Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a casing, a driving motor, a main frame, an orbiting scroll, a fixed scroll, a rotary shaft, and a bearing oil supply passage. One end of the bearing oil supply passage is connected to an oil supply hole, and the other end of the bearing oil supply passage can be opened toward an oil storage space of the casing. Accordingly, oil suctioned through an oil flow path is collected back into the oil storage space of the casing through the bearing oil supply passage, thereby improving the cooling and / or lubricating effect on bearing surfaces and preventing a decline in the capacity to cool a compression chamber and / or an increase in the oil discharge amount therein.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor.

[0002] Compressors used in refrigeration cycles such as refrigerators and air conditioners compress refrigerant gas and transmit it to the condenser. Air conditioners primarily use rotary or scroll compressors. Scroll compressors are increasingly being used not only in air conditioners but also in water heater compressors, which require even higher compression ratios.

[0003] Scroll compressors can be divided into sealed scroll compressors in which the drive unit (or electric unit) and the compression unit are provided together inside the casing, and open scroll compressors in which the drive unit (or electric unit) is provided outside the casing and only the compression unit is provided inside the casing.

[0004] 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.

[0005] Scroll compressors can be categorized into low-pressure scroll compressors, in which the internal space of the casing equipped with a compression unit forms suction pressure, and high-pressure scroll compressors, in which the discharge pressure forms. Upper compression scroll compressors can be configured as low-pressure or high-pressure types, but lower compression scroll compressors are generally configured as high-pressure scroll compressors, taking into account the location of the refrigerant suction pipe.

[0006] High-pressure scroll compressors utilize the difference between the internal pressure of the casing and the internal pressure of the compression chamber (hereinafter referred to as differential pressure) to supply oil from the casing to the compression chamber, as the internal space of the casing generates discharge pressure. Consequently, high-pressure scroll compressors can simplify the use of oil pumps. Unless otherwise specified, scroll compressors are defined as bottom-compression compressors and high-pressure scroll compressors.

[0007] Patent Document 1 (Korean Patent Publication No. 10-2019-0011115) discloses a scroll compressor that supplies oil to a sliding member using differential pressure. Patent Document 1 comprises a rotating shaft, a main frame, an orbiting scroll, and a fixed scroll, which are sequentially connected through the rotating shaft. Accordingly, the rotating shaft is formed with multiple oil supply holes axially, each opening toward the main frame, the orbiting scroll, and the fixed scroll.

[0008] However, in the conventional scroll compressor described above, the oil sucked through the oil passage of the rotating shaft is distributed to a plurality of oil supply holes, lubricates each bearing part, and then is collected and fed into the compression chamber. As a result, the amount of oil fed into the compression chamber is greater than the amount of oil supplied to each bearing part. Therefore, when the operating pressure ratio is high, a large amount of oil flows into the compression chamber, increasing the oil discharge amount. However, when the operating pressure ratio is low, the amount of oil supplied to the bearing part is insufficient, which may lower the reliability of cooling and / or lubrication.

[0009] The purpose of the present invention is to provide a scroll compressor capable of securing a sufficient amount of oil to a bearing section while maintaining an appropriate amount of oil to be supplied to a compression chamber.

[0010] Another object of the present invention is to provide a scroll compressor capable of maintaining an appropriate amount of oil supplied to a compression chamber and a bearing section regardless of the operating pressure ratio.

[0011] Another object of the present invention is to provide a scroll compressor capable of connecting a passage for guiding oil to a compression chamber and a passage for guiding oil to a bearing section while maintaining an appropriate amount of oil supplied to the compression chamber and the bearing section.

[0012] Another object of the present invention is to provide a scroll compressor in which oil sucked through an oil passage of a rotating shaft is sequentially supplied toward each bearing section.

[0013] In order to achieve the object of the present invention, a scroll compressor including a casing, a driving motor, a main frame, an orbiting scroll, a fixed scroll, a rotating shaft, and a bearing lubrication passage may be provided. The casing may be provided with an oil storage space. The driving motor may be provided in an internal space of the casing. The main frame may be provided on one side of the driving motor, and may be provided with a main shaft drain hole. The orbiting scroll may be provided to face the main frame, and may be provided with a rotating shaft coupling portion. The fixed scroll may be coupled to the orbiting scroll to form a compression chamber together with the orbiting scroll, and may be provided with a fixed shaft drain hole. The rotating shaft may have one end coupled to the driving motor, and the other end rotatably provided to penetrate the main shaft drain hole, the rotating shaft coupling portion, and the fixed shaft drain hole, and an oil passage may be formed inside, and an oil supply hole may penetrate from the oil passage to an outer circumference. The bearing oil supply passage can guide oil to a bearing surface supporting the rotating shaft. One end of the bearing oil supply passage can be connected to the oil supply hole, and the other end of the bearing oil supply passage can be opened toward an oil storage space of the casing. Accordingly, oil sucked through the oil passage can be returned to the oil storage space of the casing through the bearing oil supply passage, thereby enhancing the cooling and / or lubricating effect on the bearing surface, while suppressing a decrease in cooling capacity and / or an increase in oil discharge amount for the compression chamber.

[0014] For example, the bearing lubrication passage may include a first lubrication groove, a second lubrication groove, and a third lubrication groove. The first lubrication groove is provided on a main bearing surface of the rotary shaft facing the inner surface of the main shaft drain hole, and one end may be connected to the lubrication hole and the other end may be open toward the orbiting scroll. The second lubrication groove is provided on an eccentric portion of the rotary shaft facing the inner surface of the rotary shaft coupling portion, and both ends may be open. The third lubrication groove is provided on a fixed bearing surface of the rotary shaft facing the inner surface of the fixed shaft drain hole, and both ends may be open. Through this, one end of the bearing lubrication passage is blocked and the other end is open toward the oil storage space, so that oil sucked through the oil passage can be quickly recovered to the oil storage space.

[0015] For example, at least some of the first to third oil refueling grooves may be formed on the same axis. This allows the multiple oil refueling grooves forming the bearing oil refueling passage to be directly connected, thereby preventing oil from becoming choked in the bearing oil refueling passage, thereby enabling faster recovery.

[0016] Alternatively, at least some of the first and third oil supply grooves may be formed on different axes. This allows the bearing surface to be cooled and / or lubricated more effectively as a plurality of oil supply grooves forming the bearing oil supply passage are formed in an alternating manner on the axis.

[0017] As another example, a compression chamber oil supply passageway may be further included to guide oil from the oil storage space to the compression chamber. The compression chamber oil supply passageway may branch off from the bearing oil supply passageway and be connected to the compression chamber. This allows the bearing oil supply passageway and the compression chamber oil supply passageway to be connected to each other, while the outlets of each passageway are dualized, thereby increasing the amount of oil supplied to the bearing oil supply passageway while maintaining an appropriate amount of oil supplied to the compression chamber.

[0018] For example, the compression chamber lubrication passage may be connected to the bearing lubrication passage by penetrating the inner surface of the fixed shaft hole at one end. Through this, the compression chamber lubrication passage can be connected to the bearing lubrication passage while minimizing the length of the compression chamber lubrication passage.

[0019] Specifically, an intermediate pressure chamber is formed between the main frame and the orbiting scroll, and an intermediate pressure passage may be formed between the intermediate pressure chamber and the compression chamber. The compression chamber oil supply passage may be formed separately from the intermediate pressure passage. Through this, the compression chamber oil supply passage may be connected to a compression chamber having a lower pressure than the intermediate pressure passage, thereby enhancing the cooling and / or lubricating effect on the compression chamber.

[0020] Alternatively, the compression chamber oil supply passage may include a first compression chamber oil supply passage and a second compression chamber oil supply passage. One end of the first compression chamber oil supply passage may pass through the inner surface of the rotating shaft coupling portion, and the other end may be connected to an intermediate pressure chamber between the main frame and the orbiting scroll. One end of the second compression chamber oil supply passage may be connected to the intermediate pressure chamber, and the other end may pass through the fixed scroll and be connected to the compression chamber. Through this, the intermediate pressure passage and the compression chamber oil supply passage may be unified, so that the structure of the orbiting scroll and / or the fixed scroll forming the compression unit may be simplified.

[0021] In another embodiment, a compression chamber oil supply passageway for guiding oil from the oil storage space to the compression chamber may be further included. The compression chamber oil supply passageway may include a compression chamber oil supply hole and an oil supply pipe. The compression chamber oil supply hole may penetrate the fixed scroll and be connected to the compression chamber. The oil supply pipe may have one end inserted into the compression chamber oil supply hole, and the other end may be extended so as to be submerged in the oil storage space. Through this, the length of the compression chamber oil supply passageway can be minimized to quickly supply oil from the oil storage space to the compression chamber, and at the same time, the amount of oil supplied to the compression chamber can be more appropriately maintained, while the amount of oil supplied to the bearing oil supply passageway can be further increased.

[0022] For example, an intermediate pressure chamber may be formed between the main frame and the orbiting scroll, and an intermediate pressure passage may be formed penetrating between the intermediate pressure chamber and the compression chamber. The compression chamber oil supply passage may be formed separately from the intermediate pressure passage. Through this, the length of the compression chamber oil supply passage can be minimized, while the compression chamber oil supply passage is connected to a compression chamber having a lower pressure than the intermediate pressure passage, thereby enhancing the cooling and / or lubricating effect on the compression chamber.

[0023] In another embodiment, the rotary shaft may be rotatably coupled to the fixed shaft water hole by penetrating the rotary shaft coupling portion. A portion of the bearing lubrication passage may be formed on the outer surface of the rotary shaft facing the fixed shaft water hole. This allows for easy formation of the bearing lubrication passage.

[0024] In another embodiment, the rotating shaft may be rotatably coupled to the fixed shaft hole by penetrating the rotating shaft coupling portion, and a concentric bushing coupled to the rotating shaft may be provided between the rotating shaft and the fixed shaft hole. A portion of the bearing oil supply passage may be formed on an outer peripheral surface of the concentric bushing facing the fixed shaft hole. This makes it possible to lower the surface pressure between the rotating shaft and the fixed scroll while suppressing excessive oil supplied to the bearing surface from flowing into the compression chamber.

[0025] In another embodiment, the rotary shaft may include a main bearing surface portion inserted into the main shaft bore, an eccentric portion inserted into the rotary shaft coupling portion, and a fixed bearing surface portion inserted into the fixed shaft bore. A communication groove may be formed on at least one side of the periphery of the fixed shaft bore and one side of the eccentric portion axially facing it to communicate the bearing oil supply passage between the eccentric portion and the fixed bearing surface portion. Through this, even if the eccentric portion of the rotary shaft is supported by axial contact with the fixed scroll, oil between the eccentric portion and the orbiting scroll can smoothly move between the fixed bearing surface portion and the fixed scroll.

[0026] For example, the above-described oil supply holes may be formed only on the main bearing surface. This minimizes the number of oil supply holes, facilitating machining of the rotating shaft, while allowing oil to quickly move to the top of the bearing oil supply passage to effectively cool and / or lubricate each bearing surface.

[0027] In another embodiment, the compression chamber may be connected to the casing by inserting a refrigerant suction pipe, and the internal space of the casing may be connected to the refrigerant discharge pipe through the refrigerant discharge pipe. An oil pump communicating with the oil path may be provided on the rotating shaft or the oil guide pipe coupled to the rotating shaft. Through this, even in a high-pressure scroll compressor, by applying an oil pump, the amount of oil supplied to the compression chamber can be minimized while the amount of oil supplied to the bearing surface can be increased, thereby increasing the reliability of each bearing surface in both high-pressure ratio operation and low-pressure ratio operation.

[0028] A scroll compressor according to the present invention comprises a casing, a driving motor, a main frame, an orbiting scroll, a fixed scroll, a rotating shaft, and a bearing oil supply passage, wherein one end of the bearing oil supply passage is connected to an oil supply hole, and the other end of the bearing oil supply passage can be opened toward an oil storage space of the casing. Accordingly, oil sucked through the oil passage is returned to the oil storage space of the casing through the bearing oil supply passage, thereby enhancing the cooling and / or lubricating effect on the bearing surface, while suppressing a decrease in cooling capacity and / or an increase in oil discharge amount for the compression chamber.

[0029] The scroll compressor according to the present invention further includes a compression chamber oil supply passage for guiding oil from an oil storage space to the compression chamber, wherein the compression chamber oil supply passage can be branched off from the bearing oil supply passage and communicated with the compression chamber. Through this, while the bearing oil supply passage and the compression chamber oil supply passage are connected to each other, the outlets of each passage are dualized, thereby increasing the amount of oil supplied to the bearing oil supply passage while simultaneously maintaining an appropriate amount of oil supplied to the compression chamber.

[0030] The scroll compressor according to the present invention further includes a compression chamber oil supply passage that guides oil from an oil storage space to a compression chamber, wherein the compression chamber oil supply passage may include a compression chamber oil supply hole and an oil supply pipe. This allows the length of the compression chamber oil supply passage to be minimized, thereby quickly supplying oil from the oil storage space to the compression chamber, while further increasing the amount of oil supplied to the bearing oil supply passage while maintaining a more appropriate amount of oil supplied to the compression chamber.

[0031] A scroll compressor according to the present invention may be provided with an oil pump communicating with an oil path in a rotating shaft or an oil guide pipe coupled to the rotating shaft, wherein a refrigerant suction pipe is inserted into and communicated with a compression chamber, a refrigerant discharge pipe penetrates and communicates with an internal space of a casing, and an oil pump communicating with an oil path may be provided in the rotating shaft or an oil guide pipe coupled to the rotating shaft. Through this, even in a high-pressure scroll compressor, by applying an oil pump, the amount of oil supplied to the compression chamber can be minimized while the amount of oil supplied to the bearing surface can be increased, thereby increasing the reliability of each bearing surface in both high-pressure ratio operation and low-pressure ratio operation.

[0032] Fig. 1 is a cross-sectional view showing the inside of a scroll compressor according to the present embodiment.

[0033] Fig. 2 is an exploded perspective view showing an example of a bearing oil supply passage and a compression chamber oil supply passage in a scroll compressor according to the present embodiment.

[0034] Figure 3 is a cross-sectional view illustrating the refueling process in Figure 2.

[0035] Fig. 4 is an enlarged cross-sectional view of part “A” of Fig. 3.

[0036] Fig. 5 is a perspective view showing the flue groove in Fig. 2.

[0037] Figure 6 is a bottom view of Figure 5.

[0038] Fig. 7 is a perspective view showing another example of a flue gasket according to the present embodiment.

[0039] Figure 8 is an exploded perspective view showing another embodiment of a bearing lubrication passage and a compression chamber lubrication passage.

[0040] Figure 9 is a cross-sectional view showing the refueling process in Figure 8.

[0041] Figure 10 is an exploded perspective view showing another embodiment of a bearing lubrication passage and a compression chamber lubrication passage.

[0042] Fig. 11 is a cross-sectional view showing the refueling process in Fig. 10.

[0043] Figure 12 is a cross-sectional view illustrating the lubrication process in a case where a concentric bushing is applied between a rotating shaft and a fixed scroll.

[0044] 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.

[0045] In addition, the term "upper side" used in the following description 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 toward the drive unit (power unit or drive motor) when looking at the drive unit (power unit or drive motor) and the compression unit in the center. The term "lower side" means the direction approaching the support surface, that is, the lower side toward the compression unit when looking at the drive unit (power unit or drive motor) and the compression unit in the center.

[0046] Additionally, the term "axial" used in the following description refers to the longitudinal direction of the axis of rotation. "Axial" can be understood as the vertical direction. "Radial" refers to the direction intersecting the axis of rotation.

[0047] In addition, in the following description, the scroll compressor is described as a sealed scroll compressor in which the drive unit (electric unit or drive motor) and the compression unit are provided in the casing. However, the same can be applied to an open compressor in which the drive unit (electric unit or drive motor) is provided outside the casing and connected to the compression unit provided inside the casing.

[0048] In addition, the following description will be given as an example a lower compression type scroll compressor in which the drive unit and the compression unit are arranged in the vertical axial direction and the compression unit is located lower than the drive unit (the drive unit or the drive motor). However, the same can be applied to a horizontal scroll compressor in which the drive unit (the drive unit or the drive motor) and the compression unit are arranged left and right, as well as an upper compression type scroll compressor in which the compression unit is located higher than the drive unit (the drive unit or the drive motor).

[0049] In addition, the following description takes as an example a high-pressure scroll compressor having a lower compression type and a refrigerant suction pipe forming a suction passage directly connected to a compression section, and a refrigerant discharge pipe connected to the internal space of the casing so that the internal space of the casing forms a discharge pressure.

[0050] Fig. 1 is a cross-sectional view showing the inside of a scroll compressor according to the present embodiment.

[0051] 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 drive motor (120) forming an electric part 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) may be provided on the lower side of the drive motor (120). Typically, the drive motor (120) forms an electric part as described above, and the main frame (130), the orbiting scroll (140), the fixed scroll (150), and the discharge cover (160) form a compression part (C).

[0052] The drive motor (120) forming the electric part is coupled to the upper end of the rotation shaft (125) to be described later, and the compression part (C) can be coupled to the lower end of the rotation shaft (125). Accordingly, the compressor (10) forms the lower compression structure described above, and the compression part (C) is connected to the drive motor (120) by the rotation shaft (125) and can be operated by the rotational force of the drive motor (120). Therefore, the drive motor (120) can be understood as a drive part that drives the compression part (C), and thus, in the following description, the drive motor can be used interchangeably as the electric part or the drive part.

[0053] 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) may be coupled to cover the opened upper end of the cylindrical shell (111), and the lower shell (113) may be coupled to cover the opened lower end of the cylindrical shell (111). Accordingly, the internal space (110a) of the casing (110) is sealed, and the sealed internal space (110a) of the casing (110) may be separated into a lower space (110a) and an upper space (110b) based on the driving motor (120).

[0054] The lower space (110a) is a space formed on the lower side of the driving motor (120), and the lower space (110a) can be divided into an oil storage space (110c) and a discharge space (110d) based on the compression section (C).

[0055] The upper space (110b) is a space formed on the upper side of the driving motor (120), and forms an oil separation space in which oil is separated from the refrigerant discharged from the compression section (C), and a refrigerant discharge pipe (116) to be described later can be connected to the upper space (110b).

[0056] The aforementioned driving motor (120) and main frame (130) can be inserted and fixed inside the cylindrical shell (111). An oil recovery passage (not shown) can 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).

[0057] A refrigerant suction pipe (115) can be connected by penetrating the side of the cylindrical shell (111). Accordingly, the refrigerant suction pipe (115) can be connected by penetrating the cylindrical shell (111) forming the casing (110) in the radial direction.

[0058] The upper part of the upper shell (112) can be connected to the inner space (110a) of the casing (110), specifically, the upper space (110b) formed on the upper side of the driving motor (120), by penetrating the inner end of the refrigerant discharge pipe (116).

[0059] 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.

[0060] Referring to FIG. 1, the driving motor (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) may be inserted and fixed into the inner surface of the cylindrical shell (111), and the rotor (122) may be rotatably provided inside the stator (121).

[0061] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0062] The stator core (1211) is formed in an annular or hollow cylindrical shape and can be fixed to the inner surface of the cylindrical shell (111) by hot pressing.

[0063] The stator coil (1212) is wound around the stator core (1211) and can be electrically connected to an external power source through a power cable (not shown) that penetrates the casing (110).

[0064] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0065] The rotor core (1221) can be rotatably inserted into the stator core (1211) at a predetermined gap (not shown). The permanent magnet (1222) can be embedded in the rotor core (1221) at a predetermined gap along the circumference.

[0066] A balance weight (123) may be coupled to the lower end of the rotor core (1221). However, the balance weight (123) may also be coupled to the rotation shaft (125). This embodiment illustrates an example in which the balance weight (123) is coupled to the rotation shaft (125). The balance weights (123) are installed at the lower end and upper end of the rotor, respectively, and the two may be installed symmetrically to each other.

[0067] A rotational shaft (125) may be coupled to the center of the rotor core (1221). Accordingly, the rotational force of the driving motor (120) is transmitted to the orbiting scroll (140) forming the compression section (C) through the rotational shaft (125), and the orbiting scroll (140) rotates relative to the fixed scroll (150).

[0068] The rotation shaft (125) is formed to be long in the axial direction, and one end can be connected to the driving motor (120) and the other end can be connected to the compression section (C). In other words, the upper end of the rotation shaft (125) is connected to be fixed to the rotor (122), and the lower end of the rotation shaft (125) can be inserted to be rotatable by sequentially penetrating the main frame (130), the orbiting scroll (140), and the fixed scroll (150) described later.

[0069] For example, the upper half of the rotation shaft (125) may be pressed into the rotor (122) of the driving motor (120), and the lower half of the rotation shaft (125) may be eccentrically coupled to the orbiting scroll (140). Accordingly, the rotation shaft (125) may transmit the rotational force of the driving motor (120) to the orbiting scroll (140) described later.

[0070] Specifically, the lower half of the rotary shaft (125) may be formed with a main bearing surface portion (1251), an eccentric portion (1252), and a fixed bearing surface portion (1253). The main bearing surface portion (1251) is a portion that is rotatably inserted into the main shaft hole (1321) of the main frame (130) to be described later, the eccentric portion (1252) is a portion that is rotatably inserted into the rotary shaft coupling portion (143) of the orbiting scroll (140) to be described later, and the fixed bearing surface portion (1253) is a portion that is rotatably inserted into the fixed shaft hole (1531) of the fixed scroll (150) to be described later. Accordingly, the lower half of the rotary shaft (125) can be inserted into the main frame (130), the orbiting scroll (140), and the fixed scroll (150) to rotate relative to them.

[0071] Bearings (not shown) made of bushing bearings can be inserted into the inner surface of the main shaft bore (1321), the inner surface of the rotary shaft coupling portion (143), and the inner surface of the fixed shaft bore (1531) to rotatably support the lower end of the rotary shaft (125), respectively. Accordingly, the lower end of the rotary shaft (125) inserted into the main frame (130) can rotate smoothly inside the main frame (130). Hereinafter, the bearings inserted into the inner surface of the main shaft bore (1321), the inner surface of the rotary shaft coupling portion (143), and the inner surface of the fixed shaft bore (1531) are collectively referred to as the main shaft bore (1321), the rotary shaft coupling portion (143), and the fixed shaft bore (1531).

[0072] In addition, an oil passage (1261) and an oil supply hole (1262) are formed inside the rotating shaft (125), and an oil pump (1272) for pumping oil filled in the oil storage space (110c) can be coupled to the lower end of the oil passage (1261). Accordingly, the oil stored in the oil storage space (110c) of the casing (110) can be smoothly guided toward the sliding part (bearing surface and / or sliding surface) through the oil passage (1261) and the oil supply hole (1262).

[0073] The oil passage (1261) may be formed in the axial direction and / or inclined direction inside the rotary shaft (125). In other words, the oil passage (1261) may be formed by digging a groove from the lower end of the rotary shaft (125) to approximately the lower end or middle height of the stator (121), or around the upper end of the main bearing portion (133) to be described later, as the compression portion (C) is located lower than the driving motor (120). However, in some cases, the oil passage (1261) may be formed by penetrating between both ends of the rotary shaft (125). This embodiment illustrates a shape in which the oil passage (1261) is sunken into the interior of the rotary shaft (125) along the axial direction to a preset height.

[0074] The oil supply hole (1262) may be formed to penetrate toward the outer surface of the rotating shaft (125) from the upper end or near the upper end of the oil passage (1261). In other words, the oil supply hole (1262) may be formed to penetrate radially toward the main shaft suction hole (1321) of the main bearing, which will be described later. Accordingly, the oil in the oil storage space may be sucked up along the oil passage (1261) to the oil supply hole (1262), and then supplied to the main bearing formed by the main shaft suction hole (1321) and the main bearing surface (1251) through the oil supply hole (1262).

[0075] In addition, a bearing lubrication passage (180) may be formed between the outlet of the lubrication hole (1262), for example, the outer surface of the rotating shaft (125) and the inner surface of the main frame (130) facing it, the inner surface of the orbiting scroll (140), and the inner surface of the fixed scroll (150). The bearing lubrication passage (180) may be closed on the upper side, for example, toward the driving motor, while being open on the lower side, for example, toward the oil storage space (110c). Accordingly, oil flowing into the bearing lubrication passage (180) through the lubrication hole (1262) may be returned to the oil storage space (110c) while passing through the bearing lubrication passage (180). The bearing lubrication passage (180) will be described later together with the compression chamber lubrication passage (190).

[0076] Meanwhile, an oil guide pipe (1271) forming part of an oil pickup (127) may be connected to the lower end of the oil passage (1251). The oil guide pipe (1271) may be formed axially long so that its lower end is immersed in the oil storage space (110c), and its inner surface may be formed as a smooth pipe. However, in the case where only one oil supply hole (1262) is formed at or near the upper end of the oil passage as in the present embodiment, the amount of oil supplied to the compression chamber (V) may be limited. Accordingly, in the present embodiment, an oil pump (1272) forming another part of the oil pickup (127) may be provided at the lower end or upper end of the oil guide pipe (1271).

[0077] For example, an oil pump (1272) such as a viscous pump may be installed at the bottom of the oil guide pipe (1271), or an oil pump (not shown) such as a trochoidal gear pump may be installed between the top of the oil guide pipe (1271) and the bottom of the oil passage (1261). This embodiment illustrates an example in which an oil pump (1272) as a viscous pump is installed at the bottom of the oil guide pipe (1271).

[0078] In the case where the oil pump (1272) is installed at the bottom of the oil guide pipe (1271) as described above, the oil filled in the oil storage space (110c) can be sufficiently pumped by the oil pump (1272). Accordingly, even if the oil supply hole (1262) is formed only at the top of the oil passage (1261), the oil in the oil storage space (110c) can be sucked up along the oil guide pipe (1271) and the oil passage (1261) and then supplied to each sliding part through the oil supply hole (1262), the bearing oil supply passage (180), and the compression chamber oil supply passage (190). This can be more effective during low pressure ratio operation.

[0079] Referring to FIG. 1, the compression unit (C) according to the present embodiment may include a main frame (130), a rotating scroll (140), a fixed scroll (150), and a discharge cover (160). For example, the fixed scroll (150) may be provided on the lower side of the main frame (130), and the rotating scroll (140) may be axially supported by the fixed scroll (150) and may be provided so as to be rotatable between the main frame (130) and the fixed scroll (150).

[0080] The main frame (130) may include a frame plate portion (131) and a main bearing portion (132).

[0081] The frame plate portion (131) is formed in a circular shape and can be fixedly connected to the inner surface of the casing (110) at the lower side of the driving motor (120). For example, the frame plate portion can be fixed to the inner surface of the cylindrical shell (111) by hot pressing or welding.

[0082] The main bearing part (132) protrudes from the center of the frame plate part (131) toward the driving motor (120) by a preset height, and a main shaft hole (1321) into which a rotary shaft (125) is rotatably inserted may be formed axially through the center of the main bearing part (132). Accordingly, the inner circumferential surface of the main shaft hole (1321) forms a main bearing surface (B1) together with the main bearing surface portion (1251) of the rotary shaft (125) facing it, and can support the rotary shaft in the radial direction. As described above, a bushing bearing (not shown) is press-fitted into the inner circumferential surface of the main shaft hole (1321), and the bushing bearing forms the actual main bearing surface (B1). However, for convenience, the inner circumferential surface of the main shaft hole (1321) is described below as forming a part of the main bearing surface (B1).

[0083] The rotary scroll (140) according to the present embodiment may include a rotary plate portion (141), a rotary wrap (142), and a rotary shaft coupling portion (143).

[0084] The pivot plate (141) is formed in a circular shape and is accommodated between the main frame (130) and the fixed scroll (150), and the upper surface of the pivot plate (141) can be axially supported by the main frame (130) with a pressure sealing member (not shown) interposed therebetween.

[0085] An intermediate pressure chamber (Sm) can be formed at the edge of the pivot member (141), i.e., on the outer surface of the pivot member (141), together with the main frame (130) and / or the fixed scroll (150). The intermediate pressure chamber (Sm) is connected to the compression chamber (V) through an intermediate pressure passage (170) to be described later, thereby forming an intermediate pressure (back pressure). Accordingly, the pivot member (141) receives the back pressure of the intermediate pressure chamber (Sm) and is axially supported toward the fixed scroll (150), thereby suppressing leakage between the compression chambers (V). The intermediate pressure passage (170) will be described again later together with the fixed scroll (150).

[0086] The pivoting wrap (142) can extend from the lower surface of the pivoting plate portion (141) toward the fixed plate portion (151) to be described later. Accordingly, the pivoting wrap (142) can be 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.

[0087] 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 wrap shape.

[0088] The rotary shaft coupling portion (143) may be formed by penetrating axially through the inner end of the orbiting wrap (142), that is, the central portion of the orbiting plate portion (141). Accordingly, the discharge port (1511) described later may be formed at the center of the orbiting scroll (140), that is, at an eccentric position from the rotary shaft coupling portion (143).

[0089] 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 rotary wrap (142) to form a first compression chamber (V1) together with the fixed wrap (154) during the compression process. As described above, a bushing bearing (not shown) is press-fitted into the inner circumference of the rotary shaft coupling portion (143) so that the bushing bearing forms a substantial rotary bearing surface (B2). However, in the following, the inner circumference of the rotary shaft coupling portion (143) is described as forming a part of the rotary bearing surface (B2) together with the outer circumference of the eccentric portion (1252).

[0090] The rotary shaft coupling portion (143) can be formed at a height that overlaps the orbiting wrap (142) on the same plane. For example, the rotary shaft coupling portion (143) can be positioned at a height that overlaps the eccentric portion (1252) of the rotary shaft (125) on the same plane with the orbiting wrap (142). Accordingly, the repulsive force and the compressive force of the refrigerant are applied on the same plane based on the orbiting plate portion (141) and cancel each other out, thereby suppressing the tilting of the orbiting scroll (140) due to the action of the compressive force and the repulsive force.

[0091] A fixed scroll (150) according to the present embodiment may include a fixed plate portion (151), a fixed side wall portion (152), a fixed bearing portion (153), and a fixed wrap (154).

[0092] The fixed plate portion (151) may be formed in a circular shape and may be arranged at a preset interval on the lower side of the frame plate portion (131). A fixed shaft hole (1531) forming a fixed bearing portion (153) may be formed vertically through the center of the fixed plate portion (151). A discharge port (1511) may be formed around the fixed shaft 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). As previously explained, a bushing bearing (not shown) is pressed into the inner surface of the fixed shaft hole (1531) to form a practical fixed bearing surface (B3), but below, the inner surface of the fixed shaft hole (1531) is explained as forming a part of the fixed bearing surface (B3) together with the outer surface of the fixed bearing surface portion (1253).

[0093] 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 fixed shaft 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 fixed shaft hole (1531).

[0094] In addition, a second intermediate pressure passage (170), which forms another part of the intermediate pressure passage (170), may be formed by penetrating the fixed plate portion (1531). For example, the intermediate pressure passage (170) may be formed on one circumferential side of the suction port (1521) described later. Accordingly, the intermediate pressure passage (170) may be connected to the compression chamber (V) by penetrating the interior of the fixed plate portion (1531) without interfering with the suction port (1521).

[0095] One end of the intermediate pressure passage (170) may be connected to an intermediate pressure chamber (Sm), and the other end of the intermediate pressure passage (170) may be connected to a compression chamber (V). For example, one end of the intermediate pressure passage (170) may be connected to the intermediate pressure chamber (Sm) by penetrating a fixed side wall portion (152) to be described later, and the other end of the intermediate pressure passage (170) may be connected to a compression chamber (V) that forms an intermediate pressure between the suction pressure and the discharge pressure by penetrating a fixed plate portion (1531). Accordingly, the intermediate pressure chamber (Sm) may appropriately form a back pressure depending on the pressure of the compression chamber (V) connected to the intermediate pressure chamber (Sm).

[0096] In addition, a compression chamber oil supply passage (190) to be described later may be formed in the fixed plate portion (1531). In other words, the compression chamber oil supply passage (190) may be formed on one circumferential side of the suction port (1521) like the intermediate pressure passage (170), but may be formed separately from the intermediate pressure passage (170) so as not to interfere with the intermediate pressure passage (170). Accordingly, the compression chamber oil supply passage (190) may be connected to a compression chamber (V) having a different pressure from the intermediate pressure passage (170) without interfering with the suction port (1521). Through this, the compression chamber oil supply passage (180) may be connected to a compression chamber (V) forming a lower pressure than the intermediate pressure passage (170), thereby enhancing the cooling and / or lubricating effect between the orbiting scroll (140) and the fixed scroll (150) forming the compression chamber.

[0097] For example, one end of the compression chamber lubrication passage (190) may be formed to face the fixed bearing surface portion (1253) of the rotary shaft (125) by penetrating the inner surface of the fixed shaft hole (1531) forming the fixed bearing surface (B3), and the other end of the compression chamber lubrication passage (190) may be opened to the upper surface of the fixed plate portion (151) so as to be connected to the compression chamber (V). In other words, one end of the compression chamber lubrication passage (190) may be connected to the bearing lubrication passage (180), and the other end of the compression chamber lubrication passage (190) may be formed to be connected to the compression chamber (V) at which the compression chamber (V) forms suction pressure based on the rotation angle of the rotary shaft (125) or to the compression chamber (V) at the rotation angle immediately after suction is completed. Accordingly, the compression chamber oil supply passage (190) can be directly connected to the bearing oil supply passage (180) without passing through the intermediate pressure chamber (Sm). Accordingly, a portion of the oil sucked from the internal space (110a) of the casing (110) through the oil passage (1261) of the rotating shaft (125) can move directly to the compression chamber oil supply passage (190) through the oil supply hole (1262) and the bearing oil supply passage (180), and then be supplied to the compression chamber (V) through the compression chamber oil supply passage (190). The compression chamber oil supply passage (190) will be described later together with the bearing oil supply passage (180).

[0098] The fixed side wall portion (152) can be extended in the vertical direction from the upper edge of the fixed plate portion (151) and connected to the main frame (130). A suction port (1521) is formed in the fixed side wall portion (152) that penetrates the fixed side wall portion (152) in the radial direction, and a refrigerant suction pipe (115) that penetrates the cylindrical shell (111) as described above can be inserted and connected to the suction port (1521). Accordingly, the refrigerant that has passed through the evaporator (not shown) of the refrigeration cycle is directly sucked into the compression chamber (V), and the internal space of the casing (110) is filled with the refrigerant discharged from the compression chamber (V), thereby forming a high-pressure scroll compressor.

[0099] The fixed bearing portion (153) protrudes from the center of the fixed plate portion (151) toward the discharge cover (160) to be described later by a preset height, and a fixed shaft hole (1531) into which a rotational shaft (125) is rotatably inserted may be formed axially through the center of the fixed bearing portion (153). Accordingly, the inner circumferential surface of the fixed shaft hole (1531) forms a fixed bearing surface (B3) together with the fixed bearing surface portion (1253) of the rotational shaft (125) facing it, and may support the rotational shaft (125) in the radial direction. As previously explained, a bushing bearing (not shown) is pressed into the inner surface of the fixed shaft hole (1531) so that the bushing bearing forms a practical fixed bearing surface (B3). However, for convenience, the inner surface of the fixed shaft hole (1531) is described below as forming part of the main bearing surface (B1).

[0100] The fixed wrap (154) may be formed to extend axially from the upper surface of the fixed plate portion (151) toward the orbiting scroll (140). The fixed wrap (154) may be interlocked with the orbiting wrap (142) to be described later to form a compression chamber (V). The compression chamber (V) may include a first compression chamber (V1) formed between the inner surface of the fixed wrap (154) and the outer surface of the orbiting wrap (142), and a second compression chamber (V2) formed between the outer surface of the fixed wrap (154) and the inner surface of the orbiting wrap (142).

[0101] Since the fixed wrap (154) is formed to correspond to the shape of the rotating wrap (144) described above, the description of the fixed wrap (154) is replaced with the description of the rotating wrap (142).

[0102] The discharge cover (160) can be coupled to the back surface of the fixed scroll (150). A muffler space (160a) is provided inside the discharge cover (160), and a discharge port (1511) penetrating the fixed scroll (150) can be accommodated in the muffler space (160a). Accordingly, the refrigerant discharged from the compression chamber (V) through the discharge port (1511) moves to the upper space (110b) via the muffler space (160a).

[0103] The unexplained symbol 1512 in the drawing is a bypass hole.

[0104] The scroll compressor according to the above embodiment operates as follows.

[0105] 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 orbiting scroll (140) eccentrically coupled to the rotation shaft (125) performs a rotational movement with respect to the fixed scroll (150) by the Oldham ring (145).

[0106] 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).

[0107] 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.

[0108] 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 (110d) between the main frame (130) and the drive motor (120), passes through the drive motor (120), and moves to the upper space (110b) 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 (110b), 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 (110c) of the casing (110) through the oil recovery passage (not shown) described above. This oil is supplied to each of the wetted parts and compression chambers (V) through the oil passage (1261) of the rotating shaft (125) and then returned to the oil storage space (110c) of the casing (110), repeating a series of processes.

[0109] Meanwhile, the oil stored in the oil storage space (110c) is sucked up along the oil guide tube (1271) and oil path (1261) when the rotary shaft (125) rotates, and is then supplied to the bearing surfaces (B1) (B2) (B3) between the outer surface of the rotary shaft (125) and the members facing it through the oil supply hole (1262), thereby lubricating each bearing surface. In other words, oil is supplied to the main bearing surface (B1) formed between the main bearing surface (1251) of the rotary shaft (125) and the main shaft hole (1321) of the main frame (130) through the oil supply hole (1262), the rotary bearing surface formed between the eccentric portion (1252) of the rotary shaft (125) and the rotary shaft coupling portion (143) of the rotary scroll (140), and the fixed bearing surface (B3) formed between the fixed bearing surface (1253) of the rotary shaft (125) and the fixed shaft hole (1531) of the fixed scroll (150), thereby lubricating each of the bearing surfaces (B1), (B2), and (B3).

[0110] At this time, when the space between the main bearing surface (B1) and the slewing bearing surface, the space between the slewing bearing surface (B2) and the fixed bearing surface (B3), and the space between the fixed bearing surface and the oil storage space (110c) are blocked as in the past, the oil supplied to each bearing surface (B1)(B2)(B3) cools and / or lubricates each bearing surface (B1)(B2)(B3) and then almost all of it flows into the compression chamber (V) due to the differential pressure. And, as described above, the oil flowing into the compression chamber (V) is discharged into the internal space of the casing (110) together with the refrigerant, and some of it is returned to the oil storage space (110c) of the casing (110) and some of it can flow out into the refrigeration cycle. Therefore, from the perspective of increasing the cooling and / or lubrication of the bearing surfaces (B1)(B2)(B3) and discharging foreign substances from the bearing surfaces (B1)(B2)(B3), it may be advantageous to increase the amount of oil supplied to the bearing surfaces. However, this may cause excessive oil supply to the compression chamber (V), which may result in a decrease in cooling capacity due to volume loss in the compression chamber (V) and an increase in the amount of oil discharged. This phenomenon may occur more severely during high pressure ratio operation where the amount of oil supplied to the bearing surfaces is increased.

[0111] On the other hand, if the amount of oil supplied to each bearing surface (B1)(B2)(B3) is lowered in consideration of this, reliability of each bearing surface (B1)(B2)(B3) may be reduced. This is because when the differential pressure decreases during low pressure ratio operation, the amount of oil supplied to the bearing surfaces (B1)(B2)(B3) may be significantly reduced.

[0112] Accordingly, in this embodiment, by dualizing the outlets of the bearing oil supply passage (180) and the compression chamber oil supply passage (190), it is possible to increase the amount of oil supplied to the bearing surface regardless of the operating conditions of the compressor, while suppressing an excessive increase in the amount of oil supplied to the compression chamber.

[0113] FIG. 2 is an exploded perspective view showing an example of a bearing lubrication passage and a compression chamber lubrication passage in a scroll compressor according to the present embodiment, FIG. 3 is a cross-sectional view showing the lubrication process in FIG. 2, FIG. 4 is an enlarged cross-sectional view showing part “A” of FIG. 3, FIG. 5 is a perspective view showing a communication groove in FIG. 2, FIG. 6 is a bottom view of FIG. 5, and FIG. 7 is a perspective view showing another example of a communication groove according to the present embodiment.

[0114] Referring to FIGS. 2 and 3, the scroll compressor according to the present embodiment may be provided with the aforementioned bearing oil supply passage (180) and compression chamber oil supply passage (190) that are connected to the oil passage (1261) and oil supply hole (1262) between the outer surface of the rotating shaft (125) and the members facing it.

[0115] For example, the oil passage (1261) is formed to be sunken from the bottom to the top of the rotating shaft (125) by a preset height, and the oil supply hole (1262) is formed to penetrate radially toward the outer surface of the rotating shaft (125) at or near the top of the oil passage (1261), the bearing oil supply passage (180) is connected to the oil supply hole (1262), and the compression chamber oil supply passage (190) can be branched from the middle of the bearing oil supply passage (180) and connected thereto. Accordingly, oil sucked through the oil passage (1261) can be supplied to the bearing oil supply passage (180) and the compression chamber oil supply passage (190) through the oil supply hole (1262) at or near the top of the oil passage (1261).

[0116] Specifically, the bearing lubrication passage (180) according to the present embodiment may include a main bearing lubrication groove (181), an eccentric lubrication groove (182), and a fixed bearing lubrication groove (183). Since the main bearing lubrication groove (181), the eccentric lubrication groove (182), and the fixed bearing lubrication groove (183) are sequentially formed along the oil movement path, the main bearing lubrication groove (181) may be defined as a first lubrication groove, the eccentric lubrication groove (182) as a second lubrication groove, and the fixed bearing lubrication groove (183) as a third lubrication groove, respectively, and described below.

[0117] Referring to FIGS. 2 and 3, the first oil supply groove (181) can be formed on the main bearing surface (1251) of the rotary shaft (125) facing the inner surface of the main shaft hole (1321) (more precisely, a bearing pressed into the inner surface of the main shaft hole). Accordingly, the first oil supply groove (181) can be directly connected to the oil supply hole (1262).

[0118] The first oil supply groove (181) may be formed to be recessed or de-cut to a preset depth in the main bearing surface portion (1251) of the rotary shaft (125). For example, the outer diameter of the main bearing surface portion (1251) may be spaced apart by approximately 15 ㎛ from the inner surface of the main shaft drain hole (1321), while the depth of the first oil supply groove (181) may be formed to be spaced apart by approximately 1 mm or more from the inner surface of the main shaft drain hole (1321). Accordingly, a portion of the oil flowing into the first oil supply groove (181) through the oil supply hole (1262) is spread in the circumferential direction by the centrifugal force generated when the rotary shaft (125) rotates, thereby cooling and / or lubricating the main bearing surface (B1), and at the same time, a portion of the oil quickly moves along the first oil supply groove (181) toward the slewing bearing surface (B2). In addition, a portion of the oil that has cooled and / or lubricated the main bearing surface (B1) also flows into the first oil supply groove (181) and moves toward the slewing bearing surface (B2).

[0119] The first oil supply groove (181) may be formed along the axial direction or may be formed to be inclined in the forward direction with respect to the rotational direction of the rotation shaft (125). In the former case, the oil moves quickly along the first oil supply groove (181), whereas in the latter case, the oil flowing into the first oil supply groove (181) through the oil supply hole (1262) is widely spread to the main bearing surface (B1) by centrifugal force, so that even if the main bearing surface (B1) receives a high load and the bearing area is formed large, the cooling and / or lubricating effect for the main bearing surface (B1) can be increased. This embodiment illustrates an example in which the main bearing surface (B1) is formed to be inclined with the first oil supply groove (181).

[0120] The upper end of the first oil supply groove (181) may be formed to be closed, while the lower end may be open. In other words, the upper end of the first oil supply groove (181) facing the driving motor (120) may be formed to be spaced apart from the upper edge of the main bearing surface (1251), and the lower end of the first oil supply groove (181) facing the orbiting scroll (150) may be extended to end up to the lower edge of the main bearing surface (1251). Accordingly, the upper end of the first oil supply groove (181) is connected to the oil supply hole (1262), so that a large amount of oil flowing in through the oil supply hole (1262) does not scatter toward the driving motor (120), but flows down along the first oil supply groove (181) to the lower edge of the main bearing surface (1251) and quickly moves to the orbiting bearing surface (B2). Through this, even if a separate oil supply hole (1262) is not formed in the eccentric portion (1252) of the rotating shaft (125), a sufficient amount of oil can be secured to the slewing bearing surface (B2).

[0121] Referring to FIGS. 2 and 3, the second oil refueling groove (182) may be formed in the eccentric portion (1252) of the rotary shaft (125) facing the inner surface of the rotary shaft coupling portion (143) (more precisely, a bearing pressed into the inner surface of the rotary shaft coupling portion (143)). Accordingly, the second oil refueling groove (182) may be indirectly connected to the oil refueling hole (1262) with the first oil refueling groove (181) interposed therebetween.

[0122] The second oil supply groove (182) may be formed so that the upper edge of the eccentric portion (1252) facing the main frame and the lower edge of the eccentric portion (1252) facing the fixed scroll (150) are open, respectively. Accordingly, the second oil supply groove (182) may be directly connected to the main bearing surface (B1) and the fixed bearing surface (B3) by extending between the two ends of the eccentric portion (1252). Through this, even if a separate oil supply hole (1262) is not formed in the fixed bearing surface portion (1253) of the rotary shaft (125), a sufficient amount of oil can be supplied to the fixed bearing surface (B3).

[0123] The second oil supply groove (182) can be formed to approximately the same specifications as the first oil supply groove (181) described above. In other words, the second oil supply groove (182), like the first oil supply groove (181), can be formed to be sunken or de-cut to a preset depth in the eccentric portion (1252) of the rotary shaft (125). Accordingly, a portion of the oil flowing from the main bearing surface (B1) to the slewing bearing surface (B2) spreads circumferentially by the centrifugal force generated when the rotary shaft (125) rotates, thereby cooling and / or lubricating the slewing bearing surface (B2), while at the same time, a portion of the oil moves along the second oil supply groove (182) toward the fixed bearing surface (B3). In addition, a portion of the oil that has cooled and / or lubricated the slewing bearing surface (B2) also flows into the second oil supply groove (182) and moves toward the fixed bearing surface (B3).

[0124] The second oil supply groove (182) may be formed along the axial direction or may be formed to be inclined in a forward direction with respect to the rotational direction of the rotary shaft (125). In the former case, the oil moves quickly along the second oil supply groove (182), whereas in the latter case, the oil flowing into the second oil supply groove (182) is widely spread to the slewing bearing surface (B2) by centrifugal force, thereby enhancing the cooling and / or lubricating effect on the slewing bearing surface (B2). This embodiment illustrates an example in which the second oil supply groove (182) is formed in the axial direction.

[0125] The second oil refueling groove (182) may be formed on the same axis as the first oil refueling groove (181) at least in part. In other words, since the first oil refueling groove (181) described above is formed to be inclined with respect to the axial direction of the rotation shaft (125), the second oil refueling groove (182) may be formed axially while still being formed within the circumferential range of the first oil refueling groove (181). Accordingly, oil passing through the first oil refueling groove (181) may quickly flow into the second oil refueling groove (182).

[0126] Although not shown in the drawing, the second oil supply groove (182) may be formed on a different axis with respect to the first oil supply groove (181). In other words, the second oil supply groove (182) may be formed outside the circumferential range of the first oil supply groove (181). In this case, some of the oil flowing into the slewing bearing surface (B2) through the first oil supply groove (181) may not flow directly into the second oil supply groove (182) but may be widely spread on the slewing bearing surface (B2). This can enhance the cooling and / or lubricating effect on the slewing bearing surface (B2).

[0127] Referring to FIGS. 5 and 6, a communication groove (184) may be formed on one side of the eccentric portion (1252), that is, on the lower surface of the eccentric portion (1252) facing the periphery of the fixed shaft hole (1531) in the fixed plate portion (151). For example, the outer circumference of the communication groove (184) may be connected to the second oil supply groove (182), and the inner circumference of the communication groove (184) may extend to the fixed bearing surface portion (more precisely, the outer circumference of the rotary shaft between the eccentric portion and the fixed bearing surface portion) (1253). Accordingly, even if the eccentric portion (1252) of the rotary shaft (125) is supported by axial contact with the fixed scroll (150), the oil of the slewing bearing surface (B2) can smoothly move toward the fixed bearing surface (B3).

[0128] In this case, the flue groove (184) may be formed in a radial direction toward the outermost circumferential surface of the eccentric portion (1252) in an eccentric direction, for example, from the axis center of the rotational shaft (125). However, the outer circumferential end of the flue groove (184) may be formed in a plane so as to be inclined or spirally formed in the rotational direction of the rotational shaft (125). In the former case, the processing of the flue groove (184) is easy, while in the latter case, the oil of the second oil supply groove (182) can move more quickly toward the fixed bearing surface (B3).

[0129] Referring to Fig. 7, the communication groove (184) may be formed on one side of the fixed scroll (150) facing the eccentric portion (1252). For example, at least one communication groove (184) may be formed along the circumferential direction around the fixed shaft hole (1531) that forms a thrust surface (not shown) together with the eccentric portion (1252) in the fixed plate portion (151). In this case, the communication groove (184) may be formed in the radial direction or may be formed to be inclined in the rotational direction of the rotational shaft (125). This embodiment illustrates an example in which a plurality of communication grooves (184) are inclined in the rotational direction of the rotational shaft (125). In this case, the communication groove (184) may be formed so that a portion thereof axially overlaps the periphery of the rotational shaft coupling portion (143) of the orbiting scroll (140). Accordingly, not only does the oil of the slewing bearing surface (B2) move smoothly to the fixed bearing surface (B3), but when the rotary shaft (125) rotates, some of the communication grooves (184) overlap with the periphery of the rotary shaft coupling portion (143), effectively cooling and / or lubricating the thrust surface (not shown) between the rotary shaft coupling portion (143) and the fixed plate portion (151) facing it.

[0130] Although not shown in the drawing, the communication grooves (184) may be formed on the lower surface of the eccentric portion (1252) and the upper surface of the fixed scroll (150) facing it, respectively. In other words, a first communication groove (not shown) may be formed on the lower surface of the eccentric portion (1252), and a second communication groove (not shown) may be formed around the fixed shaft hole (1531) of the fixed scroll (150). Accordingly, not only does the oil of the slewing bearing portion move more smoothly to the fixed bearing portion, but when the rotary shaft (125) rotates, some of the communication grooves (184) overlap with the periphery of the rotary shaft coupling portion (143), thereby more effectively cooling and / or lubricating the thrust surface between the rotary shaft coupling portion (143) and the fixed plate portion (151).

[0131] Referring again to FIGS. 2 and 3, the third oil supply groove (183) may be formed on the fixed bearing surface (1253) of the rotary shaft (125) facing the inner surface of the fixed shaft hole (1531) (more precisely, a bearing pressed into the inner surface of the fixed shaft hole (1531)). Accordingly, the third oil supply groove (183) may be indirectly connected to the oil supply hole (1262) with the first oil supply groove (181) and the second oil supply groove (18) interposed therebetween.

[0132] The third oil supply groove (183) may be formed so that both axial ends are open, similar to the second oil supply groove (182). In other words, the upper end of the third oil supply groove (183) facing the orbiting scroll (140) may extend longitudinally to the upper edge of the fixed bearing surface (1253), and the lower end of the third oil supply groove (183) facing the oil storage space (110c) may extend longitudinally to the lower edge of the fixed bearing surface (1253). Accordingly, the upper end of the third oil supply groove (183) is directly connected to the orbiting bearing surface (B2), so that the oil of the orbiting bearing surface (B2) flows down along the third oil supply groove (183) to the lower edge of the fixed bearing surface (1253) forming the lower end of the rotary shaft (125), thereby quickly moving to the oil storage space (110c). Through this, even if a separate oil supply hole (1262) is not formed on the fixed bearing surface (1253) of the rotating shaft (125), a sufficient amount of oil can be supplied to the fixed bearing surface (B3), and at the same time, the oil supplied to the main bearing surface (B1) through the oil supply hole (1262) described above can be quickly recovered to the oil storage space (110c) through the slewing bearing surface (B2) and the fixed bearing surface (B3) in sequence.

[0133] The third oil supply groove (183) may be formed by being recessed or de-cut to a preset depth in the fixed bearing surface portion (1253) of the rotary shaft (125). For example, the third oil supply groove (183) may be formed to have approximately the same specifications as the first oil supply groove (181) and / or the second oil supply groove (182) described above. Accordingly, a portion of the oil flowing from the slewing bearing surface (B2) to the fixed bearing surface (B3) is spread in the circumferential direction of the fixed bearing surface (B3) by the centrifugal force generated when the rotary shaft (125) rotates, thereby cooling and / or lubricating the fixed bearing surface (B3), and at the same time, a portion of the oil moves along the third oil supply groove (183) toward the oil storage space (110c) of the casing. In addition, a portion of the oil that has cooled and / or lubricated the fixed bearing surface (B3) also flows into the third oil supply groove (183) and quickly moves toward the oil storage space (110c).

[0134] Even in this case, the third oil supply groove (183) may be formed along the axial direction, or may be formed to be inclined in the forward direction with respect to the rotational direction of the rotary shaft (125). In the former case, the oil moves quickly along the third oil supply groove (183), while in the latter case, the oil flowing into the third oil supply groove (183) is widely spread to the fixed bearing surface (B3) by centrifugal force, thereby increasing the cooling and / or lubricating effect on the fixed bearing surface (B3). This embodiment illustrates an example in which the third oil supply groove (183) is formed in the axial direction, taking into account that the fixed bearing surface receives a relatively small load and also has a relatively small bearing area.

[0135] The third oil supply groove (183) may be formed on an axis that is at least partially different from that of the second oil supply groove (182). In other words, the third oil supply groove (183) may be formed axially but outside the circumferential range of the second oil supply groove (182). Accordingly, among the oil flowing into the fixed bearing surface (B3) through the second oil supply groove (182), some of the oil may not flow directly into the third oil supply groove (183) but may be widely spread into the fixed bearing surface (B3). This may enhance the cooling and / or lubricating effect on the fixed bearing surface.

[0136] Although not shown in the drawing, the third oil supply groove (183) may be formed on the same axis as the second oil supply groove (182). In this case, most of the oil flowing into the fixed bearing surface (B3) through the second oil supply groove (182) flows directly into the third oil supply groove (183) and can be quickly recovered to the oil storage space (110c).

[0137] Meanwhile, referring to FIGS. 2 to 4, the compression chamber oil supply passage (190) according to the present embodiment may be formed to branch off from the middle of the bearing oil supply passage (180) and communicate with the compression chamber (V). In other words, even if the inlet of the compression chamber oil supply passage (190) is communicated with the bearing oil supply passage (180), the outlet of the compression chamber oil supply passage (190) may be separated from the outlet of the bearing oil supply passage (180). Accordingly, the outlet of the bearing oil supply passage (180) and the outlet of the compression chamber oil supply passage (190) are separated, so that a portion of the oil recovered to the oil storage space (110c) through the bearing oil supply passage (180) can be supplied to the compression chamber (V). This makes it possible to increase the amount of oil supplied to the bearing oil supply passage (180) while suppressing an excessive increase in the amount of oil supplied to the compression chamber (V).

[0138] For example, the compression chamber oil supply passage (190) may be formed to communicate with the compression chamber (V) from the inner surface of the fixed shaft hole (1531) forming the fixed bearing surface (B3). In other words, one end of the compression chamber oil supply passage (190) may be formed to penetrate the inner surface of the fixed shaft hole (1531), and the other end of the compression chamber oil supply passage (190) may be formed to pass through the fixed plate portion (151) and penetrate the upper surface of the fixed plate portion (151) facing the orbiting scroll (140). Accordingly, a portion of the oil passing through the fixed bearing surface (B3) may be supplied to the compression chamber (V) through the compression chamber oil supply passage (190).

[0139] In this case, one end of the compression chamber oil supply passage (190) may be formed to be positioned radially on the same line with respect to the third oil supply groove (183) forming part of the bearing oil supply passage (180). In other words, one end of the compression chamber oil supply passage (190) may be formed to be radially connected with the third oil supply groove (183) at a predetermined rotation angle when the rotation shaft (125) rotates. Accordingly, oil passing through the third oil supply groove (183) can be quickly and continuously supplied to the compression chamber (V) through the compression chamber oil supply passage (190).

[0140] In addition, in this case, a pressure reducing pin (190a) may be provided inside the compression chamber oil supply passage (190). Accordingly, oil at or near the discharge pressure may be prevented from directly flowing into the compression chamber (V), thereby preventing a decrease in cooling capacity.

[0141] Although not shown in the drawing, the compression chamber lubrication passage (190) may be formed by sequentially penetrating the main frame (130) and the fixed scroll (150). For example, the compression chamber lubrication passage (190) may be formed by a first compression chamber lubrication passage (not shown) penetrating from the inner surface of the main shaft hole (1321) to the lower surface of the main frame (130) facing the fixed scroll (150), and a second compression chamber lubrication passage (not shown) penetrating from the upper surface of the fixed side wall portion (152) facing the main frame (130) to the compression chamber (V) so as to communicate with the first compression chamber lubrication passage. In this case, since one end of the first compression chamber lubrication passage, which forms the entrance of the compression chamber lubrication passage (190), is connected to the main bearing surface (B1) adjacent to the lubrication hole (1262), lubrication to the compression chamber (V) can be quickly accomplished. Of course, even in this case, a pressure reducing pin (not shown) may be provided in the first compression chamber oil supply passage and / or the second compression chamber oil supply passage to appropriately reduce the pressure of the oil flowing into the compression chamber (V).

[0142] In this way, the oil sucked through the oil passage (1261) flows into the bearing lubrication passage (180) through the lubrication hole (1262) at or near the upper end of the oil passage (1261) to lubricate each bearing surface (B1) (B2) (B3) and at the same time can be returned to the oil storage space (110c) through the bearing lubrication passage (180). In addition, a part of the oil returned to the oil storage space (110c) through the bearing lubrication passage (180) can be supplied to the compression chamber (V) through the compression chamber lubrication passage (190). Accordingly, even if the bearing lubrication passage (180) and the compression chamber lubrication passage (190) are connected in parallel and the amount of lubrication supplied to the bearing surfaces (B1) (B2) (B3) is increased, the amount of lubrication supplied to the compression chamber (V) can be suppressed from increasing excessively. By doing so, the amount of oil supplied to the bearing surface (B1)(B2)B3) of the rotating shaft (125) can be increased, thereby enhancing the cooling and / or lubricating effect on the bearing surface (B1)(B2)(B3), while suppressing a decrease in cooling capacity and / or an increase in oil discharge amount for the compression chamber (V).

[0143] Meanwhile, there are other examples of compressed air supply channels as follows.

[0144] That is, in the embodiment described above, the compression chamber oil supply passage communicates between the bearing oil supply passage and the compression chamber without passing through the intermediate pressure chamber, but in some cases, the compression chamber oil supply passage may communicate between the bearing oil supply passage and the compression chamber through the intermediate pressure chamber.

[0145] Fig. 8 is an exploded perspective view showing another embodiment of a bearing lubrication passage and a compression chamber lubrication passage, and Fig. 9 is a cross-sectional view showing the lubrication process in Fig. 8.

[0146] Referring to FIGS. 8 and 9, the scroll compressor according to the present embodiment is provided with a bearing oil supply passage (180) and a compression chamber oil supply passage (190), but the basic configuration and the resulting operational effects of the bearing oil supply passage (180) and the compression chamber oil supply passage (190) may be the same or similar.

[0147] For example, an oil passage (1261) may be formed inside the rotating shaft (125), an oil supply hole (1262) may be formed at or near the upper end of the oil passage (1261) that penetrates toward the main bearing surface (1251), and a bearing oil supply passage (180) may be formed on the outer circumferential surface of the rotating shaft (125). In other words, the bearing oil supply passage includes a first oil supply groove (181) provided in the main bearing surface (1251), a second oil supply groove (182) provided in the eccentric portion (1252), and a third oil supply groove (183) provided in the fixed bearing surface (1253). However, the first oil supply groove (181), the second oil supply groove (182), and the third oil supply groove (183) may be formed to be connected to each other on the same axis as in the above-described embodiment, or may be formed to be connected to each other on different axis lines.

[0148] In addition, a communication groove (184) may be formed on the lower surface of the eccentric portion (1252) forming the thrust surface and / or around the fixed shaft hole (1531) facing it. Accordingly, not only does the oil of the slewing bearing surface (B2) move smoothly toward the fixed bearing surface (B3), but when the rotary shaft (125) rotates, some of the communication grooves (184) overlap with the periphery of the rotary shaft coupling portion (143), thereby cooling and / or lubricating the thrust surface (not shown) between the rotary shaft coupling portion (143) and the fixed plate portion (151) facing it.

[0149] Also in this case, the compression chamber oil supply passage (190) may be formed by branching from the middle of the bearing oil supply passage (180). In other words, one end of the compression chamber oil supply passage (190) may be connected to the middle of the bearing oil supply passage (180), and the other end of the compression chamber oil supply passage (190) may be connected to the compression chamber (V). Accordingly, the outlet of the compression chamber oil supply passage (190) may be separated from the outlet of the bearing oil supply passage (180), so that the amount of oil supplied to the compression chamber (V) may be appropriately maintained while increasing the amount of oil supplied to the bearing oil supply passage (180).

[0150] However, in the present embodiment, the compression chamber oil supply passage (190) may be formed to communicate between the bearing oil supply passage (180) and the compression chamber (V) via the intermediate pressure chamber (Sm). For example, the compression chamber oil supply passage (190) may be formed of a first compression chamber oil supply passage (191) penetrating the orbiting scroll (140) and a second compression chamber oil supply passage (192) penetrating the fixed scroll (150). Accordingly, the compression chamber oil supply passage (190) may be formed to communicate between the orbiting bearing surface (B2) and the compression chamber (V) by sequentially penetrating the orbiting scroll (140) and the fixed scroll (150).

[0151] Referring to Fig. 8, one end of the first compression chamber oil supply passage (191) passes through the inner surface of the rotary shaft coupling portion (143) forming the rotary bearing surface (B2), and the other end of the first compression chamber oil supply passage (191) passes through the rotary plate portion (141) so that the rotary plate portion (141) can pass through the upper surface of the rotary plate portion (141) facing the main frame (130). Accordingly, the other end of the first compression chamber oil supply passage (191) can be connected to the intermediate pressure chamber (Sm).

[0152] In this case, one end of the first compression chamber oil supply passage (191) may be formed to be positioned radially on the same line with respect to the second oil supply groove (182) forming part of the bearing oil supply passage (180). In other words, one end of the first compression chamber oil supply passage (191) may be formed to be radially connected with the second oil supply groove (182) at a predetermined rotation angle when the rotation shaft (125) rotates. Accordingly, oil passing through the third oil supply groove (183) can be quickly and continuously supplied to the compression chamber (V) through the compression chamber oil supply passage (190).

[0153] In addition, in this case, a decompression pin (190a) may be provided inside the first compression chamber oil supply passage (191). Accordingly, oil at or near the discharge pressure is decompressed as it passes through the first compression chamber oil supply passage (191), thereby suppressing high-pressure oil from directly flowing into the compression chamber (V), thereby preventing a decrease in cooling capacity. Although not shown in the drawing, the decompression pin (190a) may also be provided inside the second compression chamber oil supply passage (192).

[0154] One end of the second compression chamber oil supply passage (192) penetrates the upper surface of the fixed side wall portion (152) forming the intermediate pressure chamber (Sm), and the other end of the second compression chamber oil supply passage (192) can be connected to the compression chamber (V) forming the intermediate pressure. Accordingly, oil flowing into the intermediate pressure chamber (Sm) through the first compression chamber oil supply passage (191) can flow into the compression chamber (V) through the second compression chamber oil supply passage (192) to cool and / or lubricate the bearing surface in the compression chamber.

[0155] In the case where the compression chamber oil supply passage (190) is formed to pass through the intermediate pressure chamber (Sm) as described above, the intermediate pressure passage (intermediate pressure hole) that guides the refrigerant to the intermediate pressure chamber (Sm) can be excluded. In other words, in the present embodiment, depending on the difference between the pressure of the intermediate pressure chamber (Sm) and the pressure of the compression chamber (V) connected to the intermediate pressure chamber (Sm), the refrigerant or oil can move between the intermediate pressure chamber (Sm) and the compression chamber (V) to form a back pressure in the intermediate pressure chamber (Sm) or to supply oil to the compression chamber (V). Accordingly, the intermediate pressure passage (170) provided in the fixed scroll (150) in the above-described embodiment can be excluded, and thus the structure of the fixed scroll (150) can be simplified to that extent.

[0156] Meanwhile, another example of a compressed air supply channel is as follows.

[0157] That is, in the embodiments described above, the compression chamber oil supply passage is formed by branching from the middle of the bearing oil supply hole, but in some cases, the compression chamber oil supply passage may be formed by being separated from the bearing oil supply passage.

[0158] Fig. 10 is an exploded perspective view showing another embodiment of a bearing lubrication passage and a compression chamber lubrication passage, and Fig. 11 is a cross-sectional view showing the lubrication process in Fig. 10.

[0159] Referring to FIGS. 10 and 11, the scroll compressor according to the present embodiment is provided with a bearing oil supply passage (180) and a compression chamber oil supply passage (190), but the basic configurations and corresponding operational effects of the bearing oil supply passage (180) and the compression chamber oil supply passage (190) may be the same or similar.

[0160] For example, an oil passage (1261) may be formed inside the rotating shaft (125), an oil supply hole (1262) may be formed at or near the upper end of the oil passage (1261) that penetrates toward the main bearing surface (1251), and a bearing oil supply passage (180) may be formed on the outer circumferential surface of the rotating shaft (125). In other words, the bearing oil supply passage includes a first oil supply groove (181) provided in the main bearing surface (1251), a second oil supply groove (182) provided in the eccentric portion (1252), and a third oil supply groove (183) provided in the fixed bearing surface (1253). However, the first oil supply groove (181), the second oil supply groove (182), and the third oil supply groove (183) may be formed to be connected to each other on the same axis as in the above-described embodiment, or may be formed to be connected to each other on different axis lines.

[0161] In addition, a communication groove (184) may be formed on the lower surface of the eccentric portion (1252) forming the thrust surface and / or around the fixed shaft hole (1531) facing it. Accordingly, not only does the oil of the slewing bearing surface (B2) move smoothly toward the fixed bearing surface (B3), but when the rotary shaft (125) rotates, some of the communication grooves (184) overlap with the periphery of the rotary shaft coupling portion (143), thereby cooling and / or lubricating the thrust surface (not shown) between the rotary shaft coupling portion (143) and the fixed plate portion (151) facing it.

[0162] However, in the present embodiment, the compression chamber oil supply passage (190) may be formed to be directly connected to the oil storage space (110c) without passing through the bearing oil supply passage (180). Accordingly, the length of the compression chamber oil supply passage (190) can be minimized to quickly supply oil to the compression chamber (V). In addition, as the compression chamber oil supply passage (190) is completely separated from the bearing oil supply passage (180), the amount of oil supplied to the compression chamber (V) can be more appropriately maintained while the amount of oil supplied to the bearing oil supply passage (180) can be further increased.

[0163] For example, the compression chamber oil supply passage (190) according to the present embodiment may include a compression chamber oil supply hole (or second oil supply hole) (195) and an oil supply pipe (196). One end of the compression chamber oil supply hole (195) may be formed to penetrate the lower surface of the fixed scroll (150) from the outside of the discharge cover (160), and the other end of the compression chamber oil supply hole (195) may penetrate the upper surface of the fixed scroll (150) to communicate with the compression chamber (V) that has passed the intermediate pressure or the suction completion angle. Accordingly, oil at or near the discharge pressure may be smoothly supplied to the compression chamber (V), while suppressing suction loss caused by the oil.

[0164] One end of the oil supply pipe (196) is inserted and fixed into the compression chamber oil supply hole (195), and the other end of the oil supply pipe (196) can be extended to be submerged in the oil storage space (110c) of the casing (110). Accordingly, the oil in the oil storage space (110c) can quickly move to the compression chamber oil supply hole (195) through the oil supply pipe (196) and be supplied to the compression chamber (V).

[0165] In this case, a pressure reducing pin (190a) is inserted into the interior of the compression chamber oil supply hole (195) and / or the interior of the oil supply pipe (196), or the inner diameter of the oil supply pipe (196) is formed small so that the pressure of the oil flowing into the compression chamber (V) can be appropriately reduced. This embodiment illustrates an example in which a pressure reducing pin (190a) is inserted into the interior of the compression chamber oil supply hole (195).

[0166] In the case where the compression chamber oil supply passage (190) is formed separately from the bearing oil supply passage (180) as described above, the length of the compression chamber oil supply passage (190) is minimized as described above, so that oil in the oil storage space (110c) can be quickly supplied to the compression chamber (V), and the amount of oil supplied to the compression chamber (V) can be further increased while maintaining a more appropriate amount of oil supplied to the bearing oil supply passage (180).

[0167] Meanwhile, another embodiment of the bearing lubrication passage and / or the compression chamber lubrication passage is as follows.

[0168] That is, in the above-described embodiments, the fixed bearing surface of the rotating shaft was examined mainly as an example in which the fixed shaft hole of the fixed scroll was rotatably inserted (more precisely, a bearing press-fitted into the fixed shaft hole), but in some cases, even when a bushing bearing is inserted and combined on the outer surface of the rotating shaft, the bearing lubrication passage and / or compression chamber lubrication passage described above may be applied identically or almost identically.

[0169] Figure 12 is a cross-sectional view illustrating the lubrication process in a case where a concentric bushing is applied between a rotating shaft and a fixed scroll.

[0170] Referring to FIG. 12, the scroll compressor according to the present embodiment is provided with a bearing oil supply passage (180) and a compression chamber oil supply passage (190), but the basic configuration and the resulting operational effects of the bearing oil supply passage (180) and the compression chamber oil supply passage (190) may be the same or similar.

[0171] For example, an oil passage (1261) may be formed inside the rotating shaft (125), an oil supply hole (1262) may be formed at or near the upper end of the oil passage (1261) that penetrates toward the main bearing surface (1251), and a bearing oil supply passage (180) may be formed on the outer circumferential surface of the rotating shaft (125). In other words, the bearing oil supply passage includes a first oil supply groove (181) provided in the main bearing surface (1251), a second oil supply groove (182) provided in the eccentric portion (1252), and a third oil supply groove (183) provided in the fixed bearing surface (1253). However, the first oil supply groove (181), the second oil supply groove (182), and the third oil supply groove (183) may be formed to be connected to each other on the same axis as in the above-described embodiment, or may be formed to be connected to each other on different axis lines.

[0172] In addition, a communication groove (184) may be formed on the lower surface of the eccentric portion (1252) forming the thrust surface and / or around the fixed shaft hole (1531) facing it. Accordingly, not only does the oil of the slewing bearing surface (B2) move smoothly toward the fixed bearing surface (B3), but when the rotary shaft (125) rotates, some of the communication grooves (184) overlap with the periphery of the rotary shaft coupling portion (143), thereby cooling and / or lubricating the thrust surface (not shown) between the rotary shaft coupling portion (143) and the fixed plate portion (151) facing it.

[0173] However, in a scroll compressor of the shaft-through type as in the present embodiment, the outer diameter of the fixed bearing surface portion (1253) of the rotating shaft (125) may be formed smaller than the outer diameter of the eccentric portion (1252) in consideration of the assembling ability. As a result, the surface pressure may be greatly increased between the fixed bearing surface portion (1253) and the fixed shaft hole (more precisely, the bearing pressed into the fixed shaft hole) (1531) facing it in the radial direction.

[0174] Accordingly, in the present embodiment, a concentric bushing (128) forming a part of the fixed bearing surface (1253) may be inserted between the fixed bearing surface (1253) of the rotary shaft (125) and the fixed shaft bore (1531) of the fixed scroll (150). For example, the concentric bushing (128) may be press-fitted onto the outer circumferential surface of the fixed bearing surface (1253) or may be integrally coupled with the rotary shaft (125) using a separate fixed member (not shown). Accordingly, the actual outer diameter of the fixed bearing surface (1253) increases, thereby reducing the surface pressure between the fixed bearing surface (substantially the concentric bushing) (1253) and the fixed shaft bore (1531).

[0175] In this case, the third oil supply groove (183) may be formed on the outer surface of the concentric bushing (128) forming the actual fixed bearing surface portion (1253). In other words, the third oil supply groove (183) may be formed to extend between the axial ends of the concentric bushing (128). Accordingly, a portion of the oil passing through the slewing bearing surface (B2) may spread along the outer surface of the concentric bushing (128) to cool and / or lubricate the fixed bearing surface (B3), while a portion of the oil may be quickly recovered to the oil storage space (110c) along the third oil supply groove (183) provided in the concentric bushing (128).

[0176] In addition, even in this case, the compression chamber lubrication passage (190) may be branched from the middle of the bearing lubrication passage (180) and connected to the compression chamber (V), or may be provided separately from the bearing lubrication passage (180) and directly connected to the compression chamber (V). Since their basic configuration and operational effects are the same as those of the above-described embodiments, the description thereof will be replaced with the description of the above-described embodiments.

[0177] Meanwhile, in the above-described embodiments, the explanation was made with a focus on an example in which only one oil supply hole (1262) of the rotary shaft (125) is formed and connected to the bearing oil supply passage (180), but in some cases, the rotary shaft (125) may be formed with a plurality of oil supply holes. For example, in the above-described embodiments, the oil supply hole (1262) is connected to the first oil supply groove (181) forming the upper end of the bearing oil supply passage (180), but in some cases, the oil supply holes may be formed in the first oil supply groove (181), the second oil supply groove (182), and / or the third oil supply groove (183). However, in this case, the inner diameter of the oil supply hole connected to the second oil supply groove (182) may be smaller than the inner diameter of the oil supply hole connected to the first oil supply groove (181), and the oil supply hole connected to the third oil supply groove (183) may be formed smaller than the inner diameter of the oil supply hole connected to the second oil supply groove (182). Accordingly, oil can be quickly supplied to each oil supply groove when the compressor is started.

Claims

1. Casing having an oil storage space; A driving motor provided in the internal space of the above casing; A main frame provided on one side of the above driving motor and having a main shaft hole; A rotating scroll equipped to face the main frame and equipped with a rotating shaft coupling part; A fixed scroll coupled to the above-mentioned orbiting scroll to form a compression chamber together with the orbiting scroll, and having a fixed shaft hole; A rotary shaft which is coupled to the driving motor at one end and is rotatable by penetrating the main shaft hole, the rotary shaft coupling portion, and the fixed shaft hole at the other end, and has an oil passage formed therein and an oil supply hole penetrating from the oil passage to the outer surface; and It includes a bearing oil supply passage that guides oil to the bearing surface that supports the above-mentioned rotating shaft, A scroll compressor in which one end of the bearing oil supply passage is connected to the oil supply hole, and the other end of the bearing oil supply passage is opened toward the oil storage space of the casing.

2. In paragraph 1, The above bearing lubrication passage is, A first oil supply groove is provided on the main bearing surface of the rotary shaft facing the inner surface of the main shaft hole, one end of which is connected to the oil supply hole and the other end is opened toward the rotating scroll; A second oil supply groove provided on the eccentric portion of the above-mentioned rotary shaft facing the inner surface of the above-mentioned rotary shaft coupling portion and having open ends; and A scroll compressor including a third oil supply groove which is provided on the fixed bearing surface of the rotating shaft facing the inner surface of the fixed shaft hole and is open at both ends.

3. In paragraph 2, A scroll compressor in which at least some of the first and third refueling grooves are formed on the same axis.

4. In paragraph 2, A scroll compressor in which at least some of the first and third refueling grooves are formed on different axes.

5. In paragraph 1, A compression chamber oil supply passage is further included to guide oil from the above oil storage space to the compression chamber, The above compressed air supply passage is, A scroll compressor branched from the above bearing lubrication passage and connected to the above compression chamber.

6. In paragraph 5, The above compressed air supply passage is, A scroll compressor having a first end that penetrates the inner surface of the fixed shaft hole and is connected to the bearing lubrication passage.

7. In paragraph 6, An intermediate pressure chamber is formed between the main frame and the rotating scroll, and an intermediate pressure passage is formed through the intermediate pressure chamber and the compression chamber. The above compressed air supply passage is, A scroll compressor formed by separating from the above intermediate pressure passage.

8. In paragraph 5, The above compressed air supply passage is, A first compression chamber oil supply passageway having one end penetrating the inner surface of the above-mentioned rotary shaft coupling and the other end connected to the intermediate pressure chamber between the main frame and the above-mentioned rotary scroll; and A scroll compressor including a second compression chamber oil supply passageway, one end of which is connected to the intermediate pressure chamber and the other end of which penetrates the fixed scroll and is connected to the compression chamber.

9. In paragraph 1, A compression chamber oil supply passage is further included to guide oil from the above oil storage space to the compression chamber, The above compressed air supply passage is, A compression chamber oil supply hole penetrating the fixed scroll and communicating with the compression chamber; and A scroll compressor including a refueling pipe, one end of which is inserted into the compression chamber refueling hole and the other end of which is extended to be immersed in the oil storage space.

10. In paragraph 9, An intermediate pressure chamber is formed between the main frame and the rotating scroll, and an intermediate pressure passage is formed through the intermediate pressure chamber and the compression chamber. The above compressed air supply passage is, A scroll compressor formed by separating from the above intermediate pressure passage.

11. In paragraph 1, The above rotational axis is rotatably connected to the fixed axis hole through the rotational axis coupling portion, Part of the above bearing lubrication passage, A scroll compressor formed on the outer surface of the rotating shaft facing the fixed shaft hole.

12. In paragraph 1, The above-mentioned rotary shaft is rotatably connected to the fixed shaft hole through the rotary shaft coupling portion, and a concentric bushing connected to the rotary shaft is provided between the rotary shaft and the fixed shaft hole. Part of the above bearing lubrication passage, A scroll compressor formed on the outer surface of the concentric bushing facing the fixed shaft hole.

13. In paragraph 1, The above rotation axis is, It includes a main bearing surface portion inserted into the main shaft hole, an eccentric portion inserted into the rotary shaft coupling portion, and a fixed bearing surface portion inserted into the fixed shaft hole. A scroll compressor in which a communication groove is formed on at least one side of the periphery of the fixed shaft hole and one side of the eccentric portion facing it in the axial direction, for connecting the bearing lubrication passage between the eccentric portion and the fixed bearing surface portion.

14. In paragraph 13, The above fueling hole is, A scroll compressor formed only on the main bearing surface.

15. In any one of paragraphs 1 to 14, The above compression chamber is connected by a refrigerant suction pipe inserted therein, and the internal space of the casing is connected by a refrigerant discharge pipe penetrating therein. A scroll compressor having an oil pump connected to the oil path on the above-mentioned rotating shaft or an oil guide pipe coupled to the above-mentioned rotating shaft.

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