided in a straight line so as to face each other with the center of the swivel shaft 22c in between. The oil grooves G10 and G11 communicate with the through hole 7c (see FIG. 10) alternately and intermittently, and also communicate with the first axial groove G1 (see FIG. 3) provided on the peripheral surface of the eccentric hole 71b (see FIG. 3) alternately and intermittently.

[0079] Therefore, even when the crankshaft 7 (see FIG. 10) floats and the lower surface of the swivel shaft 22c abuts against the bottom surface of the eccentric hole 71b (see FIG. 10), oil is guided to the swivel bearing 12 through the oil grooves G10 and G11. Since there is a predetermined gap between the upper end of the crankshaft 7 (see FIG. 10) and the lower surface of the mirror plate 22a, oil is guided from the swivel bearing 12 to the main bearing 11 (see FIG. 10) through this gap. Thus, even when the crankshaft 7 floats during a lying start or the like, the main bearing 11 and the swivel bearing 12 can be appropriately lubricated.

[0080] ≪Modification of the Fourth Embodiment≫ In the fourth embodiment, the case where the radial oil grooves G10 and G11 (see FIG. 11) are provided on the lower surface of the swivel shaft 22c has been described, but it is not limited thereto. For example, an annular oil groove G12 (see FIG. 12) may be provided on the lower surface of the swivel shaft 22c.

[0081] FIG. 12 is a bottom view of the swivel scroll 22E provided in the scroll compressor according to the modification of the fourth embodiment. The oil groove G12 shown in FIG. 12 is an annular groove recessed upward from the lower surface of the swivel shaft 22c. The inner peripheral edge of the oil groove G12 is provided at a position where the oil groove G12 communicates with the through hole 7c (see FIG. 10). Further, the outer peripheral edge of the oil groove G12 is located at the lower end of the peripheral surface of the swivel shaft 22c. That is, the annular oil groove G12 is configured such that the vicinity of the lower end of the swivel shaft 22c is cut out radially inward over the entire circumference. According to such a configuration, since the oil groove G12 is constantly in communication with the through hole 7c, the amount of oil supplied per unit time to the main bearing 11 (see FIG. 10) and the swivel bearing 12 (see FIG. 10) can be increased as compared with the fourth embodiment (see FIG. 11).

[0082] <<Fifth Embodiment>> In the fifth embodiment, an air conditioner W1 (see FIG. 13) including any one of the scroll compressors of the first to fourth embodiments will be described.

[0083] FIG. 13 is a configuration diagram of the air conditioner W1 according to the fifth embodiment. Note that the solid arrows in FIG. 13 indicate the flow of the refrigerant in the heating cycle. On the other hand, the broken arrows in FIG. 13 indicate the flow of the refrigerant in the cooling cycle. The air conditioner W1 is a device that performs air conditioning such as cooling operation and heating operation. As shown in FIG. 13, the air conditioner W1 includes a scroll compressor 100, an outdoor heat exchanger 91, an outdoor fan 92, an expansion valve 93, a four-way valve 94, an indoor heat exchanger 95, and an indoor fan 96. In the example of FIG. 13, the scroll compressor 100, the outdoor heat exchanger 91, the outdoor fan 92, the expansion valve 93, and the four-way valve 94 are provided in the outdoor unit U1. Also, the indoor heat exchanger 95 and the indoor fan 96 are provided in the indoor unit U2.

[0084] The scroll compressor 100 is a device that compresses gaseous refrigerant and has the same configuration as any of the first to fourth embodiments. The outdoor heat exchanger 91 is a heat exchanger in which heat exchange is performed between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent from the outdoor fan 92. The outdoor fan 92 is a fan that sends outside air into the outdoor heat exchanger 91. The outdoor fan 92 includes an outdoor fan motor 92a as a drive source and is installed near the outdoor heat exchanger 91.

[0085] The indoor heat exchanger 95 is a heat exchanger in which heat exchange is performed between the refrigerant flowing through its heat transfer tubes (not shown) and the indoor air (the air in the air-conditioned room) sent from the indoor fan 96. The indoor fan 96 is a fan that sends indoor air into the indoor heat exchanger 95. The indoor fan 96 includes an indoor fan motor 96a as a drive source and is installed near the indoor heat exchanger 95.

[0086] The expansion valve 93 is a valve that reduces the pressure of the refrigerant condensed in one of the "condensers" (either the outdoor heat exchanger 91 or the indoor heat exchanger 95). Note that the refrigerant whose pressure has been reduced by the expansion valve 93 is guided to the other of the "evaporators" (either the outdoor heat exchanger 91 or the indoor heat exchanger 95).

[0087] The four-way valve 94 is a valve that switches the refrigerant flow path according to the operation mode of the air conditioner W1. For example, during cooling operation (refer to the dashed arrows in FIG. 13), the refrigerant circulates sequentially through the scroll compressor 100, the outdoor heat exchanger 91 (condenser), the expansion valve 93, and the indoor heat exchanger 95 (evaporator). Also, during heating operation (refer to the solid arrows in FIG. 13), the refrigerant circulates sequentially through the scroll compressor 100, the indoor heat exchanger 95 (condenser), the expansion valve 93, and the outdoor heat exchanger 91 (evaporator).

[0088] <Effect> According to the fifth embodiment, since the air conditioner W1 is equipped with the highly reliable scroll compressor 100, the reliability of the entire air conditioner W1 can be enhanced.

[0089] <<Modification Example>> As described above, the scroll compressor 100 and the air conditioner W1 according to the present disclosure have been described in each embodiment, but the present disclosure is not limited to these descriptions, and various modifications can be made. For example, in each embodiment, the case where a predetermined oil groove is provided in the crankshaft 7 or the orbiting scroll 22 has been described, but the cross-sectional shape of these oil grooves may be as shown in FIGS. 14A and 14B.

[0090] FIG. 14A is a schematic cross-sectional view of a scroll compressor according to a modified example, in which the oil groove Ga is a square groove. The oil groove Ga shown in FIG. 14A schematically shows an example of the cross-section of the oil grooves G2, G3, G6, G7, G8, G9, G10, G11, G12 described in each embodiment (the same applies to the oil groove Gb in FIG. 14B). The member Q shown in FIG. 14A is the crankshaft 7 (see FIG. 1) or the orbiting scroll 22 (see FIG. 1). As shown in FIG. 14A, the oil groove Ga may have a square cross-section. Such an oil groove Ga can be easily machined with a tool such as an end mill, so an increase in manufacturing cost can be suppressed.

[0091] FIG. 14B is a schematic cross-sectional view of a scroll compressor according to another modified example, in which the oil groove Gb is an arc groove. As shown in FIG. 14B, the oil groove Gb may have an arc-shaped cross-section. Such an oil groove Gb can also be easily machined with a tool such as an end mill, so an increase in manufacturing cost can be suppressed.

[0092] Also, in each embodiment, although the case where a predetermined oil groove is provided in one of the "first contact surface", which is the contact surface on the crankshaft 7 side when the crankshaft 7 floats, and the "second contact surface", which is the contact surface on the orbiting scroll 22 side, has been described, it is not limited to this. That is, predetermined oil grooves may be provided on both the "first contact surface", which is the contact surface on the crankshaft 7 side when the crankshaft 7 floats, and the "second contact surface", which is the contact surface on the orbiting scroll 22 side. For example, by combining the first embodiment and the second embodiment, oil grooves G2 and G3 (see FIG. 3) are provided on the upper surface of the eccentric portion 7b, and on the lower surface of the mirror plate 22a of the orbiting scroll 22, radial oil grooves G6 and G7 (see FIG. 5) are provided directly above the oil grooves G2 and G3. It is also possible to combine the first embodiment (see FIG. 3) and a modified example of the second embodiment (see FIG. 7). In addition, for example, by combining the third embodiment and the fourth embodiment, an oil groove G9 (see FIG. 9) is provided on the bottom surface of the eccentric hole 71b, and a radial oil groove G10 (see FIG. 11) is provided on the lower surface of the orbiting shaft 22c. It is also possible to combine the third embodiment (see FIG. 9) and a modified example of the fourth embodiment (see FIG. 12).

[0093] Also, in the first embodiment, the case where two oil grooves G2 and G3 (see FIG. 3) are provided on the upper surface of the eccentric portion 7b of the crankshaft 7 has been described, but it is not limited to this. That is, one of the oil grooves G2 and G3 may be omitted, or three or more radial oil grooves may be provided on the upper surface of the eccentric portion 7b. The same applies to the second embodiment (see FIG. 5) and the fourth embodiment (see FIG. 11). Also, the circumferential positions of the respective oil grooves described in each embodiment can be changed as appropriate.

[0094] Also, in each embodiment, the configuration in which the scroll compressor 100 includes the balance weight 9 (see FIG. 1) has been described, but the present invention is not limited to this. That is, the balance weight 9 can be appropriately omitted. In this case, the main frame 31 (see FIG. 1) and the frame plate 32 (see FIG. 1) may be integrated so that the frame 3 is constituted by a single member.

[0095] Further, in each embodiment, the case where the crankshaft 7 is cantilever-supported inside the frame 3 has been described, but the present invention is not limited to this. For example, the present embodiments can also be applied to the case where a sub-frame (not shown) for pivotally supporting the crankshaft 7 is provided below the frame 3.

[0096] Also, the air conditioner W1 (see FIG. 13) described in the fifth embodiment can be applied to various types of air conditioners such as multi-air conditioners for buildings, package air conditioners, and room air conditioners. Further, in the fifth embodiment, the air conditioner W1 including the scroll compressor 100 has been described, but the present invention is not limited to this. For example, the fifth embodiment can also be applied to other refrigeration cycle devices such as refrigerators, oil supply machines, air-conditioning oil supply devices, chillers, and refrigerators.

[0097] Also, in the fifth embodiment, the case where the air conditioner W1 (see FIG. 13) includes the four-way valve 94 has been described, but the present invention is not limited to this. That is, the four-way valve 94 can be appropriately omitted to form an air conditioner dedicated to cooling or heating. Further, in each embodiment, the case where the scroll compressor 100 is vertically placed has been described, but the present invention is not limited to this. For example, the scroll compressor 100 may be horizontally placed or obliquely placed. In this case, the side where the eccentric portion 7b is provided on the crankshaft 7 shall be regarded as the "upper side", and the opposite side shall be regarded as the "lower side".

[0098] Also, each embodiment has been described in detail for the purpose of easily understanding the present disclosure, and is not necessarily limited to the one having all the configurations described. Further, for a part of the configuration of each embodiment, addition, deletion, and replacement of other configurations can be appropriately performed. In addition, the mechanisms and configurations described above show those considered necessary for explanation, and not necessarily all mechanisms and configurations are shown in the product.

Description of Reference Numerals

[0099] 1 Sealed container 2 Compression mechanism section 3 Frame 4 Thrust receiving section 5 First resin ring 6 Second resin ring 7, 7C Crankshaft 7a Main shaft portion 7b Eccentric portion 8 O-ring 9 Balance weight 11 Main bearing (first bearing) 12 Swivel bearing (second bearing) 13 Sub-bearing 14 Thrust bearing 15 Electric motor 16 Oil return pipe 21 Fixed scroll 21c Fixed wrap 22, 22A, 22B, 22D, 22E Swivel scroll 22a Mirror plate 22b Swivel wrap 22c Swivel shaft 31 Main frame (frame) 32 Frame plate (frame) 71b Eccentric hole 91 Outdoor heat exchanger 92 Outdoor fan 93 Expansion valve 94 Four-way valve 95 Indoor heat exchanger 96 Indoor fan 100 Scroll compressor C1 Compression chamber G2, G3, G6, G7, G8, G9, G10, G11, G12 Oil groove S1 Upper surface of eccentric portion (first contact surface) The portion (second contact surface) on the lower surface of the S2 mirror plate facing the eccentric portion The bottom surface of the S3 eccentric hole (first contact surface) The lower surface of the S4 pivot shaft (second contact surface) W1 Air conditioner

Claims

1. A sealed container, a frame installed inside the sealed container, a fixed scroll having a spiral fixed wrap and fixed to the frame, a swivel scroll having a spiral swivel wrap that forms a compression chamber with the fixed wrap and having a swivel shaft provided on the opposite side of the swivel wrap with respect to the mirror plate, a crankshaft having an eccentric portion provided with an eccentric hole fitted to the swivel shaft, a first bearing rotatably supporting the eccentric portion with respect to the frame, a second bearing rotatably supporting the swivel shaft with respect to the circumferential surface of the eccentric hole, and comprising, a structure in which the crankshaft and the swivel scroll come into contact when the crankshaft floats, and an oil groove is provided in one or both of a first contact surface that is the contact surface on the crankshaft side and a second contact surface that is the contact surface on the swivel scroll side, the oil groove being a groove that guides oil flowing out into the eccentric hole through a through hole of the crankshaft toward the upper end of the first bearing, the depth dimension of the eccentric hole being longer than the axial length of the swivel shaft, the first contact surface being the upper surface of the eccentric portion, the second contact surface being a portion of the lower surface of the mirror plate that faces the eccentric portion, the oil groove being a radial groove recessed downward from the upper surface of the eccentric portion, the radially inner end of the oil groove being located at the edge of the eccentric hole, the radially outer end of the oil groove being located at the outer peripheral edge of the upper surface of the eccentric portion, a scroll compressor.

2. A sealed container, a frame installed inside the sealed container, a fixed scroll having a spiral fixed wrap and fixed to the frame, a swivel scroll having a spiral swivel wrap that forms a compression chamber with the fixed wrap and having a swivel shaft provided on the opposite side of the swivel wrap with respect to the mirror plate, a crankshaft having an eccentric portion provided with an eccentric hole fitted to the swivel shaft, a first bearing rotatably supporting the eccentric portion with respect to the frame, a second bearing rotatably supporting the swivel shaft with respect to the circumferential surface of the eccentric hole, and comprising, a structure in which the crankshaft and the swivel scroll come into contact when the crankshaft floats, and an oil groove is provided in one or both of a first contact surface that is the contact surface on the crankshaft side and a second contact surface that is the contact surface on the swivel scroll side, The oil groove is a groove that guides the oil flowing out of the eccentric hole through the through hole of the crankshaft toward the upper end of the first bearing. The depth dimension of the eccentric hole is longer than the axial length of the swivel shaft. The first contact surface is the upper surface of the eccentric portion. The second contact surface is a portion of the lower surface of the mirror plate that faces the eccentric portion. The oil groove is a radial groove that is recessed upward from the lower surface of the mirror plate. The radially inner end of the oil groove is located near the periphery at the root of the swivel shaft. The radially outer end of the oil groove is provided at a position where, in a plan view, the radially outer end intermittently extends radially outward from the eccentric portion. A scroll compressor.

3. A sealed container, A frame installed inside the sealed container, A fixed scroll having a spiral fixed wrap and fixed to the frame, A swivel scroll having a spiral swivel wrap that forms a compression chamber between the fixed wrap and having a swivel shaft provided on the opposite side of the swivel wrap with respect to the mirror plate, A crankshaft having an eccentric portion provided with an eccentric hole that fits onto the swivel shaft, A first bearing that rotatably supports the eccentric portion with respect to the frame, A second bearing that rotatably supports the swivel shaft with respect to the peripheral surface of the eccentric hole, and comprising, When the crankshaft floats, the structure is such that the crankshaft and the swivel scroll come into contact with each other. An oil groove is provided on one or both of the first contact surface, which is the contact surface on the crankshaft side, and the second contact surface, which is the contact surface on the swivel scroll side. The oil groove is a groove that guides the oil flowing out of the eccentric hole through the through hole of the crankshaft toward the upper end of the first bearing. The depth dimension of the eccentric hole is longer than the axial length of the swivel shaft. The first contact surface is the upper surface of the eccentric portion. The second contact surface is a portion of the lower surface of the mirror plate that faces the eccentric portion. The oil groove is an annular groove that is recessed upward from the lower surface of the mirror plate. The inner peripheral edge of the oil groove is located near the periphery at the root of the swivel shaft. The outer peripheral edge of the oil groove is provided at a position where, in a plan view, a part of the outer peripheral edge extends radially outward from the eccentric portion. A scroll compressor.

4. A sealed container, A frame installed inside the sealed container, A fixed scroll having a spiral fixed wrap and fixed to the frame, A scroll compressor having a spiral orbiting wrap that forms a compression chamber between the fixed wrap and an orbiting scroll having an orbiting shaft provided on the opposite side of the orbiting wrap from the mirror plate, a crankshaft having an eccentric portion provided with an eccentric hole that fits onto the orbiting shaft, a first bearing that rotatably supports the eccentric portion with respect to the frame, a second bearing that rotatably supports the orbiting shaft with respect to the circumferential surface of the eccentric hole, and a structure in which the crankshaft and the orbiting scroll come into contact when the crankshaft floats, and an oil groove is provided in one or both of a first contact surface that is the contact surface on the crankshaft side and a second contact surface that is the contact surface on the orbiting scroll side, wherein the oil groove is a groove that guides oil flowing out into the eccentric hole through a through hole of the crankshaft toward the upper end of the first bearing, wherein the depth dimension of the eccentric hole is shorter than the axial length of the orbiting shaft, wherein the first contact surface is the bottom surface of the eccentric hole, wherein the second contact surface is the lower surface of the orbiting shaft, wherein the oil groove is a radial groove that is recessed downward from the bottom surface of the eccentric hole, wherein the radially inner end of the oil groove is continuous with the upper end of the through hole, wherein the radially outer end of the oil groove is located near the periphery of the bottom surface of the eccentric hole. **Claim 5** A sealed container, a frame installed inside the sealed container, a fixed scroll having a spiral fixed wrap and fixed to the frame, a scroll compressor having a spiral orbiting wrap that forms a compression chamber between the fixed wrap and an orbiting scroll having an orbiting shaft provided on the opposite side of the orbiting wrap from the mirror plate, a crankshaft having an eccentric portion provided with an eccentric hole that fits onto the orbiting shaft, a first bearing that rotatably supports the eccentric portion with respect to the frame, a second bearing that rotatably supports the orbiting shaft with respect to the circumferential surface of the eccentric hole, and a structure in which the crankshaft and the orbiting scroll come into contact when the crankshaft floats, and an oil groove is provided in one or both of a first contact surface that is the contact surface on the crankshaft side and a second contact surface that is the contact surface on the orbiting scroll side, wherein the oil groove is a groove that guides oil flowing out into the eccentric hole through a through hole of the crankshaft toward the upper end of the first bearing, wherein the depth dimension of the eccentric hole is shorter than the axial length of the orbiting shaft, The first contact surface is the bottom surface of the eccentric hole, The second contact surface is the lower surface of the swivel shaft, The oil groove is a radial groove recessed upward from the lower surface of the swivel shaft, The radially inner end of the oil groove is provided at a position where the oil groove intermittently communicates with the through hole, The radially outer end of the oil groove is located at the periphery of the lower surface of the swivel shaft, scroll compressor.

6. A hermetic container, A frame installed inside the hermetic container, A fixed scroll having a spiral fixed wrap and fixed to the frame, A swivel scroll having a spiral swivel wrap that forms a compression chamber between the fixed wrap and having a swivel shaft provided on the opposite side of the swivel wrap with respect to the mirror plate, A crankshaft having an eccentric portion provided with an eccentric hole fitted to the swivel shaft, A first bearing that rotatably supports the eccentric portion with respect to the frame, A second bearing that rotatably supports the swivel shaft with respect to the peripheral surface of the eccentric hole, A structure in which the crankshaft and the swivel scroll come into contact when the crankshaft floats, and an oil groove is provided on one or both of the first contact surface that is the contact surface on the crankshaft side and the second contact surface that is the contact surface on the swivel scroll side, The oil groove is a groove that guides the oil flowing out of the eccentric hole through the through hole of the crankshaft toward the upper end of the first bearing, The depth dimension of the eccentric hole is shorter than the axial length of the swivel shaft, The first contact surface is the bottom surface of the eccentric hole, The second contact surface is the lower surface of the swivel shaft, The oil groove is an annular groove recessed upward from the lower surface of the swivel shaft, The inner peripheral edge of the oil groove is provided at a position where the oil groove communicates with the through hole, The outer peripheral edge of the oil groove is located at the lower end of the peripheral surface of the swivel shaft, scroll compressor.

7. The oil groove is a square groove with a square cross-section or an arc groove with an arc-shaped cross-section The scroll compressor according to claim 1, characterized in that.

8. Comprising the scroll compressor according to any one of claims 1 to 7, An air conditioner comprising an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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