Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a casing, a main frame, a fixed scroll, an orbiting scroll, and a back pressure chamber assembly, wherein: the orbiting scroll has a rotary-shaft coupling unit recessed therein to overlap with an orbiting wrap in the radial direction; the back pressure chamber assembly may be disposed between the orbiting scroll and the main frame facing same; and the orbiting scroll may have, formed therein, at least one oil supply passage penetrating the inner circumferential surface of the rotary-shaft coupling unit. Therefore, when using a method for pressing the orbiting scroll, the oil supply passage, which connects the rotary-shaft coupling unit and the sliding surface, can be simplified, thereby reducing manufacturing costs. In addition, friction losses due to delayed oil supply can be mitigated by making the oil supply passage as short as possible.

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] A scroll compressor is classified as a sealed compressor if the drive unit (or electric unit) and the compression unit are included in one casing, and as an open type if they are provided independently. If the compression unit is located above the drive unit, it is classified as an upper compression type, and if located below, it is classified as a lower compression type. If the space where the drive unit is accommodated is suction pressure, it is classified as a low pressure type, and if it is discharge pressure, it is classified as a high pressure type.

[0004] In addition, a scroll compressor includes a fixed scroll having a fixed wrap and an orbiting scroll having an orbiting wrap meshed with the fixed wrap. Scroll compressors can be classified into orbiting back-pressure types and fixed back-pressure types depending on the back-pressure method. In the orbiting back-pressure method, a back-pressure chamber is formed on the back surface of the orbiting scroll, and in the fixed back-pressure method, a back-pressure chamber is formed on the back surface of the fixed scroll. In the fixed back-pressure method, the fixed scroll is usually restrained in the circumferential direction but is provided to be movable in the axial direction, so it is sometimes defined and described as a non-orbiting scroll. Hereinafter, it will be described uniformly as a fixed scroll.

[0005] Patent Document 1 (Korean Patent Publication No. 10-2011-0064663) discloses a scroll compressor of a low-pressure type and a rotating back-pressure type. A scroll compressor such as Patent Document 1 has an oil passage that supplies oil to a thrust surface formed by radially penetrating the orbiting scroll. However, in Patent Document 1, the rotating shaft coupling portion extends from one side of the orbiting plate portion to the opposite side of the orbiting wrap, which causes the discharge-side orbiting wrap to become longer, weakening the strength of the orbiting wrap. Furthermore, the distance between the point of application of the rotational force and the point of application of the compressive force increases, increasing the overturning moment relative to the orbiting scroll, which may cause the behavior of the orbiting scroll to become unstable. Considering this, if the rotating shaft joint is sunk toward the fixed wrap so as to overlap with the rotating wrap, the oil supply passage that guides the oil sucked through the rotating shaft to the wetted surface will be bent several times, which will not only increase the manufacturing cost but also increase the friction loss on the wetted surface due to the delay in oil supply.

[0006] The purpose of the present invention is to provide a scroll compressor capable of reducing manufacturing costs by simplifying a fuel supply passage connecting a rotating shaft coupling portion and a sliding surface in a rotary back pressure type.

[0007] Another object of the present invention is to provide a scroll compressor capable of suppressing friction loss due to delay in fuel supply by forming a fuel supply passage connecting a rotating shaft coupling portion and a sliding surface as short as possible.

[0008] Another object of the present invention is to provide a scroll compressor capable of securing suction volume while reducing the overturning moment for the orbiting scroll and increasing wrap strength.

[0009] In order to achieve the object of the present invention, the present invention may include a casing, a main frame, a fixed scroll, an orbiting scroll, and a back-pressure chamber assembly. The main frame may be fixed to the inside of the casing. The rotating shaft may be supported by the main frame, and an oil passage may be provided. The fixed scroll may be coupled to the main frame. The orbiting scroll may include an orbiting plate provided between the main frame and the fixed scroll, an orbiting wrap provided on a first side of the orbiting plate facing the fixed scroll to form a compression chamber together with the fixed wrap of the fixed scroll, and a rotating shaft coupling portion recessed from a second side of the orbiting plate facing the main frame toward the first side to radially overlap the orbiting wrap. The back-pressure chamber assembly may be provided between the orbiting scroll and the main frame facing the orbiting scroll to pressurize the orbiting scroll toward the fixed scroll. At least one fuel supply passage may be formed inside the above-mentioned pivot plate, the first stage of which penetrates the inner surface of the above-mentioned rotary shaft coupling. This simplifies the fuel supply passage connecting the rotary shaft coupling and the sliding surface in the rotary back pressure method, thereby reducing manufacturing costs. In addition, by forming the fuel supply passage as short as possible, frictional loss due to delayed fuel supply can be suppressed.

[0010] For example, a bushing bearing may be press-fitted into the interior of the rotary shaft coupling. The bushing bearing may be spaced apart from one end of the oil supply passage in the axial direction of the rotary shaft. This allows the oil supply passage to be easily processed by passing through the inner surface of the rotary shaft coupling while avoiding the bushing bearing, and also allows the oil supply passage to be straightened to facilitate the oil supply to the sliding surface.

[0011] For example, the above-described oil supply passage may include a oil supply hole penetrating the pivot plate, and an oil supply groove provided at an inner peripheral edge of the rotary shaft coupling portion, one end of which is connected to the oil supply hole. The bushing bearing may have an axial cross-section adjacent to the oil supply groove formed flat so as to be spaced apart from the oil supply groove in the axial direction of the rotary shaft. Through this, the inlet of the oil supply passage may be formed on the inner peripheral surface of the rotary shaft coupling portion while being further spaced apart from the rotary shaft by the depth of the oil supply groove, and oil may move more smoothly toward the oil supply passage.

[0012] As another example, a bushing bearing may be press-fitted into the inner surface of the rotary shaft coupling portion, and a recessed groove may be formed in the cross section of the bushing bearing toward the second side surface of the pivot plate portion. The recess may be communicated with one end of the oil supply passage. Through this, while an oil supply hole and / or an oil supply groove is formed on the inner surface of the rotary shaft coupling portion, the bearing area of ​​the bushing bearing may be expanded as much as possible, thereby suppressing frictional loss between the rotary shaft and the bushing bearing.

[0013] For example, the above-mentioned fuel supply passage may include a fuel hole penetrating the pivot plate portion, and a fuel supply groove provided at an inner peripheral edge of the rotation shaft coupling portion, with one end of the fuel hole communicating with the fuel supply groove. The communicating groove may be formed to accommodate the fuel supply groove. This makes it possible to form the bush bearing longer while preventing the fuel supply groove from being covered by the bush bearing.

[0014] As another example, a bushing bearing may be press-fitted into the interior of the rotary shaft coupling. The bushing bearing may radially overlap one end of the oil supply passage. This allows for the formation of oil supply holes and / or oil supply grooves on the inner surface of the rotary shaft coupling, while further expanding the bearing area of ​​the bushing bearing, thereby more effectively suppressing frictional loss between the rotary shaft and the bushing bearing.

[0015] For example, the above-described oil supply passage may include a oil supply hole penetrating the pivot plate portion, and a oil supply groove provided at an inner peripheral edge of the rotation shaft coupling portion, one end of which is connected to the oil supply hole. The oil supply groove may be radially covered by the bush bearing. This allows the bush bearing to be formed as long as possible, thereby expanding the bearing area of ​​the bush bearing while simplifying the processing and assembly of the bush bearing.

[0016] As another example, the other end of the above-mentioned fuel supply passage may penetrate at least one of the first and second sides of the above-mentioned pivot plate. This allows oil to be quickly supplied to the contact surface while the rotating shaft coupling part radially overlaps with the pivoting wrap in the pivoting back pressure method.

[0017] As another example, a second keyway may be formed on the second side of the pivot plate to slidably engage with the key of the Oldham ring. The second end of the oil supply passage may penetrate the inner surface of the second keyway. As a result, oil in the oil supply space may be directly supplied between the second keyway of the pivot plate and the key of the Oldham ring through the oil supply hole, thereby suppressing frictional loss between the pivot scroll and the Oldham ring.

[0018] For example, the second stage of the above-mentioned oil supply passage may be formed eccentrically in a direction opposite to the rotational direction of the rotational shaft with respect to the radial center line of the second keyway. This allows oil to be supplied more quickly and smoothly to the surface where the second keyway of the orbiting scroll and the key of the Oldham ring actually come into contact.

[0019] As another example, the back pressure chamber assembly may be provided on one side of the main frame facing the rotating scroll. This simplifies the back pressure chamber assembly, thereby reducing manufacturing costs.

[0020] For example, the back pressure chamber assembly may include a back pressure passage, a back pressure space, and a sealing member. The back pressure passage may pass through the orbiting scroll so as to be connected to the compression chamber. The back pressure space may be formed in an annular shape to accommodate the back pressure passage. The sealing member may be provided on an end surface of the back pressure space facing the orbiting scroll to form a back pressure chamber inside the back pressure space. The oil supply passage may be formed at a predetermined interval from one side of the back pressure passage. Through this, the back pressure chamber assembly may be simplified while allowing smooth and rapid oil supply to the sliding surface.

[0021] As another example, the back pressure chamber assembly may be provided on one side of the orbiting scroll facing the main frame. This allows the back pressure chamber assembly to increase the sealing force between the main frame and the orbiting scroll, effectively preventing refrigerant leakage from the back pressure chamber or inflow into the back pressure chamber, thereby suppressing suction loss and / or compression loss. Furthermore, by increasing the area of ​​the back pressure chamber, the orbiting scroll can be more securely supported.

[0022] For example, the back pressure chamber assembly may include a back pressure passage, a back pressure space, and a floating member. The back pressure passage may penetrate the orbiting scroll so as to be in communication with the compression chamber. The back pressure space may be formed in an annular shape to accommodate the back pressure passage. The floating member may be slidably coupled to the back pressure space to form a back pressure chamber inside the back pressure space. The oil supply passage may be formed at a predetermined interval from one side of the back pressure passage. Through this, the open side of the back pressure space may be sealed to more effectively seal the back pressure chamber, while also smoothly and quickly supplying oil to the sliding surface.

[0023] A scroll compressor according to the present invention comprises a casing, a main frame, a fixed scroll, an orbiting scroll, and a back pressure chamber assembly, wherein the orbiting scroll is formed by recessing a rotating shaft coupling portion so as to radially overlap an orbiting wrap, and the back pressure chamber assembly may be provided between the orbiting scroll and a main frame facing the orbiting scroll. At least one oil supply passage may be formed inside the orbiting scroll, penetrating into the inner circumference of the rotating shaft coupling portion. Through this, not only can the manufacturing cost be reduced by simplifying the oil supply passage connecting the rotating shaft coupling portion and the sliding surface in the orbiting back pressure method, but also the oil supply passage can be formed as short as possible to suppress friction loss due to oil supply delay.

[0024] In a scroll compressor according to the present invention, a bushing bearing is formed with a flat axial cross-section adjacent to a lubrication groove provided at a corner of a rotary shaft coupling portion, such that the bushing bearing can be spaced apart from the lubrication groove in the axial direction of the rotary shaft. As a result, the inlet of the lubrication passage is formed on the inner surface of the rotary shaft coupling portion while being spaced further apart from the rotary shaft by the depth of the lubrication groove, and oil can move more smoothly toward the lubrication passage.

[0025] According to the scroll compressor of the present invention, a communication groove may be formed in the cross section of a bush bearing that is press-fitted into the interior of the rotary shaft coupling to accommodate an oil supply groove provided at an edge of the rotary shaft coupling. Through this, while forming an oil supply hole and / or an oil supply groove on the inner circumference of the rotary shaft coupling, the bearing area of ​​the bush bearing can be expanded as much as possible, thereby suppressing frictional loss between the rotary shaft and the bush bearing.

[0026] In a scroll compressor according to the present invention, the cross-section of a bush bearing pressed into the interior of a rotary shaft coupling portion can radially overlap with one end of a lubrication passage. This allows for the formation of lubrication holes and / or lubrication grooves on the inner surface of the rotary shaft coupling portion while further expanding the bearing area of ​​the bush bearing, thereby more effectively suppressing frictional loss between the rotary shaft and the bush bearing.

[0027] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0028] Fig. 2 is a perspective view showing the compression part in Fig. 1 in an exploded view.

[0029] Fig. 3 is a perspective view showing the rotary scroll according to the present embodiment from the bottom.

[0030] Fig. 4 is a plan view showing the rotary scroll of Fig. 3 combined with the main frame.

[0031] Figure 5 is a cross-sectional view taken along the line “Ⅴ-Ⅴ” of Figure 4.

[0032] Fig. 6 is a perspective view of a slewing scroll having a bushing bearing of another embodiment, viewed from below.

[0033] Fig. 7 is a cross-sectional view showing the fuel passage of the rotating scroll in Fig. 6.

[0034] Fig. 8 is a perspective view of a slewing scroll having a bushing bearing of another embodiment, viewed from below.

[0035] Fig. 9 is a cross-sectional view showing the fuel passage of the rotating scroll in Fig. 8.

[0036] Fig. 10 is a cross-sectional view showing a portion of a scroll compressor to which another embodiment of a back pressure chamber assembly is applied.

[0037] Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0038] Scroll compressors can be classified as sealed or open, depending on whether the drive motor and compression unit are installed together within the internal space of the casing. This embodiment uses a sealed scroll compressor as a representative example. However, the same principles can be applied to open scroll compressors.

[0039] Scroll compressors can also be categorized into fixed scroll compressors and mobile scroll compressors. Fixed scroll compressors are typically used for building air conditioning, while mobile scroll compressors are used for vehicle air conditioning. This embodiment uses a fixed scroll compressor as a representative example. However, the same principles can be applied to mobile scroll compressors.

[0040] Scroll compressors can also be categorized as low-pressure or high-pressure depending on the pressure of the refrigerant filled within the internal space of the casing. In a low-pressure type, the internal space of the casing is filled with refrigerant at suction pressure, while in a high-pressure type, the internal space of the casing is filled with refrigerant at discharge pressure. This embodiment describes a low-pressure scroll compressor as a representative example. However, the same principles can be applied to high-pressure scroll compressors.

[0041] Additionally, scroll compressors can be categorized into upper compression types and lower compression types depending on the installation location of the compression unit. In the upper compression type, the compression unit is installed above the driving motor, and in the lower compression type, the compression unit is installed below the driving motor. This embodiment describes an upper compression type scroll compressor as a representative example. However, the same principles can be applied to a lower compression type scroll compressor.

[0042] In addition, scroll compressors can be classified into single-rotating scroll compressors and reciprocating scroll compressors depending on whether the scrolls rotate. Single-rotating scroll compressors are configured such that one scroll is fixed or has limited rotational movement while the other scroll rotates, while reciprocating scroll compressors are configured such that both scrolls rotate. This embodiment will be described using a single-rotating scroll compressor as a representative example. However, the same principles can be applied to reciprocating scroll compressors.

[0043] In addition, scroll compressors can be divided into vertical scroll compressors in which the rotation axis is arranged perpendicular to the ground and horizontal scroll compressors in which the rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side can be defined as the side opposite to the ground, and the lower side can be defined as the side facing the ground. The following description will be given using a vertical scroll compressor as an example. However, the same or similar application can be applied to a horizontal scroll compressor. Therefore, the axial direction is understood as the axial direction of the rotation axis, the radial direction is understood as the radial direction of the rotation axis, and the axial direction can be understood as the up-down direction, the radial direction can be understood as the left and right sides, the inner surface can be understood as the upper surface, and the axial radial direction can be understood as the side, respectively.

[0044] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment, and Fig. 2 is a perspective view showing the compression unit in Fig. 1 in an exploded manner.

[0045] Referring to FIG. 1, the scroll compressor according to the present embodiment may be provided with a driving motor (120) forming an electric power unit in the lower half of a casing (110), and a main frame (130), a fixed scroll (140), an orbiting scroll (150), and a back pressure chamber assembly (160) forming a compression unit may be provided in the upper part of the driving motor (120). The electric power unit may be coupled to one end of a rotating shaft (125), and the compression unit may be coupled to the other end of the rotating shaft (125). Accordingly, the compression unit is connected to the electric power unit by the rotating shaft (125) and operates by the rotational force of the electric power unit.

[0046] The casing (110) may include a cylindrical shell (111), an upper cap (112), and a lower cap (113).

[0047] The cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and the aforementioned driving motor (120) and main frame (130) can be inserted and fixed into the inner surface. A refrigerant suction pipe (115), which will be described later, can be connected by penetrating the upper half of the cylindrical shell (111), for example, the upper side of the driving motor (120).

[0048] The upper cap (112) can be coupled to cover the opened upper portion of the cylindrical shell (111), and the lower cap (113) can be coupled to cover the opened lower portion of the cylindrical shell (111). Accordingly, the internal space of the casing (110) can be sealed.

[0049] An annular high-low pressure separator (114) can be inserted and connected between the cylindrical shell (111) and the upper cap (112). In other words, the outer circumference of the high-low pressure separator (114) is connected between the cylindrical shell (111) and the upper cap (112), and the inner circumference of the high-low pressure separator (114) can be tightly fastened to the back surface of the fixed scroll (140). Accordingly, the internal space of the casing (110) can be separated into a low-pressure portion (110a) forming a suction space centered on the high-low pressure separator (114) and a high-pressure portion (110b) forming a discharge space.

[0050] A refrigerant suction pipe (115) may be connected through the middle of the cylindrical shell (111), and a refrigerant discharge pipe (116) may be connected through the upper cap (112). Accordingly, the refrigerant suction pipe (115) may be connected to the low-pressure portion (110a) of the casing (110) forming the suction space, and the refrigerant discharge pipe (116) may be connected to the high-pressure portion (110b) of the casing (110) forming the discharge space.

[0051] Referring to FIG. 1, a driving motor (120) according to the present embodiment may include a stator (121) and a rotor (122). The stator (121) may be fixed to the inner wall surface of a cylindrical shell (111) by hot pressing, and the rotor (122) may be rotatably provided inside the stator (121).

[0052] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0053] The stator core (1211) is formed in a cylindrical shape and is fixed to the inner surface of the cylindrical shell (111) by hot pressing. The stator coil (1212) is wound around the stator core (1211) and can be electrically connected to an external power source through a terminal (not shown) that is connected through the casing (110).

[0054] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0055] The rotor core (1221) is formed in a cylindrical shape and can be rotatably inserted into the interior of the stator core (1211) at a predetermined gap interval. The permanent magnet (1222) can be embedded in the interior of the rotor core (1222) at a predetermined gap interval along the circumference.

[0056] In addition, a rotation shaft (125) can be press-fitted and coupled to the center of the rotor core (1221). An eccentric portion (1251) is provided at the upper end of the rotation shaft (125), so that an orbiting scroll (150), which will be described later, can be eccentrically coupled thereto. Accordingly, the rotational force of the driving motor (120) can be transmitted to the orbiting scroll (150) through the rotation shaft (125).

[0057] In addition, an oil passage (1252) may be formed axially through the inside of the rotating shaft (125), and an oil pickup (126) for sucking up oil stored in the lower part of the casing (110) may be provided at the lower end of the rotating shaft (125) so as to be in communication with the oil passage (1252). Accordingly, the oil stored in the oil storage space (110c) of the casing (110) is pumped by the oil pickup and sucked up through the oil passage (1252), thereby lubricating the sliding surface.

[0058] Referring to FIGS. 1 and 2, the main frame (130) according to the present embodiment may include a main flange portion (131) and a shaft support portion (132).

[0059] The main flange portion (131) may be fixed in close contact with the inner surface of the cylindrical shell (111). In this case, at least one oil recovery passage (not shown) may be formed on the outer surface of the main flange portion (131) and spaced apart from the inner surface of the cylindrical shell (111). Accordingly, oil supplied between the main frame (130) and the orbiting scroll (150) may be recovered to the oil storage space (110c) of the casing (110) through the oil recovery passage (not shown).

[0060] In addition, a scroll fixing surface (1311) is formed on one side of the main flange portion (131), that is, on the edge of the upper surface facing the fixed scroll (140), an old ring support surface (1312) is formed on the inner side of the scroll fixing surface (1311), and a thrust support surface (1313) can be formed on the inner side of the old ring support surface (1312).

[0061] The scroll fixing surface (1311) is a portion where the fixed scroll (140) is fixed and secured, and may be formed to have a predetermined height difference from the old ring support surface (1312) and / or the thrust support surface (1313). Accordingly, a step surface is formed between the inner surface of the scroll fixing surface (1311) and the outer surface of the old ring support surface (1312), so that a certain amount of oil flowing into the old ring support surface (1312) and / or the thrust support surface (1313) can be stored on the inner side of the scroll fixing surface (1311).

[0062] In addition, the scroll fixing surfaces (1311) may be formed at predetermined intervals along the circumferential direction by extending in the radial direction. Accordingly, a type of oil recovery passage (not shown) may be formed between the scroll fixing surfaces (1311) through which oil supplied to the sliding surface through the oil supply passage (154) described later is recovered to the oil storage space (110c).

[0063] Although not shown in the drawing, the scroll fixing surface (1311) may be formed at the same height as the old ring support surface (1312) and / or the thrust support surface (1313). In this case, the entire or most of the upper surface of the main flange portion (131) forms the same plane, so that the main frame (130) can be easily formed.

[0064] The Oldham ring support surface (1312) is a portion where the Oldham ring (170), which will be described later, is seated and slides, and can be formed flat. Accordingly, the Oldham ring (170) is seated on the Oldham ring support surface (1312) and slides smoothly, thereby suppressing the rotation of the orbiting scroll (150).

[0065] A first key groove (1312a) into which a first key (172) of an Oldham ring (170) is slidably inserted may be formed on the Oldham ring support surface (1312). The first key groove (1312a) may be formed to be radially long to correspond to the first key. For example, the first key groove (1312a) may be formed by being recessed into the Oldham ring support surface (1312) by a preset depth.

[0066] The thrust support surface (1313) is a portion where the sealing member (163) of the pressure relief assembly (160) described later is inserted to form the pressure relief space (162), and can be formed flat like the old ring support surface (1312). Accordingly, the turning plate can be secured and supported in the axial direction during operation stoppage and / or abnormal operation.

[0067] The shaft support protrusion (132) extends from the center of the main flange portion (131) toward the driving motor (120), and a shaft support hole (1321) may be formed on the inside of the shaft support protrusion (132) so as to penetrate both axial side surfaces of the main flange portion (131). Accordingly, the main frame (130) can radially support the rotation shaft (125) inserted into the shaft support hole (1321).

[0068] Referring to Fig. 1, a fixed scroll (140) according to the present embodiment can be fixed to a main frame (130) with a rotating scroll (150) to be described later therebetween. For example, the fixed scroll (140) can include a fixed plate portion (141), a fixed wrap (142), and a fixed side wall portion (143).

[0069] The fixed plate portion (141) is formed in a disc shape and can be fixed laterally in the low-pressure portion (110a) of the casing (110). A discharge port (1411) and a bypass hole (1412) can be formed to penetrate axially through the central portion of the fixed plate portion (141). Accordingly, the refrigerant compressed in the compression chamber (V) can be discharged to the high-pressure portion (110b), which is a discharge space, through the discharge port (1411), or can be discharged to the high-pressure portion (110b) through the bypass hole (1412) before reaching the discharge port (1411).

[0070] The fixed wrap (142) can extend from the lower surface of the fixed plate portion (141) toward the orbiting scroll (150). The fixed wrap (142) can be formed in various shapes, such as an involute. For example, the fixed wrap (142) can be formed in a logarithmic spiral or in a plurality of circular arc curves.

[0071] However, when the fixed wrap (142) is formed in a logarithmic spiral, the rotating wrap (152) to be described later must also be formed in a logarithmic spiral, so not only is the shape of the rotating shaft coupling part (153) to be described later limited, but the stroke volume may also be reduced at the same wrap height and plate width.

[0072] Accordingly, the fixed wrap (142) according to the present embodiment may be formed in a form in which the wrap curve connects multiple circular arcs with different diameters and origins. Accordingly, the fixed wrap (142) may be formed with different wrap thicknesses along the wrap formation direction.

[0073] For example, the fixed wrap (142) according to the present embodiment may be formed so that the wrap thickness at the discharge end, which is the center, is thicker than the wrap thickness at the suction end, which is the outermost. Accordingly, the wrap strength at the discharge end of the fixed wrap (142), which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142). In addition, the wrap curve of the fixed wrap (142) can be formed wide, so that the stroke volume can be expanded at the same wrap height and plate width. The same applies to the rotating wrap (152) described later.

[0074] In addition, the fixed wrap (142) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In the present embodiment, an example is shown in which the wrap heights of the fixed wrap (142) are different along the wrap formation direction of the fixed wrap (142). For example, in the present embodiment, a fixed step surface (1421) is formed in the middle of the fixed wrap (142), so that the wrap height of the discharge end, which is the center based on the fixed step surface (1421), may be formed lower than the wrap height of the suction end, which is the outermost. Accordingly, the wrap strength of the discharge end of the fixed wrap (142), which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142).

[0075] The fixed step surface (1421) can be formed at a position where the compression chamber (e.g., the first compression chamber) (V1) that starts discharging relatively early among the two compression chambers (V1) (V2) is connected to the discharge port (1411) at the discharge start angle (discharge start time). This also applies to the pivot step surface (1511) described later, which will be described later.

[0076] The fixed side wall portion (143) may be formed in a ring shape by extending axially from the compression surface edge of the fixed plate portion (141) to wrap around the fixed wrap (142). One side of the fixed side wall portion (143) facing the main frame (130) may be fastened to and placed on the scroll support surface (1311) of the main frame (130). Accordingly, the fixed scroll (140) may be axially supported and axially fixed to the main frame (130).

[0077] Referring to FIGS. 1 and 2, the orbiting scroll (150) according to the present embodiment may be coupled to an eccentric portion (1251) of a rotation shaft (125) and provided between a main frame (130) and a fixed scroll (140). Specifically, the orbiting scroll (150) may include a rotation plate portion (151), a rotation wrap (152), a rotation shaft coupling portion (153), and a fuel supply passage (154).

[0078] The pivot plate (151) is formed in a roughly circular shape and can be accommodated on the inner side of the scroll support surface (1311) of the main frame (130). A second key groove (151a) can be formed on one side of the pivot plate (151), that is, on the lower edge facing the main frame (130), so that a second key (173) of an Oldham ring (170) can be inserted. Accordingly, the pivot plate (151) can perform a pivotal movement on the inner side of the scroll support surface (1311) by the Oldham ring (170).

[0079] The pivot plate (151) may be formed with the same thickness, or may be formed with different thicknesses in parts. For example, if the rotation shaft coupling portion (153) of the pivot plate (151) extends only from the rear surface of the pivot plate (151) toward the main frame (130), the pivot plate (151) may be formed with the same thickness throughout. However, if the rotation shaft coupling portion (153) is formed to penetrate the pivot plate (151) and overlap radially with the pivot wrap (152) to be described later, the thickness of the pivot plate (151) may be formed to be thicker in parts, that is, in the part where the rotation shaft coupling portion (153) is formed.

[0080] In this embodiment, an example is shown in which the center side thickness of the pivot plate part (151) is formed thicker than the edge side thickness. Accordingly, the upper surface (compression surface) of the pivot plate part (151) is formed so that the height of the pivot plate part (151) on the discharge side is higher than the height of the pivot plate part (151) on the suction side, centered on the pivot step surface (1511). Through this, the rotary shaft coupling part (153) described later protrudes in the direction toward the fixed plate part (141), so that the gap between the first point of action where the rotational force is applied to the pivot scroll (150) and the second point of action where the compression force is applied is shortened, thereby reducing the overturning moment of the pivot scroll (150).

[0081] The turning step surface (1511) connects the outer surface of the discharge end of the turning wrap (152) and the inner surface of the turning wrap (152) facing it in the radial direction, but, like the fixed step surface (1421) above, it can be formed at a position where the compression chamber (e.g., the first compression chamber) (V1) adjacent to the discharge port (1411) among the compression chambers on both sides communicates with the discharge port (1411) at the discharge start angle (discharge start time).

[0082] In other words, since the discharge port (1411) is formed in an irregular elliptical shape, at the point where the turning step surface (1511) and the fixed step surface (1421) are separated, one end of the turning step surface (1511) (more precisely, the outer side of the turning wrap) can be formed to be connected to or axially overlap a part of the discharge port (1411). Accordingly, at the moment when the turning step surface (1511) is separated from the fixed step surface (1421) during the turning movement of the turning scroll (150), the two compression chambers (V1) (V2) are communicated with each other, and at the same time, one compression chamber (e.g., the first compression chamber) (V1) is communicated with the discharge port (1411). Then, even if the two compression chambers (V1)(V2) are connected, the refrigerant in the two compression chambers (V1)(V2) moves to the discharge port (1411) and is discharged together, thereby suppressing the compression loss in the two compression chambers (V1)(V2).

[0083] In addition, a plurality of fuel supply passages (154) may be formed in the pivot member (151). For example, the plurality of fuel supply passages (154) may be formed by a plurality of fuel holes (1541a)(1541b) penetrating the interior of the pivot member (151) and a plurality of fuel grooves (1542a)(1542b) recessedly formed at the corners of the inner surface of the rotary shaft coupling portion (153) so as to be connected to the plurality of fuel holes (1541a)(1541b), respectively. Accordingly, the plurality of fuel supply passages (154) may penetrate from the inner surface of the rotary shaft coupling portion (153) to the first side (151b) and / or the second side (151c) of the pivot member (151) or to the second key groove (151a). Through this, the oil in the oil supply space (S) described later can be quickly and smoothly supplied to each sliding surface, such as the thrust surface (TS), through a plurality of oil supply passages (154). The oil supply passages (154) will be described again later together with the bushing bearing (155).

[0084] The orbiting wrap (152) according to the present embodiment can extend from the upper surface (compression surface) of the orbiting plate portion (151) toward the fixed scroll (140). Accordingly, the orbiting wrap (152) can be interlocked with the fixed wrap (142) to form two pairs of compression chambers (V1) (V2).

[0085] The orbital wrap (152) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (142). For example, the orbital wrap (152) can be formed in a logarithmic spiral or in a plurality of circular arc curves.

[0086] However, as described above in the fixed wrap (142), when the orbital wrap (152) is formed in a logarithmic spiral, not only is the shape of the rotating shaft coupling portion (153) limited, but the stroke volume may also be reduced at the same wrap height and plate width. Accordingly, the orbital wrap (152) according to the present embodiment, like the fixed wrap (142), may be formed in a form in which the wrap curve connects a plurality of circular arcs having different diameters and origins. Accordingly, the orbital wrap (152), like the fixed wrap (142), may be formed such that the wrap thickness varies along the wrap formation direction.

[0087] For example, the swirl wrap (152) according to the present embodiment may be formed so that the wrap thickness of the discharge end, which is the center, is thicker than that of the suction end, which is the outermost end. Accordingly, the wrap strength of the swirl wrap (152) at the discharge end, which receives a relatively high gas force, can be increased, thereby suppressing damage to the swirl wrap (152). In addition, the wrap curve of the fixed wrap (142) can be formed wide, so that the stroke volume can be expanded at the same wrap height and plate width.

[0088] The orbital wrap (152) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In the present embodiment, an example is shown in which the wrap heights of the orbital wrap (152) are different along the wrap formation direction. For example, the wrap height of the orbital wrap (152) according to the present embodiment may be formed so that the wrap height of the discharge end, which is the center, is lower than the wrap height of the suction end, which is the outermost, based on the orbital step surface (1511). Accordingly, the wrap strength of the orbital wrap (152) at the discharge end, which receives a relatively high gas force, can be increased, thereby suppressing damage to the fixed wrap (142).

[0089] The rotary shaft coupling portion (153) is a portion where the eccentric portion (1251) of the rotary shaft (125) is coupled, and may be formed in a cylindrical shape and may have a bushing bearing (155) provided on the inner surface thereof. Accordingly, the inner surface of the bushing bearing (155) may form the inner surface of the actual rotary shaft coupling portion (153).

[0090] The rotating shaft coupling portion (153) may be formed to be located on the inside of the orbital wrap (152). For example, the inner circumference of the rotating shaft coupling portion (153) may be formed at a position overlapping the discharge end of the orbital wrap (152) when projected in the axial direction. In other words, the outer circumference of the rotating shaft coupling portion (153) may be formed to be located on the same circle as an imaginary circle connecting the outer surface of the discharge end of the orbital wrap (152). Accordingly, the inner surface around the discharge end of the orbital wrap (152) is located inside the outer circumference of the rotating shaft coupling portion (153) as described above, that is, on the front end surface (153a) of the rotating shaft coupling portion (153). Then, the rotary shaft coupling portion (153) is formed to overlap the rotary wrap (152) in the radial direction, and the bearing area of ​​the rotary shaft coupling portion (153) is secured widely to stably support the rotary scroll (150) while forming a compression chamber (V1) (V2) in the front end face (153a) of the rotary shaft coupling portion (153).

[0091] Referring to FIGS. 1 and 2, the back pressure chamber assembly (160) according to the present embodiment may be provided on the main frame (130) so as to be in sliding contact with the orbiting scroll (150). In other words, the back pressure chamber assembly (160) may have a back pressure space portion (162) forming part of the back pressure chamber assembly (160) formed on the thrust support surface (1313) of the main frame (130) facing the orbiting scroll (150). Accordingly, the structure of the back pressure chamber assembly (160) may be simplified, making it easy to manufacture and assemble.

[0092] Specifically, the back pressure chamber assembly (160) may include a back pressure passage (161), a back pressure space (162), and a sealing member (163). The back pressure passage (161) penetrates the orbiting plate (151) to communicate between the compression chamber and the back pressure space (162), the back pressure space (162) is formed in an annular shape to accommodate the back pressure passage (161), and the sealing member (163) is a member provided on an end surface of the back pressure space (162) facing the orbiting scroll (150) to form a back pressure chamber (160a) inside the back pressure space (162). Accordingly, the back pressure chamber assembly (160) forms a back pressure chamber (160a) that is connected to the compression chamber (V) between the main frame (130) and the orbiting scroll (150), thereby pressurizing the orbiting scroll (150) toward the fixed scroll (140).

[0093] The back pressure passage (161) may be formed to penetrate between the axial sides of the pivot plate (151). For example, only one back pressure passage (161) may be formed to communicate with one compression chamber (V1) (V2), or multiple back pressure passages (161) may be formed to communicate with each of the compression chambers (V1) (V2). This embodiment illustrates an example in which only one back pressure passage (161) is formed.

[0094] In this case, one end of the back pressure passage (161) may be formed to penetrate the side of the compression chamber (V1) (V2), and the other end of the back pressure passage (161) may be formed to penetrate the side of the back pressure chamber (160a). Accordingly, the compression chamber (V1) (V2) and the back pressure chamber (160a) are connected to each other through the back pressure passage (161), so that a portion of the refrigerant compressed in the compression chamber (V1) (V2) can quickly move to the back pressure chamber (160a).

[0095] Although not shown in the drawing, a back pressure valve (not shown) that opens and closes the back pressure passage (161) may be provided in the middle of the back pressure passage (161). For example, the back pressure valve may be formed to allow the movement of refrigerant from the compression chamber (V1)(V2) to the back pressure chamber (160a), while blocking the movement of refrigerant from the back pressure chamber (160a) to the compression chamber (V1)(V2). Accordingly, the pressure in the back pressure chamber (160a) can be varied, thereby suppressing pulsating pressure in the back pressure chamber (160a).

[0096] The back pressure space (162) may extend from one side of the main frame (130) facing the orbiting scroll (150), that is, from the thrust support surface (1313) of the main frame (130) toward the orbiting scroll (150). For example, the back pressure space (162) may be formed of a plurality of back pressure guides (1621)(1622) that extend annularly from the thrust support surface (1313) of the main frame (130) and are spaced apart from each other by a preset interval in the radial direction.

[0097] Specifically, the plurality of back pressure guides (1621)(1622) may be formed of an inner back pressure guide (1621) provided on the inner side and an outer back pressure guide (1622) provided on the outer side with the back pressure passage (161) therebetween. Each of the inner back pressure guides (1621) and the outer back pressure guides (1622) may be formed in an annular shape. Accordingly, a back pressure room (160a) may be formed between the inner back pressure guide (1621) and the outer back pressure guide (1622) together with a sealing member (1631)(1632) described later.

[0098] Among the plurality of back pressure guides (1621)(1622), the inner back pressure guide (1621) may be formed radially spaced apart from the inner surface of the rotation shaft coupling portion (153) provided at the center of the pivot plate portion (151) by a preset interval. Accordingly, when the inner back pressure guide (1621) is spaced apart from the outer surface of the rotation shaft (125) by a preset interval, a fuel supply space (S) may be formed between the inner surface of the inner back pressure guide (1621) and the outer surface of the rotation shaft (125). Through this, a portion of the oil sucked in through the oil passage (1252) of the rotating shaft (125) can be stored in the oil supply space (S) between the inner surface of the inner pressure guide (1621) and the outer surface of the rotating shaft (125), so that the oil can be smoothly supplied to the oil supply passage (154) provided inside the rotating scroll (150) while lubricating the space between the orbiting scroll (150) and the sealing member (163).

[0099] In addition, an inner sealing groove (1651) may be formed on the leading surface of the inner pressure guide (1621), and an outer sealing groove (1652) may be formed on the leading surface of the outer pressure guide (1622). An inner sealing member (1631) may be slidably inserted into the inner sealing groove (1651), and an outer sealing member (1632) may be slidably inserted into the outer sealing groove (1652), respectively, in the axial direction. The side walls of the inner sealing member (1631) and the outer sealing member (1632) are pressed against the side walls of the inner sealing groove (1651) and the outer sealing groove (1652), respectively, by the pressure of the fuel supply space (S) and / or the pressure of the back pressure chamber (160a), and the axial side surface of the inner sealing member (1631) and the axial side surface of the outer sealing member (1632) facing the main frame (130) can be pressed against the main frame (130), respectively. Accordingly, the back pressure chamber (160a) provided inside the back pressure space (162) can be sealed.

[0100] Although not shown in the drawing, the back pressure space (162) may be formed in a circular shape that is sunken to a preset depth in the thrust support surface (1313) of the main frame (130). In this case, an inner sealing groove (1651) may be formed in a circular shape on the inner side of the back pressure space (162), and an outer sealing groove (1652) may be formed in a circular shape on the outer side. The inner sealing member (1631) and the outer sealing member (1632) described above may be inserted into these sealing grooves (1651)(1652) so as to be in close contact in the radial direction and movable in the axial direction, respectively.

[0101] In the drawing, the unexplained symbol 118 is a subframe, and 171 is the ring body of the Oldham ring.

[0102] The operational effects of the scroll compressor according to the present embodiment as described above are as follows.

[0103] That is, when power is applied to the driving motor (120) and rotational force is generated, the orbiting scroll (150) eccentrically coupled to the rotation shaft (125) rotates relative to the fixed scroll (140) by the old ring (170). At this time, a first compression chamber (V1) and a second compression chamber (V2) that move continuously are formed between the fixed scroll (140) and the orbiting scroll (150).

[0104] Then, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually narrows as the orbiting scroll (150) moves from the suction port (or suction chamber) (1411) toward the discharge port (or discharge chamber) (1412) while performing the orbiting motion.

[0105] Then, the refrigerant is sucked into the low pressure section (110a) of the casing (110) through the refrigerant suction pipe (115), and a portion of this refrigerant is directly sucked into each of the suction pressure chambers (not shown) forming the first compression chamber (V1) and the second compression chamber (V2) and compressed, while the remaining refrigerant moves toward the drive motor (120), cools the drive motor (120), and is then sucked into the suction pressure chamber (not shown) together with other refrigerants.

[0106] Then, the refrigerant is compressed while moving along the movement path of the first compression chamber (V1) and the second compression chamber (V2). The refrigerant is discharged from the final compression chamber into the upper space (110b) of the casing (110) through the discharge port (1411) of the fixed scroll (140), and the refrigerant is discharged to the outside of the compressor through the refrigerant discharge pipe (116).

[0107] At this time, a portion of the refrigerant compressed in the compression chamber (V1)(V2) moves to the back pressure chamber (160a) of the back pressure chamber assembly (160) provided between the rotating scroll (150) and the main frame (130) through the back pressure passage (161) before reaching the discharge port (1411). Accordingly, the back pressure chamber (160a) forms an intermediate pressure and pushes the sealing member (163) of the back pressure chamber assembly (160) toward the main frame (130).

[0108] Then, the orbiting scroll (150) is pressurized in the direction toward the fixed scroll (140) by the pressure of the back pressure chamber (160a) and rises. Accordingly, as the orbiting scroll (150) is pressed against the fixed scroll (140), it is possible to prevent the refrigerant in the compression chambers (V1) and (V2) on both sides from leaking from the high-pressure side compression chamber forming the intermediate pressure chamber to the low-pressure side compression chamber.

[0109] Meanwhile, the oil stored in the oil storage space (110c) of the casing (110) is sucked up through the oil passage (1252) of the rotary shaft (125), and some of this oil is sprayed from the upper end of the rotary shaft (125) into the internal space of the rotary shaft coupling portion (153). This oil flows down through the inner surface of the rotary shaft coupling portion (153), that is, between the inner surface of the bush bearing (155) and the outer surface of the rotary shaft (125), lubricates the space between the bush bearing (155) and the rotary shaft (125), and then accumulates in the oil supply space (S) between the main frame (130) and the orbiting scroll (150). Some of this oil flows between the sealing member (1631)(1632) forming the back pressure chamber assembly (160) and the orbiting scroll (150) to lubricate the space between the sealing member (1631)(1632) and the orbiting scroll (150), while the other oil lubricates the thrust surface (TS) between the orbiting scroll (150) and the fixed scroll (140) and / or the space between the second key (173) of the Oldham ring (170) and the second key groove (151a) of the orbiting scroll (150) through a plurality of oil supply passages (154) penetrating the orbiting plate (151).

[0110] Fig. 3 is a perspective view of the pivoting scroll according to the present embodiment from the bottom, Fig. 4 is a plan view showing the pivoting scroll of Fig. 3 combined with a main frame, and Fig. 5 is a cross-sectional view along the line “Ⅴ-Ⅴ” of Fig. 4.

[0111] Referring to FIGS. 3 to 5, the fuel supply passage (154) according to the present embodiment may be formed of a plurality of fuel supply holes (1541a) (1541b) and a plurality of fuel supply grooves (1542a) (1542b) as described above. In other words, a first fuel supply groove (1542a) may be formed at a first end of a first fuel supply hole (1541a) facing the rotation shaft coupling portion (153), and a second fuel supply groove (1542b) may be formed at a first end of a second fuel supply hole (1541b). Accordingly, the oil in the oil supply space (S) located lower than the first stage forming the lower side of the turning plate (151), that is, the entrance of the first oil supply hole (1541a) and the second oil supply hole (1541b), can smoothly move to the first oil supply hole (1541a) and the second oil supply hole (1541b) through the first oil supply groove (1542a) and the second oil supply groove (1542b), respectively.

[0112] For example, the first stage forming the entrance of the first oil supply hole (1541a) penetrates into the inner surface of the rotary shaft coupling part (153) through the first oil supply groove (1542a) described later, and the second stage forming the exit of the first oil supply hole (1541a) penetrates into the thrust surface (TS) between the orbiting scroll (150) and the fixed scroll (140), that is, between the first side surface (151b) of the orbiting plate part (151) and one side surface of the fixed side wall part (143) facing it. Accordingly, the oil sucked into the interior of the rotary shaft coupling portion (153) along the oil path (1252) of the rotary shaft (125) is smoothly supplied to the thrust surface (TS) between the orbiting scroll (150) and the fixed scroll (140) through the first oil supply hole (1541a), thereby suppressing the friction loss at the thrust surface (TS) described above.

[0113] In this case, the first end of the first oil supply hole (1541a) can be formed as close as possible to the upper end of the first oil supply groove (1542a) to be described later. Accordingly, the length of the bushing bearing (155) can be formed as long as possible, which can be advantageous in securing a wide bearing area.

[0114] Although not shown in the drawing, the second end of the first oil supply hole (1541a) may be formed to face the main frame (130), i.e., to penetrate the first side surface (151b) of the pivot plate (151). In this case, the second end of the first oil supply hole (1541a) may be formed to face between the main frame (130) and the Oldham ring (170), for example, between the first keyway (1312a) of the main frame (130) and the first key (172) of the Oldham ring (170). Accordingly, during initial operation, oil is quickly supplied between the main frame (130) and the Oldham ring (170), thereby suppressing frictional loss between the main frame (130) and the Oldham ring (170).

[0115] In addition, the first stage forming the entrance of the second fueling hole (1541b) may penetrate the inner surface of the rotary shaft coupling portion (153) through the second fueling groove (1542b) described later, similar to the first stage of the first fueling hole (1541a) described above, and the second stage forming the exit of the second fueling hole (1541b) may penetrate the inner surface of the second key groove (151a) provided on the second side (151c) of the pivot plate portion (151). Accordingly, the oil sucked into the interior of the rotary shaft coupling portion (153) along the oil path (1252) of the rotary shaft (125) is directly supplied between the second key groove (151a) of the rotary plate portion (151) and the second key (173) of the Oldham ring (170) through the second oil supply hole (1541b), thereby suppressing frictional loss between the rotary scroll and the Oldham ring.

[0116] In this case, the second end of the second oil supply hole (1541b) may be formed eccentrically in the opposite direction of the rotational direction of the rotational shaft (125) with respect to the radial center line (CL) of the second keyway (151a). Accordingly, oil can be supplied more quickly and smoothly to the surface where the second keyway (151a) of the orbiting scroll (150) and the second key (173) of the Oldham ring (170) actually come into contact.

[0117] Although not shown in the drawing, a pressure reducing member (not shown) may be inserted into each of the plurality of first oil supply holes (1541a) and the plurality of second oil supply holes (1541b). Accordingly, the high-pressure refrigerant sucked into the rotary shaft coupling portion (153) may be depressurized by each pressure reducing member while passing through each of the oil supply holes (1541a)(1541b) and supplied to the thrust surface (TS) and / or the second keyway (151a). However, if the high-pressure refrigerant sucked into the rotary shaft coupling portion (153) is already depressurized while passing between the inner surface of the rotary shaft coupling portion (bush bearing) (153) and the rotary shaft (eccentric portion) (125), it may not be necessary to provide a separate pressure reducing member in each of the rotary shaft coupling holes (1541a)(1541b).

[0118] Referring to FIGS. 3 to 5, the first refueling groove (1542a) and the second refueling groove (1542b) according to the present embodiment may be recessed at the corner of the rotary shaft coupling portion (153) as described above and may extend axially toward the respective refueling holes (1541a) (1541b). In other words, the first refueling groove (1542a) and the second refueling groove (1542b) may be formed in multiple numbers spaced apart from each other by a preset interval along the circumferential direction so as to independently communicate with the respective refueling holes (1541a) (1541b). Accordingly, while forming the refueling grooves (1542a) (1542b) on the inner surface of the rotary shaft coupling portion (153), processing of the rotary shaft coupling portion (153) may be facilitated.

[0119] In this case, the plurality of oil supply grooves (1542a)(1542b) can be formed to be lower than or equal to the lower end of the bush bearing (155), like the oil supply holes (1541a)(1541b) described above. Accordingly, the width of the inlet side of each oil supply hole (1541a)(1541b) can be expanded by each oil supply groove (1542a)(1542b). Through this, the oil accumulated in the oil supply space (S) between the thrust support surface (1313) of the main frame (130) and the second side surface (151c) of the turning plate (151) facing it can smoothly move to each oil supply hole (1541a)(1541b) through each oil supply groove (1542a)(1542b).

[0120] Specifically, the first oil refueling groove (1542a) and the second oil refueling groove (1542b) may be formed in a shape in which the lower surface facing the main frame (130) and the inner surface facing the rotation shaft (125) are open, and the upper surface facing the fixed scroll (140) and both circumferential side surfaces are closed. Accordingly, as described above, oil accumulated in the oil refueling space (S) can smoothly move to the respective oil refueling holes (1541a) (1541b) through the respective oil refueling grooves (1542a) (1542b).

[0121] In this case, the first oil refueling groove (1542a) may be formed to be larger than or equal to the first oil refueling hole (1541a), and the second oil refueling groove (1542b) may be formed to be larger than or equal to the second oil refueling hole (1541b). For example, the circumferential width of the first oil refueling groove (1542a) may be formed to be larger than the inner diameter of the first oil refueling hole (1541a), and the circumferential width of the second oil refueling groove (1542b) may be formed to be larger than the inner diameter of the second oil refueling hole (1541b). Accordingly, as described above, the oil accumulated in the oil refueling space (S) can move more smoothly to the respective oil refueling holes (1541a) (1541b) through the respective oil refueling grooves (1542a) (1542b).

[0122] Although not shown in the drawing, the oil supply groove may be formed as a single ring so as to be connected to each of the oil supply holes (1541a)(1541b) in a single manner. In this case, the volume of the oil supply groove increases, allowing the oil in the oil supply space (S) to move more quickly and smoothly to each of the oil supply holes (1541a)(1541b).

[0123] As described above, since the first oil supply groove (1542a) is formed in the first stage of the first oil supply hole (1541a) and the second oil supply groove (1542b) is formed in the first stage of the second oil supply hole (1541b) so as to open toward the oil supply space (S), the oil accumulated in the oil supply space (S) can smoothly move to the first oil supply hole (1541a) and the second oil supply hole (1541b) through the respective oil supply grooves (1542a)(1542b). Through this, in the rotary back pressure method, the rotary shaft coupling part (153) is formed to be sunken so as to overlap the rotary wrap (152) in the radial direction, while simplifying the path of the oil supply passage (154), so as to smoothly supply oil to each sliding surface.

[0124] In this case, since the lower surface of the bushing bearing (155) inserted into the rotary shaft coupling portion (153) is formed so as not to radially interfere with the first oil supply groove (1542a) and / or the second oil supply groove (1542b) forming the entrance of the oil supply hole (1541a)(1541b), the oil in the oil supply space (S) can smoothly move to the first oil supply hole (1541a) and / or the second oil supply hole (1541b) through the first oil supply groove (1542a) and / or the second oil supply groove (1542b).

[0125] In this way, since the oil supply passage connecting the rotary shaft coupling portion (153) and the sliding surface in the rotary back pressure method is formed to penetrate the rotary plate portion (151) on the inner surface of the rotary shaft coupling portion (153) to the first side (or second side) (151b) and / or the second keyway (151a), the oil supply passage (154) can be simplified as described above, thereby reducing the manufacturing cost for the rotary scroll (150).

[0126] In addition, since the lower surface of the bushing bearing (155) is formed flat and spaced apart from the first oil refueling groove (1542a) and / or the second oil refueling groove (1542b) forming the entrance of the oil refueling passage (154), the length of the oil refueling passage (154) can be formed as short as possible. Accordingly, while simplifying the manufacturing of the oil refueling passage (154), the oil refueling passage (154) can be formed as short as possible, thereby suppressing frictional loss due to delayed oil refueling.

[0127] In addition, since the rotating shaft coupling portion (153)(153) is formed to overlap the orbiting wrap (152) in the radial direction and a part of the orbiting wrap (152) is extended to the front end face (153a) of the rotating shaft coupling portion (153), a compression chamber (V) can be formed at the center of the orbiting scroll (or fixed scroll) (150). Through this, as the rotating shaft coupling portion (153) is extended toward the orbiting wrap (152), the compression cycle of the compression chamber (V) is lengthened, thereby increasing the compression ratio and improving the volumetric efficiency. In addition, the wrap height at the discharge end of the orbiting wrap (152) is lowered and the wrap thickness is thickened, so that the wrap strength of the orbiting wrap (152) is increased, thereby suppressing wrap breakage. The same applies to the fixed wrap (142).

[0128] Meanwhile, there are other examples of bushing bearings as follows.

[0129] That is, in the embodiment described above, the lower end of the bushing bearing is formed to be higher than or equal to the entrance of the fuel passage, but in some cases, the lower end of the bushing bearing may be formed to be lower than the entrance of the fuel passage.

[0130] FIG. 6 is a perspective view of a bottom view of an orbiting scroll having a bush bearing of another embodiment, FIG. 7 is a cross-sectional view showing a lubrication passage of the orbiting scroll in FIG. 6, FIG. 8 is a perspective view of a bottom view of an orbiting scroll having a bush bearing of another embodiment, and FIG. 9 is a cross-sectional view showing a lubrication passage of the orbiting scroll in FIG. 8.

[0131] Referring to FIGS. 6 to 9, the scroll compressor according to the present embodiment has a back pressure chamber assembly (160) provided between the main frame (130) and the orbiting scroll (150), but the basic configuration and the resulting operational effects of the orbiting scroll (150) are almost the same. For example, the orbiting scroll (150) may have an orbiting wrap (152) formed on the first side (151b) of the orbiting plate portion (151), and a rotating shaft coupling portion (153) formed to be recessed by a preset depth in the direction from the second side (151c) of the orbiting plate portion (151) toward the first side (151b). Accordingly, the rotary shaft coupling part (153) overlaps the orbiting wrap (152) in the radial direction, so that the gap between the point of application where the rotational force is applied to the orbiting scroll (150) and the point of application where the compressive force is applied is narrowed, thereby stabilizing the behavior of the orbiting scroll (150).

[0132] In addition, a bushing bearing (155) may be formed to be press-fitted onto the inner surface of the rotary shaft coupling portion (153), but may be formed so as not to interfere radially with the lubrication passage (154) penetrating the pivot plate portion (151). In other words, the inner surface of the rotary shaft coupling portion (153) may be formed so that the lower surface and inner surface of each lubrication groove (1542a) (1542b) connected to a plurality of lubrication holes (1541a) (1541b) are open, but the bushing bearing (155) facing these lubrication grooves (1542a) (1542b) may be formed so as not to block the lower surface or inner surface of the lubrication groove (1542a) (1542b). Accordingly, the oil stored in the oil supply space (S) between the main frame (130) and the rotating scroll (150) can move quickly and smoothly to each oil supply hole (1541a) (1541b) without being blocked by the bush bearing (155).

[0133] However, as shown in FIGS. 6 and 7, in the present embodiment, the lower end of the bush bearing (155) may be formed to be identical or nearly identical to the second side edge of the pivot plate portion (151) forming the lower end of the rotary shaft coupling portion (153). In other words, the lower end of the bush bearing (155) may be formed to have a length that radially overlaps the plurality of oil supply grooves (1542a) (1542b) forming the entrance of the oil supply passage (154), and a plurality of communication grooves (155a) (155b) may be formed in the portions radially facing the plurality of oil supply grooves (1542a) (1542b).

[0134] For example, the flue groove (155a)(155b) may be formed in a rough manner at the bottom of the bushing bearing (155) facing the main frame (130), and the cross-sectional area of ​​the flue groove (155a) may be formed to be larger than or equal to the cross-sectional area of ​​the lubricating groove (1542a)(1542b) so that the lubricating groove (1542a)(1542b) is accommodated inside the flue groove (155a)(155b). In this case, the center of the lubricating groove (1542a)(1542b) and the center of the flue groove (155a)(155b) may be formed to be positioned on the same line. Accordingly, the entirety of the refueling groove (1542a)(1542b) is accommodated inside each of the communication grooves (155a)(155b), thereby preventing the refueling passage (154) including the refueling groove (1542a)(1542b) from being covered by the bushing bearing (155).

[0135] In the case where the lower surface of the bush bearing (155) is extended to the lower end of the rotary shaft coupling portion (153) as described above and a communication groove (155a)(155b) is formed on the lower surface of the bush bearing (155), oil can smoothly move from the oil supply space (S) to the oil supply hole (1541a)(1541b) and / or the oil supply groove (1542a)(1542b), while the bearing area of ​​the bush bearing (155) can increase. Accordingly, the bearing area of ​​the bush bearing (155) can be expanded as much as possible while the oil supply hole (1541a)(1541b) and / or the oil supply groove (1542a)(1542b) is formed on the inner surface of the rotary shaft coupling portion (153). This can suppress the increase in surface pressure in the bushing bearing (155), thereby reducing the friction loss between the rotating shaft (125) and the bushing bearing (155).

[0136] In addition, as shown in FIGS. 8 and 9, the bushing bearing (155) according to the present embodiment may be formed so that its lower surface is flat without a communication groove and extends almost identically to the lower surface of the rotary shaft coupling portion (153). In other words, on the inner surface of the rotary shaft coupling portion (153), a plurality of lubrication grooves (1542a) (1542b) are formed on the lower surface of the rotary shaft coupling portion (153), and the lower surface and the inner surface are open, as in the embodiments of FIG. 3 described above. However, the inner surface of the lubrication grooves (1542a) (1542b) may be blocked by the bushing bearing (155).

[0137] However, even in this case, the lower surfaces of the plurality of oil supply grooves (1542a)(1542b) may be opened to communicate with the oil supply space (S) between the main frame (130) and the rotating scroll (150). Accordingly, the oil in the oil supply space (S) may smoothly move to each oil supply hole (1541a)(1541b) through the lower surfaces of the opened oil supply grooves (1542a)(1542b).

[0138] Even when the lower surface of the bush bearing (155) is extended to the lower end of the rotary shaft coupling portion (153) as described above, oil can be smoothly transferred to the oil supply hole (1541a)(1541b) through the oil supply groove (1542a)(1542b) while the bearing area of ​​the bush bearing (155) can be increased.

[0139] In addition, in this case, unlike the embodiment 6 described above, since the uneven communication groove (155a) (155b) is excluded from the lower part of the bush bearing (155), damage such as scratches between the inner surface of the bush bearing (155) and the rotation shaft (125) can be suppressed, thereby increasing reliability.

[0140] Meanwhile, there are other embodiments of the back pressure chamber assembly as follows.

[0141] That is, in the above-described embodiment, the back pressure chamber assembly is formed on the main frame facing the orbiting scroll, but in some cases, the back pressure chamber assembly may be formed on the orbiting scroll facing the main frame.

[0142] Fig. 10 is a cross-sectional view showing a portion of a scroll compressor to which another embodiment of a back pressure chamber assembly is applied.

[0143] Referring to FIG. 10, the back pressure chamber assembly (160) according to the present embodiment is provided between the main frame (130) and the orbiting scroll (150), and may be formed on the second side surface (151c) of the orbiting plate portion (151) facing the main frame (130). For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so as to be able to orbit together with the orbiting scroll (150), and the back pressure space portion (162) forming a part of the back pressure chamber assembly (160) may extend as a single body from the rear surface of the orbiting plate portion (151) facing the main frame (130) toward the main frame (130).

[0144] In addition, a floating member (165) is slidably inserted into the back pressure space (162), and the floating member (165) can form a sealed back pressure chamber (160a) inside the back pressure space (162) by connecting a plurality of first sliding members (1651) forming the side surfaces thereof to each other by a second sliding member (1652). Accordingly, even if the floating member (165) moves along the back pressure guides (1621)(1622) on both sides forming the back pressure space (162), the inside of the back pressure space (162) forming the back pressure chamber (160a) can be sealed by the floating member (165).

[0145] In this case, a lubrication passage (154) comprising a lubrication hole (1541a)(1541b) and a lubrication groove (1542a)(1542b) may be formed in the orbiting scroll (151). These lubrication holes (1541a)(1541b) and the lubrication groove (1542a)(1542b) as well as the bushing bearing (155) are the same as those in the embodiments of FIGS. 5, 7 and 9 described above, and therefore, the description thereof will be replaced with the description of the embodiments described above.

[0146] As described above, the back pressure chamber assembly (160) is provided on the orbiting scroll (150), and the back pressure chamber assembly (160) can perform a rotational movement together with the orbiting scroll (150). Accordingly, the back pressure area of ​​the back pressure chamber assembly (160) can be expanded.

[0147] In addition, the opening side of the back pressure space portion (162) forming part of the back pressure chamber assembly (160) may be blocked by a floating member (165) that is slidably coupled to the back pressure space portion (162). Accordingly, it is possible to effectively prevent the refrigerant in the back pressure chamber (160a) from leaking into the low pressure portion (110a).

[0148] Although not illustrated in the drawing, the back pressure space (162) may be inserted into and joined to the orbiting scroll. In this case, the back pressure space (162) may be formed of a lightweight material and / or a low-hardness material. This reduces the weight of the orbiting scroll, including the back pressure space (162), while simultaneously suppressing wear between the back pressure space (162) and the floating member (165), thereby enhancing reliability.

Claims

1. Casing; A main frame fixed inside the above casing; A fixed scroll coupled to the above mainframe; An orbiting scroll having a pivot plate provided between the main frame and the fixed scroll, an orbiting wrap provided on a first side of the orbiting plate facing the fixed scroll to form a compression chamber together with the fixed wrap of the fixed scroll, and a rotation shaft coupling portion recessed from a second side of the orbiting plate facing the main frame toward the first side and radially overlapping with the orbiting wrap; and It includes a back pressure chamber assembly provided between the above-mentioned orbiting scroll and the above-mentioned main frame facing it, and pressurizes the above-mentioned orbiting scroll toward the above-mentioned fixed scroll. Inside the above-mentioned pivot plate, A scroll compressor in which at least one fuel supply passage is formed through the inner surface of the above-mentioned rotary shaft coupling.

2. In paragraph 1, A bushing bearing is press-fitted into the inside of the above-mentioned rotary shaft joint, The above bushing bearing, A scroll compressor spaced apart in the axial direction of the rotating shaft from one end of the above fuel passage.

3. In paragraph 2, The above refueling route is, a fueling hole penetrating the above pivot plate; and It includes a refueling groove provided at the inner peripheral edge of the above-mentioned rotary shaft coupling part and through which one end of the refueling hole is connected, The above bushing bearing, A scroll compressor in which an axial cross-section adjacent to the above-mentioned oil supply groove is formed flat and spaced apart from the above-mentioned oil supply groove in the axial direction of the above-mentioned rotating shaft.

4. In paragraph 1, A bushing bearing is press-fitted into the inside of the above-mentioned rotary shaft joint, and a sunken communication groove is formed in the cross-section of the bushing bearing. The above-mentioned chimney, A scroll compressor connected to one end of the above fuel supply passage.

5. In paragraph 4, The above refueling route is, a fueling hole penetrating the above pivot plate; and It includes a refueling groove provided at the inner peripheral edge of the above-mentioned rotary shaft coupling part and through which one end of the refueling hole is connected, The above-mentioned chimney, A scroll compressor formed to accommodate the above-mentioned fuel refueling groove.

6. In paragraph 1, A bushing bearing is press-fitted into the inside of the above-mentioned rotary shaft joint, The above bushing bearing, A scroll compressor radially overlapping one end of the above fuel passage.

7. In paragraph 6, The above refueling route is, a fueling hole penetrating the above pivot plate; and It includes a refueling groove provided at the inner peripheral edge of the above-mentioned rotary shaft coupling part and through which one end of the refueling hole is connected, The above refueling home is, A scroll compressor radially rotated by the above bushing bearing.

8. In paragraph 1, The other end of the above fueling route is A scroll compressor that penetrates at least one of the first and second sides of the above-mentioned rotating plate.

9. In paragraph 1, A second keyway is formed on the second side of the above-mentioned pivot plate to be slidably engaged with the key of the Oldham ring. The other end of the above fueling route is A scroll compressor that penetrates the inner surface of the second key home.

10. In paragraph 9, The other end of the above fueling route is A scroll compressor formed eccentrically in the opposite direction of rotation of the rotation shaft based on the radial center line of the second keyway.

11. In any one of paragraphs 1 to 10, The above pressure chamber assembly is, A scroll compressor provided on one side of the main frame facing the above-mentioned rotating scroll.

12. In paragraph 11, The above pressure chamber assembly is, A pressure relief passage penetrating the rotating scroll to communicate with the compression chamber; A pressure relief space formed in an annular shape to accommodate the pressure relief passage; and It includes a sealing member provided on the end surface of the back pressure space portion facing the above-mentioned rotating scroll and forming a back pressure room inside the back pressure space portion. The above refueling route is, A scroll compressor formed by being spaced apart by a preset interval from one side of the above-mentioned pressure passage.

13. In any one of paragraphs 1 to 10, The above pressure chamber assembly is, A scroll compressor provided on one side of the above-mentioned rotating scroll facing the above-mentioned main frame.

14. In paragraph 13, The above pressure chamber assembly is, A pressure relief passage penetrating the rotating scroll to communicate with the compression chamber; A pressure relief space formed in an annular shape to accommodate the pressure relief passage; and It includes a floating member that is slidably connected to the above pressure relief space to form a pressure relief chamber inside the pressure relief space, The above refueling route is, A scroll compressor formed by being spaced apart by a preset interval from one side of the above-mentioned pressure passage.

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