Scroll compressor

Abstract

The present invention provides a scroll compressor provided with: a casing; an electric motor unit; a rotatable shaft rotatably mounted on the electric motor unit; a compression unit provided with an orbiting scroll, which is mounted on the rotatable shaft so as to be orbitally rotatable, and a fixed scroll, which is engaged with and coupled to the orbiting scroll so as to form a compression chamber between the fixed scroll and the orbiting scroll; a bushing that is located between the fixed scroll and the rotatable shaft and disposed on the outer circumference of the rotatable shaft so as to rotate with the rotatable shaft; and a fixed member that is provided to support the bushing and the rotatable shaft and provided with a portion that protrudes so as to catch on at least one of the bushing or the rotatable shaft.

Description

scroll compressor

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

[0002] Scroll compressors can be categorized as upper compression or lower compression types based on the location of the drive motor and compression unit, which form the drive or transmission unit. Upper compression types have the compression unit positioned above the drive motor, while lower compression types have the compression unit positioned below the drive motor. This classification is based on examples where the casing is installed vertically or horizontally. If the casing is installed horizontally, the left side can be conveniently designated as the upper side and the right side as the lower side.

[0003] Scroll compressors can be classified into back-mounted and shaft-through types depending on how the rotating shaft is coupled to the orbiting scroll. In the back-mounted type, the rotating shaft is coupled to the back of the orbiting scroll, while in the shaft-through type, the rotating shaft is coupled by penetrating the orbiting scroll.

[0004] In the back-to-back coupling method, the orbiting wrap and fixed wrap are extended long to the center of the orbiting scroll and fixed scroll, but the gap between the point of application of the gas reaction force and the support point of the bearing is large, which may cause the behavior of the orbiting scroll to become unstable.

[0005] The shaft-through method minimizes the gap between the point of application of the gas reaction force and the support point of the bearing, thereby stabilizing the behavior of the orbiting scroll. In addition, since the rotating shaft penetrates the orbiting scroll and is rotatably connected to the fixed scroll, the length of the orbiting wrap and the fixed wrap can be shortened, thereby reducing the compression length.

[0006] Patent Document 1 (Korean Patent Publication No. 10-2019-0011115, February 1, 2019) discloses a through-axis scroll compressor. In Patent Document 1, a rotating shaft sequentially penetrates and connects a main frame, an orbiting scroll, and a fixed scroll. In other words, the rotating shaft of Patent Document 1 is provided with an eccentric member that eccentrically penetrates the orbiting scroll and is rotatably connected to the main frame and the fixed scroll, respectively.

[0007] However, in the conventional shaft-through scroll compressor as described above, the surface pressure between the sub-bearing surface of the rotating shaft coupled to the fixed scroll and the sub-bearing of the fixed scroll into which the sub-bearing surface is inserted may increase. In other words, since the rotating shaft eccentrically penetrates the orbiting scroll and is rotatably coupled to the fixed scroll, the outer diameter of the sub-bearing surface is formed to be smaller than the outer diameter of the eccentric portion, which ultimately increases the surface pressure between the sub-bearing surface and the sub-bearing. In consideration of this, when the outer diameter of the sub-bearing surface is enlarged, the outer diameter of the eccentric portion is also enlarged, which may reduce the compression length or increase the outer diameter of the compression portion.

[0008] Meanwhile, the concentric bushing is coupled with the rotating shaft and rotates concentrically with the rotating shaft during operation.

[0009] In order to join a concentric bushing, there is a method of forcibly pressing it into the rotating shaft, and a method of inserting the concentric bushing into the rotating shaft with a gap and then fixing the concentric bushing in the rotational direction and axial direction with a separate member.

[0010] In the conventional structure, in which a concentric bushing is inserted into a gap on a rotating shaft and then fixed as a separate member, separate members were applied for fixing in the rotational direction and the axial direction.

[0011] To secure the rotational direction, a key or pin is applied to the rotational axis, or a concentric bushing and a self-shaped D-Cut shape are implemented on the rotational axis. A C-Ring is applied to prevent axial downward displacement.

[0012] The concentric bushing that inserts the concentric bushing into the rotational axis with a gap must have the freedom of rotational and axial movement for geometric tolerance compensation, so it must not be completely fixed to the rotational axis by a fixed member.

[0013] The key structure has poor assembly performance due to the compression section being assembled and then fastened, and the D-Cut shape has the disadvantage of increased machining costs for the shaft and concentric bushing. Furthermore, the C-Ring structure is a small component that requires manual processing after the compression section is fastened, which also reduces assembly performance.

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

[0015] The present invention has been devised to solve the above problems, and a first object of the present invention is to provide a scroll compressor having a structure capable of reducing the surface pressure of a bearing of a fixed scroll.

[0016] A second object of the present invention is to provide a scroll compressor having a bushing assembly structure that does not allow the concentric bushing to move in either the rotational or axial direction without completely fixing the concentric bushing to the rotational shaft in order to compensate or absorb the bearing gap and geometric tolerance and the concentric bushing that slides with the bearing.

[0017] The third object of the present invention is to provide a scroll compressor having a structure in which a member for fixing a concentric bushing is simply and easily assembled to enable automation in order to increase productivity.

[0018] A fourth object of the present invention is to provide a scroll compressor having a structure that enables smooth lubrication between a rotating shaft and a bearing.

[0019] In order to solve the above problem, the scroll compressor of the present invention includes a casing forming an exterior; a motor installed inside the casing and generating power; a rotary shaft rotatably installed in the motor; a compression unit having an orbiting scroll installed to be rotatable around the rotary shaft and a fixed scroll coupled to the orbiting scroll so as to be engaged with the orbiting scroll and forming a compression chamber between the orbiting scrolls; and 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 fixed member provided to support the bushing and the rotary shaft and having a portion protruding so as to be caught by at least one of the bushing and the rotary shaft.

[0020] This allows the bushing to be restrained axially and radially about the axis of rotation.

[0021] The above-mentioned fixed member may be formed as a fixed cap having a body portion arranged to surround the outer circumference of the rotational shaft and a guide support portion protruding in the axial direction in which the rotational shaft extends from one side of the body portion to support the bushing on the rotational shaft.

[0022] In this way, the fixing of the bushing to the rotation axis can be implemented with a fixing cap that can form a structure in which the bushing is supported on the rotation axis by a guide support member while supporting the bushing to surround the rotation axis.

[0023] According to one example of the present invention, the guide support member may have a first engaging restraint member formed to be bent outward from an end portion, and the inner circumference of the bushing may have a groove that receives the first engaging restraint member and restricts the bushing from axially deviating from the fixed cap.

[0024] In this way, the first engaging restraint member is accommodated in the home portion, so that the bushing can be restricted from axial movement about the rotation axis.

[0025] Preferably, the body part can be joined to the rotation axis by a press-fit method.

[0026] As a result, since the body of the bushing is press-fitted to the rotational shaft, the bushing can be prevented from being dislodged in the axial and rotational directions with respect to the rotational shaft.

[0027] The above guide support member may be formed to be inclined inward at a predetermined angle, and a guide groove for accommodating the guide support member may be provided on the outer periphery of the rotational axis.

[0028] According to this configuration, the fixed cap can be assembled stably and with minimal damage during the process of assembling it between the rotating shaft and the bushing.

[0029] Preferably, the guide support portion is provided in a plurality of pieces, and the first engaging restraint portion may be provided on some of the plurality of guide support portions.

[0030] By providing multiple guide supports, the assembly of the rotary shaft and the bushing can be performed more stably, and by providing a first engaging restraint on some of the multiple guide supports, the bushing can be prevented from axially detaching from the rotary shaft.

[0031] Another part of the plurality of guide supports may be provided with a second engaging restraint portion formed to be bent inward from the end, and a engaging groove portion that is engaged and fixed to the second engaging restraint portion may be provided on the outer periphery of the rotation shaft.

[0032] The engaging groove can be engaged by a second engaging restraint member at one end, thereby limiting the axial movement of the fixed cap.

[0033] Preferably, the catch groove may be provided in a circumferential direction on the outer periphery of the rotation shaft.

[0034] The above body part can be connected to the rotation axis by sliding.

[0035] Due to this, compared to the press-fit method described above, it can have a limited degree of freedom without being completely fixed in the axial direction, and it can absorb or compensate for the gap or geometric tolerance between the rotating shaft and the bushing, so it can respond to concerns about reduced reliability.

[0036] The above-mentioned fixed member is defined as a pin that is coupled to a bushing and is provided to protrude inwardly of the bushing and has an elastically deformable diameter, and the rotational axis may be provided with a slit groove that extends a predetermined distance to guide movement of the pin; and a mounting groove that is provided on one side of the slit groove and in which the pin is mounted to limit movement.

[0037] Due to this, the bushing can be stably guided and assembled by the slit groove, and in the assembled state, the movement of the pin is restricted by the fixing groove, so that the bushing can be prevented from being dislodged in the axial and rotational directions.

[0038] The maximum diameter of the pin may be smaller than or equal to the diameter of the mounting groove and larger than the width of the slit groove, and the minimum diameter of the pin may be smaller than or equal to the width of the slit groove.

[0039] Due to this, the bushing rotates along with the rotation axis without being subjected to forces in the up-down (axial) or circumferential direction, so that the bushing can be prevented from being dislodged from the rotation axis in the direction and circumferential direction, and can be stably supported.

[0040] The above-mentioned fixed member is defined to include a pin that is coupled to the bushing and is provided to protrude inwardly of the bushing; and a fixed ring that is coupled to the outer periphery of the rotational shaft and contacts the lower end of the bushing to support the bushing so that it does not come off, and the rotational shaft may be provided with a slit groove that extends a predetermined distance to guide movement of the pin.

[0041] According to this configuration, the retaining ring can be brought into contact with the lower end of the bushing to support the bushing so that it does not move downward from the rotation axis.

[0042] Preferably, the pin can be elastically deformed in diameter.

[0043] The above fixed ring can be press-fitted to the outer circumference of the rotating shaft.

[0044] This eliminates the need for tapping on the retaining ring, saving man-hours and enabling a relatively simple assembly process, thus improving productivity. Furthermore, the bushing is prevented from axially dislodging.

[0045] The above fixed ring can be connected to the outer circumference of the rotating shaft by a bolt fastening method.

[0046] When the fixed ring is connected to the outer circumference of the rotating shaft by a bolt fastening method, it may be easier to repair or replace the fixed ring compared to the press-fit method, which may be advantageous in terms of maintenance.

[0047] The above-mentioned fixing member is defined to include a pin that is coupled to the bushing and is provided to protrude inwardly of the bushing; and a fixing ring that is coupled to the outer circumference of the rotational shaft and contacts the lower end of the bushing to support the bushing so that it does not come off. The fixing ring may include a ring body that is installed on the outer circumference of the rotational shaft, and a restraining pin that protrudes axially from the ring body and is installed on at least one of the bushing and the rotational shaft.

[0048] By installing the restraining pin of the fixed ring on at least one of the bushing and the rotating shaft, the bushing can be prevented from being dislodged in the axial and rotating directions.

[0049] The above pin can be elastically deformed in diameter.

[0050] At least one of a bushing coupling groove provided at one end of the bushing and a rotary shaft coupling groove provided at the rotary shaft is provided, and the restraining pin can be inserted into at least one of the bushing coupling groove and the rotary shaft coupling groove.

[0051] The above bushing coupling groove is formed along the inner circumference of one end of the bushing, the above rotary shaft coupling groove is formed along the outer circumference of the rotary shaft, the above bushing coupling groove and the above rotary shaft coupling groove are formed in communication so as to face each other, and the above restraining pin can be inserted between the above bushing coupling groove and the above rotary shaft coupling groove that are in communication with each other.

[0052] By inserting the retaining pin of the fixed ring between the bushing coupling groove and the rotary shaft coupling groove, the bushing can be prevented from being dislodged in the axial and rotary directions.

[0053] For example, the restraint pin may be provided in at least one number, and the restraint pin may be provided to protrude from one surface of the ring body, be inserted into one surface of the ring body, or penetrate one surface and the other surface of the ring body.

[0054] The upper end of the above bushing is provided with a lubrication groove, and the lubrication groove can be formed to penetrate the inner and outer peripheries of the bushing.

[0055] Due to this, when the shaft rotates, the oil supply path is not blocked through the oil supply groove even when the bushing moves upward and the top of the bushing comes into contact with the sealing projection.

[0056] Preferably, the above-mentioned refueling grooves may be provided in multiple numbers spaced apart in the circumferential direction.

[0057] 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.

[0058] The scroll compressor of the present invention can be applied to an automated process on a line without a manual process by simply coupling a bushing to a rotating shaft, including a fixed cap.

[0059] The scroll compressor of the present invention has a fixed cap having a catch portion, a catch groove of a rotating shaft is supported, and the catch portion is supported by a groove portion of a bushing, so that the bushing can be restrained in the axial and radial directions with respect to the rotating shaft.

[0060] The scroll compressor of the present invention has a limited degree of freedom in the rotational and axial directions without the bushing being completely fixed to the rotational shaft, so that the gap or geometric tolerance between the rotational shaft and the bushing can be absorbed or compensated during operation of the compressor, thereby enabling a response to concerns about reduced reliability.

[0061] The scroll compressor of the present invention has a structure in which the pin of the bushing contacts one side of the slit groove of the rotating shaft and the fixing ring contacts and supports the bushing, thereby preventing the bushing from being dislodged in the axial and rotational directions.

[0062] In the scroll compressor of the present invention, the guide support part is formed to be inclined inward, and a guide groove is provided on the rotation shaft, so that damage is minimized and the fixed cap can be stably assembled during the process of assembling it between the rotation shaft and the bushing.

[0063] In the scroll compressor of the present invention, since a lubrication groove is provided at the top of the bushing, even when the bushing moves upward and the top of the bushing comes into contact with the sealing protrusion during rotation of the rotating shaft, the lubrication path is not blocked through the lubrication groove.

[0064] The scroll compressor of the present invention can enable smooth lubrication between the rotating shaft and the bearing by forming an oil supply hole in the bushing and forming an oil hole in the rotating shaft provided on the inner periphery of the bushing.

[0065] Figure 1 is a cross-sectional view illustrating a scroll compressor of the present invention.

[0066] Figure 2 is an exploded perspective view showing the rotating shaft, bushing, and fixed scroll of the present invention.

[0067] Fig. 3 is a perspective view showing an example in which a bushing is installed by a fixed cap on the rotation shaft in Fig. 2.

[0068] Figure 4 is an exploded perspective view showing an example in which a bushing is installed by a fixed cap on a rotating shaft.

[0069] Fig. 5 is an enlarged cross-sectional view of part A of Fig. 1, showing an example in which a bushing is installed by a fixed cap on a rotating shaft.

[0070] Figure 6 is an exploded perspective view showing another example in which a bushing is installed by a fixed cap on a rotating shaft.

[0071] Figure 7 is a cross-sectional view of the bushing coupled to the rotation shaft in Figure 6.

[0072] Fig. 8 is a perspective view showing a third embodiment in which a bushing is fixed to a rotating shaft.

[0073] Figure 9 is an exploded perspective view showing the rotating shaft and bushing in Figure 8.

[0074] FIG. 10 is a conceptual diagram illustrating an example in which a pin is mounted on a rotation axis in the embodiment of FIG. 8.

[0075] Fig. 11 is a cross-sectional view of Fig. 8.

[0076] Fig. 12 is a perspective view showing a fourth embodiment in which a bushing is fixed to a rotating shaft.

[0077] Fig. 13 is an exploded perspective view showing the rotating shaft and bushing in Fig. 12 disassembled.

[0078] FIG. 14 is a conceptual diagram illustrating an example in which a pin is guided to a rotation axis in the embodiment of FIG. 12.

[0079] Fig. 15 is a cross-sectional view of Fig. 12.

[0080] Fig. 16 is a perspective view showing a fifth embodiment in which a bushing is fixed to a rotating shaft.

[0081] Fig. 17 is an exploded perspective view showing the rotating shaft and bushing in Fig. 16 disassembled.

[0082] Fig. 18 is a cross-sectional view of Fig. 16.

[0083] Fig. 19 is a conceptual diagram illustrating various examples of fixed rings in the embodiment of Fig. 16.

[0084] 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.

[0085] In the following description, "upper side" means the direction away from the support surface supporting the scroll compressor according to the embodiment of the present invention, that is, the upper side is the drive unit (power unit (120) or drive motor) side when looking at the drive unit (power unit (120) or drive motor) and the compression unit (C) as the center. "Lower side" means the direction approaching the support surface, that is, the lower side is the compression unit (C) side when looking at the drive unit (power unit (120) or drive motor) and the compression unit (C) as the center.

[0086] Additionally, the term "axial" used in the following description refers to the longitudinal direction of the rotation axis (125). "Axial" can be understood as an up-down direction. "Radial" refers to a direction intersecting the rotation axis (125).

[0087] In addition, in the following description, the scroll compressor is described as a sealed scroll compressor in which a drive unit (electric unit (120) or drive motor) and a compression unit (C) are provided in a casing (110). However, the same may be applied to an open compressor in which a drive unit (electric unit (120) or drive motor) is provided outside the casing (110) and connected to a compression unit (C) provided inside the casing (110).

[0088] In addition, the following description will be given as an example a lower compression type scroll compressor in which the electric part (120) and the compression part (C) are arranged in the vertical axial direction and the compression part (C) is positioned lower than the driving part (electric part (120) or the driving motor). However, the same can be applied to a horizontal scroll compressor in which the driving part (electric part (120) or the driving motor) and the compression part (C) are arranged left and right, as well as an upper compression type scroll compressor in which the compression part (C) is positioned higher than the driving part (electric part (120) or the driving motor).

[0089] In addition, the following description is given as an example a high-pressure scroll compressor in which a refrigerant suction pipe forming a suction passage while being a lower compression type is directly connected to a compression section (C), and a refrigerant discharge pipe is connected to the internal space of the casing (110) so that the internal space of the casing (110) forms a discharge pressure.

[0090] The scroll compressor of the present invention comprises: a casing (110) forming an exterior; a motor (120) installed inside the casing (110) to generate power; a rotary shaft (125) rotatably installed on the motor (120); a compression unit (C) having an orbiting scroll (140) installed on the rotary shaft (125) to be rotatable and a fixed scroll (150) coupled to the orbiting scroll (140) to be engaged with the orbiting scroll (140) and forming a compression chamber (V) between the orbiting scroll (140); a bushing (180) disposed between the fixed scroll (150) and the rotary shaft (125) and disposed on the outer periphery of the rotary shaft (125) to rotate together with the rotary shaft (125); And it includes a fixing member (190, 191, 192, 193) which is provided to support the bushing (180) and the rotation shaft (125) and has a protruding portion to be caught by at least one of the bushing (180) and the rotation shaft (125).

[0091] Due to this, the bushing (180) can be restrained without being dislodged in the axial and radial directions with respect to the rotation axis (125).

[0092] In addition, since the bushing (180) is not completely fixed to the rotational shaft (125), it can have a limited degree of freedom in the rotational and axial directions, so that the gap or geometric tolerance between the rotational shaft (125) and the bushing (180) can be absorbed or compensated during operation of the compressor, thereby enabling a response to concerns about reduced reliability.

[0093] First, with reference to Fig. 1, the overall configuration of the scroll compressor of the present invention will be described.

[0094] Referring to FIG. 1, a high-pressure, bottom-compression scroll compressor (hereinafter, abbreviated as a scroll compressor) according to the present embodiment is provided with a motor (120) in the upper half of a casing (110), and a main frame (130), an orbiting scroll (140), a fixed scroll (150), and a discharge cover (160) are provided on the lower side of the motor (120). Typically, the main frame (130), the orbiting scroll (140), the fixed scroll (150), and the discharge cover (160) form a compression section (C).

[0095] The drive motor (120) forming the electric unit (120) is coupled to the upper end of the rotation shaft (125) to be described later, and the compression unit (C) is coupled to the lower end of the rotation shaft (125). Accordingly, the compressor forms the lower compression structure described above, and the compression unit (C) is connected to the drive motor (120) by the rotation shaft (125) and operates by the rotational force of the drive motor (120). Therefore, the electric unit (120) can be understood as a drive unit that drives the compression unit (C). Hereinafter, the electric unit (120) can be a drive motor or a drive unit.

[0096] 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) has a cylindrical shape with both upper and lower ends open, the upper shell (112) is coupled to cover the opened upper end of the cylindrical shell (111), and the lower shell (113) is coupled to cover the opened 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 divided into a lower space (S1) and an upper space (S2) based on the driving motor (120).

[0097] The lower space (S1) is a space formed on the lower side of the driving motor (120), and the lower space (S1) can be divided into a storage space (S1) and a discharge space (S12) based on the compression section (C).

[0098] The upper space (S2) is a space formed above the driving motor (120) and forms an oil separation space where 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).

[0099] The aforementioned driving 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 driving motor (120) and the outer surface of the main frame (130) at a predetermined interval from the inner surface of the cylindrical shell (111).

[0100] A refrigerant suction pipe (115) is connected by penetrating the side of the cylindrical shell (111). Accordingly, the refrigerant suction pipe (115) is connected by penetrating the cylindrical shell (111) forming the casing (110) in the radial direction.

[0101] The upper part of the upper shell (112) is connected to the inner space (not shown) of the casing (110), specifically, the upper space (S2) formed on the upper side of the driving motor (120), through which the inner end of the refrigerant discharge pipe (116) is connected.

[0102] One end of an oil circulation pipe (not shown) may be radially connected to the lower half of the lower shell (113). The oil circulation pipe is open at both ends, and the other end of the oil circulation pipe may be connected to the refrigerant suction pipe (115). An oil circulation valve (not shown) may be installed in the middle of the oil circulation pipe.

[0103] Referring to Fig. 1, the driving motor (120) according to the present embodiment includes a stator (121) and a rotor (122). The stator (121) is inserted and fixed into the inner surface of the cylindrical shell (111), and the rotor (122) is rotatably provided inside the stator (121).

[0104] The stator (121) includes a stator core (1211) and a stator coil (1212).

[0105] The stator core (1211) is formed in a circular or hollow cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot pressing.

[0106] 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 shown) that penetrates the casing (110).

[0107] The rotor (122) includes a rotor core (1221) and a permanent magnet (1222).

[0108] The rotor core (1221) is rotatably inserted into the stator core (1211) at a predetermined gap (not shown). Permanent magnets (1222) are embedded in the rotor core (1221) at a predetermined gap along the circumference.

[0109] A rotation shaft (125) is coupled to the center of the rotor core (1221). The upper part of the rotation shaft (125) is press-fitted and coupled to the rotor (122), and the lower part of the rotation shaft (125) is rotatably inserted into the main frame (130) and supported in the radial direction.

[0110] The rotary shaft (125) transmits the rotational force of the driving motor (120) to the orbiting scroll (140) forming the compression section (C). Accordingly, the orbiting scroll (140) eccentrically coupled to the rotary shaft (125) rotates relative to the fixed scroll (150).

[0111] For example, the rotation shaft (125) may be composed of a main shaft portion (1251), a main bearing surface portion (1252), an eccentric portion (1253), and a sub-bearing surface portion (1254). The main shaft portion (1251) is a portion coupled to the rotor (122), the main bearing surface portion (1252) is a portion supported radially by a main frame (130) to be described later, the eccentric portion (1253) is a portion eccentrically coupled to a rotating scroll (140) to be described later, and the sub-bearing surface portion (1254) is a portion supported radially by a fixed scroll (150) to be described later. In other words, the rotating shaft (125) has a main shaft portion (1251) forming one end coupled to the rotor (122), and the main bearing surface portion (1252), the eccentric portion (1253), and the western bearing surface portion (1254) forming the other end can be coupled by penetrating the main frame (130), the orbiting scroll (140), and the fixed scroll (150), respectively.

[0112] The main shaft portion (1251), the main bearing surface portion (1252), and the sub-bearing surface portion (1254) are formed on the shaft center line (CL), and the eccentric portion (1253) can be formed eccentrically with respect to the shaft center line (CL). For example, when the shaft center line (CL) is used as a reference, the outer diameter of the eccentric portion (1253) can 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) can be formed to be 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, even if the main frame (130) is inserted from the other end of the rotating shaft (125) during assembly of the compressor, the bearing gap between the main frame (e.g., the main shaft hole described later) (130) and the main bearing surface (1252) can be maintained.

[0113] In this case, the outer diameter of the sub-bearing surface portion (1254) may be formed to be smaller than the outer diameter of the main bearing surface portion (1252), for example, the outer diameter of the sub-bearing surface portion (1254) may be formed to be smaller than or equal to the outer diameter of the eccentric portion (1253) based on the shaft center line (CL). In other words, the outer diameter of the sub-bearing surface portion (1254) may be formed to be smaller than the outer diameter of the eccentric portion (1253) so that the outer surface of the sub-bearing surface portion (1254) does not protrude beyond the outer surface of the eccentric portion (1253). Accordingly, even if the orbiting scroll (140) is inserted from the other end of the rotating shaft (125) during assembly of the compressor, the bearing gap between the orbiting scroll (e.g., the rotating shaft coupling portion to be described later) (140) and the eccentric portion (1253) can be maintained.

[0114] However, since the outer diameter of the sub-bearing surface portion (1254) is formed smaller than the outer diameter of the eccentric portion (1253), the surface pressure may increase significantly on the bearing surface (BS) between the sub-bearing surface portion (1254) and the sub-bearing (1532) to be described later, which faces it in the radial direction. Accordingly, a bushing (180), which forms a part of the sub-bearing surface portion (1254), may be inserted between the sub-bearing surface portion (1254) and the sub-bearing (1532). For example, the bushing (180) may be press-fitted onto the outer surface of the sub-bearing surface portion (1254) or may be fixedly connected using a separate fixing member (190, 191, 192, 193). Accordingly, the actual outer diameter of the sub-bearing surface (1254) increases, thereby reducing the surface pressure between the sub-bearing surface (1254) (or bushing (180)) and the sub-bearing (1532). The bushing (180) will be described later.

[0115] In addition, an oil passage (126) is formed in an axial or inclined direction inside the rotating shaft (125) to guide the oil stored in the oil storage space (S1) of the casing (110) to the compression chamber (V) and / or the bearing surface (BS), and an oil hole (1262) may be formed in the middle of the oil passage (126) so that the oil sucked through the oil passage (126) is supplied to each bearing surface (BS). For example, the oil holes (1262) may be formed on both axial sides of the eccentric portion (1253), and may be formed to be received in oil receiving grooves (1255) formed annularly on both axial sides of the eccentric portion (1253).

[0116] In addition, an oil pickup (127) for pumping oil filled in the oil storage space (S1) may be coupled to the lower end of the oil passage (126). Accordingly, the oil filled in the oil storage space (S1) may be sucked along the rotation shaft (125) through the oil pickup (127) and the oil passage (126) when the rotation shaft (125) rotates, and may be supplied to the compression chamber (V), the shaft thrust surface (STS), and / or each bearing surface (BS).

[0117] The compression unit (C) according to the present embodiment includes a main frame (130), a rotating scroll (140), and a fixed scroll (150). The main frame (130) is fixedly connected to the lower side of the driving motor (120), and the rotating scroll (140) is axially supported by a fixed scroll (150) connected to the lower side of the main frame (130) and can be provided to be rotatable between the main frame (130) and the fixed scroll (150).

[0118] 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).

[0119] The frame plate portion (131) is formed in a circular shape, and a main shaft hole (1331) forming a main support portion (133) to be described later can be formed axially through the center.

[0120] The frame side wall portion (132) extends in a cylindrical shape from the lower edge of the frame plate portion (131) and can be fixed by hot pressing or welding to the inner surface of the cylindrical shell (111).

[0121] The main support member (133) may be formed by having a main shaft hole (1331) extending axially therethrough so that the rotary shaft (125) may be rotatably inserted therein. A main bearing (not shown) that supports the main bearing surface portion (1252) of the rotary shaft (125) may be provided in the main shaft hole (1331). Accordingly, the main bearing surface portion (1252) of the rotary shaft (125) may be supported radially while smoothly rotating within the main shaft hole (1331).

[0122] Referring to Fig. 1, the turning scroll (140) includes a turning plate portion (141), a turning wrap (142), and a rotating shaft coupling portion (143).

[0123] The pivot plate (141) is formed in a circular shape and can be accommodated between the frame pivot plate (131) and the fixed pivot plate (151) described later. The upper surface of the pivot plate (141) can be axially supported on the main frame (130) with a back pressure sealing member (not shown) therebetween. Accordingly, the back surface of the pivot plate (141) forms a back pressure chamber (not shown) between it and the main frame (130) facing it.

[0124] The pivoting wrap (142) extends from the lower surface of the pivoting plate portion (141) toward the fixed plate portion (151) to be described later, and is interlocked with the fixed wrap (154) to be described later to form the first compression chamber (V1) and the second compression chamber (V2) described above.

[0125] The orbital wrap (142) may be formed in an involute shape. However, the orbital wrap (142) and the fixed wrap (154) may be formed in various shapes other than the involute shape. For example, the orbital wrap (142) may have a shape that connects multiple circular arcs with different diameters and origins, and the outermost curve may be formed in a roughly elliptical shape with a major axis and a minor axis. The fixed wrap (154) may also be formed in the same manner. Hereinafter, this may be described by defining it as a hybrid or irregular wrap shape.

[0126] The rotary shaft coupling portion (143) can be formed by penetrating axially from the center of the turning plate portion (141). Accordingly, the discharge port (1511) described later can be formed at the center of the turning scroll (140), that is, at an eccentric position from the rotary shaft coupling portion (143).

[0127] A rotary shaft (125) can be rotatably inserted and coupled to the rotary shaft coupling portion (143). Accordingly, the outer circumference of the rotary shaft coupling portion (143) is connected to the rotating wrap (142) to form a first compression chamber (V1) together with the fixed wrap (154) during the compression process.

[0128] The rotation shaft coupling portion (143) can be formed at a height that overlaps the rotation wrap (142) on the same plane. In other words, the rotation shaft coupling portion (143) can be formed at a height that overlaps the eccentric portion (1253) of the rotation shaft (125) on the same plane as the rotation wrap (142).

[0129] 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).

[0130] The fixed plate part (151) may be formed in a circular shape and may be arranged at a preset interval on the lower side of the frame plate part (131). A sub-axial hole (1531) forming a sub-support part (153) to be described later may be formed through the center of the fixed plate part (151) in the vertical direction. A discharge port (1511) may be formed around the sub-axial hole (1531) to communicate with the first compression chamber (V1) and the second compression chamber (V2) to be described later, respectively, through which the compressed refrigerant is discharged to the muffler space (160a) of the discharge cover (160).

[0131] 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-axis hole (1531) is formed at the center of the fixed plate portion (151), the discharge port (1511) can be formed at an eccentric position from the sub-axis hole (1531).

[0132] The fixed side wall portion (152) may extend in the vertical direction from the upper edge of the fixed plate portion (151) and be coupled to the frame side wall portion (132) of the main frame (130). An intake 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 described above, an end of a refrigerant suction pipe (115) that penetrates the cylindrical shell (111) may be inserted and coupled to the intake port (not shown).

[0133] A cylindrical sub-axis hole (1531) may be formed axially through the center of the sub-support member (153). The sub-axis hole (1531) may be formed on the same axis as the main axis hole (1331) provided in the main frame (130). Accordingly, the inner diameter of the sub-axis hole (1531) may be formed smaller than the inner diameter of the main axis hole (1331).

[0134] A sealing protrusion (155) may be provided on the inner surface of the fixed scroll (150).

[0135] 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-axial bore (1531). The sealing protrusion (155) may extend in an annular direction. The sealing protrusion (155) may have a thrust surface (STS) that comes into contact with a portion of the rotational shaft (125). The thrust surface (STS) of the sealing protrusion (155) may come into contact with an eccentric portion (1253) of the rotational shaft (125), for example. In the present invention, the shaft thrust surface (STS) may be a thrust surface (STS) that comes into contact between the sealing protrusion (155) and the eccentric portion (1253) of the rotational shaft (125).

[0136] The fixed wrap (154) can be formed to extend axially from the upper surface of the fixed plate portion (151) toward the orbiting scroll (140). Since the fixed wrap (154) is formed to correspond to the shape of the orbiting wrap (142) described above, the description of the fixed wrap (154) is replaced with the description of the orbiting wrap (142).

[0137] Referring to Fig. 1, a discharge cover (160) can be coupled to the back surface of a fixed scroll (150). A muffler space (160a) is provided inside the discharge cover (160), and a discharge port (1511) penetrating through the fixed scroll (150) can be accommodated in the muffler space (160a). Accordingly, refrigerant discharged from the compression chamber (V) through the discharge port (1511) moves to the upper space (S2) via the muffler space (160a).

[0138] In the drawing, the unexplained symbol 170 is an Oldham ring, and 192 is a key fixing ring (193).

[0139] The scroll compressor according to the above embodiment operates as follows.

[0140] That is, when power is applied to the drive motor (120), rotational force is generated in the rotor (122) and the rotation shaft (125), causing them to rotate, and the rotary scroll (140) eccentrically coupled to the rotation shaft (125) performs a rotational movement with respect to the fixed scroll (150) by the Oldham ring (170).

[0141] Then, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually decreases from the outside toward the center of each compression chamber (V1) (V2). Then, the refrigerant is sucked into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (115).

[0142] 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 chamber (V1)(V2).

[0143] Then, the refrigerant is discharged through the discharge hole (not shown) provided in the fixed scroll (150) and the main frame (130) into the discharge space (not shown) between the main frame (130) and the drive motor (120), passes through the drive motor (120), and moves to the upper space (S2) of the casing (110) formed on the upper side of the drive motor (120). The refrigerant is separated into refrigerant and oil in the upper space (S2), 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 to the oil storage space (S1) of the casing (110) through the oil recovery passage (not shown) described above. This oil is supplied to the compression chamber (V), shaft thrust surface (STS) and / or each bearing surface (BS) through the oil passage (126) of the rotating shaft (125) and then returned to the oil storage space (S1) of the casing (110), a series of processes are repeated.

[0144] Meanwhile, as described above, the rotation shaft (125) may be supported radially by having the main bearing surface (1252) forming part of the lower half inserted into the main shaft hole (1331) of the main frame (130), and the sub-bearing surface (1254) inserted into the sub-bearing surface 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) interposed therebetween, the outer diameter of the sub-bearing surface (1254) may be formed smaller than that of the main bearing surface (1252). This may increase the surface pressure between the sub-bearing surface (1254) and the sub-bearing (1532) facing it, which may lower reliability.

[0145] Taking this into consideration, as described above, a bushing (180) having a preset thickness is combined on the outer surface of the sub-bearing surface portion (1254) to increase the actual outer diameter of the sub-bearing surface portion (1254), thereby reducing the surface pressure between the sub-bearing surface portion (1254) and the sub-bearing (1532).

[0146] However, when a bushing (180) is coupled to the sub-bearing surface (1254) of the rotating shaft (125), the surface pressure may be relatively reduced, but as the oil passes through the bushing (180), the amount of oil supplied may decrease due to an increase in the resistance of the oil path, and the efficiency of the compressor and the reliability of the sub-bearing (1532) may be reduced.

[0147] Accordingly, in this embodiment, since the bushing (180) is coupled to the fixed member (190, 191, 192, 193) on the rotation axis (125), it is possible to prevent the bushing from being dislodged in the axial and rotational directions.

[0148] The bushing (180) provided in the scroll compressor of the present invention can be arranged concentrically with the sub-bearing surface (1254) of the rotation shaft (125), and thus can be understood as a concentric bushing.

[0149] In the present invention, an assembled structure in which a bushing (180) is coupled to a rotation shaft (125) is disclosed through various embodiments, which will be described below.

[0150] Fig. 2 is an exploded perspective view illustrating a rotary shaft (125), a bushing (180), and a fixed scroll (150) of the present invention. Fig. 3 is a perspective view illustrating an example in which a bushing (180) is installed on a rotary shaft (125) by a fixed cap (191) in Fig. 2. Fig. 4 is an exploded perspective view illustrating an example in which a bushing (180) is installed on a rotary shaft (125) by a fixed cap (191). Fig. 5 is a cross-sectional view illustrating an example in which a bushing (180) is installed on a rotary shaft (125) by a fixed cap (191).

[0151] In the present invention, the fixing member (190, 191, 192, 193) may be formed as a fixing cap (191) having a body portion (191a) arranged to surround the outer circumference of the rotation shaft (125) and a guide support portion (191b) that protrudes in the axial direction in which the rotation shaft (125) extends from one side of the body portion (191a) to support the bushing (180) on the rotation shaft (125).

[0152] In the present invention, the bushing may be provided with a sealing surface portion (184) that comes into contact with the rotation shaft (125), and an inclined portion (1822) that is connected to the sealing surface portion (184) but is inclined on one side.

[0153] As shown in FIGS. 3 to 5, the fixed cap (191) has a body portion (191a) and a guide support portion (191b).

[0154] The body part (191a) is connected to the outer periphery of the rotation shaft (125).

[0155] For example, the body part (191a) can be joined to the rotation axis (125) by a press-fit method.

[0156] The body part (191a) can be coupled to the rotation shaft (125) together with the bushing (180) in the direction of the arrow shown in FIG. 4.

[0157] The guide support member (191b) protrudes axially from one side of the body member (191a) to support the bushing (180) on the rotation axis (125).

[0158] In the present invention, the axial direction may be the direction in which the rotation axis (125) extends.

[0159] The guide support member (191b) may be provided with a first engaging restraint member (191b1) formed to be bent outward from the end.

[0160] A groove (184a) may be provided on the inner surface of the bushing (180). The groove (184a) may accommodate a first engaging restraint portion (191b1) to limit axial movement of the bushing (180) with respect to the rotational axis (125). The groove (184a) may be provided on the sealing surface (184) of the bushing (180).

[0161] The home portion (184a) can be formed concavely on the inner surface of the bushing (180).

[0162] The home portion (184a) may have a polygonal cross-section. For example, the home portion (184a) may have a rectangular cross-section.

[0163] In addition, since the fixed cap (191) is coupled to the rotation shaft (125), the bushing (180) can be restrained to the rotation shaft (125).

[0164] The guide support member (191b) may be formed to be inclined inward at a predetermined angle. As a result, the guide support member (191b) can be advantageously structured for being guided while minimizing the risk of interference or damage to the contact surface (1254a1) of the guide groove (1254a) of the rotation shaft (125) described later.

[0165] A plurality of guide support members (191b) may be provided.

[0166] A plurality of guide support members (191b) may be provided so as to be spaced apart in the circumferential direction from one side of the body member (191a).

[0167] A guide groove (1254a) that accommodates a guide support member (191b) may be provided on the outer periphery of the rotation shaft (125).

[0168] The guide groove (1254a) can guide the assembly of the guide support member (191b) during assembly. For this purpose, it is preferable that the guide groove (1254a) have a width that is almost the same as or slightly larger than the width of the guide support member (191b).

[0169] Additionally, the guide home (1254a) can prevent the rotational direction of the guide support member (191b) from deviating.

[0170] For this purpose, the guide groove (1254a) may be provided with a detachment prevention portion (1254a2). The detachment prevention portion (1254a2) may be formed to protrude from the side of the guide groove (1254a) toward the outer periphery of the rotation shaft (125).

[0171] The thickness of the anti-separation part (1254a2) must be selected so that the guide support part (191b) does not come off and can be caught, taking into consideration the thickness of the guide support part (191b) and the angle in the diagonal direction.

[0172] The guide support member (191b) may be provided with a first engaging restraint member (191b1) formed to be bent in a direction toward the inside of the bushing (180) at the end.

[0173] The first restraining member (191b1) is bent outward with respect to the body member (191a).

[0174] The first retaining member (191b1) may be provided on only some of the plurality of guide support members (191b), as illustrated in Fig. 4. However, it is not necessarily limited thereto, and may be provided on all of the plurality of guide support members (191b).

[0175] The first retaining member (191b1) is fixedly caught in the groove (184a) of the bushing (180), so that the fixed cap (191) and the bushing (180) are prevented from being axially separated from each other.

[0176] In addition, since the body part (191a) of the fixed cap (191) is coupled to the rotation shaft (125), the bushing (180) can be coupled to the rotation shaft (125) by the fixed cap (191).

[0177] The rotation shaft (125) may be provided with a guide groove (1254a) on the outer periphery.

[0178] The guide groove (1254a) may be provided with a guide groove (1254a) that guides the guide support member (191b) when it is assembled. The guide groove (1254a) may have a predetermined width to guide the guide support member (191b).

[0179] Additionally, the guide groove (1254a) may further include a curved portion on the opposite side of the direction in which the guide support portion (191b) is assembled. By virtue of the curved portion, the possibility of damage to the guide support portion (191b) can be reduced when assembled. By including the curved portion, the guide groove (1254a) may have an inverted U-shape.

[0180] A plurality of guide grooves (1254a) may be provided on the outer periphery of the rotation shaft (125). The plurality of guide grooves (1254a) may be spaced apart from each other in the circumferential direction.

[0181] As the guide home (1254a) is provided in multiple numbers, the guide support part (191b) of the fixed cap (191) can be supported more stably on the rotation shaft (125).

[0182] As the guide support member (191b) is caught in the guide home (1254a), the movement of the fixed cap (191) in the rotational direction is restricted.

[0183] The guide home (1254a) may be provided with a contact surface (1254a1) that comes into contact with the inner circumference of the guide support portion (191b) and a separation prevention portion (1254a2) that is supported on the side of the guide support portion (191b).

[0184] The contact surface (1254a1) is formed to have an outer diameter that is smaller than a predetermined distance from the outer circumference of the rotation axis (125).

[0185] The anti-separation portion (1254a2) is formed to have an outer diameter larger than that of the contact surface portion (1254a1), thereby limiting the rotation of the guide support portion (191b).

[0186] In this way, by means of the fixed cap (191), the bushing (180) can be prevented from being dislodged in the rotational direction and axial direction with respect to the rotational axis (125).

[0187] In order to fix the bushing (180) to the rotation shaft (125), there should be no deviation in both the rotational direction (circumferential direction of the rotation shaft (125)) and the axial direction, and when applying the fixing member (190, 191, 192, 193) to compensate or absorb the bearing gap and geometric tolerance between the bushing (180) and the bearing that slides with the bearing, the bushing (180) should not be completely restrained to the rotation shaft (125).

[0188] In the present invention, productivity can be improved during assembly of a scroll compressor by using a structure for fixing a bushing (180).

[0189] Fig. 6 is an exploded perspective view showing another example in which a bushing (180) is installed on a rotating shaft (125) by a fixed cap (191). In addition, Fig. 7 is a cross-sectional view showing the bushing (180) coupled to the rotating shaft (125) in Fig. 6.

[0190] Referring to FIGS. 6 and 7, the fixing members (190, 191, 192, 193) of another example (second embodiment) will be described.

[0191] Optionally, the guide support member (191b) may further include a second catch restraint member (191b3).

[0192] The second engaging restraint portion (191b3) is bent inward toward the rotation axis (125). That is, the second engaging restraint portion (191b3) can be formed to be bent in the opposite direction to the first engaging restraint portion (191b1).

[0193] As illustrated in Fig. 6, some of the plurality of guide support members (191b) may be provided with a second engaging restraint member (191b3). In addition, an example in which other some of the plurality of guide support members (191b) are provided with the aforementioned first engaging restraint member (191b1) is illustrated in Fig. 6.

[0194] For example, the guide support part (191b) provided with the second catch (191b3) may have a longer height than the guide support part (191b) provided with the first catch (191b1).

[0195] The rotation shaft (125) may be provided with a catch groove (1254b2) in which the second catch restraint (191b3) is caught and fixed.

[0196] The catch groove (1254b2) may, for example, be formed in a circumferential direction on the outer periphery of the rotation axis (125).

[0197] In addition, the engaging groove (1254b2) must have a width sufficient to accommodate the second engaging restraint (191b3). One end of the engaging groove (1254b2) can be engaged by the second engaging restraint (191b3), thereby limiting the axial movement of the fixed cap (191).

[0198] The rotation shaft (125) may further include a catch groove guide portion (1254b1) that guides the movement of the second catch restraint portion (191b3) when assembling the fixed cap (191). The catch groove guide portion (1254b1) has a predetermined width and is formed in the axial direction.

[0199] The fixed cap (191) of the structure illustrated in FIGS. 6 and 7 can be connected so that the body portion (191a) can slide to the rotation shaft (125). That is, the fixed cap (191) of the previous embodiment illustrated in FIGS. 2 to 5 is different from the fixed cap (191) of FIGS. 6 and 7 in that the body portion (191a) is press-fitted to the rotation shaft (125) and is not slidable.

[0200] Fig. 8 is a perspective view showing another embodiment (third embodiment) in which a bushing (180) is fixed to a rotation shaft (125), and Fig. 9 is an exploded perspective view showing the rotation shaft (125) and bushing (180) in Fig. 8 in an exploded manner. In addition, Fig. 10 is a conceptual diagram showing an example in which a pin (192) is fixed to a rotation shaft (125) in the embodiment of Fig. 8, and Fig. 11 is a cross-sectional view of Fig. 8.

[0201] Hereinafter, a third embodiment of the fixing member (190) will be described with reference to FIGS. 8 to 11.

[0202] Referring to FIG. 8, a pin (192) can be coupled to a bushing (180).

[0203] For this purpose, the bushing (180) may be provided with a coupling hole (184b) into which a pin (192) can be coupled.

[0204] The pin (192) coupled to the bushing (180) can be positioned to protrude toward the inside of the bushing (180).

[0205] Additionally, the pin (192) can be elastically deformed, so that the diameter of the pin (192) can be changed. To this end, the pin (192) may have an elastic member inside. Alternatively, the pin (192) may be made of an elastic material, so that it can be deformed by itself.

[0206] Optionally, the pin (192) can be made to have an elastically variable length.

[0207] For example, the pin (192) can be arranged on the inner side of the bushing (180) so as to face the center of the bushing (180), so that the pin (192) of the bushing (180) can support the rotational axis (125) in the radial direction.

[0208] The rotation axis (125) can be configured to guide the movement of the pin (192) while limiting the movement by allowing the pin (192) to be seated.

[0209] For this purpose, the rotation shaft (125) may be provided with a slit groove (1254c1) and a settling groove (1254c2).

[0210] The slit groove (1254c1) can be extended by a predetermined distance to guide the movement of the pin (192).

[0211] The slit groove (1254c1) can guide the axial movement of the pin (192).

[0212] The anchoring groove (1254c2) allows the pin (192) to be anchored and restricts the movement of the pin (192). The anchoring groove (1254c2) may be provided on one side of the slit groove (1254c1).

[0213] A slit groove (1254c1) and a settling groove (1254c2) are provided on the rotating shaft (125), so that when the bushing (180) is coupled to the rotating shaft (125), the pin (192) moves while being stably guided along the slit groove (1254c1) and is caught in the settling groove (1254c2), thereby coupling the bushing (180) to the rotating shaft (125).

[0214] Due to this, the bushing (180) is prevented from being displaced in the axial and rotational directions with respect to the rotation axis (125).

[0215] As described above, the pin (192) is configured to be elastically deformable, so that when an external force is applied, the pin (192) is compressed and the diameter thereof decreases from a state in which no external force is initially applied, and when the external force is released, the compressed deformation is released and the pin is restored to its original size.

[0216] The maximum diameter of the pin (192) may be smaller than or equal to the diameter of the mounting groove (1254c2) and larger than the width of the slit groove (1254c1). The maximum diameter of the pin (192) may be the diameter of the pin (192) when no external force is applied.

[0217] The minimum diameter of the pin (192) may be smaller than or equal to the width of the slit groove (1254c1). For example, in the process of assembling the bushing (180) to the rotary shaft (125), the minimum diameter of the pin (192) may be the diameter of the pin (192) when it is compressed and deformed by being pressed by the slit groove (1254c1).

[0218] The pin (192) of the bushing (180) is guided along the slit groove (1254c1) of the rotation shaft (125) and can be fastened and assembled in the mounting groove (1254c2).

[0219] Due to this, a stable assembly structure can be formed, and a structure is formed in which the bushing (180) does not deviate from the rotational axis (125) in the axial and rotational directions.

[0220] In particular, when the pin (192) is accommodated inside the mounting groove (1254c2), movement in the reverse direction along the slit groove (1254c1) is restricted, and it is stably supported in the mounting groove (1254c2) and does not come off.

[0221] The bushing (180) rotates together with the rotation axis (125), but is not subject to force in the vertical direction or in the circumferential direction of the rotation axis (125) as shown in the drawing.

[0222] The diameter of the anchoring groove (1254c2) may be larger than the maximum diameter of the pin (192). The maximum diameter of the pin (192) may be larger than the width of the slit groove (1254c1). The width of the slit groove (1254c1) may be larger than the minimum diameter of the pin (192).

[0223] Here, the maximum diameter of the pin (192) may be the diameter when the outer periphery of the pin (192) is not in contact with or pressurized by another member.

[0224] Additionally, as described above, the minimum diameter of the pin (192) may be the diameter when pressed by the slit groove (1254c1).

[0225] Optionally, the condition of diameter of the settling groove (1254c2) ≥ maximum diameter of the pin (192) > width of the slit groove (1254c1) ≥ minimum diameter of the pin (192) may be satisfied.

[0226] In other words, the diameter of the mounting groove (1254c2) may be greater than or equal to the maximum diameter of the pin (192). The maximum diameter of the pin (192) may be greater than the width of the slit groove (1254c1). The width of the slit groove (1254c1) may be greater than or equal to the minimum diameter of the pin (192).

[0227] Due to this, the bushing (180) rotates together with the rotation axis (125), but is not subjected to a force in the vertical direction or in the circumferential direction of the rotation axis (125) as shown in the drawing. Due to this, the bushing (180) can be prevented from being dislodged from the rotation axis (125) in the axial and circumferential directions, and can be stably supported.

[0228] Referring to Fig. 10a, in a state where the pin (192) of the bushing (180) is guided along the slit groove (1254c1) of the rotational axis (125), the diameter of the pin (192) of the bushing (180) is elastically compressed and deformed in the left and right directions by the slit groove (1254c1).

[0229] Referring to FIG. 10b, when the pin (192) of the bushing (180) is accommodated inside the mounting groove (1254c2) of the rotation shaft (125), the diameter of the pin (192) of the bushing (180) can be deformed to be almost the same as the inner diameter of the mounting groove (1254c2), and the mounting groove (1254c2) prevents the pin (192) from being dislodged in the axial and rotational directions.

[0230] In order to fix the bushing (180) to the rotation shaft (125), it should not be displaced in either the rotational direction (circumferential direction of the rotation shaft (125)) or the axial direction, and in order to compensate or absorb the bearing gap and geometric tolerance between the bushing (180) and the bearing in sliding contact with the bearing, it is preferable that the bushing (180) is not completely restrained to the rotation shaft (125) when applying the fixing member (190, 191, 192, 193).

[0231] In the present invention, it is possible to improve productivity during assembly of a scroll compressor by using a structure that fixes a bushing (180).

[0232] Fig. 12 is a perspective view showing another embodiment (fourth embodiment) in which a bushing (180) is fixed to a rotational shaft (125). Fig. 13 is an exploded perspective view showing the rotational shaft (125) and bushing (180) in Fig. 12 in an exploded manner. Fig. 14 is a conceptual diagram showing an example in which a pin (192) is guided to a rotational shaft (125) in the embodiment of Fig. 12. In addition, Fig. 15 is a cross-sectional view of Fig. 12.

[0233] Hereinafter, a fourth embodiment will be described with reference to FIGS. 12 to 15.

[0234] A pin (192) can be coupled to the bushing (180).

[0235] For this purpose, the bushing (180) may be provided with a coupling hole (184b) into which a pin (192) can be coupled.

[0236] The pin (192) coupled to the bushing (180) can be positioned to protrude toward the inside of the bushing (180).

[0237] Additionally, the pin (192) can be elastically deformed, so that the diameter of the pin (192) can be changed. To this end, the pin (192) may be provided with an elastic member inside. Alternatively, the pin (192) may be formed to enable its own elastic deformation.

[0238] Optionally, the pin (192) may be elastically length-changeable. Accordingly, when the bushing (180) is assembled to the rotation shaft (125), the pin (192) may be assembled without being elastically deformed and broken when a load is applied in the longitudinal direction of the pin (192).

[0239] For example, the pin (192) can be arranged on the inner side of the bushing (180) so as to face the center of the bushing (180), so that the pin (192) of the bushing (180) can support the rotational axis (125) in the radial direction.

[0240] The rotation axis (125) can be configured to guide the movement of the pin (192) while limiting the movement by allowing the pin (192) to be seated.

[0241] Referring to FIGS. 12 to 15, a slit groove (1254c1) may be provided on the rotation shaft (125).

[0242] Unlike the previous third embodiment, the fourth embodiment does not have a mounting groove (1254c2) on the rotation shaft (125). The slit groove (1254c1) may be provided with a curved surface on one side so that the pin (192) of the bushing (180) can be supported in contact.

[0243] Instead, a retaining ring (193) is provided on one side of the bushing (180) to support the bushing (180) so that it does not come off from the rotation shaft (125).

[0244] The fixed ring (193) comes into contact with the lower end of the bushing (180) and serves to support the bushing (180) so that it does not move downward from the rotation shaft (125).

[0245] The fixed ring (193) can be coupled to the outer circumference of the rotation shaft (125).

[0246] For example, the fixed ring (193) can be press-fitted to the outer periphery of the rotation shaft (125).

[0247] When the fixed ring (193) is press-fitted to the rotating shaft (125), the work is saved because the processing of a tap on the fixed ring (193) is not required, and since assembly can be done in a relatively simple manner, productivity is improved.

[0248] As another example, the fixed ring (193) may be bolt-fastened to the rotation shaft (125). To this end, a tab may be formed on the rotation shaft (125), and a tab may be formed on the fixed ring (193) so as to be in communication with the tab of the rotation shaft (125). By fastening the bolt while the tab of the rotation shaft (125) and the tab of the fixed ring (193) are in communication with each other, the fixed ring (193) may be bolt-fastened to the rotation shaft (125).

[0249] Referring to Fig. 14a, when the pin (192) of the bushing (180) is guided along the slit groove (1254c1) of the rotational axis (125), the diameter of the pin (192) of the bushing (180) is not elastically compressed in the left-right direction by the slit groove (1254c1).

[0250] In this way, referring to FIG. 14a, the diameter of the pin (192) of the bushing (180) may be provided with a diameter that is almost the same as the width of the slit groove (1254c1).

[0251] Referring to Fig. 14b, when the pin (192) of the bushing (180) is in contact with one side (1254c3) of the slit groove (1254c1) of the rotation shaft (125), the diameter of the pin (192) of the bushing (180) may be provided to be approximately the same as the diameter of one side (1254c3) of the slit groove (1254c1). Although not shown in Fig. 14b, when the pin (192) of the bushing (180) is in contact with one side (1254c3) of the slit groove (1254c1) of the rotation shaft (125), the upper end of the fixed ring (193) is in contact with the lower end of the bushing (180) to support it.

[0252] In this way, the pin (192) of the bushing (180) is in contact with one side (1254c3) of the slit groove (1254c1) of the rotation shaft (125), and the fixed ring (193) is in contact with the bushing (180) and is supported by the structure, so that the bushing (180) is prevented from being dislodged in the axial and rotational directions.

[0253] Fig. 16 is a perspective view showing another embodiment (fifth embodiment) in which a bushing (180) is fixed to a rotation shaft (125), and Fig. 17 is an exploded perspective view showing the rotation shaft (125) and the bushing (180) in Fig. 16 in an exploded manner. In addition, Fig. 18 is a cross-sectional view of Fig. 16, and Fig. 19 is a conceptual diagram showing various examples of a fixing ring (193) in the embodiment of Fig. 16.

[0254] Hereinafter, with reference to FIGS. 16 to 19, a fifth embodiment of the fixing member (190, 191, 192, 193) will be described.

[0255] In the fifth embodiment of the fixed member (190, 191, 192, 193), a restraining pin (193b) is provided on the fixed ring (193), so that the fixed ring (193) is fastened to the bushing (180) and the rotational shaft (125). As a result, the bushing (180) is prevented from being dislodged in the axial and rotational directions.

[0256] A joining groove may be formed at one end of the bushing (180) and at the rotary shaft (125) connected to one end of the bushing (180).

[0257] The coupling groove may include a bushing coupling groove (184c) provided at one end of the bushing (180) and a rotation shaft coupling groove (1254d) provided at the rotation shaft (125).

[0258] The bushing coupling groove (184c) can be formed on the inner surface of the bushing (180) at one end of the bushing (180).

[0259] The rotary shaft coupling groove (1254d) can be formed to communicate with the bushing coupling groove (184c) on the outer periphery of the rotary shaft (125).

[0260] The bushing coupling groove (184c) may be formed, for example, as an arc having a predetermined diameter.

[0261] The rotary shaft coupling groove (1254d) can also be formed as an arc having a predetermined diameter.

[0262] The diameter of the rotary shaft coupling groove (1254d) may be approximately the same as the diameter of the bushing coupling groove (184c).

[0263] In this embodiment, the fixed ring (193) may be provided with a ring body (193a) installed on the outer periphery of the rotation shaft (125), and a restraining pin (193b) that protrudes axially from the ring body (193a) and is installed on at least one of the bushing (180) and the rotation shaft (125).

[0264] The restraint pin (193b) is accommodated in the coupling groove and restrains the rotation shaft (125) and the bushing (180) simultaneously.

[0265] However, the bushing (180) is configured to be axially movable. If the bushing (180) moves axially and touches the sealing projection (155) of the fixed scroll (150), the fuel supply path may be temporarily blocked.

[0266] To improve the performance of supplying oil to the fixed scroll (150) through the upper part of the bushing (180), a supply groove (187) may be provided on the upper part of the bushing (180).

[0267] The refueling groove (187) can be formed radially so as to penetrate the outer and inner peripheries at the top of the bushing (180).

[0268] A plurality of refueling grooves (187) may be formed. The plurality of refueling grooves (187) may be spaced apart from each other in the circumferential direction.

[0269] As the oil supply groove (187) is provided at the top of the bushing (180), when the rotating shaft (125) rotates, even if the bushing (180) moves upward and the top of the bushing (180) comes into contact with the sealing protrusion (155), the oil supply path is not blocked through the oil supply groove (187).

[0270] Due to this, the oil supply to the compression chamber (V) and the wetted part is not blocked, and oil can be supplied smoothly.

[0271] Meanwhile, a lubrication part (185) may be provided on the outer periphery of the bushing (180). In addition, a lubrication hole may be provided on the bushing (180). The lubrication part (185) may be connected to the lubrication hole (183). The lubrication part (185) may be formed as a groove structure that is concavely formed inwardly on the outer periphery of the bushing (180).

[0272] Accordingly, the oil sucked along the inner circumference of the rotating shaft (125) through the oil pickup (127) and the oil flowing through the oil supply hole (183) can flow axially in the oil supply portion (185) and be smoothly provided to the bearing surface (see FIG. 1) between the sub-bearing (1532).

[0273] For example, the oil supply portion (185) may be extended axially to guide the axial flow of oil. The oil may flow axially along the oil supply portion (185). Referring to Fig. 18, the oil that has exited the oil supply hole (183) flows upward along the oil supply portion (185) and is connected to the oil supply groove (187) described later.

[0274] The oil supply part (185) may be connected to a oil supply groove (187) formed at one end of the bushing (180). The oil supply groove (187) may provide a path through which oil flowing along the oil supply part (185) flows to the inner circumference or upper portion of the bushing (180).

[0275] Meanwhile, for the fixed ring (193), the bushing (180) can be connected so as to be slidable.

[0276] That is, the restraining pin (193b) of the fixed ring (193) can be completely press-fitted and fixed against the bushing coupling groove (184c) of the bushing (180). Alternatively, the restraining pin (193b) of the fixed ring (193) can be slidably supported against the bushing coupling groove (184c) of the bushing (180).

[0277] In addition, the fixed ring (193) can be coupled to the rotation shaft (125) while the restraining pin (193b) is guided to the rotation shaft coupling groove (1254d) of the rotation shaft (125).

[0278] The fixed ring (193) can be press-fitted to the rotation shaft (125). For example, the fixed ring (193) can be press-fitted to the sub-bearing surface (1254) of the rotation shaft (125).

[0279] To explain in more detail, the fixed ring (193) can be press-fitted and fixed to the outer periphery of the rotation shaft (125) by the ring body (193a).

[0280] As described above, the restraining pin (193b) of the fixed ring (193) can be coupled or slid into the rotation shaft coupling groove (1254d) of the rotation shaft (125). When the restraining pin (193b) of the fixed ring (193) is coupled into the rotation shaft coupling groove (1254d) of the rotation shaft (125), the coupling can be done by press-fitting.

[0281] The restraining pin (193b) of the fixed ring (193) can be slidably connected to the bushing coupling groove (184c) of the bushing (180).

[0282] The restraint pin (193b) can be formed upward in FIGS. 17 and 18.

[0283] Additionally, one or more restraint pins (193b) may be provided.

[0284] Figures 17 and 18 illustrate examples in which two restraint pins (193b) are provided.

[0285] Also, referring to FIG. 19c, the restraining pin (193b) may be provided to penetrate the upper and lower surfaces of the ring body (193a). Optionally, referring to FIG. 19b, the restraining pin (193b) may be provided to be inserted only into the upper surface without penetrating the upper and lower surfaces of the ring body (193a).

[0286] Referring again to FIG. 18, an example is also shown in which the restraint pin (193b) is inserted only into the upper surface of the ring body (193a) to a predetermined length.

[0287] The structure in which the restraining pin (193b) is inserted into the upper surface of the ring body (193a) (Fig. 19b) may have a somewhat weaker supporting force than the structure in which the restraining pin (193b) penetrates the ring body (193a) described later (Fig. 19c). However, the cost can be reduced in terms of the material cost and assembly man-hours of the restraining pin (193b). In addition, it may also be advantageous in terms of weight.

[0288] The structure in which the restraining pin (193b) is connected by penetrating the upper and lower surfaces of the ring body (193a) (Fig. 19c) can have a greater supporting force that the restraining pin (193b) can withstand to support the bushing (180) compared to the structure in which the restraining pin (193b) is inserted into the upper surface of the ring body (193a) (Fig. 19b).

[0289] Meanwhile, FIGS. 19d and 19e also illustrate an example in which only one restraint pin (193b) is provided in the ring body (193a).

[0290] FIG. 19d illustrates a structure in which a single restraining pin (193b) is provided, and the restraining pin (193b) is inserted into the upper surface of the ring body (193a). Compared to the structure described below in which the restraining pin (193b) penetrates the ring body (193a), the supporting force that the restraining pin (193b) can provide may be somewhat weaker.

[0291] Since one restraining pin (193b) is provided and inserted into the upper surface of the ring body (193a), compared to a structure in which two restraining pins (193b) are provided or the restraining pin (193b) penetrates the upper and lower surfaces of the ring body (193a) (Fig. 19e), the cost can be reduced in terms of the material cost of the restraining pin (193b) and the assembly man-hours. In addition, it can be advantageous in terms of weight as well.

[0292] In addition, Fig. 19e shows a structure in which one restraint pin (193b) is provided and is connected by penetrating the upper and lower surfaces of the ring body (193a).

[0293] The structure in which the restraining pin (193b) is connected by penetrating the upper and lower surfaces of the ring body (193a) can have a greater supporting force that the restraining pin (193b) can withstand to support the bushing (180) compared to the structure in which the restraining pin (193b) is inserted into the upper surface of the ring body (193a) as shown in FIG. 19d.

[0294] In this way, the bushing (180) is prevented from being dislodged in the axial and rotational directions by the structure in which the restraining pin (193b) of the fixed ring (193) is coupled to the rotation shaft (125) and the bushing (180).

[0295] The scroll compressor described above is not limited to the configuration and method of the embodiments described above, and the embodiments may be configured by selectively combining all or part of each embodiment so that various modifications can be made.

[0296] It will be apparent to those skilled in the art that the present invention may be embodied in other specific forms without departing from the spirit and essential characteristics thereof. Therefore, the above detailed description should not be construed in any way as limiting but rather as illustrative. The scope of the present invention should be determined by a reasonable interpretation of the appended claims, and all modifications within the scope of equivalents of the present invention are intended to be included within the scope of the present invention.

[0297] The present invention can be used in a scroll compressor that facilitates assembly and increases productivity.

Claims

1. Casing forming the exterior; An electric motor installed inside the above casing to generate power; A rotary shaft rotatably installed in the above-mentioned electric motor; A compression unit having a rotating scroll installed to be rotatable on the rotating shaft and a fixed scroll coupled to the rotating scroll to form a compression chamber between the rotating scrolls; and 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 scroll compressor comprising a fixing member that is provided to support the bushing and the rotating shaft and has a portion that protrudes to be caught by at least one of the bushing and the rotating shaft.

2. In paragraph 1, A scroll compressor in which the above-mentioned fixed member is formed by a body portion arranged to surround the outer circumference of a rotating shaft and a fixed cap having a guide support portion that protrudes in the axial direction in which the rotating shaft extends from one side of the body portion to support the bushing on the rotating shaft.

3. In paragraph 2, The above guide support part has a first engaging restraint part formed to be bent outward from the end, A scroll compressor having a groove provided on the inner surface of the bushing to accommodate the first engaging restraint member and to limit the bushing from axially moving away from the fixed cap.

4. In paragraph 2, A scroll compressor in which the above body part is joined to the above rotating shaft by a press-fit method.

5. In paragraph 3, The above guide support portion is formed to be inclined inward at a predetermined angle, A scroll compressor having a guide groove for accommodating the guide support member provided on the outer periphery of the above-mentioned rotating shaft.

6. In paragraph 3, A scroll compressor in which the above guide support portion is provided in a plurality of pieces, and the first engaging restraint portion is provided on some of the plurality of guide support portions.

7. In paragraph 6, Another part of the above plurality of guide supports is provided with a second engaging restraint formed to be bent inward at the end, A scroll compressor having a locking groove provided on the outer periphery of the above-mentioned rotating shaft to be locked and fixed to the second locking restraint member.

8. In paragraph 7, The above-mentioned hanging groove is a scroll compressor provided in a circumferential direction on the outer periphery of the rotating shaft.

9. In paragraph 7, A scroll compressor in which the above body part is connected to the above rotating shaft by a sliding method.

10. In paragraph 1, The above-mentioned fixed member is defined as a pin that is coupled to a bushing and is provided to protrude inside the bushing and whose diameter is elastically deformable. A scroll compressor, wherein the above-mentioned rotating shaft is provided with a slit groove extending a predetermined distance to guide movement of the pin; and a mounting groove provided on one side of the slit groove and in which the pin is mounted to restrict movement.

11. In paragraph 10, A scroll compressor in which the maximum diameter of the pin is smaller than or equal to the diameter of the seating groove and larger than the width of the slit groove, and the minimum diameter of the pin is smaller than or equal to the width of the slit groove.

12. In paragraph 1, The above fixed member is, A pin coupled to the above bushing and provided to protrude into the inside of the bushing; and It is defined to include a retaining ring that is coupled to the outer circumference of the above-mentioned rotating shaft and contacts the lower end of the bushing to support the bushing so that it does not come off. A scroll compressor having a slit groove extending a predetermined distance on the above rotational axis to guide movement of the pin.

13. In paragraph 12, The above pin is a scroll compressor whose diameter is elastically deformable.

14. In paragraph 12, The above fixed ring is a scroll compressor that is press-fitted to the outer periphery of the rotating shaft.

15. In paragraph 12, A scroll compressor in which the above-mentioned fixed ring is connected to the outer circumference of the above-mentioned rotating shaft by a bolt fastening method.

16. In paragraph 1, The above fixed member is, A pin coupled to the above bushing and provided to protrude into the inside of the bushing; and It is defined to include a retaining ring that is coupled to the outer circumference of the above-mentioned rotating shaft and contacts the lower end of the bushing to support the bushing so that it does not come off. The above fixed ring is, A scroll compressor having a ring body installed on the outer periphery of a rotating shaft, and a restraining pin protruding axially from the ring body and installed on at least one of a bushing and the rotating shaft.

17. In paragraph 16, The above pin is a scroll compressor whose diameter is elastically deformable.

18. In paragraph 16, A scroll compressor having at least one of a bushing coupling groove provided at one end of a bushing and a rotary shaft coupling groove provided at a rotary shaft, and wherein the restraining pin is inserted into at least one of the bushing coupling groove and the rotary shaft coupling groove.

19. In paragraph 18, A scroll compressor in which the bushing coupling groove is formed along the inner circumference of one end of the bushing, the rotary shaft coupling groove is formed along the outer circumference of the rotary shaft, the bushing coupling groove and the rotary shaft coupling groove are formed in communication so as to face each other, and the restraining pin is inserted between the bushing coupling groove and the rotary shaft coupling groove that are in communication with each other.

20. In paragraph 16, The above restraint pin is provided in at least one number, A scroll compressor in which the restraining pin is provided so as to protrude from one surface of the ring body, be inserted into one surface of the ring body, or penetrate one surface and the other surface of the ring body.

21. In paragraph 16, The upper part of the above bushing is provided with a refueling groove, A scroll compressor in which the above-mentioned oil supply groove is formed to penetrate the inner and outer peripheries of the above-mentioned bushing.

22. In paragraph 20, A scroll compressor having a plurality of the above-mentioned refueling grooves spaced apart in the circumferential direction.

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