Scroll compressor and air conditioner

Abstract

We provide scroll compressors with high performance and reliability. [Solution] The scroll compressor 100 comprises a sealed container 1, a frame 3, a fixed scroll 21, an orbiting scroll 22 having an orbiting axis 22c, a crankshaft 7 having an eccentric portion 7b with an eccentric hole 71b that fits onto the orbiting axis 22c and supported cantilevered inside the frame 3, a frame plate 5 having a fitting portion that fits onto the inside of the frame 3 and having an insertion hole for the eccentric portion 7b, a main bearing 11 that rotatably supports the eccentric portion 7b relative to the frame plate 5, a orbiting bearing 12 that rotatably supports the orbiting axis 22c relative to the circumferential surface of the eccentric hole 71b, and a first resin ring 61 that seals between the frame plate 5 and the end plate 22a.

Description

[Technical Field]

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

[0002] Known scroll compressor structures include those described in, for example, Patent Documents 1 and 2. Patent Document 1 describes a scroll compressor having an eccentric hole formed in the upper end of a crankshaft, into which a scroll pin is fitted. A main bearing is disposed on the outer periphery of the eccentric hole, and an orbiting bearing is disposed on the inner periphery.

[0003] Furthermore, Patent Document 2 describes a scroll compressor having a double bearing structure in which a main bearing and an orbiting bearing overlap in the radial direction. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 2923582 [Patent Document 2] Patent No. 7263553 Summary of the Invention [Problem to be solved by the invention]

[0005] As mentioned above, Patent Documents 1 and 2 describe scroll compressors with a double bearing structure, but there is room for further improvement in the performance and reliability of scroll compressors.

[0006] Therefore, an object of the present disclosure is to provide a scroll compressor or the like with high performance and reliability. [Means for solving the problem]

[0007] In order to solve the above-mentioned problems, a scroll compressor according to the present disclosure includes: a sealed container; a frame installed inside the sealed container; a fixed scroll having a spiral-shaped fixed wrap and fixed to the frame; an orbiting scroll having a spiral-shaped orbiting wrap that forms a compression chamber between the fixed wrap and the orbiting wrap and having an orbiting shaft provided on the opposite side of an end plate from the orbiting wrap; a crankshaft having an eccentric portion provided with an eccentric hole that fits onto the orbiting shaft and supported in a cantilever manner inside the frame; a frame plate having a fitting portion that fits inside the frame and in which an insertion hole of the eccentric portion is provided; a first bearing that rotatably supports the eccentric portion relative to the frame plate; a second bearing that rotatably supports the orbiting shaft relative to a circumferential surface of the eccentric hole; and a first resin ring that seals between the frame plate and the end plate. and an Oldham ring interposed between the orbiting scroll and the frame plate, the frame plate having an annular base portion in which the insertion hole is provided, an annular protruding portion protruding upward from the inner peripheral edge of the base portion, and a pair of support portions arranged on opposite sides of the protruding portion, the first resin ring being installed in a first annular groove recessed downward from the upper surface of the protruding portion, and a second key of the Oldham ring being guided via radial key grooves provided in the upper surfaces of the pair of support portions. It was decided that. [Effects of the Invention]

[0008] According to the present disclosure, a scroll compressor and the like with high performance and reliability can be provided. [Brief explanation of the drawings]

[0009] [Figure 1] 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment. [Figure 2] 2 is a partial enlarged view of a region including a frame plate in FIG. 1 in the scroll compressor according to the first embodiment. [Figure 3A] 2 is a perspective view of the scroll compressor according to the first embodiment, when viewed from above, of a frame plate. FIG. [Figure 3B] 2 is a perspective view of the scroll compressor according to the first embodiment, showing a frame plate viewed from below. FIG. [Figure 4] FIG. 1 is an exploded perspective view of a scroll compressor according to a first embodiment. [Figure 5] FIG. 2 is an explanatory diagram showing the flow of oil in the scroll compressor according to the first embodiment. [Figure 6]FIG. 10 is a configuration diagram of an air conditioner according to a second embodiment. [Figure 7] FIG. 10 is a perspective view of a frame plate viewed from below in a scroll compressor according to a modified example. DETAILED DESCRIPTION OF THE INVENTION

[0010] First Embodiment <Scroll compressor configuration> FIG. 1 is a vertical cross-sectional view of a scroll compressor 100 according to a first embodiment. The scroll compressor 100 is a device that compresses a gaseous refrigerant. As shown in Fig. 1, the scroll compressor 100 includes a sealed container 1, a compression mechanism 2, a frame 3, a thrust bearing 4, a frame plate 5, a first resin ring 61, and a second resin ring 63. In addition to the components described above, the scroll compressor 100 also includes a crankshaft 7, an Oldham ring 8, balance weights 9 and 10, a main bearing 11 (first bearing), an orbiting bearing 12 (second bearing), an auxiliary bearing 13 (third bearing), and a thrust bearing 14. The scroll compressor 100 also includes an electric motor 15, an oil return pipe 16, a centrifugal pump 17, and legs 18.

[0011] The sealed container 1 is a metal container that houses components such as the compression mechanism 2, crankshaft 7, and electric motor 15, and is substantially sealed. Oil is sealed in the sealed container 1 to lubricate each sliding part, and the oil is stored as an oil reservoir R1 at the bottom of the sealed container 1. The sealed container 1 includes a cylindrical chamber 1a, a lid chamber 1b that closes the upper side of the cylindrical chamber 1a, and a bottom chamber 1c that closes the lower side of the cylindrical chamber 1a.

[0012] As shown in Fig. 1, a suction pipe P1 is inserted and fixed to the cover chamber 1b of the sealed container 1. The suction pipe P1 is a pipe that guides refrigerant to a suction chamber (not shown) of the compression mechanism 2. A discharge pipe P2 is inserted and fixed to the cylindrical chamber 1a of the sealed container 1. The discharge pipe P2 is a pipe that guides refrigerant compressed by the compression mechanism 2 to the outside of the scroll compressor 100.

[0013] The compression mechanism 2 is a mechanism that compresses the refrigerant as the crankshaft 7 rotates. The compression mechanism 2 includes a fixed scroll 21 and an orbiting scroll 22, and is disposed in the upper space within the sealed container 1. The fixed scroll 21 is a member that forms a compression chamber C1 together with the orbiting scroll 22, and is fixed to the upper side of the frame 3 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.

[0014] The base plate 21a is a thick portion that has a circular shape in a 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. The annular lower surface of the support portion 21b forms a mirror plate surface that slides between the orbiting scroll 22. The height position of this mirror plate surface is approximately 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.

[0015] The orbiting scroll 22 is a member that orbits in conjunction with the rotation of the crankshaft 7, and is disposed between the fixed scroll 21 and the frame plate 5. The orbiting scroll 22 is disposed so as to face the fixed scroll 21 with its central axis being eccentric by a predetermined distance from the central axis of the fixed scroll 21.

[0016] As shown in FIG. 1, the orbiting scroll 22 includes an end plate 22a, an orbiting wrap 22b, and an orbiting shaft 22c, which are integrally formed. The end plate 22a is a portion that slides between itself and the fixed scroll 21 and is disk-shaped. The orbiting wrap 22b is spiral-shaped and extends upward from the end plate 22a. The orbiting shaft 22c is cylindrical and extends downward from the center of the back surface of the end plate 22a. In other words, the orbiting shaft 22c is provided on the opposite side of the end plate 22a from the orbiting wrap 22b. The orbiting shaft 22c is fitted into the eccentric hole 71b of the crankshaft 7.

[0017] A compression chamber C1 is formed between the spiral fixed wrap 21c and the spiral orbiting wrap 22b. The compression chamber C1 is a space for compressing a gaseous refrigerant, and is formed on each of the inner and outer line sides of the orbiting wrap 22b. A discharge port K1 is provided near the center of the base plate 21a of the fixed scroll 21, and guides the refrigerant compressed in the compression chamber C1 to a discharge space C2 above the compression mechanism 2. The refrigerant discharged into the discharge space C2 through the discharge port K1 is guided to a motor chamber C3 below the compression mechanism 2 via a predetermined gap between the sealed container 1 and the compression mechanism 2.

[0018] The frame 3 is a metal member for supporting the fixed scroll 21 and for fixing the sub-bearing 13. The frame 3 has a roughly rotationally symmetrical shape, with the diameters of its inner and outer peripheral surfaces gradually decreasing toward its lower end. The lower part of the frame 3 (the part including the installation location of the sub-bearing 13) is close to the middle part 71a of the crankshaft 7. The frame 3 is installed inside the sealed container 1 and fixed to the inner peripheral surface of the cylindrical chamber 1a by welding or the like. The frame 3 is provided with an insertion hole 3a for inserting the crankshaft 7. Furthermore, the frame 3 is provided with an oil return hole 3b extending laterally. An oil return pipe 16 is inserted into the oil return hole 3b.

[0019] As shown in FIG. 1, a thrust bearing 4 is provided at the lower end of the frame 3. The thrust bearing 4 is a portion that receives axial (thrust direction) force from the stepped surface 73a of the crankshaft 7 via the thrust bearing 14, and is annular in plan view. The diameter of the inner peripheral edge of the thrust bearing 4 is shorter than the diameter of the intermediate portion 71a of the crankshaft 7. The inner peripheral edge of the thrust bearing 4 is also radially close to the peripheral surface of the small diameter portion 72a of the crankshaft 7. In the axial direction of the crankshaft 7, the thrust bearing 4 is spaced upward by a predetermined distance from the rotor 152 of the electric motor 15.

[0020] The thrust bearing 4 is a separate member from the frame 3 and is separable from the frame 3. Specifically, the thrust bearing 4 is fixed to the lower end of the frame 3 with a bolt B1. When replacing the thrust bearing 14, a worker removes the bolt B1 to separate the thrust bearing 4 from the frame 3. Having the frame 3 and the thrust bearing 4 as separate members in this way not only makes it easier to replace the thrust bearing 14, but also makes it possible to install a thrust bearing 14 with a relatively long outer diameter.

[0021] The frame plate 5 is an annular metal member that is fitted inside the frame 3. By providing such a frame plate 5, a balance weight 9 can be placed in the second space A2 between the frame 3 and the frame plate 5. Details of the frame plate 5 will be described later.

[0022] The first resin ring 61 is an annular resin member that seals the gap between the frame plate 5 and the end plate 22a of the orbiting scroll 22. The first resin ring 61 is installed in an annular first groove V1 (see FIG. 4) on the upper end surface of the frame plate 5. The second resin ring 63 is an annular resin member that seals the gap between the frame 3 and the frame plate 5. The second resin ring 63 is installed in an annular second groove V2 (see FIG. 4) on the outer circumferential surface of the frame plate 5.

[0023] 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 fixed coaxially 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.

[0024] The intermediate portion 71a is connected to the lower side of the eccentric portion 7b and is surrounded by the frame 3. The small diameter portion 72a has a smaller diameter than the intermediate portion 71a and is connected to the lower side of the intermediate portion 71a via a step surface 73a. Most of the small diameter portion 72a is located outside the frame 3 in the radial direction. In addition, the upper end of the small diameter portion 72a overlaps with the thrust receiving portion 4 in the radial direction.

[0025] 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 abuts against the upper surface of the thrust bearing 14. The surface direction of the stepped surface 73a is approximately perpendicular to the axial direction of the crankshaft 7.

[0026] The eccentric portion 7b has a cylindrical shape with a bottom 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 over the cylindrical revolving shaft 22c and opens upward. 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 a plan view, and its central axis is eccentric to a predetermined degree relative to the central axis of the main shaft portion 7a. As the electric motor 15 is driven, the revolving shaft 22c moves eccentrically relative to the main shaft portion 7a. As a result, the revolving scroll 22 eccentrically orbits relative to the fixed scroll 21.

[0027] 1, a through-hole 7c through which oil flows is provided in the axial direction inside the crankshaft 7. A radial horizontal hole 7d is also provided in the crankshaft 7 so as to communicate with the through-hole 7c. Some of the oil flowing through the through-hole 7c is guided to the sub-bearing 13 via the horizontal hole 7d.

[0028] The Oldham ring 8 is a ring-shaped member that receives the eccentric rotation of the orbiting shaft 22c and orbits the orbiting scroll 22 without rotating on its axis. The Oldham ring 8 is installed between the orbiting scroll 22 and the frame plate 5.

[0029] The balance weight 9 is a member for suppressing vibration of the scroll compressor 100, and is attached to the crankshaft 7. More specifically, the balance weight 9 is attached to the intermediate portion 71a of the crankshaft 7, directly below the eccentric portion 7b. By attaching the balance weight 9 near the upper end of the crankshaft 7 in this manner, it is possible to suppress deflection of the crankshaft 7 due to the centrifugal force of the balance weight 9. As shown in FIG. 1, the balance weight 9 is provided in the space between the frame 3 and the frame plate 5 (i.e., the second space A2). When the electric motor 15 is driven, the crankshaft 7 and the balance weight 9 rotate together.

[0030] 1, the second space A2 and the motor chamber C3 are separated by the frame 3. Therefore, even if the oil mist present in the second space A2 is agitated by the rotation of the balance weight 9, the rotation has almost no effect on the oil in the motor chamber C3. In other words, the oil present in the motor chamber C3 is less likely to be agitated, which can prevent the oil from leaking out through the discharge pipe P2.

[0031] The other balance weight 10 is installed below the rotor 152 of the electric motor 15. The rotor 152 and balance weight 10 rotate integrally. The balance weights 9 and 10 are arranged so that their centers of gravity are located on opposite sides of the crankshaft 7. This makes it easier to suppress vibrations in the scroll compressor 100. The number and installation locations of the balance weights can be changed as appropriate.

[0032] 1 supports the eccentric part 7b rotatably relative to the frame plate 5, and is fixed to the inner peripheral surface of the frame plate 5 by press-fitting or the like. A cylindrical sliding bearing, for example, is used as this main bearing 11. Note that the main bearing 11 may also be fixed to the outer peripheral surface of the eccentric part 7b instead of the inner peripheral surface of the frame plate 5.

[0033] The orbiting bearing 12 (second bearing) rotatably supports the orbiting shaft 22c relative to the circumferential surface of the eccentric hole 71b, and is disposed radially inward of the main bearing 11 (first bearing). For example, a cylindrical plain bearing is used as such an orbiting bearing 12. The orbiting bearing 12 is fixed to the circumferential surface of the eccentric hole 71b by press-fitting or the like. Alternatively, the orbiting bearing 12 may be fixed to the circumferential surface of the orbiting shaft 22c.

[0034] The sub-bearing 13 (third bearing) rotatably supports the middle section 71a of the crankshaft 7 relative to the frame 3. The sub-bearing 73 is fixed to the circumferential surface of the insertion hole 3a of the frame 3 by press-fitting or the like. The height position of the sub-bearing 13 is lower than the main bearing 11 and the slewing bearing 12, but higher than the height position of the electric motor 15. For example, a cylindrical plain bearing is used as this sub-bearing 13. Using plain bearings for the main bearing 11, slewing bearing 12, and sub-bearing 13 ensures durability during high-speed operation while reducing the cost of each bearing.

[0035] The thrust bearing 14 is a bearing that receives the axial (thrust direction) load from the crankshaft 7, and is in the shape of a thin ring. As shown in FIG. 1, the thrust bearing 14 is placed on the thrust bearing portion 4. The upper surface of the thrust bearing 14 functions as a thrust bearing surface that receives the axial force from the stepped surface 73a of the crankshaft 7. The thrust bearing 14 is positioned below the sub-bearing 13, slightly spaced apart from it in the up-down direction.

[0036] The electric motor 15 is a drive source that rotates the crankshaft 7. For example, a permanent magnet synchronous motor is used as the electric motor 15, but other types of motors may also be used. The electric motor 15 includes a stator 151 and a rotor 152, and is disposed below the compression mechanism 2.

[0037] The stator 151 has a stator core 151a and a winding 151b, and is fixed to the inner circumferential surface of the cylindrical chamber 1a. The stator core 151a is a cylindrical member made of a magnetic material. The winding 151b is wound around the stator core 151a in a predetermined manner.

[0038] The rotor 152 rotates around the central axis of the crankshaft 7 and is disposed radially inside the stator 151. The rotor 152 is configured, for example, by embedding a plurality of permanent magnets (not shown) in a cylindrical iron core made of laminated electromagnetic steel sheets. The plurality of electromagnetic steel sheets are fixed with rivets T1. When a predetermined current flows through the winding 151b, magnetic attractive and repulsive forces are generated between the stator 151 and the rotor 152, causing the rotor 152 to rotate.

[0039] The oil return pipe 16 is a pipe for returning the oil that has lubricated the main bearing 11, the slewing bearing 12, and the sub-bearing 13 to the oil reservoir R1. The oil return pipe 16 has an inverted L shape in side view, and as described above, is inserted into the oil return hole 3b of the frame 3. The upstream end of the oil return pipe 16 faces the second space A2 (the space between the frame 3 and the frame plate 5).

[0040] The upstream end of the oil return pipe 16 is preferably positioned above the sub-bearing 13 (third bearing) and below the balance weight 9. With this configuration, oil moved radially outward by the centrifugal force of the balance weight 9 adheres to the inner circumferential surface of the frame 3, and oil that flows down the inner circumferential surface of the frame 3 due to its own weight is more likely to be guided to the oil return pipe 16. In addition, because the lower side of the sub-bearing 73 is blocked by the thrust bearing 14, the oil that lubricated the sub-bearing 73 is also guided to the oil return pipe 16 via the second space A2.

[0041] The centrifugal pump 17 is a pump for sucking up oil from an oil reservoir R1 at the bottom of the sealed container 1, and is installed near the lower end of the crankshaft 7. In the example of FIG. 1, the centrifugal pump 17 is shown to be hollow inside, but this is not limiting. For example, a plate-shaped or spiral-shaped metal piece (not shown) may be installed inside the centrifugal pump 17. The multiple legs 18 are members for supporting the sealed container 1, and are installed in the bottom chamber 1c.

[0042] <About the double bearing structure> In the example of Fig. 1, the axial installation area of ​​the main bearing 11 and the axial installation area of ​​the slewing bearing 12 are substantially the same, but this is not limited to this. In other words, it is sufficient that the axial installation areas of the main bearing 11 and the slewing bearing 12 are configured to at least partially overlap. This type of configuration is called a "double bearing structure."

[0043] By adopting a double bearing structure, when a predetermined force associated with a gas load acts from the orbiting shaft 22c, the axial height positions of the point of application at the orbiting bearing 12 and the point of application at the main bearing 11 become approximately equal. This suppresses the generation of a moment that tilts the crankshaft 7, thereby suppressing one-sided contact of the crankshaft 7. Furthermore, even when the scroll compressor 100 is operated at high speed, deflection of the crankshaft 7 can be suppressed. Furthermore, compared to a configuration in which an orbiting bearing is arranged above the main bearing (not shown), the double bearing structure shortens the vertical dimension of the scroll compressor 100, allowing for a more compact design.

[0044] <About the cantilever support structure> As shown in Fig. 1, crankshaft 7 is supported in a cantilever manner inside frame 3. Here, "cantilever" means that the upper part of crankshaft 7 is journaled inside frame 3 without a sub-frame (not shown) being provided to journal the lower part of crankshaft 7. In the example of Fig. 1, crankshaft 7 is journaled inside frame 3 by main bearing 11 and sub-bearing 13. By adopting such a cantilever support structure, it is not necessary to provide a separate sub-frame (not shown), which contributes to cost reduction.

[0045] If a subframe is provided, a process for aligning the axes of the frame 3 and the subframe is required during assembly. However, even if attempts are made to align the axes of the frame 3 and the subframe, there is a limit to how much coaxiality can be improved by assembling two components. In addition, there is the effect of thermal deformation caused by welding the frame 3 to the cylindrical chamber 1a, which may result in a large error in the axis alignment between the main bearing 11 and the sub-bearing 13.

[0046] In contrast, in the first embodiment, there is no particular need to provide a subframe (not shown), and therefore coaxiality can be significantly improved compared to when the axes of the subframe and the frame are aligned. As a result, tilt of the crankshaft 7 can be suppressed, and ultimately, whirling and uneven contact of the crankshaft 7 can be suppressed. Furthermore, since there is no need to provide a subframe, material costs can be reduced, and the subframe assembly process can be omitted, improving production efficiency.

[0047] <About the first and second resin rings> FIG. 2 is a partial enlarged view of the area including the frame plate 5 in FIG. As shown in Fig. 2, the frame plate 5 is provided with an insertion hole 5h for inserting the eccentric portion 7b of the crankshaft 7. The frame plate 5 also has an annular first groove V1 (reference numeral omitted in Fig. 2; see Fig. 3A) recessed downward from its upper end surface. A leaf spring 62 and a first resin ring 61 are sequentially installed in this first groove V1.

[0048] As described above, the first resin ring 61 is an annular resin member for sealing the gap between the frame plate 5 and the end plate 22a of the orbiting scroll 22. For example, a square ring having a rectangular cross section is used as the first resin ring 61. By using a square ring as the first resin ring 61, durability against a downward load from the orbiting scroll 22 is improved.

[0049] The first resin ring 61 functions to separate a high-pressure space communicating with the through-hole 7c (see FIG. 1) of the crankshaft 7 (see FIG. 1) from a first space A1 of a predetermined intermediate pressure. That is, the space radially inside the first resin ring 61 is a high-pressure space whose pressure is approximately equal to the discharge pressure. On the other hand, the space radially outside the first resin ring 61 is the first space A1 of an intermediate pressure lower than the discharge pressure. The pressure in this first space A1 pushes the orbiting scroll 22 upward to an appropriate degree.

[0050] The leaf spring 62 (see also FIG. 4) has the function of pushing the first resin ring 61 upward (i.e., toward the orbiting scroll 22). The leaf spring 62 has an annular shape in a plan view and is installed in the first groove V1. Specifically, the leaf spring 62 is installed at the bottom of the first groove V1, and the first resin ring 61 is installed above this leaf spring 62. The first resin ring 61 is compressed in the vertical direction between the leaf spring 62 and the lower surface of the end plate 22a of the orbiting scroll 22. Note that the leaf spring 62 may be omitted as appropriate.

[0051] The frame plate 5 is provided with a second groove V2 (reference numeral omitted in FIG. 2, see FIG. 3B) circumferentially recessed from its outer circumferential surface toward the inside in the radial direction. A second resin ring 63 is installed in this second groove V2. The second resin ring 63 is an annular resin member for sealing the gap between the frame 3 and the fitting portion 54 (see FIG. 3B) of the frame plate 5. For example, an O-ring with a circular cross section is used as this second resin ring 63. Using an O-ring as the second resin ring 63 improves sealing properties and airtightness.

[0052] The second resin ring 63 has the function of separating the first space A1 and the second space A2. That is, the space above the second resin ring 63 forms the first space A1. On the other hand, the space below the second resin ring 63 forms the second space A2. The pressure in the second space A2 is higher than that in the first space A1, but slightly lower than that of the high-pressure space radially inward of the first resin ring 61. The second resin ring 63 is compressed radially between the wall surface of the second groove V2 (see FIG. 3B) and the inner circumferential surface of the frame 3, and is appropriately crushed.

[0053] It is possible that the central axis of the frame 3 may be slightly displaced from its original position due to thermal deformation when the frame 3 is fixed to the sealed container 1 by welding or the like. Even in such a case, the second resin ring 63 between the frame 3 and the frame plate 5 is appropriately compressed in the radial direction, thereby preventing a decrease in assembly accuracy due to the thermal deformation. As a result, it becomes easier to ensure coaxiality between the main bearing 11 mounted on the frame plate 5 and the sub-bearing 13 (see FIG. 1) mounted on the frame 3.

[0054] FIG. 3A is a perspective view of the frame plate 5 as viewed from above. As shown in Fig. 3A, the frame plate 5 includes a base portion 51, a protruding portion 52, a pair of support portions 53, and a fitting portion 54, which are integrally formed. An insertion hole 5h is provided near the center of the frame plate 5, through which the eccentric portion 7b (see Fig. 1) of the crankshaft 7 (see Fig. 1) is inserted. The base portion 51 is used for fastening to the frame 3, and has an annular shape in plan view. A total of 12 bolt insertion holes 51k are provided near the outer periphery of the upper surface of the base portion 51. Counterbore holes (reference numerals not shown) shaped to correspond to the heads of bolts are provided around each bolt insertion hole 51k.

[0055] The protruding portion 52 is a portion that protrudes upward from the inner peripheral edge of the base portion 51 and has an annular shape in a plan view. The protruding portion 52 is provided with a first annular groove V1 that is recessed downward from its upper surface. As described above, the leaf spring 62 (see FIG. 4) and the first resin ring 61 (see FIG. 4) are sequentially installed in the first groove V1.

[0056] The pair of support portions 53 are portions that support the pair of second keys 8c (see FIG. 4) of the Oldham ring 8 (see FIG. 4) and guide the movement of these second keys 8c. The pair of support portions 53 are arranged on opposite sides of the annular protruding portion 52, and extend radially outward in a straight line beyond the base portion 51. A key groove 53a is provided on each of the upper surfaces of the pair of support portions 53. The key groove 53a is a radial groove that guides the second keys 8c (see FIG. 4) of the Oldham ring 8 (see FIG. 4).

[0057] FIG. 3B is a perspective view of the frame plate 5 as viewed from below. The fitting portion 54 shown in FIG. 3B is a portion that fits inside the frame 3 (see FIG. 2). The fitting portion 54 has an annular shape with an outer diameter shorter than that of the base portion 51 and is continuous with the lower side of the base portion 51. The base portion 51 and the fitting portion 54 have the same inner diameter (i.e., the circumferential surfaces of the insertion holes 5h are flush). When the frame plate 5 is installed on the frame 3 (see FIG. 2), a portion 51a of the base portion 51 that extends radially outward beyond the fitting portion 54 abuts against the inner horizontal surface 3c (see FIG. 2) of the frame 3. A ring-shaped second groove V2 that is recessed radially inward is provided in the circumferential direction on the outer peripheral surface of the fitting portion 54. As described above, the second resin ring 63 (see FIG. 4) is installed in this second groove V2.

[0058] FIG. 4 is an exploded perspective view of the scroll compressor 100. As shown in FIG. In addition, FIG. 4 illustrates the Oldham ring 8, the first resin ring 61, the leaf spring 62, the second resin ring 63, the frame plate 5, the plurality of bolts B2, a portion of the frame 3, and a portion of the eccentric portion 7b of the crankshaft 7, and does not illustrate the remaining components.

[0059] As shown in FIG. 4, the Oldham ring 8 includes an annular portion 8a, a pair of first keys 8b, and a pair of second keys 8c, which are integrally formed. The annular portion 8a is a portion that has an annular shape in a plan view. The pair of first keys 8b are portions that fit into key grooves (not shown) on the underside of the orbiting scroll 22 (see FIG. 1) and extend upward from the annular portion 8a. The pair of first keys 8b are provided at positions symmetrical with respect to the center of the annular portion 8a (the same applies to the pair of second keys 8c). As described above, the pair of second keys 8c are portions that fit into the key grooves 53a of the frame plate 5 and extend downward from the annular portion 8a. The first keys 8b and the second keys 8c are provided alternately in the circumferential direction of the annular portion 8a at 90° intervals (at 90° circumferential angles based on the center of the annular portion 8a).

[0060] As described above, the first resin ring 61 is installed in the first groove V1 of the frame plate 5. The leaf spring 62 is installed in the first groove V1 below the first resin ring 61. The second resin ring 63 is installed in the second groove V2 of the frame plate 5.

[0061] 4, the multiple bolts B2 fix the frame plate 5 to the frame 3 and are inserted one by one into the bolt insertion holes 51k. Note that multiple bolt holes 3d shaped to correspond to the bolts B2 are also provided on the inner horizontal surface 3c of the frame 3. When assembling the frame plate 5, the frame plate 5 is first installed on the frame 3 by being pushed downward. In this state, the second resin ring 63 is compressed in the radial direction between the outer peripheral surface of the fitting portion 54 and the inner peripheral surface of the frame 3.

[0062] Furthermore, a bolt B2 is inserted through the bolt insertion hole 51k of the frame plate 5 and the bolt hole 3d of the frame 3 in this order. As a result, the opening H1 on the upper side of the frame 3 (the side of the orbiting scroll 22 in FIG. 1) is closed by the frame plate 5. Note that a plurality of bolt holes 3e provided in the upper end surface of the frame 3 are used for fastening to the fixed scroll 21 (see FIG. 1).

[0063] As shown in Fig. 4, a pair of end face grooves 72b is provided in the eccentric portion 7b of the crankshaft 7. The end face grooves 72b are radial grooves provided in the upper end surface of the eccentric portion 7b. The end face grooves 72b have the function of guiding oil that has lubricated the orbiting bearing 12 (see Fig. 1) to the main bearing 11 (see Fig. 1). In the example shown in Fig. 4, the pair of end face grooves 72b are provided in a straight line so as to sandwich the orbiting bearing 12, but this is not limited to this. That is, the number of end face grooves 72b may be one, or may be three or more.

[0064] FIG. 5 is an explanatory diagram showing the flow of oil in the scroll compressor 100. The configuration of the scroll compressor 100 shown in Fig. 5 is the same as that shown in Fig. 1. The dashed arrows in Fig. 5 indicate the flow of oil. Oil is sucked up by the centrifugal pump 17 as the electric motor 15 is driven, and flows upward through the through-hole 7c of the crankshaft 7, and a portion of the oil is guided to the sub-bearing 13 through the horizontal hole 7d. The oil that lubricates the sub-bearing 13 is returned to the oil reservoir R1 via the second space A2 and the oil return pipe 16 in this order.

[0065] As described above, the thrust bearing 14 is provided below the auxiliary bearing 13. A downward load is applied to the thrust bearing 14 from the crankshaft 7. As a result, the stepped surface 73a of the crankshaft 7 and the upper surface of the thrust bearing 14 come into close contact with each other. In other words, there is almost no gap between the stepped surface 73a and the thrust bearing 14 that would allow oil to flow, which prevents the oil that lubricates the auxiliary bearing 13 from dripping onto the rotor 152. This prevents the oil from being agitated by the rotating rotor 152, which in turn prevents the oil from leaking out through the discharge pipe P2.

[0066] Furthermore, a portion of the oil flowing through the through hole 7c rises along the orbiting bearing 12 (second bearing). That is, the oil rises through a groove (not shown) between the orbiting shaft 22c and the orbiting bearing 12, lubricating the orbiting bearing 12. After lubricating the orbiting bearing 12 and reaching the upper end of the eccentric portion 7b, the oil flows radially outward through the end face groove 72b (see FIG. 4) and then descends along the main bearing 11 (first bearing). That is, the oil descends through a groove (not shown) between the outer circumferential surface of the eccentric portion 7b and the main bearing 11, lubricating the main bearing 11. The oil that has lubricated the main bearing 11 is returned to the oil reservoir R1 via the second space A2 and the oil return pipe 16 in this order.

[0067] In this way, the oil that rises along the orbiting bearing 12 (second bearing) flows through the end face groove 72b (see FIG. 4), and then this oil descends along the main bearing 11 (first bearing) and is led to the second space A2 (the space between the frame 3 and the frame plate 5). As a result, the orbiting bearing 12 and the main bearing 11 are lubricated sequentially with oil, which makes it possible to suppress wear of the orbiting bearing 12 and the main bearing 11.

[0068] A portion of the oil that has risen through the through hole 7c is guided to an oil groove (not shown) on the end plate surface of the fixed scroll 21 via an oil supply passage (not shown) inside the orbiting scroll 22. The oil guided to the oil groove (not shown) is used for sealing and lubricating the compression chamber C1, and then is guided to the first space A1.

[0069] <Effects> According to the first embodiment, a double bearing structure is adopted in which the main bearing 11 and the orbiting bearing 12 overlap in the radial direction, which makes it possible to suppress the generation of a moment that would tilt the crankshaft 7. Therefore, it is possible to suppress deflection and uneven contact of the crankshaft 7 even during high-speed operation. Furthermore, the double bearing structure makes it possible to shorten the vertical length of the scroll compressor 100, thereby making it more compact.

[0070] Furthermore, in the first embodiment, because the crankshaft 7 is supported at one end using a cantilever support structure, there is no particular need to provide a separate subframe (not shown) for supporting the lower part of the crankshaft 7. This makes it possible to reduce material costs, simplify the assembly process, and lower costs. Furthermore, by omitting the subframe, the concentricity between the main bearing 11 and the sub-bearing 13 is significantly improved, which, combined with the double bearing structure described above, helps to suppress deflection of the crankshaft 7.

[0071] Furthermore, a second resin ring 63 (see FIG. 4) is installed in a second groove V2 (see FIG. 4) on the outer circumferential surface of the frame 3, and the second resin ring 63 is compressed in the radial direction. This reduces the influence of thermal deformation when the frame 3 is fixed to the cylindrical chamber 1a by welding or the like. As a result, the coaxiality between the main bearing 11 installed on the frame plate 5 and the sub-bearing 13 installed on the frame 3 is improved, and ultimately the performance and reliability of the scroll compressor 100 can be improved.

[0072] Second Embodiment In the second embodiment, an air conditioner W1 (see FIG. 6) including a scroll compressor 100 (see FIG. 1) having the configuration described in the first embodiment will be described.

[0073] FIG. 6 is a configuration diagram of an air conditioner W1 according to the second embodiment. The solid arrows in FIG. 6 indicate the flow of the refrigerant in the heating cycle. On the other hand, the dashed arrows in FIG. 6 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. 6, 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.

[0074] 6, 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, while the indoor heat exchanger 95 and the indoor fan 96 are provided in the indoor unit U2.

[0075] The scroll compressor 100 is a device that compresses a gaseous refrigerant, and has a configuration similar to that of the first embodiment (see FIG. 1). The outdoor heat exchanger 91 is a heat exchanger in which heat exchange occurs between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent in from an outdoor fan 92. The outdoor fan 92 is a fan that sends outside air to the outdoor heat exchanger 91. The outdoor fan 92 is provided with an outdoor fan motor 92a that serves as a drive source, and is installed near the outdoor heat exchanger 91.

[0076] The indoor heat exchanger 95 is a heat exchanger in which heat is exchanged between the refrigerant flowing through its heat transfer pipes (not shown) and the indoor air (air in the air-conditioned room) sent in from the indoor fan 96. The indoor fan 96 is a fan that sends the indoor air to the indoor heat exchanger 95. The indoor fan 96 is provided with an indoor fan motor 96a that serves as a drive source, and is installed near the indoor heat exchanger 95.

[0077] The expansion valve 93 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 91 and the indoor heat exchanger 95). The refrigerant reduced in pressure by the expansion valve 93 is introduced to the "evaporator" (the other of the outdoor heat exchanger 91 and the indoor heat exchanger 95).

[0078] The four-way valve 94 is a valve that switches the refrigerant flow path depending on the operation mode of the air conditioner W1. For example, during cooling operation (see the dashed arrow in FIG. 6), 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). During heating operation (see the solid arrow in FIG. 6), 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).

[0079] <Effects> According to the second embodiment, the air conditioner W1 is equipped with the scroll compressor 100 which has high performance and reliability, and therefore the performance and reliability of the air conditioner W1 as a whole can be improved.

[0080] <<Variations>> The scroll compressor 100 and the air conditioner W1 according to the present disclosure have been described above in relation to the various embodiments, but they are not limited to these descriptions and can be modified in various ways. For example, in the first embodiment, a configuration in which the second resin ring 63 (see FIG. 4) is installed on the frame plate 5 (see FIG. 4) has been described, but this is not limited to this, and may be, for example, as shown in FIG. 7.

[0081] FIG. 7 is a perspective view of a frame plate 5A viewed from below in a scroll compressor according to a modified example. In the example of FIG. 7, the second groove V2 (see FIG. 4) and the second resin ring 63 (see FIG. 4) described in the first embodiment are not particularly provided in the frame plate 5A, and the outer peripheral surface of the fitting portion 54A is flush. The fitting portion 54A is fixed to the frame 3 (see FIG. 1) by clearance fit or press fit, and contacts the inner peripheral surface of the frame 3. Although not visible in FIG. 7, the first groove V1 (see FIG. 4) and the first resin ring 61 (see FIG. 4) are also provided in the frame plate 5A, as in the first embodiment. Even with this configuration, the frame plate 5A is positioned relative to the frame 3, so a decrease in assembly accuracy can be suppressed.

[0082] Furthermore, in the first embodiment, a configuration in which the thrust bearing 14 (see FIG. 1) is installed on the thrust receiving portion 4 (see FIG. 1) has been described, but it is also possible to omit the thrust bearing 14. In this case, the step surface 73a (see FIG. 1) of the crankshaft 7 abuts against the thrust receiving portion 4 (see FIG. 1) at the lower end of the frame 3. Note that the thrust receiving portion 4 has a thrust receiving surface (the upper surface of the thrust receiving portion 4) that receives an axial force from the step surface 73a. Even with this configuration, the thrust receiving portion 4 can receive a downward force from the crankshaft 7.

[0083] In the first embodiment, the frame 3 (see FIG. 1) and the thrust receiving portion 4 (see FIG. 1) are separate bodies, but the present invention is not limited to this. That is, the frame 3 and the thrust receiving portion 4 may be integrally formed. Furthermore, in the first embodiment, the case where the balance weight 9 (see FIG. 1) is provided in the second space A2 (see FIG. 1) has been described, but the balance weight 9 can also be omitted as appropriate.

[0084] In the first embodiment, the scroll compressor 100 is described as including the sub-bearing 13 (see FIG. 1), but this is not limiting. For example, the sub-bearing 13 may be omitted as appropriate. In the first embodiment, the second groove V2 is provided in the circumferential direction on the outer peripheral surface of the fitting portion 54 (see FIG. 3B) of the frame plate 5, and the second resin ring 63 (see FIG. 2) is installed in the second groove V2. However, the present invention is not limited to this. In other words, the locations where the second groove V2 and the second resin ring 63 are provided can be changed as appropriate.

[0085] The air conditioner W1 (see FIG. 6) described in the second embodiment can be applied to various types of air conditioners, such as multi-air conditioners for buildings, package air conditioners, and room air conditioners. The second embodiment describes the air conditioner W1 equipped with the scroll compressor 100, but the present invention is not limited to this. For example, the second embodiment can also be applied to other refrigeration cycle devices, such as freezers, water heaters, air-conditioning water heaters, chillers, and refrigerators.

[0086] Furthermore, in the second embodiment, the air conditioner W1 (see FIG. 6) is described as being equipped with a four-way valve 94, but this is not limiting. That is, the four-way valve 94 may be omitted as appropriate, and the air conditioner may be dedicated to cooling or heating. In the first embodiment, the scroll compressor 100 is described as being installed vertically, but this is not limiting. For example, the scroll compressor 100 may be installed horizontally or obliquely. In this case, the side of the crankshaft 7 where the eccentric portion 7b is provided is considered to be the "upper side," and the side where the small diameter portion 72a is provided is considered to be the "lower side."

[0087] Furthermore, each embodiment has been described in detail to clearly explain the present disclosure, and is not necessarily limited to having all of the configurations described. Furthermore, part of the configuration of each embodiment can be appropriately added to, deleted from, or replaced with other configurations. Furthermore, the mechanisms and configurations described above are those that are considered necessary for the explanation, and do not necessarily represent all mechanisms and configurations of the product. [Explanation of symbols]

[0088] 1. Airtight container 2 Compression mechanism 3 frames 3a Insertion port 3b Oil return hole 3c horizontal plane 3d bolt holes 3e Bolt holes 4 Thrust receiving part 5 Frame Plate 5h Insertion hole 7. Crankshaft 7a Main shaft part 7b Eccentric part 7c through hole 8 Oldham Ring 8a Annular section 8b 1st key 8c Second Key 9 Balance Weight 11 Main bearing (first bearing) 12 Slewing bearing (second bearing) 13 Sub-bearing (third bearing) 14 Thrust bearing 15 Electric motor 16 Oil return pipe 17 Centrifugal Pump 18 legs 21 Fixed Scroll 21a Base plate 21b Support part 21c fixed wrap 22 Swivel Scroll 22a Headboard 22b Circling Wrap 22c Pivot 51 Base 51k bolt insertion hole 52 Protrusion 53 Support part 53a Keyway 54,54A Mating part 61 First resin ring 62 Leaf spring 63 Second resin ring 71a Middle part 71b Eccentric hole 72b End groove 72a Small diameter section 73a Step surface 91 Outdoor heat exchanger 92 Outdoor fan 92a Outdoor fan motor 93 Expansion valve 94 Four-way valve 95 Indoor heat exchanger 96 Indoor fan 96a Indoor fan motor 100 Scroll Compressor 151 Stator 151a stator core 151b Winding 152 rotor A1 1st space A2 2nd space (space) B1, B2 bolts C1 compression chamber C2 discharge space C3 Motor Room H1 opening V1 1st groove V2 2nd groove W1 Air Conditioner

Claims

1. A sealed container and a frame installed inside the sealed container; a fixed scroll having a spiral-shaped fixed wrap and fixed to the frame; an orbiting scroll having a spiral orbiting wrap that forms a compression chamber between itself and the fixed wrap, and having an orbiting shaft that is provided on the opposite side of the orbiting wrap with respect to the end plate; a crankshaft having an eccentric portion provided with an eccentric hole that fits onto the pivot shaft, the crankshaft being cantilevered within the frame; a frame plate having a fitting portion that fits inside the frame and in which an insertion hole of the eccentric portion is provided; a first bearing that rotatably supports the eccentric portion relative to the frame plate; a second bearing that rotatably supports the pivot shaft relative to a peripheral surface of the eccentric hole; a first resin ring that seals the gap between the frame plate and the end plate; an Oldham ring interposed between the orbiting scroll and the frame plate; The frame plate is an annular base portion in which the insertion hole is provided; an annular protrusion protruding upward from an inner peripheral edge of the base portion; a pair of support portions disposed on opposite sides of the protruding portion, the first resin ring is placed in a first annular groove recessed downward from the upper surface of the protrusion; a second key of the Oldham ring being guided via a radial key groove provided on each upper surface of the pair of support portions;

2. a second resin ring that seals between the frame and the fitting portion; a second groove is provided in the outer peripheral surface of the fitting portion in the circumferential direction; The second resin ring is installed in the second groove.

2. The scroll compressor according to claim 1,

3. A balance weight is provided in the space between the frame and the frame plate and rotates integrally with the crankshaft.

2. The scroll compressor according to claim 1,

4. the crankshaft has an intermediate portion connected to a lower side of the eccentric portion, and a small diameter portion connected to the lower side of the intermediate portion via a stepped surface and having a diameter shorter than that of the intermediate portion, a third bearing that rotatably supports the intermediate portion relative to the frame; An oil return pipe is inserted into the oil return hole of the frame, and an upstream end thereof faces the space between the frame and the frame plate, The upstream end of the oil return pipe is disposed above the third bearing and below the balance weight.

4. The scroll compressor according to claim 3,

5. the crankshaft has an intermediate portion connected to a lower side of the eccentric portion, and a small diameter portion connected to the lower side of the intermediate portion via a stepped surface and having a diameter shorter than that of the intermediate portion, The step surface abuts against a thrust receiving portion provided at the lower end of the frame, or abuts against a thrust bearing placed on the thrust receiving portion.

2. The scroll compressor according to claim 1,

6. The thrust receiving portion is a separate member from the frame and is separable from the frame.

6. The scroll compressor according to claim 5,

7. a radial end surface groove is provided on the upper end surface of the eccentric portion; The oil that rises along the second bearing flows through the end face groove, and then the oil descends along the first bearing and is guided to the space between the frame and the frame plate.

2. The scroll compressor according to claim 1,

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

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