Scroll compressor

Abstract

The present invention provides a scroll compressor comprising: a casing; a motor unit; a rotary shaft; a compression unit having a rotating scroll installed to be rotatable on the rotary shaft and a fixed scroll coupled so as to be engaged with the rotating scroll to form a compression chamber between the rotating scroll and the fixed scroll; an oil pickup unit which is installed on one side of the rotary shaft and can suction oil in an oil storage space so as to provide the oil to the compression unit; and a bushing disposed between the fixed scroll and the rotary shaft and coupled to the outer circumference of the rotary shaft so as to rotate together with the rotary shaft, wherein an oil supply hole is formed in the bushing such that the oil suctioned from the oil pickup can be provided to the compression unit, and an oil hole is formed in a rotary shaft provided on the inner circumference of the bushing.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of increasing efficiency by increasing the amount of oil supplied to a compression unit.

[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. When 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) discloses a through-axis scroll compressor. In Patent Document 1, a rotating shaft sequentially penetrates a main frame, an orbiting scroll, and a fixed scroll, thereby being connected thereto. 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] In addition, when the axial length of the sub-bearing surface and the sub-bearing is formed long, the surface pressure may be relatively reduced, but the amount of oil supplied may be reduced due to an increase in the resistance of the oil, and the efficiency of the compressor and the reliability of the sub-bearing may be reduced.

[0009]

[0010] 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.

[0011] A second 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.

[0012] A third object of the present invention is to provide a scroll compressor that can increase reliability while enabling smooth refueling.

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

[0014] In order to solve the above problem, the scroll compressor of the present invention includes a casing forming an exterior and having an oil storage space; a motor installed inside the casing and generating power; a rotary shaft rotatably installed on the motor; a compression unit having an orbiting scroll installed on the rotary shaft so as to be rotatable 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 an oil pickup installed on one side of the rotary shaft and capable of sucking oil so as to provide oil in the oil storage space to the compression unit; a bushing disposed between the fixed scroll and the rotary shaft and coupled to the outer periphery of the rotary shaft so as to rotate together with the rotary shaft, wherein an oil supply hole is formed in the bushing so as to provide oil sucked from the oil pickup to the compression unit, and an oil hole may be formed in a rotary shaft provided on the inner periphery of the bushing.

[0015] Due to this, the outer diameter of the bushing can be expanded to maintain the compression length while reducing the surface pressure between the rotating shaft and the fixed scroll.

[0016] According to an example related to the present invention, the fueling hole and the oil hole may be arranged so that at least some of them overlap each other.

[0017] Accordingly, oil passing through the oil hole can quickly move to the oil supply hole, enabling smooth oil supply between the rotating shaft and the bearing.

[0018] An oil supply groove may be provided on the outer periphery of the above bushing in the axial direction to communicate with the oil supply hole.

[0019] The above-mentioned oil supply groove may be formed to be cut at one end of the bushing and may have a cut portion that provides a flow path to the inner circumference of the bushing.

[0020] For example, the cut portion may include a cut groove portion provided on one side of the cut portion; and cut side portions provided on both sides of the cut groove portion and formed to intersect the cut groove portion to provide a flow path for oil to flow to the inner circumference of the bushing.

[0021] Due to this, a path is defined between the cut groove and the cut side to enable the outer and inner peripheries of the bushing to communicate with each other, and through the path, oil flows from the outer periphery to the inner periphery of the bushing, enabling smooth lubrication of the shaft thrust surface.

[0022] The above bushing may include a first passage provided to allow oil to flow upward from the oil supply groove; a second passage provided to intersect the first passage and formed by cutting one side of the bushing; and a third passage provided on the inner circumference of the bushing and connected to intersect the second passage.

[0023] Through the first to third oil passages, oil passing through the oil supply hole flows upward along the oil supply groove to lubricate the bearing surface, and then flows back into the inner surface of the bushing to lubricate the shaft thrust surface.

[0024] The above bushing may include a sealing surface portion provided on the inner periphery of the bushing and sealably coupled to the outer periphery of the rotating shaft; a stepped portion having a wider diameter than the sealing surface portion; and an inclined portion provided between the stepped portion and the sealing surface portion.

[0025] By this configuration, oil introduced into the inner surface of the bushing through the cut portion can flow upward between the rotating shaft and the stepped portion, enabling lubrication on the shaft thrust surface.

[0026] The inner surface of the fixed scroll is provided with a sealing projection, and the rotating shaft is provided with an eccentric portion that contacts the sealing projection so as to have an axial thrust surface, and the sealing projection is arranged to be spaced apart from the upper end of the bushing in the axial direction, and the inner surface of the sealing projection can be arranged between a line extending from the outer surface of the bushing and a line extending from the inner surface of the bushing.

[0027] Due to this, a flow path for oil can be formed between the bushing and the sealing protrusion. In particular, oil introduced into the inner surface of the bushing through the cut portion can flow along the inner surface of the sealing protrusion and be smoothly supplied to the shaft thrust surface.

[0028] The above-mentioned rotary shaft may be provided with an oil hole that is spaced apart from the oil hole in the axial direction so as not to overlap with the above-mentioned bushing.

[0029] Due to this, direct oil supply to the shaft thrust surface can be made possible by providing an oil hole and a separate oil hole.

[0030] The inner circumference of the above fixed scroll is provided with a sealing protrusion, the rotating shaft is provided with an eccentric portion that contacts the sealing protrusion so as to have an axial thrust surface, and the oil hole can be arranged parallel to the sealing protrusion so that one side faces one side of the sealing protrusion.

[0031] Due to this, since the oil hole is provided on one side of the sealing block, direct oil supply to the shaft thrust surface can be made possible.

[0032] The above-mentioned fueling holes may be provided in at least two numbers spaced apart from each other, and the above-mentioned oil holes may be provided in at least two numbers so that each overlaps the above-mentioned fueling holes.

[0033] Oil supply to the bearing surface can be made smoother by forming two oil holes and oil supply holes.

[0034] An oil supply groove may be provided on the outer periphery of the above bushing in an axial direction to communicate with the oil supply hole.

[0035] According to another example of the present invention, the fueling hole and the oil hole can form a non-overlapping structure so as to be spaced apart from each other in the axial direction.

[0036] The above oil hole may be arranged between the oil supply hole and the upper side of the bushing.

[0037] The above oil hole may be positioned between the midpoint between the upper and lower ends of the bushing and the upper end of the bushing.

[0038] In this way, as the oil supply hole and the oil hole are formed in a structure spaced apart from each other, some of the oil passing through the oil hole flows upward and is supplied to the inner surface of the shaft thrust, and another part of the oil flows downward and passes through the oil supply hole and is supplied to the bearing surface between the sub-bearing and the bushing to lubricate it.

[0039] The scroll compressor of the present invention has a bushing installed between the fixed scroll and the 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.

[0040] 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.

[0041] In the scroll compressor of the present invention, since a cut portion is formed in the bushing, a lubricating passage connecting the outer and inner peripheries of the bushing is formed, so that the resistance of the lubricating passage to the bearing and the shaft thrust surface is reduced, and the reliability and efficiency of the compressor can be improved.

[0042] The scroll compressor of the present invention has an oil supply groove in the bushing to supply oil to the bearing surface, thereby enabling smoother lubrication of the bearing surface.

[0043] The scroll compressor of the present invention can have a structure advantageous for direct oil supply to the shaft thrust surface by being provided with an oil hole and a separate oil hole.

[0044] Figure 1 is a cross-sectional view illustrating a scroll compressor of the present invention.

[0045] Figure 2 is an exploded perspective view showing the rotating shaft, bushing, and fixed scroll of the present invention.

[0046] Figure 3 is an exploded perspective view showing the rotating shaft and bushing in Figure 2.

[0047] Figure 4 is a cross-sectional view taken along line “Ⅸ-Ⅸ” of Figure 3.

[0048] Figure 5 is a cross-sectional view showing the assembly of the rotary shaft and fixed scroll in Figure 2.

[0049] Figure 6 is a perspective view showing another embodiment of a bushing.

[0050] Figure 7 is a cross-sectional view of the bushing coupled to the rotation shaft in Figure 6.

[0051] Figure 8 is a perspective view showing another embodiment of a bushing.

[0052] Figure 9 is a cross-sectional view of the bushing coupled to the rotation shaft in Figure 8.

[0053] 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.

[0054] 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.

[0055] Additionally, the term "axial direction" used in the following description refers to the longitudinal direction of the rotation axis (125). "Axial direction" can be understood as an up-down direction. "Radial direction" refers to a direction intersecting the rotation axis (125).

[0056] 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).

[0057] 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).

[0058] 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.

[0059] The scroll compressor of the present invention comprises a compression unit (C) having a casing (110) that forms an exterior and has a storage space (S1), an electric unit (120) that is installed inside the casing (110) to generate power, a rotary shaft (125) that is rotatably installed on the electric unit (120), a rotating scroll (140) that is installed to be rotatable on the rotary shaft (125) and a fixed scroll (150) that is engaged with the rotating scroll (140) to form a compression chamber between the rotating scroll (140), an oil pickup (127) that is installed on one side of the rotary shaft (125) and is capable of sucking oil so that oil in the storage space (S1) can be supplied to the compression unit (C), and an oil pickup (127) that is arranged between the fixed scroll (150) and the rotary shaft (125) and rotates together with the rotary shaft (125). It includes a bushing (180) coupled to the outer circumference of the rotation shaft (125).

[0060] By placing the bushing (180) between the compression part (C) and the rotation shaft (125) and being coupled to the outer circumference of the rotation shaft (125) so as to rotate together with the rotation shaft (125), the surface pressure applied between the compression part (C) and the rotation shaft (125) can be reduced.

[0061] An oil supply hole (183) is formed in the above bushing (180) so that oil sucked from the oil pickup (127) can be supplied to the compression unit (C), and an oil hole (1262) is formed in the rotation shaft (125) provided on the inner periphery of the bushing (180).

[0062] The scroll compressor of the present invention may further include a sub-bearing (1532). The sub-bearing (1532) may be positioned between the fixed scroll (150) and the bushing (180), and may be inserted and coupled to the inner circumference of the fixed scroll (150). The bushing (180) may be supported on the inner surface of the sub-bearing (1532).

[0063] Accordingly, oil passing through the oil passage (126) and the oil hole (1262) can be smoothly supplied to the bearing surface (BS) between the outer surface of the bushing (180) and the sub-bearing (1532) facing it through the oil supply hole (183).

[0064] As a result, a lubricating passage is formed in the bushing (180), so that the resistance of the lubricating passage from the oil storage space (S1) to the sub-bearing (1532) surface and the shaft thrust surface (STS) is reduced, and the reliability and efficiency of the compressor can be improved.

[0065] First, with reference to Fig. 1, the overall configuration of the scroll compressor of the present invention will be described.

[0066] 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).

[0067] 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.

[0068] 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).

[0069] 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).

[0070] 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).

[0071] 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).

[0072] 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.

[0073] 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.

[0074] 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.

[0075] 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).

[0076] The stator (121) includes a stator core (1211) and a stator coil (1212).

[0077] 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.

[0078] 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).

[0079] The rotor (122) includes a rotor core (1221) and a permanent magnet (1222).

[0080] 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.

[0081] 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.

[0082] 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).

[0083] 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.

[0084] 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.

[0085] 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.

[0086] However, since 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 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 coupled using a separate fixing member. 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.

[0087] 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).

[0088] 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, the shaft thrust surface (STS), and / or each bearing surface (BS).

[0089] 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).

[0090] 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).

[0091] 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 by penetrating through the center in the axial direction.

[0092] 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).

[0093] 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).

[0094] 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).

[0095] 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.

[0096] 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.

[0097] 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.

[0098] 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).

[0099] 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.

[0100] 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).

[0101] 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).

[0102] 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).

[0103] 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).

[0104] 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).

[0105] 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).

[0106] A sealing protrusion (155) may be provided on the inner surface of the fixed scroll (150).

[0107] 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).

[0108] 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).

[0109] 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).

[0110] In the drawing, the unexplained symbol 170 is an Oldham ring, and 192 is a key fixing ring.

[0111] The scroll compressor according to the above embodiment operates as follows.

[0112] 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).

[0113] 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).

[0114] 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).

[0115] 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.

[0116] 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.

[0117] 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).

[0118] 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.

[0119] Accordingly, in this embodiment, an oil supply hole (183) is formed in the bushing (180) so that oil sucked from the oil pickup (127) can be supplied to the compression section (C), and an oil hole (1262) is formed in the rotary shaft (125) provided on the inner periphery of the bushing (180). Accordingly, oil passing through the oil passage (126) and the oil hole (1262) can be smoothly supplied to the bearing surface (BS) and the shaft thrust surface (STS) of the inner periphery of the sub-bearing (1532) through the oil supply hole (183).

[0120] 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 a concentric bushing (180).

[0121] In the present invention, a structure is disclosed that improves euro resistance through various embodiments to facilitate fueling.

[0122] FIG. 2 is an exploded perspective view showing the rotary shaft (125), bushing (180), and fixed scroll (150) of the present invention, FIG. 3 is an exploded perspective view showing the rotary shaft (125) and bushing (180) of FIG. 2 in an exploded manner, FIG. 4 is a cross-sectional view taken along line “Ⅸ-Ⅸ” of FIG. 3, and FIG. 5 is a cross-sectional view showing the rotary shaft (125) and fixed scroll (150) of FIG. 2 assembled.

[0123] Referring to FIGS. 2 and 3, the bushing (180) according to the present embodiment can be inserted into and coupled to the sub-bearing surface portion (1254) of the rotary shaft (125). In other words, the bushing (180) is formed in a cylindrical shape, but is formed thicker than the sub-bearing (1532) described above, so as to form a bearing surface (BS) together with the sub-bearing (1532). Accordingly, the outer circumferential surface of the bushing (180) forms the actual outer circumferential surface of the sub-bearing surface portion (1254) of the rotary shaft (125), so that the actual outer diameter of the sub-bearing surface portion (1254) increases. Through this, the surface pressure between the sub-bearing surface portion (1254) of the rotary shaft (1255) and the sub-bearing (1532) of the fixed scroll (150) facing it can be reduced.

[0124] Specifically, the bushing (180) may be press-fitted and fixed to the sub-bearing surface (1254) of the rotation shaft (125), or may be fixed using a separate fixing member. This embodiment illustrates an example in which the bushing (180) is fixed to the sub-bearing surface (1254) using a coupling key (191).

[0125] Referring to FIGS. 2 and 3, a key receiving groove (1254a) may be formed in the sub-bearing surface portion (1254) of the rotary shaft (125) so that a coupling key (191) may be inserted therein. The key receiving groove (1254a) may be recessed in the outer circumferential surface of the sub-bearing surface portion (1254) in the radial direction to a preset depth, and may also be formed to be long in the axial direction to a preset length. In other words, the inner end of the coupling key (191) that protrudes in the radial direction of the rotary shaft (125) and extends in the axial direction may be inserted and coupled into the key receiving groove (1254a). Accordingly, the contact area between the rotary shaft (125) and the coupling key (191) may be extended in the axial direction, so that the rotational force of the rotary shaft (125) may be uniformly transmitted to the bushing (180).

[0126] Referring to FIGS. 4 and 5, the inner diameter of the bushing (180) can be formed to be almost the same as the outer diameter of the sub-bearing surface portion (1254) of the rotary shaft (125). Accordingly, the bushing (180) can be closely inserted into the sub-bearing surface portion (1254) of the rotary shaft (125), thereby suppressing oil flowing between the sub-bearing surface portion (1254) and the bushing (180) from moving toward the compression chamber (V).

[0127] A key support groove (180a) may be formed on the inner surface of the bushing (180) so that the outer end of the aforementioned coupling key (191) is inserted therein. The key support groove (180a) may be recessed to a predetermined depth in the radial direction, but may also be formed to be long in the axial direction. In other words, the key support groove (180a) may be formed to correspond to the key receiving groove (1254a) of the rotary shaft (125). Accordingly, the contact area between the bushing (180) and the coupling key is extended in the axial direction, so that the rotational force of the rotary shaft (125) can be uniformly transmitted to the bushing (180).

[0128] The refueling hole (183) and the oil hole (1262) may be arranged so that at least a portion thereof overlaps with each other. For example, referring to FIGS. 4 and 5, an example is shown in which the refueling hole (183) and the oil hole (1262) are formed so as to be arranged on the same line in the radial direction.

[0129] Due to this, the gap between the oil supply hole (183) and the oil hole (1262) is minimized, so that the oil passing through the oil hole (1262) can move more quickly to the oil supply hole (183).

[0130] An oil supply groove (185) may be provided on the outer periphery of the bushing (180). The oil supply groove (185) may be connected to an oil supply hole (183). Accordingly, oil flowing through the oil supply hole (183) may flow axially in the oil supply groove (185) and be smoothly provided to the bearing surface (BS) between the bushing (1532).

[0131] For example, the oil supply groove (185) may be extended axially to guide the axial flow of oil. The oil may flow axially along the oil supply groove (185). As illustrated in FIG. 5, the oil that has exited the oil supply hole (183) flows upward along the oil supply groove (185).

[0132] The oil supply groove (185) may have a cut portion (186) formed to be cut at one end of the bushing (180). The cut portion (186) may provide a path for oil flowing along the oil supply groove (185) to flow to the inner circumference of the bushing (180).

[0133] Referring to FIG. 3, the cut portion (186) may be formed, for example, so that one side has a lower height than one end of the bushing (180). The cut portion (186) may serve as a passage connecting the flow path on the outer surface of the bushing (180) and the flow path on the inner surface of the bushing (180), thereby expanding the flow path.

[0134] The cut portion (186) may be defined by a cut groove portion (186a) and a cut side portion (186b). The cut groove portion (186a) may be provided at one end of the refueling groove (185). The cut side portion (186b) may be provided on both sides of the cut groove portion (186a) so as to intersect with the cut groove portion (186a).

[0135] In Fig. 3, an example is shown in which a cut groove (186a) is provided at the top of a refueling groove (185), and a cut side (186b) is provided on both sides of the cut groove (186a) in a direction intersecting with the cut side (186b).

[0136] The cut portion (186) may be positioned so as to be spaced apart from the sealing protrusion (155) of the fixed scroll (150). For example, the cut side portion (186b) may be positioned so as to intersect the sealing protrusion (155) of the fixed scroll (150). The sealing protrusion (155) of the fixed scroll (150) may be in contact with the upper end of the bushing (180) or may be spaced apart from it by a predetermined distance.

[0137] A path can be defined between the cut groove (186a) and the cut side (186b) to enable the outer and inner peripheries of the bushing (180) to communicate with each other.

[0138] In this way, the oil supplied to the bearing surface (BS) between the outer circumference of the bushing (180) and the inner circumference of the sub-bearing (1532) through the oil hole (1262) and the oil supply hole (183) flows upward, then flows again into the interior of the bushing (180) through the passage expanded by the cut portion (186), and then can be supplied again to the shaft thrust surface (STS) between the rotating shaft (125) and the fixed scroll (150).

[0139] The shaft thrust surface (STS) may be a thrust surface (STS) that comes into contact between the sealing projection (155) of the fixed scroll (150) and the eccentric portion (1253) of the rotating shaft (125).

[0140] Referring to FIGS. 4 and 5, the sealing protrusion (155) is formed to be spaced apart from the upper end of the bushing (180) in the axial direction, and the inner surface of the sealing protrusion (155) can be positioned between a line extending from the outer surface of the bushing (180) and a line extending from the inner surface. As a result, a flow path through which oil can flow can be formed between the bushing (180) and the sealing protrusion (155). In addition, oil introduced into the inner surface of the bushing (180) through the cut portion (186) can flow along the inner surface of the sealing protrusion (155) and be smoothly supplied to the shaft thrust surface (STS).

[0141] The upper portion of the bushing (180) has a large oil resistance due to the configuration of the sealing protrusion (155) of the fixed scroll (150) and the eccentric portion (1253) of the rotating shaft (125). The oil passage in the upper portion of the bushing (180) is expanded by the aforementioned cut portion (186), enabling smooth oil supply to the shaft thrust surface (STS).

[0142] A stepped portion (1821) may be provided on the inner periphery of the bushing (180). The stepped portion (1821) may be formed to have a wider diameter than the sealing surface portion (184). To this end, an inclined portion (1822) may be provided between the stepped portion (1821) and the sealing surface portion (184). For example, the stepped portion (1821) may be provided on the upper portion of the inner periphery of the bushing (180).

[0143] By means of the step portion (1821), oil introduced into the inner surface of the bushing (180) through the cut portion (186) can flow upward between the rotating shaft (125) and the step portion (1821), and lubrication is possible on the shaft thrust surface (STS).

[0144] For example, the bushing (180) may be formed so that the gap between the bushing (180) and the rotation shaft (125) increases as the stepped portion (1821) moves toward the end of the bushing (180). A guide portion (1823) may be provided between the stepped portion (1821) and the inclined portion (1822) to guide oil to flow into the inner periphery of the bushing (180) through the cut portion (186). The guide portion (1823) may be formed in a direction intersecting the stepped portion (1821). In addition, the guide portion (1823) may extend circumferentially from the inner periphery of the bushing (180), thereby guiding the flow of oil in the circumferential direction from the inner periphery of the bushing (180).

[0145] The bushing (180) can enable the oil flowing in through the cut portion (186) to flow upwards through the step portion (1821) and be provided to the shaft thrust surface (STS) and the compression portion (C), thereby enabling the expansion of the flow path.

[0146] Meanwhile, the bushing (180) can also be expected to have an effect of suppressing the bushing (180) from tilting together with the rotation axis (125) when tilting due to the step portion (1821).

[0147] In this way, the bushing (180) can form a flow path by means of a refueling groove (185), a cut portion (186), and a step portion (1821), and the flow paths can be understood as the first to third flow paths (185a, 186c, 1821a) described below.

[0148] The bushing (180) may include first to third flow paths (185a, 186c, 1821a).

[0149] The first flow path (185a) may be provided in the oil supply groove (185). The first flow path (185a) may be a flow path through which oil flows upward from the outer periphery of the bushing (180). As the oil flows through the first flow path (185a), the bearing surface (BS) between the sub-bearing (1532) can be smoothly lubricated.

[0150] The second flow path (186c) is provided to intersect the first flow path (185a), and may be formed by cutting off one side of the bushing (180). The second flow path (186c) may be defined by the cut portion (186) described above. The second flow path (186c) may be a flow path that connects the outer and inner peripheries of the bushing (180). By means of the second flow path (186c), oil flowing from the outer periphery of the bushing (180) may flow into the inner periphery of the bushing (180).

[0151] The third flow path (1821a) is provided to intersect the second flow path (186c) and may be provided on the inner periphery of the bushing (180). The third flow path (1821a) may be formed on the inner periphery of the bushing (180) to have a diameter wider than the sealing surface portion (184). For this purpose, an inclined portion (1822) may be provided between the third flow path (1821a) and the sealing surface portion (184).

[0152] Due to this, the bushing (180) is provided with multiple flow paths, and in particular, by expanding the flow path in the upper part of the bushing (180) where the flow resistance is relatively large, it is possible to facilitate lubrication.

[0153] Meanwhile, a sealing surface portion (184) that is sealably coupled to the outer circumference of the rotary shaft (125) may be provided on the inner circumference of the bushing (180). The sealing surface portion (184) may be formed in an annular shape on the inner circumference of the bushing (180).

[0154] The gap between the sealing surface (184) and the sub-bearing surface (1254) can be formed narrower than the gap between the step portion (1821). Accordingly, it is possible to prevent high-pressure refrigerant contained in the internal space of the oil pickup (127) and / or the casing (110) from flowing into the gap between the inner surface of the bushing (180) and the outer surface of the sub-bearing surface (1254).

[0155] In this case, the sealing surface (184) may be formed to surround all or part of the periphery of the oil supply hole (183). In other words, the sealing surface (184) may extend the same width from all or part of the periphery of the oil supply hole (183). Examples in which the sealing surface (184) is formed to surround all of the periphery of the oil supply hole (183) are illustrated in FIGS. 5 and 9 (bushings (180) of the first and third embodiments), and examples in which the sealing surface (184) is formed to surround part of the periphery of the oil supply hole (183) are illustrated in FIG. 7 (bushings (180) of the second embodiment).

[0156] For example, the sealing surface (184) may extend at least 1 mm from all or part of the periphery of the oil supply hole (183). Accordingly, the sealing surface (184) secures a sufficient area around all or part of the periphery of the oil supply hole (183), so that not only can the refrigerant described above be prevented from flowing into the oil supply passage, but also the oil supplied to the oil supply hole (183) of the bushing (180) through the oil passage (126) and the oil hole (1262) of the rotating shaft (125) can be smoothly supplied to the oil supply hole (183) without leaking between the sub-bearing surface (1254) and the bushing (180).

[0157] In addition, with reference to FIGS. 6 and 7, the structure of the bushing (180) of the second embodiment of the present invention will be described.

[0158] The above-described fuel supply hole (183) and the above-described oil hole (1262) can form a non-overlapping structure so as to be spaced apart from each other in the axial direction. This embodiment is different from other embodiments in which the fuel supply hole (183) and the above-described oil hole (1262) overlap at least partially in that the fuel supply hole (183) and the above-described oil hole (1262) do not overlap.

[0159] The oil hole (1262) can be placed between the oil supply hole (183) and the upper side of the bushing (180).

[0160] For example, the oil hole (1262) may be positioned between the midpoint between the top and bottom of the bushing (180) and the top of the bushing (180).

[0161] In this way, since the oil supply hole (183) and the oil hole (1262) are formed in a structure where they are spaced apart from each other, the oil passing through the oil hole (1262) does not flow directly to the oil supply hole (183), but can flow upward and downward, respectively. The oil flowing upward through the oil hole (1262) is supplied to the inner surface of the shaft thrust. The oil flowing downward through the oil hole (1262) is supplied to the bearing surface (BS) between the sub-bearing (1532) and the bushing (180) through the oil supply hole (183) to lubricate it.

[0162] Oil passing through the oil hole (1262) must be able to flow smoothly between the outer circumference of the rotating shaft (125) and the inner circumference of the bushing (180). To this end, a gap passage may be provided between the outer circumference of the rotating shaft (125) and the inner circumference of the bushing (180) at a predetermined interval. The gap passage may be provided on the outer circumference of the rotating shaft (125) or the inner circumference of the bushing (180). When the gap passage (1254a) is formed on the outer circumference of the rotating shaft (1255), the gap passage (1254a) may have a diameter smaller than the sub-bearing surface portion (1254) coupled to the sealing surface portion (184) of the bushing (180). When the gap passage is formed on the inner circumference of the bushing (180), the gap passage may have a diameter larger than the sealing surface portion (184). By means of the gap passage, oil passing through the oil hole (1262) can flow axially between the rotating shaft (125) and the bushing (180).

[0163] In Fig. 7, an example is shown in which a gap passage part (1254a) is provided on the outer periphery of the sub-bearing surface part (1254) of the rotating shaft, but the gap passage part may also be provided on the inner periphery of the bushing (180).

[0164] An oil supply groove (185) may be provided on the outer periphery of the bushing (180). The oil supply groove (185) may be connected to the oil supply hole (183). Therefore, oil flowing through the oil supply hole (183) may flow axially in the oil supply groove (185) and be smoothly provided to the bearing surface (BS) between the sub-bearing (1532). As illustrated in FIGS. 6 and 7, the bushing (180) of the present embodiment differs from the bushing (180) of the embodiments of FIGS. 4 and 5 in that a cutout (186) is not formed in the oil supply groove (185).

[0165] By this bushing (180) structure, it is possible to simultaneously supply lubrication to the sub-bearing (1532) and the shaft thrust. In particular, the bushing (180) structure of the second embodiment enables the oil that has escaped the oil hole (1262) to flow in the axial direction between the rotary shaft (125) and the bushing (180) without directly flowing into the oil supply hole (183), thereby enabling the lubrication of the sub-bearing (1532) and the shaft thrust with a single oil hole (1262).

[0166] Meanwhile, a flow guide part (181) may be provided on one side of the bushing (180). The flow guide part (181) guides the upward flow of oil flowing in the inner periphery of the bushing (180) to enable supply to the shaft thrust surface (STS).

[0167] Due to this, the increase in the resistance of the bearing surface (BS) between the outer circumference of the bushing (180) and the sub-bearing (1532) and the upper portion of the bushing (180) can be minimized. In addition, compared to the third embodiment described below, it is possible to supply lubrication to the sub-bearing (1532) and the shaft thrust surface (STS) with a simpler rotating shaft (125) structure.

[0168] In addition, with reference to FIGS. 8 and 9, the structure of the bushing (180) of the third embodiment of the present invention will be described.

[0169] The refueling hole (183) and the oil hole (1262) can be arranged so that at least some of them overlap each other.

[0170] The rotating shaft (125) may be provided with an oil hole (1263). The oil hole (1263) may be axially spaced from the oil hole (1262) so as not to overlap with the bushing (180). The oil hole (1263) may also be referred to as an additional oil hole. The oil hole (1263) enables direct lubrication to the shaft thrust surface (STS).

[0171] For example, the oil hole (1263) may be provided on the sub-bearing surface (1254) of the rotating shaft (125), which is the surface on which the bushing (180) is coupled.

[0172] The center of the oil hole (1263) can be placed above the top of the bushing (180).

[0173] The oil hole (1263) may be arranged parallel to the sealing protrusion (155) so that one side faces one side of the sealing protrusion (155). The oil hole (1263) may be arranged so that one side is adjacent to one side of the sealing protrusion (155). As a result, the oil hole (1263) may have a structure that is advantageous for direct oil supply to the shaft thrust surface (STS).

[0174] At least two oiling holes (183) may be provided so as to be spaced apart from each other. In addition, at least two oiling holes (1262) may be provided so as to overlap each of the oiling holes (183).

[0175] Referring to FIGS. 8 and 9, two oiling holes (183) are provided and are axially spaced apart from each other. In addition, an example is shown in which two oiling holes (1262) are provided and are axially spaced apart from each other so as to overlap the oiling holes (183).

[0176] An example is shown in which two fueling holes (183) and two oil holes (1262) are formed to be arranged on the same line in the radial direction.

[0177] An oil supply groove (185) may be provided on the outer periphery of the bushing (180). The oil supply groove (185) may be connected to an oil supply hole (183). Therefore, oil flowing through the oil supply hole (183) may flow axially in the oil supply groove (185) and be smoothly provided to the bearing surface (BS) between the sub-bearing (1532). As illustrated in FIGS. 8 and 9, the bushing (180) of the present embodiment differs from the previous embodiments in that a cutout (186) is not formed in the oil supply groove (185) and is formed to be connected to two oil supply holes (183).

[0178] In this way, by the structure of the bushing (180) of the third embodiment, it is possible to supply oil to the sub-bearing (1532) through the oil hole (1262) and the oil supply hole (183), and separately, it is possible to individually supply oil to the shaft thrust surface (STS) through the oil hole (1263).

[0179] 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.

[0180] 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.

[0181] The present invention can be used in a scroll compressor that can increase efficiency by increasing the amount of oil supplied to a compression unit.

Claims

1. A casing that forms the exterior and has a storage space; 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; An oil pickup installed on one side of the above-mentioned rotating shaft and capable of sucking oil so as to provide oil from the above-mentioned oil storage space to the above-mentioned compression unit; and A bushing is disposed between the fixed scroll and the rotational axis, and is coupled to the outer circumference of the rotational axis so as to rotate together with the rotational axis. A scroll compressor in which an oil supply hole is formed in the above bushing so that oil sucked from the above oil pickup can be supplied to the above compression unit, and an oil hole is formed in a rotating shaft provided on the inner periphery of the above bushing.

2. In paragraph 1, A scroll compressor in which the above-mentioned fueling hole and the above-mentioned oil hole are arranged so as to overlap each other at least partially.

3. In paragraph 2, A scroll compressor in which an oil supply groove is provided on the outer periphery of the above bushing in an axial direction so as to communicate with the oil supply hole.

4. In paragraph 3, A scroll compressor having a cut portion formed so as to be cut at one end of the bushing and providing a flow path for flowing to the inner circumference of the bushing.

5. In paragraph 4, The above incision is, A cutting groove provided on one side of the above-mentioned cutting portion; and A scroll compressor including a cut side provided on each side of the cut groove and formed to intersect the cut groove to provide a path for oil to flow to the inner circumference of the bushing.

6. In paragraph 3, The above bushing, A first oil passage provided to allow oil to flow upward in the above-mentioned oil supply groove; A second passage formed by cutting off one side of the bushing and arranged to intersect with the first passage; and A scroll compressor including a third passage connected to the second passage so as to cross and provided on the inner circumference of the bushing.

7. In paragraph 2, The above bushing, A sealing surface portion provided on the inner circumference of the above bushing and sealably coupled to the outer circumference of the above rotary shaft; A stepped portion having a wider diameter than the above sealing surface portion; and A scroll compressor having a sloped portion provided between the step portion and the sealing surface portion.

8. In paragraph 1, The inner surface of the above fixed scroll is provided with a sealing projection, and the rotating shaft is provided with an eccentric portion that contacts the sealing projection so as to have an axial thrust surface. The above sealing protrusion is arranged to be spaced apart from the top of the bushing in the axial direction, and the inner circumference of the sealing protrusion is A scroll compressor disposed between a line extending from the outer circumference of the above bushing and a line extending from the inner circumference of the above bushing.

9. In paragraph 2, A scroll compressor having an oil hole provided on the above rotating shaft and spaced axially from the oil hole so as not to overlap with the bushing.

10. In paragraph 9, The inner surface of the above fixed scroll is provided with a sealing projection, and the rotating shaft is provided with an eccentric portion that contacts the sealing projection so as to have an axial thrust surface. A scroll compressor in which the above oil hole is arranged parallel to the sealing protrusion so that one side thereof faces one side of the sealing protrusion.

11. In paragraph 2, A scroll compressor in which at least two of the above-mentioned oil supply holes are provided so as to be spaced apart from each other, and at least two of the above-mentioned oil holes are provided so as to overlap each of the above-mentioned oil supply holes.

12. In paragraph 11, A scroll compressor in which an oil supply groove is provided on the outer periphery of the above bushing in an axial direction so as to communicate with the oil supply hole.

13. In paragraph 1, A scroll compressor in which the above-mentioned oil supply hole and the above-mentioned oil hole form a non-overlapping structure so as to be spaced apart from each other in the axial direction.

14. In paragraph 13, A scroll compressor in which the above oil hole is positioned between the above oil supply hole and the upper side of the above bushing.

15. In paragraph 13, A scroll compressor in which the oil hole is positioned between the midpoint between the upper and lower ends of the bushing and the upper end of the bushing.

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