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 provided on the opposite side of the orbiting wrap 22b relative to the end plate 22a, a crankshaft 7 having an eccentric portion 7b in which an eccentric hole 71b that fits onto the orbiting axis 22c is provided, a frame plate 5 having an insertion hole for the eccentric portion 7b and fitting inside the frame 3, a main bearing 11 that rotatably supports the eccentric portion 7b relative to the frame plate 5, and an orbiting bearing 12 that rotatably supports the orbiting axis 22c relative to the circumferential surface of the eccentric hole 71b, and also comprises a seal ring 6 that seals between the frame plate 5 and the end plate 22a, and the height position of the upper end of the main bearing 11 is lower than the height position of the lower end of the seal ring 6.

Description

[Technical Field]

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

[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 configured such that an eccentric hole is provided at the upper end of a crankshaft and a scroll pin is fitted into this eccentric hole. Furthermore, a main bearing is disposed on the outer periphery side of the eccentric hole, and an orbiting bearing is disposed on the inner periphery side. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 2923582 Summary of the Invention [Problem to be solved by the invention]

[0004] The technology described in Patent Document 1 has a double bearing structure in which the main bearing and the orbiting bearing overlap in the radial direction, but there is still room for further improvement in the performance and reliability of the scroll compressor.

[0005] 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]

[0006] 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 that is 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, a frame plate provided with an insertion hole of the eccentric portion and fitted inside the frame, a first bearing that rotatably supports the eccentric portion relative to the frame plate, and a second bearing that rotatably supports the orbiting shaft relative to a circumferential surface of the eccentric hole. an Oldham ring interposed between the orbiting scroll and the frame plate; and a seal ring for sealing between the frame plate and the end plate, wherein the height position of the upper end of the first bearing is lower than the height position of the lower end of the seal ring. The Oldham ring has a first key guided through a first key groove of the orbiting scroll and a second key guided through a second key groove of the frame plate, and the second key groove is a groove recessed downward from the Oldham ring support surface of the frame plate, and the height position of the upper end of the first bearing is lower than the height position of the Oldham ring support surface. It was decided that. Other details will be explained in the embodiments. [Effects of the Invention]

[0007] According to the present disclosure, a scroll compressor and the like with high performance and reliability can be provided. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a vertical cross-sectional view of a scroll compressor according to a first embodiment. [Figure 2A] 2 is a perspective view of the scroll compressor according to the first embodiment, when viewed from above, of a frame plate. FIG. [Figure 2B] 2 is a perspective view of the scroll compressor according to the first embodiment, showing a frame plate viewed from below. FIG. [Figure 3] 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 4] FIG. 1 is an exploded perspective view of a scroll compressor according to a first embodiment. [Figure 5]FIG. 2 is a bottom view of the orbiting scroll included in the scroll compressor according to the first embodiment. [Figure 6A] 2 is a cross-sectional view showing a state in which a frame plate is being assembled to a frame and a crankshaft in the scroll compressor according to the first embodiment. FIG. [Figure 6B] 3 is a cross-sectional view showing a state in which a frame plate is press-fitted into a frame in the scroll compressor according to the first embodiment. FIG. [Figure 6C] 3 is a cross-sectional view showing a state in which press-fitting of a frame plate is completed in the scroll compressor according to the first embodiment. FIG. [Figure 7] FIG. 2 is a plan view of the scroll compressor according to the first embodiment, with a cover chamber, a fixed scroll, an orbiting scroll, and an Oldham ring removed. [Figure 8] FIG. 10 is a vertical cross-sectional view of a region including a frame plate of a scroll compressor according to a second embodiment. [Figure 9] FIG. 6 is an exploded perspective view of a scroll compressor according to a second embodiment. [Figure 10] FIG. 10 is a vertical cross-sectional view of a region including a frame plate of a scroll compressor according to a third embodiment. [Figure 11] FIG. 10 is a vertical cross-sectional view of a scroll compressor according to a fourth embodiment. [Figure 12] FIG. 10 is a configuration diagram of an air conditioner according to a fifth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] 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, and a seal ring 6. 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.

[0010] 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.

[0011] 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.

[0012] 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.

[0013] 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.

[0014] 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.

[0015] 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.

[0016] 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 wire 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 for guiding 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.

[0017] The frame 3 is a metal member for supporting the fixed scroll 21 and for fixing the sub-bearing 13. 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 has a roughly rotationally symmetrical shape, and the diameters of the inner peripheral surface and outer peripheral surface gradually decrease toward the 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 provided with an insertion hole 3a for inserting the crankshaft 7. The frame 3 also has an oil return hole 3b formed laterally. An oil return pipe 16 is inserted into the oil return hole 3b.

[0018] 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 example of FIG. 1, the thrust bearing 4 is a separate member from the frame 3, but it may also be formed integrally with the frame 3.

[0019] The frame plate 5 is a metal member that fits inside the frame 3. By providing such a frame plate 5, a balance weight 9 can be placed in the space between the frame 3 and the frame plate 5 (balance weight space A2 in FIG. 1). Details of the frame plate 5 will be described later.

[0020] The seal ring 6 is an annular resin member for sealing the gap between the frame plate 5 and the end plate 22a of the orbiting scroll 22. The seal ring 6 is installed in an annular groove V1 (see FIG. 4) provided in the upper end surface of the frame plate 5.

[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 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.

[0022] 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.

[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 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.

[0024] 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.

[0025] As shown in Fig. 1, a through-hole 7c through which oil flows is provided in the axial direction inside the main shaft portion 7a. The main shaft portion 7a also has a radial horizontal hole 7d that communicates 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.

[0026] The Oldham ring 8 is a metal ring-shaped member for orbiting the orbiting scroll 22 without rotating it on its axis. The Oldham ring 8 is interposed between the orbiting scroll 22 and the frame plate 5. In FIG. 1, a cross section of an annular portion 8a of the Oldham ring 8 (see also FIG. 4) is visible. Details of the Oldham ring 8 will be described later.

[0027] 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 middle 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, deflection of the crankshaft 7 due to the centrifugal force of the balance weight 9 can be suppressed.

[0028] 1, the balance weight 9 is disposed in a space (balance weight space A2) between the frame 3 and the frame plate 5. When the electric motor 15 is driven, the crankshaft 7 and the balance weight 9 rotate integrally. The balance weight space A2 and the motor chamber C3 are separated by the frame 3. Therefore, even if the mist of oil present in the balance weight space A2 is agitated by the rotation of the balance weight 9, the agitation hardly affects 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 prevents the oil from leaking out through the discharge pipe P2.

[0029] 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 centers of gravity of the balance weights 9 and 10 are located on opposite sides of the crankshaft 7. This makes it possible to effectively suppress vibrations of the scroll compressor 100. The number and installation locations of the balance weights can be changed as appropriate.

[0030] 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.

[0031] The slewing bearing 12 (second bearing) rotatably supports the slewing 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 this slewing bearing 12. The slewing bearing 12 is fixed to the circumferential surface of the eccentric hole 71b by press-fitting or the like. Note that the slewing bearing 12 may be fixed to the circumferential surface of the slewing shaft 22c instead of the circumferential surface of the eccentric hole 71b.

[0032] 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.

[0033] The thrust bearing 14 is a bearing that receives an axial (thrust direction) load from the crankshaft 7 and is shaped like 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 forms a thrust bearing surface that receives an axial force from the stepped surface 73a of the crankshaft 7. The thrust bearing 14 is positioned below the sub-bearing 13 and is slightly spaced apart from the sub-bearing 13 in the up-down direction.

[0034] 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.

[0035] 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.

[0036] 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.

[0037] 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 balance weight space A2.

[0038] The centrifugal pump 17 is a pump for sucking up oil from the oil reservoir R1 at the bottom of the sealed container 1, and is installed near the lower end of the crankshaft 7. A plurality of legs 18 are members for supporting the sealed container 1, and are installed in the bottom chamber 1c.

[0039] <About the double bearing structure> In the example of Fig. 1, the upper part of the main bearing 11 and the lower part of the slewing bearing 12 overlap in the radial direction, 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 at least partially overlap. This type of configuration is called a "double bearing structure."

[0040] By adopting a double bearing structure, when a force associated with a gas load acts from the orbiting shaft 22c, the axial height positions of the point of action at the orbiting bearing 12 and the point of action at the main bearing 11 are approximately equal. This prevents the generation of a moment that would tilt the crankshaft 7, thereby preventing 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 prevented.

[0041] <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.

[0042] 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 members, and there is also the effect of thermal deformation associated with welding of the frame 3, which could result in a large error in the axis alignment between the main bearing 11 and the sub-bearing 13.

[0043] 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 in turn, whirling and uneven contact of the crankshaft 7 can be suppressed. Furthermore, since there is no particular process for assembling the subframe, production efficiency can be improved.

[0044] FIG. 2A is a perspective view of the frame plate 5 as viewed from above. 2A, an insertion hole 5h for inserting the eccentric portion 7b (see FIG. 1) of the crankshaft 7 (see FIG. 1) is provided near the center of the frame plate 5. 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.

[0045] The base portion 51 is a portion that is fastened to the frame 3 (see FIG. 4) by a plurality of bolts B2 (see FIG. 4). The base portion 51 has an annular shape in a plan view, and has an insertion hole 5h formed near its center. A total of four bolt insertion holes 51k are formed at approximately equal intervals in the circumferential direction near the outer periphery of the upper surface of the base portion 51. From another perspective, the plurality of bolt insertion holes 51k are formed in a portion 51a (see FIG. 2B) of the base portion 51 that protrudes radially outward beyond the fitting portion 54. Around each bolt insertion hole 51k, a counterbore hole (reference numeral not shown) is formed that has a shape corresponding to the head of the bolt B2 (see FIG. 4).

[0046] 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 has an annular groove V1 that is recessed downward from its upper surface (the surface facing the end plate 22a of the orbiting scroll 22: see FIG. 1). A leaf spring 19 (see FIG. 4) and a seal ring 6 (see FIG. 4) are sequentially installed in the groove V1.

[0047] The pair of support portions 53 are portions that support the annular portion 8a (see FIG. 4) of the Oldham ring 8 (see FIG. 4) and guide the second key 8c (see FIG. 4) of the Oldham ring 8 via the second key groove 53b. The pair of support portions 53 are arranged on opposite sides of the annular protrusion 52 and extend linearly radially outward beyond the base portion 51. The upper surface of each support portion 53 serves as an Oldham ring support surface 53a for supporting the annular portion 8a (see FIG. 4) of the Oldham ring 8. That is, the Oldham ring support surface 53a contacts the lower surface of the annular portion 8a (see FIG. 4) and supports the annular portion 8a. Therefore, when the Oldham ring 8 is installed on the frame plate 5, the height position of the lower surface of the annular portion 8a approximately coincides with the height position of the Oldham ring support surface 53a.

[0048] A second key groove 53b is provided in each of the pair of support portions 53. The second key groove 53b is a radial groove recessed downward from the Oldham ring support surface 53a of the frame plate 5. The second key groove 53b has a function of guiding the second key 8c (see FIG. 4) of the Oldham ring 8 (see FIG. 4).

[0049] FIG. 2B is a perspective view of the frame plate 5 as viewed from below. The fitting portion 54 shown in Fig. 2B is a portion that fits inside the frame 3 (see Fig. 3), and is continuous with the lower side of the base portion 51. In the first embodiment, as an example of the above-mentioned "fitting," a case will be described in which the fitting portion 54 is press-fitted into the inner peripheral surface of the frame 3. The fitting portion 54 has an annular shape in a plan view, and an insertion hole 5h is provided near the center thereof.

[0050] The outer diameter of the base portion 51 is longer than the outer diameter of the fitting portion 54. Therefore, when the frame plate 5 is press-fitted into the frame 3 (see FIG. 3), a portion 51a of the base portion 51 that protrudes radially outward beyond the fitting portion 54 abuts against the horizontal surface 3c (see FIG. 3) inside the frame 3. This restricts downward movement of the frame plate 5 during press-fitting. Furthermore, when the frame plate 5 is press-fitted into the frame 3 (see FIG. 3), the outer peripheral surface of the fitting portion 54 comes into close contact with the inner peripheral surface of the frame 3. Here, "close contact" means that the two components are in contact with each other without any gaps, but does not necessarily mean that no gaps are allowed at all. In addition to press-fitting, shrink fitting can also be used as a method of "close contact."

[0051] As shown in FIG. 2B, the frame plate 5 has an extension portion 55. The extension portion 55 is a cylindrical portion extending downward from the inner peripheral edge of the fitting portion 54. The inner peripheral surfaces of the base portion 51, the protrusion portion 52 (see FIG. 2A), the fitting portion 54, and the extension portion 55 (i.e., the peripheral surface of the insertion hole 5h) are flush with each other. The main bearing 11 (see FIG. 3) is installed on the peripheral surface of the insertion hole 5h.

[0052] <Positional relationship between main bearings and other components> FIG. 3 is a partial enlarged view of the area including the frame plate 5 in FIG. The seal ring 6 shown in Fig. 3 is an annular resin member that separates a high-pressure space that communicates with the through-hole 7c of the crankshaft 7 from a back-pressure chamber A1 at a predetermined intermediate pressure. For example, a square ring with a rectangular cross section is used as this seal ring 6. Using a square ring as the seal ring 6 ensures durability against the downward load from the orbiting scroll 22.

[0053] The space radially inside the seal ring 6 is a high-pressure space with a pressure substantially equal to the discharge pressure. On the other hand, the space radially outside the seal ring 6 is a back pressure chamber A1 with a predetermined intermediate pressure lower than the discharge pressure. The pressure in the back pressure chamber A1 pushes the orbiting scroll 22 upward to an appropriate degree.

[0054] The leaf spring 19 (see also FIG. 4) is a plate-shaped spring member for pushing up the seal ring 6 upward (i.e., toward the swivel scroll 22 side). The leaf spring 19 is annular in plan view and is installed in the groove V1 (see also FIG. 4) of the frame plate 5. Specifically, the leaf spring 19 is installed at the bottom of the groove V1, and the seal ring 6 is installed above the leaf spring 19. Then, the seal ring 6 is compressed in the vertical direction between the leaf spring 19 and the lower surface of the mirror plate 22a of the swivel scroll 22. Incidentally, the leaf spring 19 can be appropriately omitted.

[0055] As shown in FIG. 3, the height position of the upper end of the main bearing 11 (first bearing) is lower than the height position of the lower end of the seal ring 6. According to such a configuration, it is possible to suppress the influence of the radial bearing load acting on the main bearing 11 from reaching the seal ring 6. That is, it is possible to suppress the deformation of the protruding portion 52 of the frame plate 5 due to a large bearing load acting on the main bearing 11. As a result, deterioration of the sealing performance of the seal ring 6 is suppressed, so that the inflow of the refrigerant from the high-pressure space inside the radial direction of the seal ring 6 into the back pressure chamber A1 can be suppressed. Thereby, it is possible to suppress the pressure in the back pressure chamber A1 from becoming too high, and as a result, it is possible to suppress the wear of the tooth tips of the swivel lap 22b (see FIG. 1).

[0056] Also, it is preferable that the axial distance L1 between the lower end of the seal ring 6 and the upper end of the main bearing 11 (first bearing) is shorter than the axial length L2 of the main bearing 11 (first bearing) (L1 < L2). According to such a configuration, since the main bearing 11 is disposed near the seal ring 6 in the vertical direction, the main bearing 11 and the swivel bearing 12 are likely to overlap in the radial direction. As a result, the advantages of the double-bearing structure described above can be utilized, and the deflection of the crankshaft 7 can be suppressed. In addition, since a region where the main bearing 11 and the swivel shaft 22c overlap in the radial direction can be secured, the deflection of the swivel shaft 22c can also be suppressed. Further, it is possible to suppress the vertical dimension of the scroll compressor 100 from becoming long.

[0057] In terms of the positional relationship with the frame plate 5, the upper end of the main bearing 11 overlaps in the radial direction with the base portion 51 of the frame plate 5. With this configuration, it is possible to prevent the radial bearing load acting on the main bearing 11 from acting on the seal ring 6 via the protrusion 52 (above the base portion 51).

[0058] Furthermore, it is preferable that the lower end of the main bearing 11 (first bearing) overlaps the extension portion 55 of the frame plate 5 in the radial direction. In the example of FIG. 3, the height position of the lower end of the main bearing 11 is approximately equal to the height position of the lower end of the extension portion 55. From another perspective, it is preferable that the height position of the lower end of the main bearing 11 is lower than the height position of the lower end of the fitting portion 54 of the frame plate 5. With this configuration, in the process of press-fitting the frame plate 5 into the frame 3, first, the eccentric portion 7b enters inside the main bearing 11 fixed to the extension portion 55 (see FIGS. 6A and 6B), and then the fitting portion 54 is press-fitted into the frame 3 (see FIG. 6C). As a result, the press-fitting is performed with the main bearing 11 and the outer peripheral surface of the eccentric portion 7b aligned with their axes, which prevents the main bearing 11 from being damaged by the press load during press-fitting.

[0059] FIG. 4 is an exploded perspective view of the scroll compressor 100. As shown in FIG. 4 shows the Oldham ring 8, the seal ring 6, the leaf spring 19, the frame plate 5, the bolts B2, a portion of the frame 3, and a portion of the eccentric portion 7b of the crankshaft 7 (the remaining components are not shown). As described above, the seal ring 6 shown in FIG. 4 is installed in the groove V1 of the protruding portion 52 of the frame plate 5. The leaf spring 19 is installed below the seal ring 6 in the groove V1.

[0060] 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 are guided via first key grooves 22d (see FIG. 5) of the orbiting scroll 22 and extend upward from the annular portion 8a. As shown in FIG. 4, the pair of first keys 8b are provided at positions symmetrical with respect to the center of the annular portion 8a (the same is true for the pair of second keys 8c).

[0061] As described above, the pair of second keys 8c are guided via the second key grooves 53b of the frame plate 5, and extend downward from the annular portion 8a. The first keys 8b and the second keys 8c are alternately provided every 90° in the circumferential direction of the annular portion 8a (every 90° in the circumferential angle based on the center of the annular portion 8a).

[0062] As described above, the Oldham ring 8 is interposed between the orbiting scroll 22 (see FIG. 3) and the frame plate 5. It is preferable that the height position of the upper end of the main bearing 11 (first bearing: see FIG. 3) is lower than the height position of the Oldham ring support surface 53a of the frame plate 5 (that is, the height position of the lower surface of the annular portion 8a: see FIG. 3). This configuration can prevent the influence of the radial bearing load acting on the main bearing 11 on the annular portion 8a of the Oldham ring 8. As a result, deformation of the annular portion 8a is suppressed, and ultimately reliability during high-speed operation can be improved.

[0063] More preferably, the height position of the upper end of the main bearing 11 (first bearing: see FIG. 3) is lower than the height position of the bottom of the second key groove 53b in the frame plate 5. With this configuration, it is possible to prevent the influence of the radial bearing load acting on the main bearing 11 from reaching the annular portion 8a of the Oldham ring 8 and the second key 8c.

[0064] 4 are used to fix the frame plate 5 to the frame 3, and are inserted axially (in the axial direction of the crankshaft 7) through the respective bolt insertion holes 51k. Note that a plurality of bolt holes 3d having shapes corresponding to the bolts B2 are also provided on the inner horizontal surface 3c of the frame 3. The frame plate 5 is fastened to the frame 3 by the plurality of bolts B2, with the fitting portion 54 fitted inside the frame 3.

[0065] 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). A pair of end face grooves 72b are provided in the radial direction on the upper end surface of the eccentric portion 7b. The pair of end face grooves 72b are grooves for guiding oil that has lubricated the orbiting bearing 12 (see FIG. 1) to the main bearing 11 (see FIG. 1).

[0066] FIG. 5 is a bottom view of the orbiting scroll 22. As shown in FIG. As shown in FIG. 5, a pair of first key grooves 22d are provided in the lower surface of the end plate 22a of the orbiting scroll 22. The first key grooves 22d are radial grooves recessed upward from the lower surface of the end plate 22a. The first key grooves 22d have the function of guiding the first keys 8b (see FIG. 4) of the Oldham ring 8 (see FIG. 4). The extending direction of the first key grooves 22d is approximately perpendicular to the extending direction of the second key grooves 53b (see FIG. 4) of the frame plate 5 (see FIG. 4) in a plan view. The multiple balance holes 22e shown in FIG. 5 are holes for adjusting the position of the center of gravity of the orbiting scroll 22 and are provided in the lower surface of the end plate 22a.

[0067] FIG. 6A is a cross-sectional view showing a state in which the frame plate 5 is being assembled to the frame 3 and the crankshaft 7. As shown in FIG. As shown in Figure 6A, when the frame plate 5 is assembled, the main bearing 11 is installed on the inner peripheral surface of the frame plate 5, and the orbiting bearing 12 is installed in the eccentric hole 71 of the crankshaft 7. The crankshaft 7 has a stepped surface 73a (see Figure 1) engaged with the thrust bearing 4 (see Figure 1). An operator (or a robot) moves the frame plate 5 downward and inserts the eccentric portion 7b of the crankshaft 7 into the radially inner side of the main bearing 11.

[0068] As described above, the main bearing 11 overlaps in the radial direction with the extension 55 of the frame plate 5. Therefore, the eccentric portion 7b can be inserted into the radially inner side of the main bearing 11 when no press load is applied to the frame plate 5.

[0069] FIG. 6B is a cross-sectional view showing a state when the frame plate 5 is press-fitted into the frame 3. As shown in FIG. 6B, when the lower end of the fitting portion 54 of the frame plate 5 comes into contact with the inner circumferential surface of the frame 3, the eccentric portion 7b has already been inserted radially inside the main bearing 11. In other words, the central axes of the main bearing 11 and the circumferential surface of the eccentric portion 7b are aligned, so there is almost no risk of the inner circumferential surface (sliding surface) of the main bearing 11 being damaged by contact with the eccentric portion 7b. The main bearing 11 and the eccentric portion 7b also function as guides when the fitting portion 54 is press-fitted.

[0070] Using a pressing machine (not shown) such as a hand press, a worker (or a robot) applies downward pressure to the frame plate 5 in a room temperature environment, thereby pressing the mating portion 54 of the frame plate 5 into the inner surface of the frame 3.

[0071] FIG. 6C is a cross-sectional view showing the state when the press-fitting of the frame plate 5 is completed. When the frame plate 5 is press-fitted into the frame 3, a portion 51a of the base portion 51 that extends radially outward beyond the fitting portion 54 abuts against the horizontal surface 3c of the frame 3, restricting downward movement of the frame plate 5. In this state, the fitting portion 54 and the inner peripheral surface of the frame 3 press against each other in the radial direction. Therefore, even if the number of bolts B2 (see FIG. 4) is small, the frame plate 5 can be firmly fixed to the frame 3.

[0072] FIG. 7 is a plan view of the scroll compressor 100 with the cover chamber, the fixed scroll, the orbiting scroll, and the Oldham ring removed. As described above, the bolt B2 shown in FIG. 7 secures the frame plate 5 to the frame 3. Since the frame plate 5 is secured by a plurality of bolts B2 in this manner, durability against radial shear force acting from the main bearing 11 (see FIG. 1) is increased. Furthermore, by fastening the frame plate 5 by bolts in addition to press-fitting it, the press-fit allowance during press-fitting of the frame plate 5 can be reduced, for example, to approximately 10 μm. Such a light press-fit can suppress deformation of the frame plate 5 due to press-fitting. As a result, coaxiality can be easily ensured between the main bearing 11 (see FIG. 1) installed in the insertion hole 5h (see FIG. 2A) of the frame plate 5 and the sub-bearing 13 (see FIG. 1) installed in the frame 3.

[0073] <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.

[0074] Furthermore, because the height position of the upper end of the main bearing 11 is lower than the height position of the lower end of the seal ring 6 (see FIG. 3), it is possible to prevent the bearing load acting on the main bearing 11 from affecting the seal ring 6. As a result, it is possible to prevent deterioration of the sealing performance of the seal ring 6. Furthermore, because the height position of the upper end of the main bearing 11 is lower than the height position of the Oldham ring support surface 53a (see FIG. 4) of the frame plate 5, it is possible to prevent the bearing load of the main bearing 11 from affecting the annular portion 8a of the Oldham ring 8. As a result, deformation of the annular portion 8a is suppressed, improving reliability during high-speed operation.

[0075] Furthermore, in the first embodiment, the crankshaft 7 is supported at one end by a cantilever, so 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 and simplify and increase the efficiency of the assembly process, as well as improve the coaxiality between the main bearing 11 and the sub-bearing 13.

[0076] Furthermore, since the balance weight 9 (see FIG. 1) is disposed in the space between the frame 3 and the frame plate 5, it is possible to suppress deflection of the crankshaft 7 due to the centrifugal force of the balance weight 9. As described above, according to the first embodiment, it is possible to provide a scroll compressor 100 with high performance and reliability.

[0077] Second Embodiment The second embodiment differs from the first embodiment in that a notch N1 (see FIG. 8) is provided in the protruding portion 52A (see FIG. 8) of the frame plate 5A (see FIG. 8), and a leaf spring 19 (see FIG. 9), a guide ring 20 (see FIG. 9), and a seal ring 6 (see FIG. 9) are installed in this notch N1. Note that the rest of the second embodiment is the same as the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0078] FIG. 8 is a vertical cross-sectional view of a region including a frame plate 5A of a scroll compressor 100A according to the second embodiment. As shown in Fig. 8, a notch N1 is provided in the protruding portion 52A of the frame plate 5A. The notch N1 is a portion cut out from the inner peripheral edge of the upper surface of the protruding portion 52A (the surface facing the end plate 22a of the orbiting scroll 22), and has an annular shape in a plan view (see also Fig. 9). The leaf spring 19, the guide ring 20, and the seal ring 6 are sequentially installed in this notch N1 (see also Fig. 9).

[0079] By providing such a notch N1, the position (radial position) of the inner peripheral surface of the seal ring 6 can be brought closer to the peripheral surface of the insertion hole 5h compared to when the groove V1 (see FIG. 4) is provided as in the first embodiment. In other words, a seal ring 6 with a smaller inner diameter can be used. As a result, the area of ​​the inner circle of the seal ring 6 can be reduced. In other words, the area over which the pressure of the high-pressure space communicating with the through hole 7c of the crankshaft 7 acts on the back surface (lower surface) of the orbiting scroll 22 is reduced. In other words, the force that pushes the orbiting scroll 22 toward the fixed scroll 21 is reduced, thereby suppressing wear on the tooth tips of the orbiting wrap 22b.

[0080] The guide ring 20 is a member with an L-shaped cross section that guides the radially inner side of the seal ring 6, and is annular in plan view (see also FIG. 9). By providing such a guide ring 20, radially inward movement of the seal ring 6 is restricted. The leaf spring 19 presses the guide ring 20 and the seal ring 6 upward (toward the orbiting scroll 22). The leaf spring 19 is annular in plan view (see also FIG. 9), and is disposed at the bottom of the notch N1.

[0081] FIG. 9 is an exploded perspective view of the scroll compressor 100A. 9 shows the seal ring 6, the guide ring 20, the leaf spring 19, the frame plate 5A, the eccentric portion 7b (part) of the crankshaft 7, and the slewing bearing 12 (the remaining components are not shown). As described above, the leaf spring 19, the guide ring 20, and the seal ring 6 are sequentially installed in the notch N1.

[0082] <Effects> According to the second embodiment, the seal ring 6 is provided in the notch N1 of the protruding portion 52, and further, the radially inward movement of the seal ring 6 is restricted by the guide ring 20. This allows the inner circumferential surface of the seal ring 6 to be brought radially closer to the outer circumferential surface of the main bearing 11. As a result, the area of ​​the circle on the inner side of the seal ring 6 (the area on which the pressure of the high-pressure space acts) is narrowed, thereby reducing the force that pushes the orbiting scroll 22 toward the fixed scroll 21. As a result, wear on the tooth tips of the orbiting wrap 22b is suppressed, and ultimately the reliability of the scroll compressor 100A can be improved.

[0083] Third Embodiment The third embodiment differs from the first embodiment in that the inner circumferential surface of the protrusion 52B (see FIG. 10) of the frame plate 5B (see FIG. 10) is located radially inward of the inner circumferential surface of the base portion 51 (see FIG. 10). The third embodiment also differs from the first embodiment in that the inner diameter of the seal ring 6 (see FIG. 10) is shorter than the inner diameter of the main bearing 11 (see FIG. 10). The rest of the third embodiment is the same as the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0084] FIG. 10 is a vertical cross-sectional view of a region including a frame plate 5B of a scroll compressor 100B according to the third embodiment. As shown in Fig. 10, the frame plate 5B has a protruding portion 52B that protrudes upward from the inner peripheral edge of the base portion 51. The protruding portion 52B has an annular shape in a plan view, and its inner peripheral surface is located radially inward of the inner peripheral surface of the base portion 51. The protruding portion 52B also has an annular groove V1 that is recessed downward from its upper surface. The inner peripheral surface of the groove V1 is located radially inward of the peripheral surface of the insertion hole 5h of the base portion 51. A seal ring 6 is installed in this groove V1B.

[0085] 10, the inner diameter Φ1 of the seal ring 6 is shorter than the inner diameter Φ2 of the main bearing 11 (first bearing) (Φ1<Φ2). With this configuration, the area of ​​the circle inside the seal ring 6 (the area on which the pressure of the high-pressure space acts) is narrowed, thereby reducing the force that pushes the orbiting scroll 22 up toward the fixed scroll 21.

[0086] <Effects> According to the third embodiment, the inner diameter Φ1 of the seal ring 6 is shorter than the inner diameter Φ2 of the main bearing 11 (first bearing), which reduces the force that pushes the orbiting scroll 22 up toward the fixed scroll 21. As a result, wear on the tooth tip of the orbiting wrap 22b is suppressed, and ultimately the reliability of the scroll compressor 100B can be improved.

[0087] Fourth Embodiment The fourth embodiment differs from the first embodiment in that a scroll compressor 100C (see FIG. 11) includes a sub-frame 81 (see FIG. 11). The fourth embodiment also differs from the first embodiment in that the lower part of the crankshaft 7 is journaled by a sub-bearing 82 (see FIG. 11). The rest of the fourth embodiment is the same as the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0088] FIG. 11 is a vertical cross-sectional view of a scroll compressor 100C according to the fourth embodiment. The scroll compressor 100C shown in FIG. 11 includes a subframe 81 for supporting the lower part of the crankshaft 7. The subframe 81 is disposed below the electric motor 15 and fixed to the cylindrical chamber 1a of the sealed container 1. An insertion hole 81a for the crankshaft 7 is provided near the center of the subframe 81. An auxiliary bearing 82 is installed on the circumferential surface of this insertion hole 81a. The auxiliary bearing 82 is a bearing for supporting the lower part of the crankshaft 7. For example, a plain bearing is used as this auxiliary bearing 82. Oil is guided to the auxiliary bearing 82 via the through hole 7c and the horizontal hole 7e of the crankshaft 7 in this order.

[0089] <Effects> According to the fourth embodiment, the lower part of the crankshaft 7 is journaled by the sub-bearing 82 fixed to the sub-frame 81. This suppresses bending and tilting of the crankshaft 7 while the scroll compressor 100C is in operation, thereby improving the reliability of the scroll compressor 100C.

[0090] Fifth Embodiment In the fifth embodiment, an air conditioner W1 (see FIG. 12) including the scroll compressor 100 (see FIG. 1) having the configuration described in the first embodiment will be described.

[0091] FIG. 12 is a configuration diagram of an air conditioner W1 according to the fifth embodiment. The solid arrows in FIG. 12 indicate the flow of the refrigerant in the heating cycle. On the other hand, the dashed arrows in FIG. 12 indicate the flow of 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. 12, 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. 12, 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. The indoor heat exchanger 95 and the indoor fan 96 are provided in the indoor unit U2.

[0092] 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.

[0093] 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.

[0094] 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).

[0095] 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. 12), 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. 12), 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).

[0096] <Effects> According to the fifth embodiment, the air conditioner W1 is provided 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.

[0097] <<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 each embodiment, the fitting portion 54 of the frame plate 5 (see FIG. 4) is press-fitted into the inner peripheral surface of the frame 3, but the present invention is not limited to this. That is, an annular groove (not shown) recessed radially inward from the outer peripheral surface of the fitting portion 54 may be provided, and an O-ring or the like may be placed in this groove. In this case, the fitting portion 54 is fitted into the frame 3 with a clearance fit or the like.

[0098] In addition, in each embodiment, the scroll compressor 100 is described as including the auxiliary bearing 13 (see FIG. 1), but this is not limiting. For example, the auxiliary bearing 13 may be omitted as appropriate. In each embodiment, the scroll compressor 100 is described as including the balance weight 9 (see FIG. 1), but this is not limiting. For example, the balance weight 9 may be omitted as appropriate. In this case, the frame 3 and the frame plate 5 may be integrated. In addition, in each embodiment, the frame plate 5 is fixed to the frame 3 by press-fitting and bolt fastening, but this is not limiting. For example, if the press-fit allowance when press-fitting the frame plate 5 is set to be large, it is possible to omit bolt fastening.

[0099] In the second embodiment, the leaf spring 19, the guide ring 20, and the seal ring 6 are sequentially installed in the annular notch N1 (see FIG. 9), but this is not limiting. For example, it is also possible to omit one or both of the leaf spring 19 and the guide ring 20 as appropriate.

[0100] In addition, in each embodiment, the scroll compressor 100 (see FIG. 1) 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."

[0101] Furthermore, in the fifth embodiment, the air conditioner W1 (see FIG. 12) 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. The air conditioner W1 (see FIG. 12) 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. The fifth embodiment describes the air conditioner W1 equipped with the scroll compressor 100, 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 freezers, water heaters, air-conditioning water heaters, chillers, and refrigerators.

[0102] Furthermore, the respective embodiments can be combined as appropriate. For example, in a configuration in which the inner circumferential surface of the protruding portion 52A of the frame plate 5A is positioned radially inward relative to the inner circumferential surface of the base portion 51 (third embodiment), a notch N1 may be provided in this protruding portion 52A (second embodiment). This reduces the inner diameter of the seal ring 6 disposed in the notch N1, thereby reducing the pressure pushing up the orbiting scroll 22. Furthermore, it is also possible to combine any of the second to fourth embodiments with the fifth embodiment (see FIG. 12) to create an air conditioner equipped with a scroll compressor.

[0103] 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]

[0104] 1. Airtight container 3 frames 5,5A,5B Frame Plate 5h Insertion hole 6 Seal ring 7. Crankshaft 7b Eccentric part 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) 20 Guide Ring 21 Fixed Scroll 21c fixed wrap 22 Rotating Scroll 22a Headboard 22b Circling Wrap 22c Pivot 22d First keyway 51 Base Part 51a (part protruding radially outward from the fitting part) 51k bolt insertion hole 52,52A,52B Protrusion 53 Support part 53a Oldham ring support surface 53b Second keyway 54 Fitting part 55 Stretching section 71b Eccentric hole 91 Outdoor heat exchanger 93 Expansion valve 95 Indoor heat exchanger 100, 100A, 100B, 100C Scroll Compressors A2 Balance weight space (space) B2 Bolt C1 compression chamber N1 notch 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 rotating shaft; a frame plate having an insertion hole for the eccentric portion and fitted inside the frame; 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; an Oldham ring interposed between the orbiting scroll and the frame plate; a seal ring for sealing between the frame plate and the end plate; a height position of an upper end of the first bearing is lower than a height position of a lower end of the seal ring; The Oldham ring is a first key guided through a first key groove of the orbiting scroll; a second key guided through a second key groove of the frame plate; the second key groove is a groove recessed downward from the Oldham ring support surface of the frame plate, a scroll compressor, wherein a height position of an upper end of the first bearing is lower than a height position of the Oldham ring support surface.

2. 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 rotating shaft; a frame plate having an insertion hole for the eccentric portion and fitted inside the frame; 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 the peripheral surface of the eccentric hole; a seal ring for sealing between the frame plate and the end plate; a height position of an upper end of the first bearing is lower than a height position of a lower end of the seal ring; 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; The seal ring is installed in an annular groove formed by recessing downward from the surface of the protruding portion facing the end plate, or the seal ring is installed in an annular notch formed by cutting out the inner peripheral edge of the surface, an upper end of the first bearing radially overlaps the base portion but does not radially overlap the protrusion portion;

3. The frame plate is an annular fitting portion having the insertion hole and fitted to the inside of the frame; a cylindrical extension portion extending downward from an inner peripheral edge of the fitting portion, The lower end of the first bearing overlaps the extension portion in the radial direction.

2. The scroll compressor according to claim 1,

4. The outer peripheral surface of the fitting portion is in close contact with the inner peripheral surface of the frame.

4. The scroll compressor according to claim 3,

5. The distance in the axial direction between the lower end of the seal ring and the upper end of the first bearing is shorter than the length in the axial direction of the first bearing.

2. The scroll compressor according to claim 1,

6. 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; an inner circumferential surface of the protrusion is located radially inward of an inner circumferential surface of the base portion; The seal ring is installed in an annular groove formed by recessing downward from the surface of the protruding portion facing the end plate, or the seal ring is installed in an annular notch formed by cutting out the inner peripheral edge of the surface, The inner diameter of the seal ring is shorter than the inner diameter of the first bearing.

2. The scroll compressor according to claim 1,

7. 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; The seal ring is installed in an annular notch formed by cutting out an inner peripheral edge of the surface of the protruding portion facing the end plate, Further provided is a guide ring having an L-shaped cross section that guides the radially inner side of the seal ring.

2. The scroll compressor according to claim 1,

8. The frame plate is an annular base portion in which the insertion hole is provided; an annular fitting portion that is connected to a lower side of the base portion and fits inside the frame, The outer diameter of the base portion is greater than the outer diameter of the fitting portion, a plurality of bolt insertion holes are provided in a portion of the base portion that protrudes radially outward from the fitting portion; The frame plate is fastened to the frame by a plurality of bolts inserted into the bolt insertion holes, with the fitting portion fitted inside the frame.

2. The scroll compressor according to claim 1,

9. a balance weight that is installed on the crankshaft and disposed in a space between the frame and the frame plate; The crankshaft is supported in a cantilever manner within the frame.

2. The scroll compressor according to claim 1,

10. The scroll compressor according to any one of claims 1 to 9, An air conditioner comprising an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

Images