Scroll compressor

Abstract

The present invention provides a scroll compressor, comprising: a housing; an electric unit; a rotating shaft; a compression unit having an orbiting scroll rotatably provided on the rotating shaft, and a fixed scroll engaged with the orbiting scroll to form a compression chamber between the orbiting scroll and the fixed scroll; the oil suction part is arranged on one side of the rotating shaft and can suck oil, so that the oil in the oil storage space can be supplied to the compression part; and a bush disposed between the fixed scroll and the rotating shaft and coupled to the outer periphery of the rotating shaft so as to rotate together with the rotating shaft, an oil supply hole is formed in the bush so that the oil sucked from the oil suction portion can be supplied to the compression portion, and an oil hole is formed in a rotating shaft provided on the inner periphery of the bush.

Description

Technical Field

[0001] This invention relates to scroll compressors, and more specifically, to a scroll compressor capable of improving efficiency by increasing the amount of oil supplied to the compression section. Background Technology

[0002] Scroll compressors can be classified into upper-compression and lower-compression types based on the position of the drive motor and compressor unit, which constitute the drive or electric unit. In an upper-compression type, the compressor unit is located higher than the drive motor, while in a lower-compression type, the compressor unit is located lower than the drive motor. This classification is based on examples of longitudinally or vertically arranged housings. In cases where the housing is horizontally arranged, for convenience, it can be divided into left-side (upper) and right-side (lower).

[0003] Scroll compressors can be categorized into two types based on how the rotating shaft is connected to the scroll plate: back-side connection and through-shaft connection. Back-side connection involves the rotating shaft connecting to the back of the scroll plate, while through-shaft connection involves the rotating shaft connecting to the scroll plate through the entire surface.

[0004] In the back-side connection method, the swirling scroll section and the fixed scroll section can extend long to the center of the swirling scroll disk and the fixed scroll disk. However, since the distance between the point of application of the gas reaction force and the support point of the bearing is large, the operating state of the swirling scroll disk may become unstable.

[0005] In the shaft-through method, the distance between the point of application of the gas reaction force and the support point of the bearing is minimized to stabilize the operation of the gyratory scroll. However, the rotating shaft passes through the gyratory scroll and is rotatably connected to the fixed scroll, which may cause the length of the gyratory scroll and the fixed scroll to be shortened, thereby shortening the compression length.

[0006] Patent Document 1 (Korean Patent Publication No. 10-2019-0011115) discloses a through-shaft scroll compressor. In Patent Document 1, a rotating shaft sequentially passes through and is coupled to a main frame, a rotary scroll, and a fixed scroll. In other words, the rotating shaft of Patent Document 1 has an eccentric portion that eccentrically passes through the rotary scroll and is rotatably coupled to both the main frame and the fixed scroll.

[0007] However, in the existing through-scroll compressor described above, the surface pressure between the secondary bearing face of the rotating shaft coupled to the fixed scroll and the secondary bearing of the fixed scroll into which the secondary bearing face is inserted may increase. In other words, because the rotating shaft eccentrically penetrates the rotary scroll and is rotatably coupled to the fixed scroll, the outer diameter of the secondary bearing face is smaller than the outer diameter of the eccentric portion, resulting in increased surface pressure between the secondary bearing face and the secondary bearing. Considering this, if the outer diameter of the secondary bearing face is increased, the outer diameter of the eccentric portion may also need to be increased, potentially leading to a shortened compression length or an increased outer diameter of the compression section.

[0008] In addition, if the surface pressure and axial length of the secondary bearing are formed in a long manner, the increased flow resistance may lead to a reduction in oil supply, which may reduce the efficiency of the compressor and the reliability of the secondary bearing. Summary of the Invention

[0009] The problem the invention aims to solve

[0010] The present invention was proposed to solve the above-mentioned problems. The first objective of the present invention is to provide a scroll compressor having a structure that can reduce the surface pressure of the bearing that fixes the scroll disk.

[0011] A second objective of the present invention is to provide a scroll compressor having a structure capable of smoothly supplying oil between the rotating shaft and the bearing.

[0012] A third objective of this invention is to provide a scroll compressor that can provide smooth oil supply while improving reliability.

[0013] A fourth objective of the present invention is to provide a scroll compressor having a structure capable of smoothly supplying oil between the rotating shaft and the bearing while suppressing wear caused by the tilting of the rotating shaft.

[0014] means for solving problems

[0015] To address the aforementioned problems, the scroll compressor of the present invention may include: a housing forming an exterior and having an oil storage space; an electric motor disposed inside the housing to generate power; a rotating shaft rotatably disposed on the electric motor; a compression section having a rotating scroll and a fixed scroll, the rotating scroll being rotatably disposed on the rotating shaft, the fixed scroll engaging with the rotating scroll to form a compression chamber between the rotating scroll and the fixed scroll; an oil suction section disposed on one side of the rotating shaft and capable of suctioning oil to supply oil from the oil storage space to the compression section; and a bushing disposed between the fixed scroll and the rotating shaft, coupled to the outer periphery of the rotating shaft to rotate together with the rotating shaft; the bushing having an oil supply hole to supply oil sucked from the oil suction section to the compression section, and the rotating shaft disposed on the inner periphery of the bushing having an oil hole.

[0016] Therefore, the outer diameter of the bushing is enlarged, which allows for maintaining the compression length while reducing the surface pressure between the rotating shaft and the fixed scroll.

[0017] According to one embodiment of the invention, the oil supply hole and the oil hole may be configured such that at least a portion of them overlap each other.

[0018] This allows the oil passing through the oil hole to move rapidly to the oil supply hole, thus enabling smooth oil supply between the rotating shaft and the bearing.

[0019] An oil supply groove may be provided on the outer periphery of the bushing, and the oil supply groove is arranged axially to communicate with the oil supply hole.

[0020] The oil supply groove may have a cut-out portion formed at one end of the bushing to provide a flow path to the inner circumference of the bushing.

[0021] As an example, the cutting portion may include: a cutting groove portion disposed on one side of the cutting portion; and cutting side portions disposed on both sides of the cutting groove portion, intersecting the cutting groove portion to provide a flow path for oil to flow to the inner circumference of the bushing.

[0022] Therefore, a flow path is defined between the cut groove and the cut side to connect the outer and inner circumferences of the bushing. Through this flow path, oil flows from the outer circumference to the inner circumference of the bushing, thereby achieving smooth lubrication of the axial thrust surface.

[0023] The bushing may include: a first flow path configured to allow oil to flow upward in the oil supply groove; a second flow path, which is intersected with the first flow path and formed by cutting open one side of the bushing; and a third flow path, which is disposed on the inner circumference of the bushing and intersected with the second flow path.

[0024] Using the first to third flow paths, the oil through the oil supply hole can flow upward along the oil supply groove and lubricate the bearing surface, and after flowing back into the inner circumferential surface of the bushing, it lubricates the axial thrust surface.

[0025] The bushing may have: a sealing face disposed on the inner circumference of the bushing and capable of sealingly engaging with the outer circumference of the rotating shaft; a stepped portion having a diameter larger than that of the sealing face; and an inclined portion disposed between the stepped portion and the sealing face.

[0026] With this configuration, the oil flowing into the inner circumferential surface of the bushing through the cut can flow upward between the rotating shaft and the stepped portion, thus lubricating the axial thrust surface.

[0027] The inner circumferential surface of the fixed scroll disk may be provided with a sealing protrusion, and the rotating shaft is provided with an eccentric part that contacts the sealing protrusion to have an axial thrust surface. The sealing protrusion may be axially separated from the upper end of the bushing, and the inner circumferential surface of the sealing protrusion may be arranged between a line extending from the outer circumferential surface of the bushing and a line extending from the inner circumferential surface of the bushing.

[0028] Therefore, a flow path for oil can be formed between the bushing and the sealing protrusion. In particular, oil flowing into the inner circumferential surface of the bushing through the cut can flow along the inner circumferential surface of the sealing protrusion, thereby enabling smooth supply to the axial thrust surface.

[0029] The rotating shaft may be provided with an oil passage hole, which is axially separated from the oil hole so as not to overlap with the bushing.

[0030] Therefore, due to the presence of oil holes and additional oil passages, oil can be directly supplied to the axial thrust surface.

[0031] The inner circumferential surface of the fixed scroll disk may be provided with a sealing protrusion, and the rotating shaft is provided with an eccentric part that contacts the sealing protrusion to have an axial thrust surface. The oil passage hole may be arranged parallel to the sealing protrusion so that one side of the oil passage hole faces the side of the sealing protrusion.

[0032] Therefore, with the oil hole located on one side of the sealing protrusion, oil can be directly supplied to the axial thrust surface.

[0033] The oil supply holes can be provided in at least two separate locations, and the oil holes can be provided in at least two locations, each overlapping the oil supply hole.

[0034] With two oil holes and two oil supply holes respectively, oil can be supplied to the bearing surface more smoothly.

[0035] The outer periphery of the bushing may be provided with an oil supply groove, which is arranged axially to communicate with the oil supply hole.

[0036] According to another embodiment of the invention, the oil supply hole and the oil hole can form a non-overlapping structure to be axially separated from each other.

[0037] The oil hole can be configured between the oil supply hole and the upper side of the bushing.

[0038] The oil hole can be configured at a midpoint between the upper and lower ends of the bushing and between the upper end of the bushing.

[0039] Thus, by forming a structure in which the oil supply hole and the oil hole are separate from each other, a portion of the oil passing through the oil hole flows upward and is supplied to the inner surface of the axial thrust, while the other portion of the oil flows downward and is supplied to the bearing surface between the secondary bearing and the bushing through the oil supply hole for lubrication.

[0040] Invention Effects

[0041] The scroll compressor of the present invention reduces the surface pressure between the rotating shaft and the fixed scroll disk by setting a bushing between the fixed scroll disk and the rotating shaft, thereby enlarging the outer diameter of the rotating shaft to the outer diameter of the bushing.

[0042] The scroll compressor of the present invention can smoothly supply oil between the rotating shaft and the bearing by forming an oil supply hole in the bushing and an oil hole in the rotating shaft provided on the inner circumference of the bushing.

[0043] The scroll compressor of the present invention has a cut-out portion in the bushing, thus forming an oil supply flow path that connects the outer and inner circumferences of the bushing. This reduces the resistance of the oil supply flow path to the bearing and the axial thrust surface, thereby improving the reliability and efficiency of the compressor.

[0044] The scroll compressor of the present invention can supply oil to the bearing surface by providing an oil supply groove in the bushing, thereby enabling smoother lubrication of the bearing surface.

[0045] The scroll compressor of the present invention has an oil hole and an additional oil passage hole, which enables it to be configured to facilitate direct oil supply to the axial thrust surface. Attached Figure Description

[0046] Figure 1 This is a cross-sectional view showing the scroll compressor of the present invention.

[0047] Figure 2 This is an exploded perspective view showing the rotating shaft, bushing, and fixed scroll plate of the present invention.

[0048] Figure 3 It is shown in decomposition Figure 2 An exploded perspective view of the rotating shaft and bushing.

[0049] Figure 4yes Figure 3 A cross-sectional view along the "IX-IX" line.

[0050] Figure 5 It is shown Figure 2 A cross-sectional view of the assembly of the rotating shaft and the fixed scroll plate.

[0051] Figure 6 This is a perspective view showing another embodiment of the bushing.

[0052] Figure 7 It is shown Figure 6 The bushing in the middle is connected to the sectional view of the rotating shaft.

[0053] Figure 8 This is a perspective view showing yet another embodiment of the bushing.

[0054] Figure 9 It is shown Figure 8 The bushing in the middle is connected to the sectional view of the rotating shaft. Detailed Implementation

[0055] The scroll compressor of the present invention will now be described in detail with reference to the accompanying drawings. In this description, descriptions of certain constituent elements may be omitted to clearly highlight the features of the invention.

[0056] In the following description, "upper side" refers to the direction away from the support surface of the scroll compressor in the embodiment of the present invention, that is, the drive part (electric part 120 or drive motor) side is referred to as the upper side when the drive part (electric part 120 or drive motor) and the compression part C are centered. "Lower side" refers to the direction closer to the support surface, that is, the compression part C side is referred to as the lower side when the drive part (electric part 120 or drive motor) and the compression part C are centered.

[0057] Additionally, the term "axial" used in the following description refers to the length direction of the rotation axis 125. "Axial" can be understood as the vertical direction. "Radial" refers to the direction intersecting the rotation axis 125.

[0058] Furthermore, in the following description, the scroll compressor is described using a hermetically sealed scroll compressor as an example. In this type, the drive unit (electric unit 120 or drive motor) and the compression unit C are disposed in the housing 110. However, the same applies to an open-type compressor in which the drive unit (electric unit 120 or drive motor) is disposed outside the housing 110 and connected to the compression unit C disposed inside the housing 110.

[0059] Furthermore, the following description will use a lower-compression scroll compressor as an example. The lower-compression scroll compressor is a longitudinally mounted scroll compressor in which the electric motor 120 and the compressor C are arranged along the vertical axis, and the compressor C is located closer to the lower side than the drive unit (electric motor 120 or drive motor). However, the same applies to a transversely mounted scroll compressor in which the drive unit (electric motor 120 or drive motor) and the compressor C are arranged horizontally, and to an upper-compression scroll compressor in which the compressor C is located closer to the upper side than the drive unit (electric motor 120 or drive motor).

[0060] Furthermore, the following description uses a high-pressure scroll compressor as an example. The high-pressure scroll compressor is a bottom-compression type, and the refrigerant suction pipe that forms the suction passage is directly connected to the compression section C, and the refrigerant discharge pipe is connected to the internal space of the housing 110 so that the internal space of the housing 110 forms a discharge pressure.

[0061] The scroll compressor of the present invention includes: a housing 110 forming the exterior and having an oil storage space S1; an electric motor 120 disposed inside the housing 110 to generate power; a rotating shaft 125 rotatably disposed on the electric motor 120; a compression section C having a rotary scroll 140 and a fixed scroll 150, the rotary scroll 140 being rotatably disposed on the rotating shaft 125, the fixed scroll 150 engaging with the rotary scroll 140 to form a compression chamber between the fixed scroll 150 and the rotary scroll 140; an oil suction section 127 disposed on one side of the rotating shaft 125, capable of suctioning oil to provide oil to the compression section C in the oil storage space S1; and a bushing 180 disposed between the fixed scroll 150 and the rotating shaft 125, engaging with the outer periphery of the rotating shaft 125 to rotate together with the rotating shaft 125.

[0062] By configuring the bushing 180 between the compression section C and the rotating shaft 125, and attaching it to the outer periphery of the rotating shaft 125 to rotate together with the rotating shaft 125, the surface pressure applied between the compression section C and the rotating shaft 125 can be reduced.

[0063] The bushing 180 is provided with an oil supply hole 183 to supply oil drawn from the oil suction part 127 to the compression part C, and the rotating shaft 125 disposed on the inner circumference of the bushing 180 is provided with an oil hole 1262.

[0064] The scroll compressor of the present invention may further include a secondary bearing 1532. The secondary bearing 1532 may be disposed between the fixed scroll disk 150 and the bushing 180, and may be inserted into the inner circumference of the fixed scroll disk 150. The bushing 180 may be supported by the inner side of the secondary bearing 1532.

[0065] Therefore, oil through oil flow path 126 and oil hole 1262 can be smoothly supplied through oil supply hole 183 to the bearing surface BS between the outer peripheral surface of bushing 180 and the opposite secondary bearing 1532.

[0066] Therefore, by forming an oil supply path in the bushing 180, the resistance of the oil supply path from the oil reservoir S1 to the secondary bearing 1532 surface and the axial thrust surface STS can be reduced, thereby improving the reliability and efficiency of the compressor.

[0067] First, refer to Figure 1 This describes the overall structure of the scroll compressor of the present invention.

[0068] Reference Figure 1 In the high-pressure, bottom-compression scroll compressor (hereinafter referred to as scroll compressor) of this embodiment, an electric motor 120 is provided in the upper half of the housing 110, and a main frame 130, a rotating scroll plate 140, a fixed scroll plate 150, and a discharge cover 160 are provided on the lower side of the electric motor 120. Typically, the main frame 130, the rotating scroll plate 140, the fixed scroll plate 150, and the discharge cover 160 constitute the compression section C.

[0069] The drive motor 120, constituting the electric unit 120, is attached to the upper end of the rotating shaft 125 (described later), and the compressor C is attached to the lower end of the rotating shaft 125. Thus, the compressor constitutes the lower compression type structure described above, with the compressor C connected to the drive motor 120 via the rotating shaft 125, and operated using the rotational force of the drive motor 120. Therefore, the electric unit 120 can be understood as the drive unit that drives the compressor C. Hereinafter, the electric unit 120 may refer to either a drive motor or a drive unit.

[0070] Reference Figure 1 The housing 110 in this embodiment may include a cylindrical outer shell 111, an upper outer shell 112, and a lower outer shell 113. The cylindrical outer shell 111 is a cylindrical shape with openings at both the top and bottom. The upper outer shell 112 is attached to cover the open upper end of the cylindrical outer shell 111, and the lower outer shell 113 is attached to cover the open lower end of the cylindrical outer shell 111. Thus, the internal space (not marked) of the housing 110 is sealed, and the sealed internal space of the housing 110 is divided into a lower space S1 and an upper space S2 with reference to the drive motor 120.

[0071] The lower space S1 is a space formed on the lower side of the drive motor 120. The lower space S1 can be divided into an oil storage space S1 and a discharge space S12 based on the compression section C.

[0072] The upper space S2, formed on the upper side of the drive motor 120, constitutes an oil separation space for separating oil from the refrigerant discharged from the compression section C. The upper space S2 is connected to the refrigerant discharge pipe 116, which will be described later.

[0073] The aforementioned drive motor 120 and main frame 130 are inserted into and fixed inside the cylindrical housing 111. The outer peripheral surface of the drive motor 120 and the outer peripheral surface of the main frame 130 can form an oil recovery passage (not marked) that is separated from the inner peripheral surface of the cylindrical housing 111 by a predetermined interval.

[0074] A refrigerant suction pipe 115 is inserted through and connected to the side of the cylindrical outer shell 111. Thus, the refrigerant suction pipe 115 is radially inserted through and connected to the cylindrical outer shell 111 that constitutes the housing 110.

[0075] In the upper part of the upper housing 112, an internal space (not marked) is formed in the housing 110. Specifically, the upper space S2 above the drive motor 120 is connected to the inner end of the refrigerant discharge pipe 116 so as to communicate with the refrigerant discharge pipe 116.

[0076] An oil circulation pipe (not shown) can be radially inserted through one end of the lower half of the lower housing 113. Both ends of the oil circulation pipe can be open, and the other end of the oil circulation pipe can be inserted through and connected to the refrigerant suction pipe 115. An oil circulation valve (not shown) can be installed in the middle of the oil circulation pipe.

[0077] Reference Figure 1 The drive motor 120 in this embodiment includes a stator 121 and a rotor 122. The stator 121 is inserted into and fixed to the inner circumferential surface of the cylindrical outer shell 111, and the rotor 122 is rotatably disposed inside the stator 121.

[0078] The stator 121 includes a stator core 1211 and a stator coil 1212.

[0079] The stator core 1211 is formed in the shape of an annular or hollow cylinder and is fixed to the inner circumferential surface of the cylindrical outer shell 111 by hot pressing.

[0080] The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source via a power cable (not marked) that passes through and is attached to the housing 110.

[0081] The rotor 122 includes a rotor core 1221 and a permanent magnet 1222.

[0082] The rotor core 1221 is rotatably inserted into the stator core 1211 with a predetermined gap (not marked). The permanent magnet 1222 can be embedded inside the rotor core 1221 with a predetermined interval in the circumferential direction.

[0083] A rotating shaft 125 is attached to the center of the rotor core 1221. The upper end of the rotating shaft 125 is pressed into the rotor 122, and the lower end of the rotating shaft 125 is rotatably inserted into the main frame 130 and radially supported.

[0084] The rotating shaft 125 transmits the rotational force of the drive motor 120 to the rotary scroll 140 that constitutes the compression section C. As a result, the rotary scroll 140, which is eccentrically coupled to the rotating shaft 125, rotates relative to the fixed scroll 150.

[0085] For example, the rotating shaft 125 may be composed of a main shaft portion 1251, a main bearing portion 1252, an eccentric portion 1253, and a secondary bearing portion 1254. The main shaft portion 1251 is the part connected to the rotor 122, the main bearing portion 1252 is the part radially supported by the main frame 130 (described later), the eccentric portion 1253 is the part eccentrically connected to the rotary scroll 140 (described later), and the secondary bearing portion 1254 is the part radially supported by the fixed scroll 150 (described later). In other words, the main shaft portion 1251, which constitutes one end of the rotating shaft 125, can be connected to the rotor 122, and the main bearing portion 1252, eccentric portion 1253, and secondary bearing portion 1254, which constitute the other end, can respectively penetrate and be connected to the main frame 130, the rotary scroll 140, and the fixed scroll 150.

[0086] The main shaft portion 1251, the main bearing portion 1252, and the auxiliary bearing portion 1254 can be formed along the shaft centerline CL, and the eccentric portion 1253 can be formed eccentrically relative to the shaft centerline CL. For example, with the shaft centerline CL as a reference, the outer diameter of the eccentric portion 1253 can be less than or equal to the outer diameter of the main bearing portion 1252. In other words, the outer diameter of the eccentric portion 1253 can be smaller than the outer diameter of the main bearing portion 1252 so that the outer peripheral surface of the eccentric portion 1253 does not protrude from the outer peripheral surface of the main bearing portion 1252. Thus, when assembling the compressor, even if the main frame 130 is inserted from the other end of the rotating shaft 125, the bearing spacing between the main frame (e.g., the main bearing bore described later) 130 and the main bearing portion 1252 can be maintained.

[0087] In this case, the outer diameter of the secondary bearing face 1254 is smaller than the outer diameter of the primary bearing face 1252. For example, with the shaft centerline CL as a reference, the outer diameter of the secondary bearing face 1254 can be less than or equal to the outer diameter of the eccentric portion 1253. In other words, the outer diameter of the secondary bearing face 1254 can be smaller than the outer diameter of the eccentric portion 1253 so that the outer peripheral surface of the secondary bearing face 1254 does not protrude from the outer peripheral surface of the eccentric portion 1253. Therefore, when assembling the compressor, even if the rotary scroll 140 is inserted from the other end of the rotating shaft 125, the bearing spacing between the rotary scroll 140 (e.g., the rotating shaft joint described later) and the eccentric portion 1253 can be maintained.

[0088] However, since the outer diameter of the secondary bearing face 1254 is smaller than the outer diameter of the eccentric portion 1253, the surface pressure between the secondary bearing face 1254 and the bearing face BS, which is radially opposite to it and will be described later, may increase significantly. Here, a bushing 180, forming part of the secondary bearing face 1254, can be inserted between the secondary bearing face 1254 and the secondary bearing 1532. For example, the bushing 180 can be pressed into the outer circumferential surface of the secondary bearing face 1254, or it can be secured using additional fixing members. This increases the actual outer diameter of the secondary bearing face 1254, thereby reducing the surface pressure between the secondary bearing face 1254 (or bushing 180) and the secondary bearing 1532. The bushing 180 will be described again later.

[0089] Additionally, an oil flow path 126 can be formed inside the rotating shaft 125 to guide the oil stored in the oil storage space S1 of the housing 110 to the compression chamber V and / or the bearing surface BS. The oil flow path 126 is formed in an axial or inclined direction, and an oil hole 1262 can be formed in the middle of the oil flow path 126 to supply the oil drawn through the oil flow path 126 to each bearing surface BS. For example, the oil holes 1262 are formed on both axial sides of the eccentric portion 1253 and are accommodated in oil receiving grooves 1255 that are formed as annular on both axial sides of the eccentric portion 1253.

[0090] Additionally, the lower end of the oil flow path 126 may be connected to an oil suction section 127 for pumping oil that fills the oil storage space S1. Thus, when the rotating shaft 125 rotates, the oil that fills the oil storage space S1 can be drawn up along the rotating shaft 125 through the oil suction section 127 and the oil flow path 126, and then supplied to the compression chamber, the axial thrust surface STS, and / or the various bearing surfaces BS.

[0091] The compression unit C in this embodiment includes a main frame 130, a rotary scroll plate 140, and a fixed scroll plate 150. The main frame 130 can be fixedly connected to the lower side of the drive motor 120, and the rotary scroll plate 140 can be axially supported on the fixed scroll plate 150 connected to the lower side of the main frame 130, and is rotatably arranged between the main frame 130 and the fixed scroll plate 150.

[0092] Reference Figure 1 The main frame 130 includes a frame end plate portion 131, a frame side wall portion 132, and a main support portion 133.

[0093] The frame end plate portion 131 is formed in the shape of a disk, and a main bearing hole 1331, which constitutes the main support portion 133 described later, can be formed axially through the center.

[0094] The frame sidewall portion 132 can extend in a cylindrical shape from the lower side edge of the frame end plate portion 131 to be fixed to the inner circumferential surface of the cylindrical outer shell 111 by thermoforming or welding.

[0095] The main support portion 133 can axially extend to form a main bearing hole 1331 for the rotating shaft 125 to be rotatably inserted. The main bearing hole 1331 can be provided with a main bearing (not marked) that supports the main bearing face 1252 of the rotating shaft 125. Thus, the main bearing face 1252 of the rotating shaft 125 can rotate smoothly inside the main bearing hole 1331 while being radially supported.

[0096] Reference Figure 1 The swirling vortex disk 140 includes a swirling end plate portion 141, a swirling vortex portion 142, and a rotating shaft connection portion 143.

[0097] The swivel end plate portion 141 is formed in a disk shape and is housed between the frame end plate portion 131 and the fixed end plate portion 151, which will be described later. The top surface of the swivel end plate portion 141 can be axially supported on the main frame 130 via a back pressure sealing member (not marked). Thus, a back pressure chamber (not marked) is formed between the back surface of the swivel end plate portion 141 and the main frame 130 opposite to it.

[0098] The swirling scroll portion 142 extends from the bottom of the swirling end plate portion 141 to the fixed end plate portion 151 described later, and engages with the fixed scroll portion 154 described later to form the first compression chamber V1 and the second compression chamber V2 described above.

[0099] The spiral scroll 142 can be formed in an involute shape. However, the spiral scroll 142 can be formed together with the fixed scroll 154 into various shapes other than an involute. For example, the spiral scroll 142 can have a shape that connects a plurality of arcs with different diameters or centers, and the outermost curve can be formed into a generally elliptical shape with a major axis and a minor axis. The fixed scroll 154 can also be formed in the same way. Hereinafter, this can be defined as a hybrid or asymmetric scroll shape and explained.

[0100] The rotating shaft connection 143 can be formed through the center of the swirling end plate 141. As a result, the discharge port 1511, which will be described later, can be formed at a position off-center from the center of the swirling vortex disk 140, in other words, at the rotating shaft connection 143.

[0101] The rotating shaft coupling 143 can be rotatably inserted into and coupled with the rotating shaft 125. Thus, the outer periphery of the rotating shaft coupling 143, through connection with the swirling scroll 142, forms the first compression chamber V1 together with the fixed scroll 154 during the compression process.

[0102] The rotating shaft joint 143 can be formed at a height that overlaps with the swirling scroll portion 142 on the same plane. In other words, the rotating shaft joint 143 can be formed at a height that overlaps with the eccentric portion 1253 of the rotating shaft 125 on the same plane.

[0103] Reference Figure 1 The fixed scroll plate 150 in this embodiment includes a fixed end plate portion 151, a fixed side wall portion 152, a secondary support portion 153, and a fixed scroll portion 154.

[0104] The fixed end plate portion 151 can be formed in the shape of a disc and can be arranged separately at predetermined intervals on the lower side of the frame end plate portion 131. A secondary bearing hole 1531 constituting the secondary support portion 153 described later can be formed vertically through the center of the fixed end plate portion 151. The periphery of the secondary bearing hole 1531 can be formed as a discharge port 1511, which communicates with the first compression chamber V1 and the second compression chamber V2 described later, respectively, to discharge the compressed refrigerant into the silencer space 160a of the discharge cover 160.

[0105] The discharge port 1511 can be formed at a position off-center from the center of the fixed end plate portion 151. In other words, since the secondary bearing hole 1531 is formed at the center of the fixed end plate portion 151, the discharge port 1511 can be formed at a position off-center from the secondary bearing hole 1531.

[0106] The fixed sidewall portion 152 extends vertically from the top edge of the fixed end plate portion 151 and is attached to the frame sidewall portion 132 of the main frame 130. The fixed sidewall portion 152 may be formed with a suction port (not shown) that extends radially through the fixed sidewall portion 152. As described above, the suction port (not shown) can be inserted into and attached to the end of the refrigerant suction pipe 115 that extends through the cylindrical outer shell 111.

[0107] A cylindrical secondary bearing hole 1531 can be formed axially through the center of the secondary support portion 153. The secondary bearing hole 1531 can be formed on the same axis as the main bearing hole 1331 provided in the main frame 130. Therefore, the inner diameter of the secondary bearing hole 1531 can be smaller than the inner diameter of the main bearing hole 1331.

[0108] A sealing protrusion 155 may be provided on the inner circumferential surface of the fixed scroll plate 150.

[0109] As an example, the inner circumferential surface of the secondary support portion 153 of the fixed scroll disk 150 may protrude to form a sealing protrusion 155. As an example, the sealing protrusion 155 may be disposed in the secondary bearing hole 1531. The sealing protrusion 155 may extend in a circumferential direction. The sealing protrusion 155 may have a thrust surface STS that contacts a portion of the rotating shaft 125. As an example, the thrust surface STS of the sealing protrusion 155 may contact the eccentric portion 1253 of the rotating shaft 125. In this invention, the axial thrust surface STS may be a thrust surface STS that contacts both the sealing protrusion 155 and the eccentric portion 1253 of the rotating shaft 125.

[0110] The fixed scroll portion 154 can be formed by extending axially from the top surface of the fixed end plate portion 151 towards the rotary scroll disk 140. The fixed scroll portion 154 is formed to correspond to the shape of the rotary scroll portion 142 described above, therefore the description of the rotary scroll portion 142 is used instead of the description of the fixed scroll portion 154.

[0111] Reference Figure 1 The discharge cover 160 can be attached to the back of the fixed scroll plate 150. The discharge cover 160 has a silencer space 160a inside, which can accommodate the discharge port 1511 that penetrates the fixed scroll plate 150. Thus, the refrigerant discharged from the compression chamber V through the discharge port 1511 moves upward to the upper space S2 via the silencer space 160a.

[0112] The unspecified markings in the attached diagram are 170 for a cross ring and 192 for a pin retaining ring.

[0113] The scroll compressor of this embodiment, as described above, performs the following operations.

[0114] That is, when power is applied to the drive motor 120, the rotor 122 and the rotating shaft 125 generate rotational force and rotate. The eccentrically coupled rotary scroll 140 of the rotating shaft 125 rotates relative to the fixed scroll 150 under the action of the cross ring 170.

[0115] As a result, the volumes of the first compression chamber V1 and the second compression chamber V2 gradually decrease from the outside of the compression chambers V1 and V2 toward the center. Consequently, refrigerant is drawn into the first compression chamber V1 and the second compression chamber V2 through the refrigerant suction pipe 115.

[0116] As a result, the refrigerant moves and is compressed along the movement trajectory of each compression chamber V1, V2, and the compressed refrigerant is discharged into the silencer space 160a of the discharge cover 160 through the discharge port 1511 connected to the compression chambers V1, V2.

[0117] Thus, the refrigerant is discharged through the fixed scroll plate 150 and the discharge port (not shown) provided on the main frame 130 into the discharge space (not marked) between the main frame 130 and the drive motor 120, and then moves through the drive motor 120 into the upper space S2 of the housing 110 formed above the drive motor 120. In the upper space S2, the refrigerant separates into refrigerant and oil. The refrigerant is discharged to the outside of the housing 110 through the refrigerant discharge pipe 116, while the oil separated from the refrigerant is recovered into the oil storage space S1 of the housing 110 through the aforementioned oil recovery passage (not shown). This oil is repeatedly supplied through the oil flow path 126 of the rotating shaft 125 to the compression chamber V, the axial thrust surface STS, and / or the various bearing surfaces BS, and then recovered into the oil storage space S1 of the housing 110.

[0118] On the other hand, as described above, the main bearing face 1252, which constitutes part of the lower half of the rotating shaft 125, can be inserted into the main bearing bore 1331 of the main frame 130 and radially supported, while the secondary bearing face 1254 is inserted into the secondary bearing bore 1531 of the fixed scroll plate 150 and radially supported. The secondary bearing face 1254 can be formed on the same axis as the main bearing face 1252 with an eccentric portion 1253 between it and the main bearing face 1252, so that the outer diameter of the secondary bearing face 1254 is smaller than that of the main bearing face 1252. As a result, the surface pressure between the secondary bearing face 1254 and the opposite secondary bearing 1532 increases, which may lead to a decrease in reliability.

[0119] With this in mind, as described above, the outer peripheral surface of the secondary bearing face 1254 can be fitted with a bushing 180 having a predetermined thickness, thereby reducing the surface pressure between the secondary bearing face 1254 and the secondary bearing 1532 by enlarging the actual outer diameter of the secondary bearing face 1254.

[0120] However, when the bushing 180 is attached to the secondary bearing face 1254 of the rotating shaft 125, although the surface pressure can be reduced relatively, the increased flow resistance as oil passes through the bushing 180 may lead to a reduction in oil supply, which may in turn reduce the efficiency of the compressor and the reliability of the secondary bearing 1532.

[0121] In this embodiment, the bushing 180 is provided with an oil supply hole 183 to supply oil drawn from the oil suction section 127 to the compression section C, and the rotating shaft 125 disposed on the inner circumference of the bushing 180 is provided with an oil hole 1262. Thus, oil through the oil flow path 126 and the oil hole 1262 can be smoothly supplied through the oil supply hole 183 to the bearing surface BS and the axial thrust surface STS on the inner circumference of the auxiliary bearing 1532.

[0122] The bushing 180 provided in the scroll compressor of the present invention can be concentrically configured with the secondary bearing face 1254 of the rotating shaft 125, and can be a concentric bushing 180.

[0123] This invention discloses, through various embodiments, structures for improving flow path resistance to ensure smooth oil supply.

[0124] Figure 2 This is an exploded perspective view showing the rotating shaft 125, bushing 180, and fixed scroll plate 150 of the present invention. Figure 3 It is shown in decomposition Figure 2 Exploded perspective view of the rotating shaft 125 and bushing 180 in the figure. Figure 4 yes Figure 3 Sectional view along line "IX-IX", Figure 5 It is shown Figure 2 A cross-sectional view of the rotating shaft 125 assembled with the fixed scroll plate 150.

[0125] Reference Figure 2and Figure 3 In this embodiment, the bushing 180 can be inserted into and joined to the secondary bearing face 1254 of the rotating shaft 125. In other words, the bushing 180 is formed in a cylindrical shape, thicker than the aforementioned secondary bearing 1532, and forms the bearing face BS together with the secondary bearing 1532. Thus, the outer peripheral surface of the bushing 180 forms the actual outer peripheral surface of the secondary bearing face 1254 of the rotating shaft 125, thereby increasing the actual outer diameter of the secondary bearing face 1254. This reduces the surface pressure between the secondary bearing face 1254 of the rotating shaft 125 and the secondary bearing 1532 of the fixed scroll plate 150 opposite it.

[0126] Specifically, the bushing 180 can be pressed into the secondary bearing face 1254 fixed to the rotating shaft 125, or it can be fixed using additional fixing members. This embodiment shows an example of the bushing 180 being fixed to the secondary bearing face 1254 using a connecting pin 191.

[0127] Reference Figure 2 and Figure 3 The secondary bearing face 1254 of the rotating shaft 125 can be formed with a pin receiving groove 1254a for the insertion of the coupling pin 191. The pin receiving groove 1254a is recessed radially to a predetermined depth from the outer peripheral surface of the secondary bearing face 1254, and is also formed axially with a predetermined length. In other words, the pin receiving groove 1254a can be inserted into the inner end of the coupling pin 191, which protrudes radially along the rotating shaft 125 and extends axially. Thus, the contact area between the rotating shaft 125 and the coupling pin 191 extends axially while uniformly transmitting the rotational force of the rotating shaft 125 to the bushing 180.

[0128] Reference Figure 4 and Figure 5 The inner diameter of the bushing 180 can be almost the same as the outer diameter of the secondary bearing face 1254 of the rotating shaft 125. Thus, the bushing 180 can be tightly inserted into the secondary bearing face 1254 of the rotating shaft 125, which can suppress the movement of oil flowing between the secondary bearing face 1254 and the bushing 180 toward the compression chamber V side.

[0129] The inner circumferential surface of the bushing 180 may be formed with a pin support groove 180a for the outer end of the aforementioned connecting pin 191 to be inserted. The pin support groove 180a may be recessed radially to a predetermined depth and also elongated axially. In other words, the pin support groove 180a may be formed to correspond to the pin receiving groove 1254a of the rotating shaft 125. Thus, while the contact area between the bushing 180 and the connecting pin extends elongated axially, the rotational force of the rotating shaft 125 can be uniformly transmitted to the bushing 180.

[0130] Oil supply hole 183 and oil hole 1262 can be configured such that at least a portion overlaps with each other. As an example, see... Figure 4 and Figure 5 An example is shown where the oil supply hole 183 and the oil hole 1262 are arranged radially on the same line.

[0131] Therefore, by minimizing the gap between the oil supply hole 183 and the oil hole 1262, the oil passing through the oil hole 1262 can move more quickly to the oil supply hole 183.

[0132] An oil supply groove 185 may be provided on the outer periphery of the bushing 180. The oil supply groove 185 may communicate with the oil supply hole 183. Therefore, the oil flowing through the oil supply hole 183 flows axially in the oil supply groove 185 so as to smoothly supply oil to the bearing surface BS between the outer peripheral surface of the bushing 180 and the secondary bearing 1532.

[0133] As an example, the oil supply groove 185 can extend axially to guide the axial flow of oil. Oil can flow axially along the oil supply groove 185. Figure 5 As shown, the oil flowing out of the oil supply hole 183 can flow upward along the oil supply groove 185.

[0134] The oil supply groove 185 may have a cut-out portion 186 formed by cutting one end of the bushing 180. The cut-out portion 186 can provide a flow path for oil flowing along the oil supply groove 185 to flow into the inner circumference of the bushing 180.

[0135] Reference Figure 3 As an example, the cut-out portion 186 can be formed such that one side has a height lower than one end of the bushing 180. The cut-out portion 186 can serve as a passage connecting the flow path of the outer peripheral surface of the bushing 180 and the flow path of the inner peripheral surface of the bushing 180, thereby expanding the flow path.

[0136] The cutting portion 186 can be defined by a cutting groove portion 186a and a cutting side portion 186b. The cutting groove portion 186a can be provided at one end of the oil supply groove 185. The cutting side portion 186b can be provided on both sides of the cutting groove portion 186a to intersect with the cutting groove portion 186a.

[0137] Figure 3 An example is shown where the cutting groove 186a is provided at the upper end of the oil supply groove 185, and the cutting side portion 186b is provided on both sides of the cutting groove 186a in a direction intersecting with the cutting side portion 186b.

[0138] The cut-out portion 186 can be configured to be separate from the sealing protrusion 155 of the fixed scroll plate 150. As an example, the cut-out side portion 186b can be configured to intersect with the sealing protrusion 155 of the fixed scroll plate 150. The sealing protrusion 155 of the fixed scroll plate 150 can contact or be separated from the upper end of the bushing 180 by a predetermined distance.

[0139] Between the cut groove portion 186a and the cut side portion 186b, a flow path can be formed that connects the outer periphery and the inner periphery of the bushing 180.

[0140] Thus, the oil supplied to the bearing surface BS between the outer periphery of the bushing 180 and the inner periphery of the secondary bearing 1532 through the oil hole 1262 and the oil supply hole 183 flows upward and then flows back into the interior of the bushing 180 through the flow path expanded by the cut-out portion 186, and then supplies again to the axial thrust surface STS between the rotating shaft 125 and the fixed scroll plate 150.

[0141] The axial thrust surface STS can be the thrust surface STS that contacts the sealing protrusion 155 of the fixed scroll disk 150 and the eccentric part 1253 of the rotating shaft 125.

[0142] Reference Figure 4 and Figure 5 The sealing protrusion 155 can be formed axially separate from the upper end of the bushing 180, and the inner circumferential surface of the sealing protrusion 155 can be positioned between a line extending from the outer circumferential surface of the bushing 180 and a line extending from the inner circumferential surface. Therefore, a flow path for oil flow can be formed between the bushing 180 and the sealing protrusion 155. Furthermore, oil flowing into the inner circumferential surface of the bushing 180 through the cut portion 186 can flow along the inner circumferential surface of the sealing protrusion 155 and be smoothly supplied to the axial thrust surface STS.

[0143] In the upper part of the bushing 180, the flow resistance is relatively large due to the sealing protrusion 155 of the fixed scroll plate 150 and the eccentric part 1253 of the rotating shaft 125. The flow path in the upper part of the bushing 180 is expanded by the cut-out part 186, thereby enabling smooth oil supply to the axial thrust surface STS.

[0144] The inner circumference of the bushing 180 may be provided with a stepped portion 1821. The stepped portion 1821 may be formed to have a larger diameter than the sealing surface 184. For this purpose, an inclined portion 1822 may be provided between the stepped portion 1821 and the sealing surface 184. As an example, the stepped portion 1821 may be provided on the upper part of the inner circumference of the bushing 180.

[0145] Under the action of the step portion 1821, the oil flowing into the inner circumferential surface of the bushing 180 through the cut portion 186 can flow upward between the rotating shaft 125 and the step portion 1821, and can achieve lubrication on the axial thrust surface STS.

[0146] As an example, the bushing 180 can be formed such that the distance between the bushing 180 and the rotating shaft 125 increases as the stepped portion 1821 approaches the end of the bushing 180. A guide portion 1823 can be provided between the stepped portion 1821 and the inclined portion 1822 to guide oil to flow into the inner circumference of the bushing 180 after passing through the cut portion 186. The guide portion 1823 can be formed in a direction intersecting the stepped portion 1821. In addition, the guide portion 1823 can extend circumferentially along the inner circumference of the bushing 180, thus guiding the flow of oil circumferentially along the inner circumference of the bushing 180.

[0147] In the bushing 180, the oil flowing in through the cut-out portion 186 flows upward under the action of the step portion 1821 and is supplied to the axial thrust surface STS and the compression portion C, thereby enabling the expansion of the flow path.

[0148] On the other hand, the bushing 180 can also be expected to have the following effect: the step portion 1821 can be used to prevent the bushing 180 from tilting when the rotating shaft 125 tilts.

[0149] Thus, the bushing 180 can form a flow path by the oil supply groove 185, the cutting part 186 and the stepped part 1821, and the flow path can be understood as the first flow path to the third flow path 185a, 186c and 1821a as described below.

[0150] The bushing 180 may include a first flow path to a third flow path 185a, 186c, 1821a.

[0151] The first flow path 185a can be provided in the oil supply tank 185. The first flow path 185a can be a flow path that allows oil to flow upward on the outer periphery of the bushing 180. The oil flows through the first flow path 185a and smoothly lubricates the bearing surface BS between the outer peripheral surface of the bushing 180 and the secondary bearing 1532.

[0152] The second flow path 186c is configured to intersect with the first flow path 185a and can be formed by cutting open one side of the bushing 180. The second flow path 186c can be defined by the aforementioned cut portion 186. The second flow path 186c can be a flow path connecting the outer and inner circumferences of the bushing 180. Through the second flow path 186c, oil flowing on the outer circumference of the bushing 180 can flow into the inner circumference of the bushing 180.

[0153] The third flow path 1821a may intersect with the second flow path 186c and may be disposed on the inner circumference of the bushing 180. The third flow path 1821a may be formed on the inner circumference of the bushing 180 with a diameter larger than that of the sealing face 184. For this purpose, an inclined portion 1822 may be provided between the third flow path 1821a and the sealing face 184.

[0154] Therefore, although multiple flow paths are provided in the bushing 180, oil supply can be carried out smoothly by increasing the flow path in the upper part of the bushing 180, which has relatively large flow path resistance.

[0155] On the other hand, the inner circumference of the bushing 180 may be provided with a sealing surface 184 capable of sealingly engaging with the outer circumference of the rotating shaft 125. The sealing surface 184 may be formed in an annular shape on the inner circumferential surface of the bushing 180.

[0156] The distance between the secondary bearing face 1254 and the sealing face 184 can be smaller than the distance between the secondary bearing face 1254 and the step portion 1821. As a result, it is possible to suppress the inflow of high-pressure refrigerant contained in the oil suction portion 127 and / or the internal space of the housing 110 into the gap between the inner peripheral surface of the bushing 180 and the outer peripheral surface of the secondary bearing face 1254.

[0157] In this case, the sealing face 184 can be formed to surround all or part of the periphery of the oil supply port 183. In other words, the sealing face 184 can extend from all or part of the periphery of the oil supply port 183 with the same width. Figure 5 and Figure 9 Examples are shown where the sealing face 184 is formed to completely surround the periphery of the oil supply port 183 (the bushing 180 of the first and third embodiments). Figure 7 An example is shown where the sealing face 184 is formed as part of the periphery of the oil supply port 183 (the bushing 180 of the second embodiment).

[0158] For example, the sealing surface 184 can extend at least 1 mm from all or part of the periphery of the oil supply hole 183. Thus, the sealing surface 184 ensures sufficient area around all or part of the periphery of the oil supply hole 183, thereby not only preventing the refrigerant from flowing into the oil supply passage, but also ensuring that the oil supplied to the oil supply hole 183 of the bushing 180 through the oil flow path 126 and oil hole 1262 of the rotating shaft 125 does not leak between the secondary bearing surface 1254 and the bushing 180, and is supplied smoothly to the oil supply hole 183.

[0159] Additionally, refer to Figure 6 and Figure 7 This describes the bushing 180 structure of the second embodiment of the present invention.

[0160] The oil supply hole 183 and the oil hole 1262 can form a non-overlapping structure to be separated from each other along the axial direction. Compared with other embodiments in which the oil supply hole 183 and the oil hole 1262 overlap by at least a portion, this embodiment has the characteristic that the oil supply hole 183 and the oil hole 1262 do not overlap.

[0161] Oil hole 1262 can be configured between the oil supply hole 183 and the upper side of the bushing 180.

[0162] As an example, the oil hole 1262 can be configured at the midpoint between the upper and lower ends of the bushing 180 and between the upper end of the bushing 180.

[0163] Thus, since the oil supply hole 183 and the oil hole 1262 are structured separately, the oil through the oil hole 1262 does not flow directly to the oil supply hole 183, but can flow upward and downward respectively. The oil flowing upward through the oil hole 1262 supplies the inner surface of the axial thrust. The oil flowing downward through the oil hole 1262 supplies and lubricates the bearing surface BS between the auxiliary bearing 1532 and the bushing 180 through the oil supply hole 183.

[0164] Oil through oil hole 1262 should be able to flow smoothly between the outer circumference of rotating shaft 125 and the inner circumference of bushing 180. For this purpose, a clearance flow path with a predetermined interval can be provided between the outer circumference of rotating shaft 125 and the inner circumference of bushing 180. The clearance flow path can be provided on the outer circumference of rotating shaft 125 or the inner circumference of bushing 180. When the clearance flow path 1254a is formed on the outer circumference of rotating shaft 125, the diameter of the clearance flow path 1254a can be smaller than the diameter of the secondary bearing surface 1254 that engages with the sealing surface 184 of bushing 180. When the clearance flow path is formed on the inner circumference of bushing 180, the diameter of the clearance flow path can be larger than the diameter of the sealing surface 184. Under the action of the clearance flow path, oil through oil hole 1262 can flow axially between rotating shaft 125 and bushing 180.

[0165] Figure 7 An example is shown where the gap flow path 1254a is provided on the outer periphery of the secondary bearing face 1254 of the rotating shaft, but the gap flow path may also be provided on the inner periphery of the bushing 180.

[0166] An oil supply groove 185 can be provided on the outer periphery of the bushing 180. The oil supply groove 185 can communicate with the oil supply hole 183. Therefore, the oil flowing through the oil supply hole 183 can flow axially in the oil supply groove 185 and be smoothly supplied to the bearing surface BS between the outer peripheral surface of the bushing 180 and the secondary bearing 1532. Figure 6 and Figure 7 As shown, in this embodiment, the oil supply groove 185 of the bushing 180 does not have a cut-out portion 186, a feature that is consistent with... Figure 4 and Figure 5 The bushing 180 in the embodiment is different.

[0167] With this bushing 180 structure, oil supply for both the secondary bearing 1532 and the axial thrust can be achieved simultaneously. In particular, the bushing 180 structure of the second embodiment ensures that the oil flowing from the oil hole 1262 does not flow directly into the oil supply hole 183, but instead flows axially between the rotating shaft 125 and the bushing 180, thereby enabling the supply of oil for both the secondary bearing 1532 and the axial thrust to be achieved using a single oil hole 1262.

[0168] On the other hand, a flow path guide 181 may be provided on one side of the bushing 180. The flow path guide 181 guides the oil flowing on the inner circumference of the bushing 180 to flow upward so as to supply it to the axial thrust surface STS.

[0169] Therefore, the flow resistance of the bearing surface BS between the outer periphery of the bushing 180 and the secondary bearing 1532, and the upper part of the bushing 180, can be minimized. In addition, compared with the third embodiment described later, the oil supply to the secondary bearing 1532 and the axial thrust surface STS can be achieved using a simpler rotating shaft 125 structure.

[0170] Additionally, refer to Figure 8 and Figure 9 The bushing 180 structure of the third embodiment of the present invention will be described.

[0171] The oil supply hole 183 and the oil hole 1262 can be configured such that at least a portion of them overlap each other.

[0172] The rotating shaft 125 may be provided with an oil passage hole 1263. The oil passage hole 1263 may be axially separated from the oil hole 1262 so as not to overlap with the bushing 180. The oil passage hole 1263 may also be named an additional oil filling hole. Oil can be directly supplied to the axial thrust surface STS through the oil passage hole 1263.

[0173] As an example, the oil passage hole 1263 can be provided on the face of the bushing 180, i.e., the secondary bearing face 1254 of the rotating shaft 125.

[0174] The center of the oil passage 1263 can be positioned closer to the upper side than the upper end of the bushing 180.

[0175] The oil passage 1263 can be arranged parallel to the sealing protrusion 155, with one side facing the side of the sealing protrusion 155. The oil passage 1263 can be configured such that one side is adjacent to one side of the sealing protrusion 155. Therefore, the oil passage 1263 can form a structure that facilitates direct oil supply to the axial thrust surface STS.

[0176] At least two oil supply holes 183 may be provided separately from each other. In addition, at least two oil holes 1262 may be provided, each overlapping with an oil supply hole 183.

[0177] Reference Figure 8 and Figure 9 Two oil supply holes 183 may be provided separately from each other along the axial direction. In addition, two oil holes 1262 are shown that are provided separately from each other along the axial direction to overlap with the oil supply holes 183.

[0178] An example is shown in which two oil supply holes 183 and two oil holes 1262 are arranged radially on the same line.

[0179] An oil supply groove 185 may be provided on the outer periphery of the bushing 180. The oil supply groove 185 may communicate with the oil supply hole 183. Therefore, the oil flowing through the oil supply hole 183 flows axially in the oil supply groove 185 and is smoothly supplied to the bearing surface BS between the outer periphery of the bushing 180 and the secondary bearing 1532. Figure 8 and Figure 9 As shown, in the bushing 180 of this embodiment, the oil supply groove 185 does not have a cut-out portion 186, and the two oil supply holes 183 are formed to be able to communicate. These features are different from those of the above embodiment.

[0180] Thus, using the bushing 180 structure of the third embodiment, oil can be supplied to the secondary bearing 1532 through the oil hole 1262 and the oil supply hole 183. In addition, oil can be supplied separately to the axial thrust surface STS through the oil passage hole 1263.

[0181] The scroll compressor described above is not limited to the configuration and method of the above embodiments. It can also be configured by selectively combining all or part of the various embodiments to achieve various modifications of the embodiments.

[0182] This invention can be embodied in other specific forms without departing from its spirit and essential features, as will be apparent to those skilled in the art. Therefore, the foregoing detailed description should not be interpreted restrictively in all respects, but rather as illustrative. The scope of this invention is determined by a reasonable interpretation of the appended claims, and all modifications within the equivalent scope of this invention are included within its scope.

[0183] Industrial applicability

[0184] This invention can be applied to scroll compressors that can improve efficiency by increasing the amount of oil supplied to the compression section.

Claims

1. A scroll compressor, wherein, include: The shell forms the exterior and provides oil storage space; An electric motor, located inside the housing, generates power; A rotating shaft is rotatably mounted on the electric unit; The compression section has a rotary scroll disk and a fixed scroll disk. The rotary scroll disk is rotatably disposed on the rotating shaft. The fixed scroll disk engages with the rotary scroll disk to form a compression chamber between the rotary scroll disk and the fixed scroll disk. An oil suction section, disposed on one side of the rotating shaft and capable of suctioning oil, is provided to supply oil from the oil storage space to the compression section; and A bushing is disposed between the fixed scroll disk and the rotating shaft, and is attached to the outer periphery of the rotating shaft so as to rotate together with the rotating shaft; The bushing is provided with an oil supply hole to supply oil drawn from the oil suction section to the compression section, and an oil hole is provided on the rotating shaft disposed on the inner circumference of the bushing.

2. The scroll compressor according to claim 1, wherein, The oil supply hole and the oil hole are configured such that at least a portion of them overlap each other.

3. The scroll compressor according to claim 2, wherein, An oil supply groove is provided on the outer periphery of the bushing, and the oil supply groove is arranged axially to communicate with the oil supply hole.

4. The scroll compressor according to claim 3, wherein, The oil supply groove has a cut-out portion formed by cutting at one end of the bushing to provide a flow path to the inner circumference of the bushing.

5. The scroll compressor according to claim 4, wherein, The cut portion includes: A cutting groove is provided on one side of the cutting portion; and The cut-open sides are respectively disposed on both sides of the cut-open groove and intersect with the cut-open groove to provide a flow path for oil to flow to the inner circumference of the bushing.

6. The scroll compressor according to claim 3, wherein, The bushing includes: The first flow path is configured to allow oil to flow upward in the oil supply tank; A second flow path, intersecting the first flow path, is formed by cutting open one side of the bushing; and The third flow path is disposed on the inner circumference of the bushing and is intersected with the second flow path.

7. The scroll compressor according to claim 2, wherein, The bushing has: A sealing face is provided on the inner circumference of the bushing, which can be sealed to the outer circumference of the rotating shaft; The stepped portion has a diameter larger than the diameter of the sealing surface; and An inclined portion is disposed between the stepped portion and the sealing surface.

8. The scroll compressor according to claim 1, wherein, The inner circumferential surface of the fixed scroll disk is provided with a sealing protrusion, and the rotating shaft is provided with an eccentric part that contacts the sealing protrusion to provide an axial thrust surface. The sealing protrusion is axially separated from the upper end of the bushing. The inner circumferential surface of the sealing protrusion is positioned between a line extending from the outer circumferential surface of the bushing and a line extending from the inner circumferential surface of the bushing.

9. The scroll compressor according to claim 2, wherein, The rotating shaft is provided with an oil passage hole, which is axially separated from the oil hole so as not to overlap with the bushing.

10. The scroll compressor according to claim 9, wherein, The inner circumferential surface of the fixed scroll disk is provided with a sealing protrusion, and the rotating shaft is provided with an eccentric part that contacts the sealing protrusion to provide an axial thrust surface. The oil passage hole is arranged parallel to the sealing protrusion, such that one side of the oil passage hole faces one side of the sealing protrusion.

11. The scroll compressor according to claim 2, wherein, The oil supply holes are provided in at least two separate locations, and the oil holes are provided in at least two locations, each overlapping the oil supply hole.

12. The scroll compressor according to claim 11, wherein, The bushing is provided with an oil supply groove on its outer periphery, and the oil supply groove is arranged axially to communicate with the oil supply hole.

13. The scroll compressor according to claim 1, wherein, The oil supply hole and the oil hole form a non-overlapping structure to be separated from each other in the axial direction.

14. The scroll compressor according to claim 13, wherein, The oil hole is located between the oil supply hole and the upper side of the bushing.

15. The scroll compressor according to claim 13, wherein, The oil hole is located at the midpoint between the upper and lower ends of the bushing and between the upper end of the bushing.

Images