Scroll compressor

Abstract

The present invention provides a scroll compressor comprising: a casing; a motor unit; a rotary shaft; a compression unit having an orbiting scroll rotatably provided on the rotary shaft, and a fixed scroll coupled to engage with the orbiting scroll so as to form a compression chamber between the orbiting scroll and the fixed scroll; a bushing disposed between the fixed scroll and the rotary shaft, and disposed on the outer periphery of the rotary shaft so as to rotate together with the rotary shaft; and a stopping member inserted at one side of the rotary shaft so as to support one side of the bushing.

Description

Scroll compressor

[0001] The present invention relates to a scroll compressor that increases assembly reliability and productivity.

[0002] Scroll compressors can be classified into upper compression type or lower compression type depending on the position of the drive motor and the compressor, which constitute the drive or electric unit. The upper compression type is a method in which the compressor is located above the drive motor, and the lower compression type is a method in which the compressor is located below the drive motor. This classification is based on examples where the casing is installed in a vertical or vertical shape; however, if the casing is installed horizontally, the left side may be classified as the upper side and the right side as the lower side for convenience.

[0003] Scroll compressors can be classified into back-coupling and shaft-through types depending on how the rotating shaft is coupled to the rotary scroll. The back-coupling method is one in which the rotating shaft is coupled to the back of the rotary scroll, while the shaft-through method is one in which the rotating shaft is coupled by penetrating the rotary scroll.

[0004] In the back-coupling method, the slewing wrap and fixed wrap extend far to the center of the slewing scroll and fixed scroll, whereas the large gap between the point of application of the gas reaction force and the support point of the bearing can cause the behavior of the slewing scroll to become unstable.

[0005] The shaft penetration method stabilizes the behavior of the slewing scroll by minimizing the distance between the point of application of the gas reaction force and the support point of the bearing, whereas the compression length can be reduced as the lengths of the slewing wrap and the fixed wrap are shortened as the rotating shaft penetrates the slewing scroll and is rotatably coupled to the fixed scroll.

[0006] Patent Document 1 (Korean Published Patent Application No. 10-2019-0011115) discloses a shaft-penetrating scroll compressor. In Patent Document 1, a rotating shaft penetrates and connects the main frame, the pivoting scroll, and the fixed scroll in sequence. In other words, the rotating shaft of Patent Document 1 is equipped with an eccentric portion that penetrates the pivoting scroll eccentrically and is rotatably connected to the main frame and the fixed scroll, respectively.

[0007] However, in the conventional shaft-through scroll compressor described above, the surface pressure between the sub-bearing surface of the rotating shaft coupled to the stationary scroll and the sub-bearing of the stationary scroll into which this sub-bearing surface is inserted may increase. In other words, as the rotating shaft penetrates the rotating scroll eccentrically and is rotatably coupled to the stationary scroll, the outer diameter of the sub-bearing surface is formed smaller than the outer diameter of the eccentric part, which ultimately leads to an increase in surface pressure between the sub-bearing surface and the sub-bearing. If the outer diameter of the sub-bearing surface is enlarged to account for this, the outer diameter of the eccentric part is also enlarged, which may result in a decrease in compression length or an increase in the outer diameter of the compression part.

[0008] Meanwhile, the concentric bushing is coupled with the rotation axis and rotates concentrically together with the rotation axis during operation.

[0009] To join concentric bushings, there are methods of forcibly pressing them into the rotating shaft and methods of inserting the concentric bushings into the rotating shaft through a gap and then fixing them in the rotational and axial directions with separate members.

[0010] In the method of fixing a concentric bushing with a separate member after inserting it into a rotation axis, the conventional structure applied individual members for fixation in the rotational direction and the axial direction, respectively.

[0011] To secure the rotational direction, a key or pin is applied to the rotation axis, or the concentric bushing and rotation axis are implemented with a D-cut shape. A C-ring is applied to prevent axial downward displacement.

[0012] A concentric bushing inserted into a rotation axis with a gap must not be completely fixed to the rotation axis by a fixing member, as it must have degrees of freedom in rotational and axial movement to compensate for geometric tolerances.

[0013] The key structure suffers from poor assembly efficiency due to the fastening mechanism occurring after the compression section is assembled, while the D-Cut shape has the disadvantage of increased machining costs when the bushing is concentric with the shaft. Additionally, the C-Ring structure also results in poor assembly efficiency because the small component requires manual processing after the compression section is fastened.

[0014] In the method of fixing a concentric bushing with a separate member after inserting it into a rotating shaft through a gap, in order to facilitate compressor assembly and increase productivity, it is necessary to implement a structure in which the member fixing the concentric bushing is assembled simply and easily so that automation is possible.

[0015] The present invention has been devised to solve the above problems, and the first objective of the present invention is to provide a scroll compressor capable of restraining a bushing with respect to a rotation axis.

[0016] The second objective of the present invention is to provide a scroll compressor having a structure in which the member fixing the concentric bushing is assembled simply and easily so as to enable automation in order to increase productivity.

[0017] The third objective of the present invention is to provide a scroll compressor with a structure capable of reducing the surface pressure of the bearing of a fixed scroll.

[0018] The fourth objective of the present invention is to provide a scroll compressor in which the bushing is not completely fixed to the rotating shaft and can have limited degrees of freedom in the rotational and axial directions, thereby enabling the absorption or correction of gaps or geometric tolerances between the rotating shaft and the bushing during operation of the compressor, thus allowing for a response to concerns regarding reduced reliability.

[0019] To solve the above problem, the scroll compressor of the present invention comprises: a casing forming an outer casing; a power transmission unit installed inside the casing to generate power; a rotating shaft rotatably installed in the power transmission unit; a compression unit having a rotating scroll installed to pivotally rotate on the rotating shaft and a fixed scroll coupled to engage with the rotating scroll to form a compression chamber between the rotating scrolls; a bushing disposed between the fixed scroll and the rotating shaft and disposed on the outer circumference of the rotating shaft to rotate together with the rotating shaft; and a stopper member inserted and installed on one side of the rotating shaft to support one side of the bushing.

[0020] As a result, since the stopping member is installed on one side of the rotating shaft to support the bushing, the bushing can be restrained with respect to the rotating shaft without being dislodged in the axial direction. In addition, since the bushing is not completely fixed to the rotating shaft and can have limited degrees of freedom in the rotational and axial directions, it is possible to absorb or correct the gap or geometric tolerance between the rotating shaft and the bushing during the operation of the compressor, thereby enabling a response to concerns regarding reduced reliability.

[0021] The above-mentioned stopper has a body installed to surround the outer circumference of a rotating shaft and a support portion that protrudes toward the bushing from one side of the body to enable the bushing to be supported on the rotating shaft.

[0022] The above support portion may be provided in a plurality of portions spaced apart from each other in the circumferential direction, and may be formed to be elastically deformable in the radial direction so as to be retractable from one side of the rotation axis and fixed to the rotation axis.

[0023] The above-mentioned stopping member has a gap formed as an empty space between a plurality of supporting parts by a predetermined distance in the axial direction, and the gap may be formed to be larger than half the total axial length of the stopping member.

[0024] Preferably, the body can be joined to the rotation axis by a press-fit method.

[0025] At the end of the support portion, a support projection is provided that protrudes inward and extends in the circumferential direction, and at the outer circumference of the rotation axis, a support groove is provided that is formed concavely and extends in the circumferential direction.

[0026] The above support groove may be positioned adjacent to one end of the bushing, and the end of the support portion may be positioned to contact the end of the bushing.

[0027] As a result, the stopper can be supported by contacting the bushing.

[0028] The protrusion length of the above support projection can be formed to be greater than the depth of the above support groove by a predetermined distance.

[0029] As a result, the support part can be easily elastically deformed while minimizing the possibility of damage, thereby improving assembly and productivity.

[0030] The above stopper is formed of PBT material and may contain 30% GF (Glass Fiber).

[0031] The above support portions are provided in a plurality of portions spaced apart from each other in the circumferential direction, and at least one of the plurality of support portions further provides a bushing support portion formed such that its end extends further toward the bushing, and the bushing may be provided with a rotation limiting groove formed concavely on its outer circumference to accommodate the bushing support portion.

[0032] The rotation limiting groove may be provided with a first contact support portion that is provided at both ends of the circumferential side of the rotation limiting groove and limits the rotation of the stop member and the bushing in the circumferential direction; and a second contact support portion that is arranged axially between the first contact support portion of the cut support portion and enables the stop member to be supported axially with respect to the bushing.

[0033] At one end of the inner circumference of the body, a support projection protruding inward is provided, and at one end of the rotation axis, a cut support portion formed by cutting a predetermined distance in the circumferential direction to accommodate the support projection may be provided.

[0034] The above-mentioned cutting support member may include a first contact support portion provided at both ends of the circumferential side of the cutting support member to support both sides of the support protrusion; and a second contact support portion disposed axially between the first contact support portions of the cutting support member to support the stop member axially.

[0035] The support protrusion and the bushing support may be provided at positions that overlap in the circumferential direction, and the rotation limiting groove and the cut support may be provided at positions that overlap in the circumferential direction. As a result, the stopper member can support the bushing more firmly and can be supported more firmly on the rotation axis.

[0036] The above support protrusion is formed in a polygonal shape and can protrude in a direction intersecting the bushing support.

[0037] The above-mentioned rotating shaft comprises a main shaft portion coupled to the above-mentioned transmission portion; an eccentric portion coupled eccentrically to the above-mentioned rotating scroll; and a sub-bearing surface portion radially supported to the above-mentioned fixed scroll, and the bushing is provided between the sub-bearing surface portion and the above-mentioned fixed scroll and can be fixed to one side of the sub-bearing surface portion.

[0038] The scroll compressor of the present invention has a bushing installed between a fixed scroll and a rotating shaft, so that the outer diameter of the rotating shaft is expanded to the outer diameter of the bushing, thereby reducing the surface pressure between the rotating shaft and the fixed scroll while maintaining the compression length.

[0039] The scroll compressor of the present invention includes a stopper member, allowing the bushing to be simply coupled to the rotating shaft, thereby enabling the application of an automated process on the line without manual processes.

[0040] The scroll compressor of the present invention has a stopper member having a locking portion, and the locking groove of the rotating shaft is supported, and the locking portion is supported in the groove portion of the bushing so that the bushing can be restrained in the axial and radial directions with respect to the rotating shaft.

[0041] The scroll compressor of the present invention allows the bushing to have limited degrees of freedom in the rotational and axial directions without being completely fixed to the rotating shaft, thereby enabling the absorption or correction of gaps or geometric tolerances between the rotating shaft and the bushing during the operation of the compressor, thus making it possible to address concerns regarding reduced reliability.

[0042] The invention of the present embodiment allows the bushing to be fixed not only in the axial direction but also by the bushing support being received and coupled in the rotation limiting groove of the rotation axis, thereby preventing the bushing from detaching in the axial direction and limiting rotation in the circumferential direction.

[0043] In the invention of the present embodiment, as the bushing support is received and coupled in the rotation limiting groove of the rotation shaft, fixing force can be secured not only in the axial direction but also in the circumferential direction.

[0044] In addition, the stopper is configured so that the support portion can be elastically deformed in the radial direction, allowing it to be simply and easily assembled to a rotating shaft, thereby lowering manufacturing costs and improving productivity.

[0045] FIG. 1 is a cross-sectional view illustrating a scroll compressor of the present invention.

[0046] FIG. 2 is an exploded perspective view illustrating the rotating shaft, bushing, stopper member, and fixed scroll of the present invention.

[0047] FIG. 3 is a perspective view illustrating an example in which a bushing is installed by a stopper member on a rotating shaft in FIG. 2, with a part of the bushing cut away.

[0048] FIG. 4 is an exploded perspective view illustrating an example in which a bushing and a stopper are installed on a rotating shaft.

[0049] FIG. 5 is a cross-sectional view to show one operation in the process of installing a stopper member on a rotating shaft with a bushing installed in part A of FIG. 1.

[0050] FIG. 6 is a cross-sectional view to show an example in which a stopper is installed on a rotating shaft with a bushing installed in part A of FIG. 1.

[0051] FIG. 7 is a perspective view of a stopper member according to one embodiment of the present invention, viewed from one side.

[0052] FIG. 8 is a perspective view of a stopper member according to one embodiment of the present invention, viewed from another side.

[0053] FIG. 9 is an exploded perspective view illustrating an example in which a bushing and a stopper are installed on a rotating shaft as another embodiment of the present invention.

[0054] FIG. 10 is an exploded perspective view illustrating an example in which a stopper is installed while a bushing is installed on a rotating shaft in the embodiment of FIG. 9.

[0055] FIG. 11 is a cross-sectional view to show one operation in the process of installing a stopper member on a rotating shaft with a bushing installed in the embodiment of FIG. 9.

[0056] FIG. 12 is a perspective view to show one operation in the process of installing a stopper member on a rotating shaft with a bushing installed in the embodiment of FIG. 9.

[0057] FIG. 13 is a perspective view for showing one operation in the process of installing a stopper member on a rotating shaft with a bushing installed in the embodiment of FIG. 9.

[0058] FIG. 14 is a perspective view for showing an example in which a stopper is installed on a rotating shaft on which a bushing is installed in the embodiment of FIG. 9.

[0059] FIG. 15 is a cross-sectional view to show an example in which a stopper is installed on a rotating shaft on which a bushing is installed, in the embodiment of FIG. 9.

[0060] Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to the attached drawings. In the following description, descriptions of some components may be omitted to clarify the features of the present invention.

[0061] In the following description, "upper side" refers to the direction away from the support surface supporting the scroll compressor according to the embodiment of the present invention, that is, when viewed from the center of the electric motor (120) and the compression unit (C), the electric motor (120) side is the upper side. "Lower side" refers to the direction closer to the support surface, that is, when viewed from the center of the electric motor (120) and the compression unit (C), the compression unit (C) side is the lower side.

[0062] Additionally, the term "axial direction" used in the following description refers to the longitudinal direction of the rotation axis (125). The "axial direction" can be understood as the up and down direction. The "radial direction" refers to the direction intersecting the rotation axis (125).

[0063] Additionally, in the following description, the scroll compressor is described using a closed-type scroll compressor in which the electric motor (120) and the compressor (C) are provided in the casing (110) as an example. However, the same can be applied to an open-type compressor in which the electric motor (120) is provided outside the casing (110) and connected to the compressor (C) provided inside the casing (110).

[0064] Additionally, the following description uses a vertical scroll compressor in which the electric motor (120) and the compression unit (C) are arranged in the vertical axial direction, and the compression unit (C) is located below the electric motor (120) as an example. However, the same can be applied to a horizontal scroll compressor in which the electric motor (120) and the compression unit (C) are arranged left and right, as well as to an upper compression scroll compressor in which the compression unit (C) is located above the electric motor (120).

[0065] In addition, the following description uses as an example a high-pressure scroll compressor in which a refrigerant suction pipe forming a suction passage is directly connected to a compression section (C) and a refrigerant discharge pipe is connected to the internal space of a casing (110) so that the internal space of the casing (110) forms the discharge pressure.

[0066] The scroll compressor of the present invention comprises: a casing (110) forming an exterior; a power generation unit (120) installed inside the casing (110) to generate power; a rotating shaft (125) rotatably installed on the power generation unit (120); a rotating scroll (140) installed to pivotally rotate on the rotating shaft (125) and a fixed scroll (150) coupled to engage with the rotating scroll (140) to form a compression chamber (V) between the rotating scrolls (140); a bushing (180) disposed between the fixed scroll (150) and the rotating shaft (125) and disposed on the outer circumference of the rotating shaft (125) to rotate together with the rotating shaft (125); and a stopper (190) inserted and installed on one side of the rotating shaft (125) to support one side of the bushing (180).

[0067] As the stopping member (190) is installed on one side of the rotation axis (125) to support the bushing (180), the bushing (180) can be restrained without being displaced in the axial direction relative to the rotation axis (125).

[0068] In addition, since the bushing (180) is not completely fixed to the rotating shaft (125) and can have limited degrees of freedom in the rotational and axial directions, it is possible to absorb or correct the gap or geometric tolerance between the rotating shaft (125) and the bushing (180) during the operation of the compressor, thereby enabling a response to concerns regarding reduced reliability. That is, tolerances and eccentricity can be absorbed through the limited degrees of freedom, thereby improving reliability.

[0069] If the bushing (180) or stopper (190) is not fully coupled with the rotation axis (125) and has a predetermined fine gap or circumferential and / or axial degrees of freedom, it can absorb fine eccentricity, vibration, error, etc. that may occur during operation, thereby reducing internal component damage and noise.

[0070] It may be a mechanism that relieves mechanical stress and improves durability (reliability) through the gap between the rotating shaft (125) and the bushing in the rotating body device of a scroll compressor.

[0071] There is a gap between the rotating shaft (125) and the bushing (180) (or stopper member (190)) that can act as a buffer, so that it may be easy to insert and remove even if dimensional deviations or tolerances occur during assembly.

[0072] Even during operation after assembly, the rotating shaft (125) and the bushing (180) do not interfere excessively with each other, so that increased friction or excessive deformation can be suppressed.

[0073] In addition, the stopper (190) can be easily assembled to one side of the rotation axis (125), thereby increasing productivity.

[0074] FIG. 1 is a cross-sectional view illustrating a scroll compressor of the present invention.

[0075] First, with reference to FIG. 1, the overall configuration of the scroll compressor of the present invention will be described.

[0076] Referring to FIG. 1, a high-pressure and bottom-compressing scroll compressor according to the present embodiment (hereinafter abbreviated as scroll compressor) is provided with a motor unit (120) in the upper half of a casing (110), and a main frame (130), a pivot scroll (140), a fixed scroll (150), and a discharge cover (160) are provided on the lower side of the motor unit (120). Typically, the main frame (130), the pivot scroll (140), the fixed scroll (150), and the discharge cover (160) form a compression unit (C).

[0077] The electric motor (120) is coupled to the upper end of the rotating shaft (125) to be described later, and the compression unit (C) is coupled to the lower end of the rotating shaft (125). Accordingly, the compressor forms a lower compression type structure as previously described, and the compression unit (C) is connected to the electric motor (120) by the rotating shaft (125) and operates by the rotational force of the electric motor (120). Therefore, the electric motor (120) can be understood as a driving unit that drives the compression unit (C). In the present invention, the electric motor (120) may be a driving motor or a driving unit.

[0078] Referring to FIG. 1, the casing (110) according to the present embodiment may include a cylindrical shell (111), an upper shell (112), and a lower shell (113). The cylindrical shell (111) is cylindrical in shape with both upper and lower ends open, the upper shell (112) is coupled to cover the open upper end of the cylindrical shell (111), and the lower shell (113) is coupled to cover the open lower end of the cylindrical shell (111). Accordingly, the internal space (not shown) of the casing (110) is sealed, and the sealed internal space of the casing (110) is separated into a lower space (S1) and an upper space (S2) based on the electric motor (120).

[0079] The lower space (S1) is a space formed on the lower side of the electric motor (120), and the lower space (S1) can be divided into a storage space (S1) and a discharge space (S12) based on the compression part (C).

[0080] The upper space (S2) is a space formed on the upper side of the electric motor (120) and forms an oil separation space in which oil is separated from the refrigerant discharged from the compression unit (C). A refrigerant discharge pipe (116), which will be described later, is connected to the upper space (S2).

[0081] The aforementioned electric motor (120) and main frame (130) are inserted and fixed inside the cylindrical shell (111). An oil recovery passage (not shown) may be formed on the outer surface of the electric motor (120) and the outer surface of the main frame (130), spaced apart from the inner surface of the cylindrical shell (111) by a predetermined distance.

[0082] A refrigerant suction pipe (115) is connected by penetrating through the side of the cylindrical shell (111). Accordingly, the refrigerant suction pipe (115) is connected by penetrating radially through the cylindrical shell (111) forming the casing (110).

[0083] The upper part of the upper shell (112) is connected by penetrating through the inner space (not shown) of the casing (110), specifically the upper space (S2) formed on the upper side of the electric motor (120), so that the inner end of the refrigerant discharge pipe (116) communicates with it.

[0084] One end of an oil circulation pipe (not shown) may be radially connected to the lower half of the lower shell (113). Both ends of the oil circulation pipe are open, and the other end of the oil circulation pipe may be connected to a refrigerant suction pipe (115). An oil circulation valve (not shown) may be installed in the middle of the oil circulation pipe.

[0085] Referring to FIG. 1, the electric motor (120) according to the present embodiment includes a stator (121) and a rotor (122). The stator (121) is inserted into and fixed to the inner circumference of a cylindrical shell (111), and the rotor (122) is rotatably provided inside the stator (121).

[0086] The stator (121) includes a stator core (1211) and a stator coil (1212).

[0087] The stator core (1211) is formed in an annular or hollow cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot press fitting.

[0088] The stator coil (1212) is wound around the stator core (1211) and is electrically connected to an external power source through a power cable (not labeled) that is coupled through the casing (110).

[0089] The rotor (122) includes a rotor core (1221) and a permanent magnet (1222).

[0090] The rotor core (1221) is rotatably inserted into the stator core (1211) at a predetermined gap (not indicated). Permanent magnets (1222) are embedded inside the rotor core (1221) at predetermined intervals along the circumferential direction.

[0091] A rotation shaft (125) is coupled to the center of the rotor core (1221). The upper end of the rotation shaft (125) is press-fitted into the rotor (122) and the lower end of the rotation shaft (125) is rotatably inserted into the main frame (130) and supported radially.

[0092] The rotating shaft (125) transmits the rotational force of the electric motor (120) to the rotating scroll (140) forming the compression part (C). Accordingly, the rotating scroll (140), which is eccentrically coupled to the rotating shaft (125), rotates relative to the fixed scroll (150).

[0093] A bushing (180) is disposed between the fixed scroll (150) and the outer circumference of the rotating shaft (125). The bushing (180) is disposed on one side of the rotating shaft (125). As shown in FIG. 1, the bushing (180) may be disposed between the fixed scroll (150) and the lower side of the rotating shaft (125). The detailed configuration in which the bushing (180) is disposed will be described later.

[0094] The rotation axis (125) can be a crankshaft.

[0095] For example, the rotation shaft (125) may include a main shaft portion (1251), an eccentric portion (1253), and a sub-bearing surface portion (1254). The main shaft portion (1251) is a part coupled to the rotor (122), the eccentric portion (1253) is a part coupled eccentrically to the pivoting scroll (140) to be described later, and the sub-bearing surface portion (1254) is a part supported radially by the fixed scroll (150) to be described later.

[0096] The rotation axis (125) may further include a main bearing surface (1252) which is a part supported radially by the main frame (130) to be described later.

[0097] In other words, the rotation shaft (125) has a main shaft portion (1251) forming one end that is coupled to the rotor (122), and the main bearing surface portion (1252), eccentric portion (1253), and western bearing surface portion (1254) forming the other end that are coupled by penetrating the main frame (130), the pivot scroll (140), and the fixed scroll (150), respectively.

[0098] The main shaft portion (1251), the main bearing surface portion (1252), and the sub-bearing surface portion (1254) are formed on the shaft centerline (CL), and the eccentric portion (1253) may be formed eccentrically with respect to the shaft centerline (CL). For example, when based on the shaft centerline (CL), the outer diameter of the eccentric portion (1253) may be formed to be smaller than or equal to the outer diameter of the main bearing surface portion (1252). In other words, the outer diameter of the eccentric portion (1253) may be formed smaller than the outer diameter of the main bearing surface portion (1252) so that the outer surface of the eccentric portion (1253) does not protrude beyond the outer surface of the main bearing surface portion (1252). Accordingly, when assembling the compressor, even if the main frame (130) is inserted at the other end of the rotating shaft (125), the bearing gap between the main frame (e.g., the main bearing hole to be described later) (130) and the main bearing surface (1252) can be maintained.

[0099] In this case, the outer diameter of the sub-bearing surface (1254) may be formed to be smaller than the outer diameter of the main bearing surface (1252), for example, when based on the shaft centerline (CL), the outer diameter of the sub-bearing surface (1254) may be formed to be smaller than or equal to the outer diameter of the eccentric part (1253). In other words, the outer diameter of the sub-bearing surface (1254) may be formed to be smaller than the outer diameter of the eccentric part (1253) so that the outer surface of the sub-bearing surface (1254) does not protrude beyond the outer surface of the eccentric part (1253). Accordingly, when assembling the compressor, even if the pivot scroll (140) is inserted at the other end of the rotating shaft (125), the bearing gap between the pivot scroll (for example, the rotating shaft (125) coupling part to be described later) (140) and the eccentric part (1253) can be maintained.

[0100] However, as the outer diameter of the sub-bearing surface portion (1254) is formed to be smaller than the outer diameter of the eccentric portion (1253), the surface pressure may be significantly increased at the bearing surface (not shown) between the sub-bearing surface portion (1254) and the sub-bearing (1532) to be described later facing it in a radial direction. Accordingly, a bushing (180) may be inserted between the sub-bearing surface portion (1254) and the sub-bearing (1532).

[0101] In the present invention, the stopper member (190) may be installed on the sub-bearing surface portion (1254). For example, the stopper member (190) may be installed on one end into which the bushing (180) is inserted.

[0102] The bushing (180) can be restrained by the stopper member (190) so as not to be disengaged in the axial direction.

[0103] The stopper member (190) can be easily assembled to one side of the rotation axis (125), for example, one side of the sub-bearing surface (1254), thereby increasing productivity.

[0104] For example, a bushing (180) can be pressed into the outer surface of the sub-bearing surface (1254). Accordingly, the actual outer diameter of the sub-bearing surface (1254) is increased, thereby reducing the surface pressure between the sub-bearing surface (1254) (or bushing (180)) and the sub-bearing (1532).

[0105] The bushing (180) will be explained again later.

[0106] Additionally, an oil passage (126) is formed in an axial or inclined direction inside the rotating shaft (125) to guide oil stored in the oil storage space (S1) of the casing (110) to the compression chamber (V) and / or bearing surface, and an oil hole (1262) may be formed in the middle of the oil passage (126) so that oil sucked through the oil passage (126) is supplied to each bearing surface. For example, the oil hole (1262) may be formed on each axial side of the eccentric part (1253), and may be formed to be received in an annular oil receiving groove (1255) formed on each axial side of the eccentric part (1253).

[0107] Additionally, an oil pickup (127) for pumping oil filled in the oil storage space (S1) may be attached to the bottom of the oil passage (126). Accordingly, when the rotating shaft (125) rotates, the oil filled in the oil storage space (S1) can be sucked along the rotating shaft (125) through the oil pickup (127) and the oil passage (126) and supplied to the compression chamber (V), the shaft thrust surface (not shown), and / or each bearing surface.

[0108] The compression unit (C) according to the present embodiment includes a main frame (130), a pivot scroll (140), and a fixed scroll (150). The main frame (130) is fixedly coupled to the lower side of the electric motor (120), and the pivot scroll (140) is axially supported by the fixed scroll (150) coupled to the lower side of the main frame (130) so as to be pivotable between the main frame (130) and the fixed scroll (150).

[0109] Referring to FIG. 1, the main frame (130) includes a frame plate portion (131), a frame side wall portion (132), and a main support portion (133).

[0110] The frame plate portion (131) is formed in the shape of a disc, and a main bearing hole (1331) forming the main support portion (133) to be described later can be formed by penetrating through the center in the axial direction.

[0111] The frame side wall portion (132) can be fixed by hot pressing or welding, extending in a cylindrical shape from the lower edge of the frame end plate portion (131).

[0112] The main support member (133) may be formed with a main bearing hole (1331) penetrating axially so that the rotation shaft (125) can be rotatably inserted. A main bearing (not shown) that supports the main bearing surface (1252) of the rotation shaft (125) may be provided in the main bearing hole (1331). Accordingly, the main bearing surface (1252) of the rotation shaft (125) can be supported radially while rotating smoothly inside the main bearing hole (1331).

[0113] Referring to FIG. 1, the rotating scroll (140) includes a rotating plate section (141), a rotating wrap (142), and a rotating shaft coupling section (143).

[0114] The rotating plate section (141) is formed in the shape of a disc and can be accommodated between the frame plate section (131) and the fixed plate section (151) to be described later. The upper surface of the rotating plate section (141) can be supported axially on the main frame (130) with a back pressure sealing member (not labeled) in between. Accordingly, the back surface of the rotating plate section (141) forms a back pressure chamber (not labeled) between it and the main frame (130) facing it.

[0115] The rotating wrap (142) extends from the lower surface of the rotating plate section (141) toward the fixed plate section (151) to be described later, and engages with the fixed wrap (154) to be described later to form the first compression chamber (V1) and the second compression chamber (V2) described above.

[0116] The pivot wrap (142) can be formed in an involute shape. However, the pivot wrap (142) can be formed in various shapes other than an involute together with the fixed wrap (154). For example, the pivot wrap (142) may have a shape formed by connecting multiple arcs with different diameters and origins, and the outermost curve may be formed in a roughly elliptical shape having a major axis and a minor axis. The fixed wrap (154) may be formed in the same way. In the following description, this may be defined as a hybrid or irregular wrap shape.

[0117] The rotational shaft coupling portion (143) can be formed by penetrating axially from the center of the pivot plate portion (141). Accordingly, the discharge port (1511), which will be described later, can be formed at an eccentric position from the center of the pivot scroll (140), that is, from the rotational shaft coupling portion (143).

[0118] A rotating shaft (125) can be rotatably inserted and coupled to the rotating shaft coupling part (143). Accordingly, the outer periphery of the rotating shaft coupling part (143) is connected to the pivoting wrap (142) to form a first compression chamber (V1) together with the fixed wrap (154) during the compression process.

[0119] The rotational shaft coupling portion (143) can be formed at a height that overlaps with the pivot wrap (142) on the same plane. In other words, the rotational shaft coupling portion (143) can be formed at a height where the eccentric portion (1253) of the rotational shaft (125) overlaps with the pivot wrap (142) on the same plane.

[0120] Referring to FIG. 1, the fixed scroll (150) according to the present embodiment includes a fixed plate portion (151), a fixed side wall portion (152), a sub-support portion (153), and a fixed wrap (154).

[0121] The fixed end plate (151) is formed in the shape of a disc and can be positioned at a predetermined interval below the frame end plate (131). A sub-axis bearing hole (1531) forming a sub-support member (153) to be described later can be formed through the center of the fixed end plate (151) in the vertical direction. Around the sub-axis bearing hole (1531), a discharge port (1511) can be formed, which is connected to the first compression chamber (V1) and the second compression chamber (V2) to be described later, respectively, and through which the compressed refrigerant is discharged into the muffler space (160a) of the discharge cover (160).

[0122] The discharge port (1511) can be formed at an eccentric position from the center of the fixed plate portion (151). In other words, as the sub-carrier hole (1531) is formed in the center of the fixed plate portion (151), the discharge port (1511) can be formed at an eccentric position from the sub-carrier hole (1531).

[0123] The fixed side wall portion (152) can be connected to the frame side wall portion (132) of the main frame (130) by extending in the vertical direction from the upper edge of the fixed end plate portion (151). A suction port (not shown) that penetrates the fixed side wall portion (152) in the radial direction may be formed in the fixed side wall portion (152). As previously described, the end of the refrigerant suction pipe (115) that penetrates the cylindrical shell (111) may be inserted into and connected to the suction port (not shown).

[0124] A cylindrical sub-carrier hole (1531) may be formed by penetrating axially through the center of the sub-support member (153). The sub-carrier hole (1531) may be formed on the same axis as the main carrier hole (1331) provided in the main frame (130). Accordingly, the inner diameter of the sub-carrier hole (1531) may be formed smaller than the inner diameter of the main carrier hole (1331).

[0125] A sealing protrusion (155) may be provided on the inner surface of the fixed scroll (150).

[0126] For example, a sealing protrusion (155) may be formed protrudingly on the inner surface of the sub-support portion (153) of the fixed scroll (150). The sealing protrusion (155) may be provided, for example, in the sub-axis hole (1531). The sealing protrusion (155) may extend in an annular direction. The sealing protrusion (155) may have a thrust surface that contacts a part of the rotation axis (125). The thrust surface of the sealing protrusion (155) may, for example, contact the eccentric portion (1253) of the rotation axis (125). In the present invention, the shaft thrust surface may be a thrust surface that contacts between the sealing protrusion (155) and the eccentric portion (1253) of the rotation axis (125).

[0127] The fixed wrap (154) can be formed to extend axially toward the pivot scroll (140) from the upper surface of the fixed plate section (151). Since the fixed wrap (154) is formed to correspond to the shape of the pivot wrap (142) described above, the description of the fixed wrap (154) is replaced by the description of the pivot wrap (142).

[0128] Referring to FIG. 1, the discharge cover (160) can be attached to the back surface of the fixed scroll (150). Inside the discharge cover (160), a muffler space (160a) is provided, and the muffler space (160a) can accommodate a discharge port (1511) that penetrates the fixed scroll (150). Accordingly, the refrigerant discharged from the compression chamber (V) through the discharge port (1511) moves to the upper space (S2) via the muffler space (160a).

[0129] The unexplained symbol 170 in the drawing is an Oldham ring.

[0130] The scroll compressor according to the present embodiment as described above operates as follows.

[0131] That is, when power is applied to the electric motor (120), rotational force is generated in the rotor (122) and the rotation shaft (125) and rotates, and the pivot scroll (140) eccentrically coupled to the rotation shaft (125) rotates relative to the fixed scroll (150) by the Oldham ring (170).

[0132] Then, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually decreases from the outside of each compression chamber (V1)(V2) toward the center. Then, the refrigerant is sucked into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (115).

[0133] Then, the refrigerant is compressed while moving along the movement path of each compression chamber (V1)(V2), and the compressed refrigerant is discharged into the muffler space (160a) of the discharge cover (160) through the discharge port (1511) connected to the compression chambers (V1)(V2).

[0134] Then, this refrigerant is discharged into a discharge space (not shown) between the main frame (130) and the electric motor (120) through a discharge hole (not shown) provided in the fixed scroll (150) and the main frame (130), and passes through the electric motor (120) to move to an upper space (S2) of the casing (110) formed on the upper side of the electric motor (120). In the upper space (S2), this refrigerant is separated into refrigerant and oil, and the refrigerant is discharged to the outside of the casing (110) through the refrigerant discharge pipe (116), while the oil separated from the refrigerant is recovered into the oil storage space (S1) of the casing (110) through the previously described oil recovery passage (not shown). This oil is supplied to the compression chamber (V), shaft thrust surface and / or respective bearing surface through the oil passage (126) of the rotating shaft (125) and then returned to the oil storage space (S1) of the casing (110), repeating a series of processes.

[0135] Meanwhile, as previously described, the rotation shaft (125) can be supported radially by having the main bearing surface (1252), which forms part of the lower half, inserted into the main bearing hole (1331) of the main frame (130), and the sub-bearing surface (1254) inserted into the sub-bearing hole (1531) of the fixed scroll (150). Since the sub-bearing surface (1254) is formed on the same axis as the main bearing surface (1252) with the eccentric portion (1253) in between, the outer diameter of the sub-bearing surface (1254) can be formed smaller than that of the main bearing surface (1252). As a result, the surface pressure between the sub-bearing surface (1254) and the sub-bearing (1532) facing it increases, which may reduce reliability.

[0136] In consideration of this, as previously explained, a bushing (180) having a predetermined thickness is coupled to the outer surface of the sub-bearing surface (1254) to increase the actual outer diameter of the sub-bearing surface (1254), thereby reducing the surface pressure between the sub-bearing surface (1254) and the sub-bearing (1532).

[0137] However, when a bushing (180) is coupled to the sub-bearing surface (1254) of the rotating shaft (125), the surface pressure may be reduced relatively, but as oil passes through the bushing (180), the amount of oil supplied may be reduced due to increased flow resistance, and the efficiency of the compressor and the reliability of the sub-bearing (1532) may be reduced.

[0138] Accordingly, in this embodiment, since the bushing (180) is coupled to the rotation axis (125) by a stopper member (190), the bushing (180) can be prevented from detaching from the rotation axis (125).

[0139] In addition, the stopper (190) can be easily assembled to one side of the rotation axis (125), for example, one side of the sub-bearing surface (1254), thereby increasing productivity.

[0140] For example, a bushing (180) can be pressed into the outer surface of the sub-bearing surface (1254). Accordingly, the actual outer diameter of the sub-bearing surface (1254) is increased, thereby reducing the surface pressure between the sub-bearing surface (1254) (or bushing (180)) and the sub-bearing (1532).

[0141] In the present invention, a sub-bearing (1532) may be installed between the bushing (180) and the fixed scroll (150).

[0142] The bushing (180) provided in the scroll compressor of the present invention can be arranged concentrically with the sub-bearing surface (1254) of the rotating shaft (125), so it can be understood as a concentric bushing (180).

[0143] In the present invention, an assembled structure is disclosed in which a bushing (180) is coupled to a rotating shaft (125), which is described in more detail below.

[0144] FIG. 2 is an exploded perspective view illustrating the rotating shaft (125), bushing (180), stopper (190), and fixed scroll (150) of the present invention. FIG. 3 is a perspective view illustrating an example in which the bushing (180) is installed by the stopper (190) on the rotating shaft (125) in FIG. 2, with a portion of the bushing (180) cut away. FIG. 4 is an exploded perspective view illustrating an example in which the bushing (180) and the stopper (190) are installed on the rotating shaft (125). FIG. 5 is a cross-sectional view to show one operation in the process of installing the stopper (190) on the rotating shaft (125) where the bushing (180) is installed in part A of FIG. 1. FIG. 6 is a cross-sectional view to show an example in which a stopper member (190) is installed on a rotating shaft (125) on which a bushing (180) is installed in part A of FIG. 1. FIG. 7 is a perspective view of a stopper member (190) according to an embodiment of the present invention viewed from one side. FIG. 8 is a perspective view of a stopper member (190) according to an embodiment of the present invention viewed from the other side.

[0145] In the present invention, the stopping member (190) may have a body (191) and a support portion (192).

[0146] The body (191) can be installed to surround the outer circumference of the rotation axis (125).

[0147] The body (191) can be installed on one side of the rotation axis (125) to surround the outer circumference of the rotation axis (125), and as shown in FIGS. 2 to 6, it can be installed on the lower side of the rotation axis (125).

[0148] More specifically, as illustrated in FIG. 3, etc., the body (191) can be installed on the sub-bearing surface (1254) of the rotating shaft (125).

[0149] The body (191) is provided with a support portion (192) so that the bushing (180) can be supported on the rotation axis (125) and simultaneously coupled to the outer circumference of the rotation axis (125).

[0150] The body (191) can be joined to the rotation axis (125) by a press-fit method.

[0151] The support portion (192) may protrude from one side of the body (191) toward the bushing (180) to enable the bushing (180) to be supported on the rotation axis (125).

[0152] The support portion (192) may be provided in multiple units spaced apart from each other in the circumferential direction.

[0153] The support portion (192) is formed to be elastically deformable in the radial direction, so that it can be inserted from one side of the rotation axis (125) and fixed to the rotation axis (125).

[0154] Referring to FIG. 5, the process of inserting a stopper member (190) into one side of the sub-bearing surface (1254) of the rotation shaft (125) is illustrated, and an example is illustrated in which the support portion (192) is elastically deformed outward as the support projection (192a) of the support portion (192) is pressed by the outer circumference of the sub-bearing surface (1254) of the rotation shaft (125).

[0155] Additionally, FIG. 6 illustrates an example in which a stopper member (190) is completely coupled to a rotation axis (125), wherein a support projection (192a) of a support portion (192) is received in a support groove (1254a) of the rotation axis (125).

[0156] The protruding length of the support projection (192a) can be formed to be greater than the depth of the support groove (1254a) by a predetermined distance. As a result, the inner circumference of the support portion (192) can be spaced at a fine distance from the outer circumference of the rotation axis (125).

[0157] The stopper member (190) may have a spaced-apart portion (193) between a plurality of support portions (192). The spaced-apart portion (193) may be formed as an empty space with a predetermined distance in the axial direction. With the spaced-apart portion (193) provided, the support portions (192) can be easily elastically deformed while minimizing the possibility of damage, thereby improving assembly and productivity.

[0158] Meanwhile, the separation portion (193) can be formed to be larger than half the total axial length of the stopping member (190). The support portion (192) can also be formed to be larger than half the total axial length of the stopping member (190).

[0159] Accordingly, the stopping member (190) can achieve the effect of reducing the possibility of breakage and increasing elasticity.

[0160] Referring to FIGS. 7 and 8, the total axial length of the stopper member (190) is shown as H1, the axial length of the gap member (193) is shown as H2, and the axial length of the body (191) from the stopper member (190) is shown as H3, and an example is shown in which H2 is formed to be larger than half of H1.

[0161] Additionally, the support portion (192) is preferably provided to have sufficient rigidity so that it is not damaged during assembly, that is, when it is fitted on one side of the rotation axis (125) and deformed radially outward.

[0162] To this end, the stopper (190) may be formed of PBT (Polybutylene terephthalate) material. Additionally, the stopper (190) may contain 30% GF (Glass Fiber) (GF 30% material). That is, the stopper (190) may be PBT and may contain GF 30% material.

[0163] As the stopper (190) is formed from PBT material, it has excellent resistance, high strength, stiffness, and low deformation due to heat, as well as excellent dimensional stability and creep resistance. In particular, PBT material has excellent low friction and wear resistance.

[0164] In addition, it may contain 30% GF (Glass Fiber), allowing for greater strength or stiffness against loads. GF ​​can be glass fiber, and when added to PBT material, it acts as a matrix reinforcement, thereby enhancing mechanical performance. In particular, mechanical indicators such as tensile strength and flexural modulus are significantly improved, which can reduce deformation or failure of parts when subjected to external forces or repetitive loads.

[0165] When PBT is reinforced with approximately 30% GF, thermal and mechanical stability, strength, stiffness, impact resistance, and dimensional stability are significantly improved compared to conventional PBT. Therefore, durability and precision can be further enhanced.

[0166] In addition, reinforcing PBT with approximately 30% GF can improve thermal deformation stability. Although PBT is relatively resistant to dimensional changes and deformation caused by heat, the inclusion of GF further enhances thermal stability. As dimensional stability and heat deformation resistance are improved in high-temperature environments, it may be suitable for cases where it is exposed to high temperatures for extended periods.

[0167] In addition, reinforcing PBT with about 30% GF can improve dimensional stability, as GF lowers the coefficient of thermal expansion of PBT, thereby reducing shrinkage and warping of the product.

[0168] In addition, reinforcing PBT with approximately 30% GF can improve impact resistance and wear resistance. Compared to standard PBT, GF-reinforced materials offer enhanced resistance to external impacts and friction. This allows for longer lifespans in environments where repetitive impacts or wear are expected, such as in mechanical or electrical / electronic components.

[0169] In addition, reinforcing PBT with about 30% GF results in a moisture absorption suppression effect. In engineering plastics, moisture absorption is a major factor affecting dimensional stability and physical properties. As the GF content increases, moisture absorption characteristics are relatively degraded (or the impact of absorption is reduced), allowing the material properties to be maintained stably even in environments with significant humidity fluctuations.

[0170] As shown in FIGS. 2 to 4, the support portion (192) may protrude upward toward the bushing (180) from the upper end of the body (191).

[0171] At one end of the inner circumference of the support portion (192), a support projection (192a) formed to protrude inward may be provided.

[0172] The rotation axis (125) may be provided with a support groove (1254a) capable of accommodating a support projection (192a).

[0173] The support groove (1254a) can be extended along the circumferential direction.

[0174] The support projection (192a) can support the stopper member (190) so as to be fixed to the rotation axis (125), and by fixing the stopper member (190) to the rotation axis (125), the bushing (180) can be prevented from moving out in the axial direction.

[0175] The support projection (192a) can be received in the support groove (1254a) and can secure a degree of freedom in the circumferential direction, which is the extension direction of the support groove (1254a).

[0176] When the bushing (180) is rotated by the rotation of the rotation axis (125), the stopper member (190) can also receive rotational force. Since the stopper member (190) is provided with a support projection (192a) and has a degree of freedom in the circumferential direction along the support groove (1254a), the stress transmitted to the stopper member (190) through the bushing (180) can be reduced, and the possibility of breakage can be lowered.

[0177] Conventionally, individual components were applied to fix the bushing (180) in the rotational and axial directions, respectively. In particular, to fix it in the rotational direction, a key or pin was applied to the rotational shaft (125), or the shape of the concentric bushing and the rotational shaft (125) was implemented as a D-Cut shape. Furthermore, the D-Cut shape has the disadvantage of increasing the machining cost of the shaft and the concentric bushing, and the C-Ring structure has the problem of poor assembly because it requires a manual process after the compression part is fastened due to the small shape of the component.

[0178] The present invention allows the process line to be automated and assembly productivity to be increased by using a stopper (190) that is easy to assemble while preventing the bushing (180) from coming off as the stopper (190) is installed on the rotation axis (125).

[0179] When the support projection (192a) is received in the support groove (1254a), the support portion (192) may be spaced apart from the outer circumference of the rotation axis (125) by a predetermined distance. The distance at which the inner circumference of the support portion (192) is spaced apart from the outer circumference of the rotation axis (125) may be an extremely fine distance.

[0180] As a result, the stopper member (190) is not firmly coupled to the rotation axis (125), thereby reducing the possibility of damage, and has degrees of freedom in the circumferential direction and can rotate about the rotation axis (125).

[0181] To this end, the protrusion length of the support projection (192a) can be formed to be greater than the depth of the support groove (1254a) by a predetermined distance.

[0182] The distance between the support part (192) and the rotation axis (125) can be separated by a small amount, so that sufficient fixing force is secured while the possibility of damage during assembly is minimized and the assembly can be performed stably. In addition, the support part (192) can secure degrees of freedom in elastic deformation in the radial direction.

[0183] To describe in more detail, it has the following effects.

[0184] By slightly separating the inner circumference of the stopper member (190) from the outer circumference of the rotation shaft (125), elastic deformation becomes easier, making assembly and disassembly simpler, and at the same time, interference between parts can be minimized even in the rotational and vibrational environment of the shaft, thereby increasing durability. These features are very advantageous in terms of ensuring long-term performance stability and ease of maintenance of the stopper member (190).

[0185] Assembly convenience can be improved through elastic deformation. In the process of inserting or removing the stopper (190), the rotation axis (125) or the stopper (190) itself must be slightly deformed. If the inner side of the flesh is slightly separated from the rotation axis (125), this elastic deformation can be made smoother.

[0186] That is, regarding the radial and axial forces generated when fitting or removing the stopper member (190) into the groove of the rotation axis (125), the stopper member (190) can easily spread apart or contract, thereby shortening assembly time and reducing the risk of damage.

[0187] In addition, if the distance between the support part (192) and the rotation axis (125) can be separated by a small amount, it is advantageous for securing the degree of freedom for rotation. That is, by keeping the inner side slightly separated rather than completely adhering to it, direct contact friction with the stop member (190) is minimized when the rotation axis (125) rotates, thereby reducing unnecessary wear or noise.

[0188] The distance between the support portion (192) and the rotation axis (125) can be separated by a small amount, which is advantageous for preventing damage during disassembly and assembly. Slight deformation may occur in the actual usage environment due to dimensional tolerances of the rotation axis (125) and the stopper (190) or temperature changes. If there is a gap in the material portion, it can partially absorb stress caused by external impact or dimensional deviation, thereby mitigating the risk of the stopper (190) itself breaking or the rotation axis (125) or the support groove (1254a) being damaged.

[0189] If the distance between the support part (192) and the rotation axis (125) can be separated to a fine degree, it may be advantageous for dimensional tolerances and temperature changes.

[0190] The diameter of the rotating shaft (125) may vary slightly depending on the material of the rotating shaft, the working environment (high temperature / low temperature), etc., but if there is a fine gap, the stopping member (190) does not interfere excessively with the rotating shaft (125) even if thermal expansion or contraction occurs, and the movement of the rotating shaft (125) and the role of the stopping member (190) may not interfere with each other.

[0191] If the distance between the support part (192) and the rotation axis (125) can be separated to a fine degree, it is also advantageous in terms of reducing vibration and noise.

[0192] If the stopper member (190) excessively tightens the rotation shaft (125) while mounted, friction noise may occur during vibration or wear may be accelerated.

[0193] Due to the small gap, contact between the stopper member (190) and the rotating shaft (125) is minimized even when vibration occurs, thereby reducing unnecessary noise and extending the lifespan of the parts.

[0194] FIG. 6 illustrates an example in which the protrusion length of the support projection (192a) is formed to be equal to the depth of the support groove (1254a) so that the support portion (192) and the rotation axis (125) are in contact, but it is also possible to have an example in which the protrusion length of the support projection (192a) is formed to be greater than the support groove (1254a) by a predetermined distance so that the distance between the support portion (192) and the rotation axis (125) is separated to a fine degree.

[0195] This circumferential degree of freedom differs from the stopper member (190) of another embodiment described later. That is, the stopper member (190) of another embodiment is fixed to the rotation axis (125) not only in the axial direction but also in the circumferential direction, so the fixing force can be further improved.

[0196] The stopping member (190) of another embodiment will be described later in the description section of FIG. 9 and below.

[0197] In the present invention, the bushing (180) can be fixed by being coupled to one side of the rotation shaft (125) so as to be fixed in the axial direction, thereby preventing the bushing (180) from moving out in the axial direction.

[0198] In the present invention, the support projection (192a) is received in the support groove (1254a) to secure a degree of freedom in the circumferential direction.

[0199] In addition, the stopper member (190) is configured such that the support portion (192) can be elastically deformed in the radial direction, so that it can be simply and easily assembled to the rotation axis (125), thereby lowering manufacturing costs and improving productivity.

[0200] In order to improve the lubrication performance to the fixed scroll (150) through the top of the bushing (180), a lubrication groove (187) may be provided on the top of the bushing (180).

[0201] The lubrication groove (187) can be formed radially at the top of the bushing (180) to penetrate the outer circumference and the inner circumference.

[0202] The lubrication groove (187) may be provided as a single groove or formed as a plurality. If the lubrication groove (187) is formed as a plurality, the plurality of lubrication grooves (187) may be spaced apart from each other in the circumferential direction.

[0203] In the present invention, an example is shown in which the lubrication groove (187) is provided as a single unit.

[0204] As a lubrication groove (187) is provided at the top of the bushing (180), when the rotating shaft (125) rotates, the bushing (180) moves upward and the top of the bushing (180) comes into contact with the sealing protrusion (155), so that the lubrication path is not blocked through the lubrication groove (187).

[0205] As a result, the oil supply to the compression chamber (V) and the sliding part is not blocked, and the oil can be supplied smoothly.

[0206] Meanwhile, a lubrication portion (185) may be provided on the outer circumference of the bushing (180). Additionally, a lubrication hole may be provided in the bushing (180). The lubrication portion (185) may be connected to the lubrication hole (183). The lubrication portion (185) may be formed as a groove structure that is concavely formed inwardly from the outer circumference of the bushing (180).

[0207] Accordingly, the oil sucked along the inner circumference of the rotating shaft (125) through the oil pickup (127), the oil flowing through the oil supply hole (183) can flow axially in the oil supply section (185) and be smoothly supplied to the bearing surface (see FIG. 1) between the sub-bearing (1532).

[0208] For example, the lubrication section (185) may be extended axially to guide the axial flow of oil. The oil may flow axially along the lubrication section (185). Referring to FIG. 18, the oil exiting the lubrication hole (183) flows upward along the lubrication section (185) and is connected to the lubrication groove (187) described later.

[0209] The lubrication section (185) may be connected to a lubrication groove (187) formed at one end of the bushing (180). The lubrication groove (187) may provide a flow path through which oil flowing along the lubrication section (185) flows to the inner circumference or upper part of the bushing (180).

[0210] FIG. 9 is an exploded perspective view illustrating an example in which a bushing (180) and a stopper (190) are installed on a rotating shaft (125) as another embodiment of the present invention, FIG. 10 is an exploded perspective view illustrating an example in which a stopper (190) is installed while the bushing (180) is installed on the rotating shaft (125) in the embodiment of FIG. 9. FIG. 11 is a cross-sectional view to show one operation in the process of installing a stopper (190) on a rotating shaft (125) with a bushing (180) installed in the embodiment of FIG. 9, FIG. 12 is a perspective view to show one operation in the process of installing a stopper (190) on a rotating shaft (125) with a bushing (180) installed in the embodiment of FIG. 9. FIG. 13 is a perspective view showing one operation in the process of installing a stopper member (190) on a rotating shaft (125) on which a bushing (180) is installed in the embodiment of FIG. 9, and FIG. 14 is a perspective view showing an example in which a stopper member (190) is installed on a rotating shaft (125) on which a bushing (180) is installed in the embodiment of FIG. 9. Additionally, FIG. 15 is a cross-sectional view showing an example in which a stopper member (190) is installed on a rotating shaft (125) on which a bushing (180) is installed in the embodiment of FIG. 9.

[0211] Hereinafter, with reference to FIGS. 9 to 15, a stopping member (190) and a coupling relationship between the stopping member (190) and surrounding components according to another embodiment of the present invention will be described.

[0212] In this embodiment, the stopping member (190) may have a body (191) and a support portion (192).

[0213] The body (191) can be installed to surround the outer circumference of the rotation axis (125).

[0214] The body (191) can be installed on one side of the rotation axis (125) to surround the outer circumference of the rotation axis (125), and as described above in the previous embodiment, it can be installed on the lower side of the rotation axis (125).

[0215] More specifically, the body (191) can be installed on the sub-bearing surface (1254) of the rotation axis (125).

[0216] The body (191) is provided with a support portion (192) so that the bushing (180) can be supported on the rotation axis (125) and simultaneously coupled to the outer circumference of the rotation axis (125).

[0217] The body (191) can be joined to the rotation axis (125) by a press-fit method.

[0218] The support portion (192) may protrude from one side of the body (191) toward the bushing (180) to enable the bushing (180) to be supported on the rotation axis (125).

[0219] The support portion (192) may be provided in multiple units spaced apart from each other in the circumferential direction.

[0220] The support portion (192) is formed to be elastically deformable in the radial direction, so that it can be inserted from one side of the rotation axis (125) and fixed to the rotation axis (125).

[0221] The support portion (192) may further include a bushing support portion (195).

[0222] The bushing support portion (195) may be formed such that at least one of the plurality of support portions (192) has an end that extends further toward the bushing (180).

[0223] The bushing (180) may have a rotation limiting groove (188) that accommodates the bushing support (195) and is formed concavely on the outer circumference.

[0224] FIG. 9 illustrates a stopper member (190) having approximately six support portions (192), wherein a bushing support portion (195) is provided on one side of one of the support portions (192), and the support portion (192) having the bushing support portion (195) is formed to be longer than the other support portions (192).

[0225] Additionally, FIG. 9 illustrates an example in which a rotation limiting groove (188) is formed on one side of a bushing (180) so as to penetrate the inner circumference and the outer circumference.

[0226] The rotation limiting groove (188) may have a first limiting support portion (188a) and a second limiting support portion (188b).

[0227] The first limiting support portion (188a) may be provided at both ends of the circumferential side of the rotation limiting groove (188). By the first contact support portion (1254b1), the stop member (190) and the bushing (180) may be supported so as to limit rotation in the circumferential direction.

[0228] The second contact support portion (1254b2) may be positioned axially between the first contact support portion (1254b1) of the cut support portion (1254b). By the second contact support portion (1254b2), the stop member (190) may be supported axially with respect to the bushing (180).

[0229] At one end of the inner circumference of the support portion (192), a support projection (197) protruding inward may be provided.

[0230] At one end of the above-mentioned rotation axis (125), a cut support portion (1254b) may be provided, which is formed by cutting a predetermined distance in the circumferential direction to accommodate the above-mentioned support protrusion (197).

[0231] FIGS. 9 and 10 illustrate an example in which a supporting projection (197) protruding inward is provided at the lower end of the supporting portion (192), and a cut supporting portion (1254b) is cut inward by a predetermined distance in the circumferential direction at the lower end of the sub-bearing surface portion (1254) of the rotating shaft (125), and formed to penetrate the inner circumference and outer circumference at the lower end of the sub-bearing surface portion (1254) of the rotating shaft (125).

[0232] The cut support portion (1254b) may have a first contact support portion (1254b1) and a second contact support portion (1254b2).

[0233] The first contact support portion (1254b1) may be provided at both ends of the circumferential side of the cut support portion (1254b). As both sides of the support protrusion (197) are supported by the first contact support portion (1254b1), the stop member (190) may be supported so as to restrict rotation in the circumferential direction.

[0234] The second contact support portion (1254b2) may be positioned axially between the first contact support portion (1254b1) of the cut support portion (1254b). As one side of the support protrusion (197) is supported axially by the second contact support portion (1254b2), the stop member (190) may be supported axially.

[0235] In the invention of the present embodiment, the stopping member (190) is not only constrained in the axial direction, but the bushing support member (195) is received and coupled to the rotation limiting groove (188) of the rotation axis (125), thereby fixing the bushing (180) so as to prevent the bushing (180) from moving out in the axial direction and to limit rotation in the circumferential direction.

[0236] The invention of the present embodiment differs from the previous embodiment in that, as the bushing support part (195) is received and coupled to the rotation limiting groove (188) of the rotation shaft (125), fixing force can be secured not only in the axial direction but also in the circumferential direction.

[0237] In addition, the stopper member (190) is configured such that the support portion (192) can be elastically deformed in the radial direction, so that it can be simply and easily assembled to the rotation axis (125), thereby lowering manufacturing costs and improving productivity.

[0238] In addition, in the invention of the present embodiment, as the support protrusion (197) is received and coupled to the cut support portion (1254b) of the rotation axis (125), the stop member (190) can be fixed not only in the axial direction but also in the circumferential direction with respect to the rotation axis (125).

[0239] Referring to FIGS. 11 to 13, the process of inserting a stopper member (190) into one side of the sub-bearing surface (1254) of the rotation shaft (125) is illustrated, and an example is illustrated in which the support portion (192) is elastically deformed outward as the support projection (192a) of the support portion (192) is pressed by the outer circumference of the sub-bearing surface (1254) of the rotation shaft (125).

[0240] Additionally, FIGS. 14 and 15 illustrate an example in which a stopper member (190) is fully coupled to a rotation axis (125), wherein a support projection (192a) of a support portion (192) is received in a support groove (1254a) of the rotation axis (125).

[0241] The protruding length of the support projection (192a) can be formed to be greater than the depth of the support groove (1254a) by a predetermined distance. As a result, the inner circumference of the support portion (192) can be spaced at a fine distance from the outer circumference of the rotation axis (125).

[0242] The stopper member (190) may have a spaced-apart portion (193) between a plurality of support portions (192). The spaced-apart portion (193) may be formed as an empty space with a predetermined distance in the axial direction. With the spaced-apart portion (193) provided, the support portions (192) can be easily elastically deformed while minimizing the possibility of damage, thereby improving assembly and productivity.

[0243] Meanwhile, the separation portion (193) can be formed to be larger than half the total axial length of the stopping member (190). The support portion (192) can also be formed to be larger than half the total axial length of the stopping member (190).

[0244] Accordingly, the stopping member (190) can achieve the effect of reducing the possibility of breakage and increasing elasticity.

[0245] The entire axial length of the stopper member (190) is shown as H1, the axial length of the separation portion (193) is shown as H2, and the axial length of the body (191) from the stopper member (190) is shown as H3. In this respect, an example is shown in which H2 is formed to be larger than half of H1, as previously described in the description of FIGS. 7 and FIGS. 8, and can also be applied in this embodiment.

[0246] Additionally, the support portion (192) is preferably provided to have sufficient rigidity so that it is not damaged during assembly, that is, when it is fitted on one side of the rotation axis (125) and deformed radially outward.

[0247] To this end, the stopper (190) may be formed of PBT (Polybutylene terephthalate) material. Additionally, the stopper (190) may contain 30% GF (Glass Fiber) (GF 30% material). That is, the stopper (190) may be PBT and may contain GF 30% material.

[0248] As the stopper (190) is formed from PBT material, it has excellent resistance, high strength, stiffness, and low deformation due to heat, as well as excellent dimensional stability and creep resistance. In particular, PBT material has excellent low friction and wear resistance.

[0249] In addition, it can contain 30% GF (Glass Fiber), allowing it to have greater strength or stiffness against load.

[0250] As shown in FIGS. 2 to 4, the support portion (192) may protrude upward toward the bushing (180) from the upper end of the body (191).

[0251] At one end of the inner circumference of the support portion (192), a support projection (192a) formed to protrude inward may be provided.

[0252] The rotation axis (125) may be provided with a support groove (1254a) capable of accommodating a support projection (192a).

[0253] The support groove (1254a) can be extended along the circumferential direction.

[0254] The support projection (192a) can support the stopper member (190) so as to be fixed to the rotation axis (125), and by fixing the stopper member (190) to the rotation axis (125), the bushing (180) can be prevented from moving out in the axial direction.

[0255] The support projection (192a) can be received in the support groove (1254a) and can secure a degree of freedom in the circumferential direction, which is the extension direction of the support groove (1254a).

[0256] When the bushing (180) is rotated by the rotation of the rotation axis (125), the stopper member (190) can also receive rotational force. Since the stopper member (190) is provided with a support projection (192a) and has a degree of freedom in the circumferential direction along the support groove (1254a), the stress transmitted to the stopper member (190) through the bushing (180) can be reduced, and the possibility of breakage can be lowered.

[0257] Conventionally, individual components were applied to fix the bushing (180) in the rotational and axial directions, respectively. In particular, to fix it in the rotational direction, a key or pin was applied to the rotational shaft (125), or the shape of the concentric bushing and the rotational shaft (125) was implemented as a D-Cut shape. Furthermore, the D-Cut shape has the disadvantage of increasing the machining cost of the shaft and the concentric bushing, and the C-Ring structure has the problem of poor assembly because it requires a manual process after the compression part is fastened due to the small shape of the component.

[0258] The present invention allows the process line to be automated and assembly productivity to be increased by using a stopper (190) that is easy to assemble while preventing the bushing (180) from coming off as the stopper (190) is installed on the rotation axis (125).

[0259] When the support projection (192a) is received in the support groove (1254a), the support portion (192) may be spaced apart from the outer circumference of the rotation axis (125) by a predetermined distance. The distance at which the inner circumference of the support portion (192) is spaced apart from the outer circumference of the rotation axis (125) may be an extremely fine distance.

[0260] As a result, the stopper member (190) is not firmly coupled to the rotation axis (125), thereby reducing the possibility of damage, and has degrees of freedom in the circumferential direction and can rotate about the rotation axis (125).

[0261] To this end, the protrusion length of the support projection (192a) can be formed to be greater than the depth of the support groove (1254a) by a predetermined distance.

[0262] The distance between the support part (192) and the rotation axis (125) can be separated by a small amount, so that sufficient fixing force is secured while the possibility of damage during assembly is minimized and the assembly can be performed stably. In addition, the support part (192) can secure degrees of freedom in elastic deformation in the radial direction.

[0263] This circumferential degree of freedom differs from the stopper member (190) of another embodiment described later. That is, the stopper member (190) of another embodiment is fixed to the rotation axis (125) not only in the axial direction but also in the circumferential direction, so the fixing force can be further improved.

[0264] The invention of the present embodiment allows the bushing (180) to be fixed not only in the axial direction but also by the bushing support member (195) being received and coupled in the rotation limiting groove (188) of the rotation axis (125), thereby preventing the bushing (180) from moving out in the axial direction and limiting rotation in the circumferential direction.

[0265] In the invention of the present embodiment, as the bushing support part (195) is received and coupled to the rotation limiting groove (188) of the rotation axis (125), fixing force can be secured not only in the axial direction but also in the circumferential direction.

[0266] In addition, the stopper member (190) is configured such that the support portion (192) can be elastically deformed in the radial direction, so that it can be simply and easily assembled to the rotation axis (125), thereby lowering manufacturing costs and improving productivity.

[0267] The scroll compressor described above is not limited to the configuration and method of the embodiments described above; rather, the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

[0268] It is obvious to those skilled in the art that the present invention may be embodied in other specific forms without departing from the spirit and essential features of the invention. Accordingly, the foregoing detailed description should not be interpreted restrictively in all respects but should be considered exemplary. The scope of the invention shall be determined by a reasonable interpretation of the appended claims, and all modifications within the equivalent scope of the invention are included within the scope of the invention.

[0269] The present invention is industrially applicable as it can be applied to scroll compressors that increase assembly reliability and productivity.

Claims

1. Casing forming the outer casing; A power generation unit installed inside the above casing to generate power; A rotating shaft rotatably installed in the above-mentioned electric motor; A compression unit comprising a pivot scroll installed to pivotally rotate on the above-mentioned rotational axis and a fixed scroll coupled to engage with the pivot scroll to form a compression chamber between the pivot scrolls; and A bushing disposed between the fixed scroll and the rotation axis and disposed on the outer circumference of the rotation axis to rotate together with the rotation axis; and A scroll compressor comprising a stopper member formed to be inserted and installed on one side of the rotating shaft to support one side of the bushing.

2. In Paragraph 1, The above-mentioned stopper is a scroll compressor having a body installed to surround the outer circumference of a rotating shaft and a support portion protruding from one side of the body toward the bushing to support the bushing on the rotating shaft.

3. In Paragraph 2, The above support portion is provided in a plurality of units spaced apart from each other in the circumferential direction, and A scroll compressor capable of being inserted from one side of the aforementioned rotating shaft and capable of elastic deformation in the radial direction so as to be fixed to the said rotating shaft.

4. In Paragraph 3, The above-described stopping member has a gap formed as an empty space between a plurality of support portions by a predetermined distance in the axial direction, and the gap is formed to be larger than half the total axial length of the stopping member, in a scroll compressor.

5. In Paragraph 2, The above body is a scroll compressor that is coupled to the above-mentioned rotating shaft by a press-fit method.

6. In Paragraph 3, At the end of the support portion, a support projection is provided that protrudes inward and extends in the circumferential direction, and A scroll compressor having a support groove formed concavely on the outer circumference of the above-mentioned rotating shaft and extending in the circumferential direction.

7. In Paragraph 6, A scroll compressor in which the support groove is positioned adjacent to one end of the bushing, and the end of the support portion is positioned to contact the end of the bushing.

8. In Paragraph 6, A scroll compressor formed such that the protrusion length of the above-mentioned support projection is greater than the depth of the above-mentioned support groove by a predetermined distance.

9. In Paragraph 1, The above-mentioned stopping member is, A scroll compressor formed of PBT material and containing 30% GF (Glass Fiber).

10. In Paragraph 2, The above support portion is provided in a plurality of units spaced apart from each other in the circumferential direction, and At least one of the plurality of support parts further comprises a bushing support part formed such that its end extends further toward the bushing, and The above bushing is a scroll compressor that accommodates the bushing support and is provided with a rotation limiting groove formed concavely on the outer circumference.

11. In Paragraph 10, The above rotation limiting groove is, A first contact support portion provided at both ends of the circumferential side of the rotation limiting groove and restricting the rotation of the stop member and the bushing in the circumferential direction; A scroll compressor having a second contact support portion disposed axially between the first contact support portions of the cut support portions to enable the stop member to be supported axially with respect to the bushing.

12. In Paragraph 10, At one end of the inner circumference of the above body, a supporting projection protruding inward is provided, and A scroll compressor having a cut support portion formed by cutting a predetermined distance in the circumferential direction at one end of the above-mentioned rotating shaft to accommodate the above-mentioned support protrusion.

13. In Paragraph 12, The above-mentioned incision support is, A first contact support portion provided at both ends of the circumferential side of the incision support portion to support both sides of the support protrusion; A scroll compressor having a second contact support portion disposed axially between the first contact support portions of the cut support portions and supporting the stop member axially.

14. In Paragraph 12, A scroll compressor in which the support protrusion and the bushing support are provided at positions where they overlap in the circumferential direction, and the rotation limiting groove and the cut support are provided at positions where they overlap in the circumferential direction.

15. In Paragraph 12, The above-mentioned support protrusion is formed in a polygonal shape and protrudes in a direction intersecting the above-mentioned bushing support.

16. In Paragraph 1, The above-mentioned rotating shaft comprises a main shaft portion coupled to the above-mentioned transmission unit; an eccentric portion coupled eccentrically to the above-mentioned rotating scroll; and a sub-bearing surface portion radially supported to the above-mentioned fixed scroll. The above bushing is provided between the sub-bearing surface and the fixed scroll, and is a scroll compressor fixed to one side of the sub-bearing surface.

Images