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 back pressure chamber assembly may be provided on one surface of the orbiting scroll facing the main frame, thereby increasing the sealing force between the main frame and the orbiting scroll so as to effectively prevent the refrigerant from leaking out of the back pressure chamber or stop the refrigerant from entering the back pressure chamber, such that losses induced by suction and / or compression can be suppressed. In addition, the back pressure chamber may have a wide area so as to support the orbiting scroll with greater stability.

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 (US2007 / 0092390 A1) discloses a low-pressure scroll compressor with an orbiting back pressure system. In scroll compressors such as Patent Document 1, a back pressure chamber is formed in the main frame facing the orbiting scroll. The sealing member forming the back pressure chamber may be separated from the orbiting scroll, potentially causing refrigerant leakage in the back pressure chamber. This can cause relatively high-temperature refrigerant to heat the refrigerant being sucked into the compression chamber, resulting in suction loss. In the case of high-pressure compressors, refrigerant from the high-pressure section forming the discharge space may flow into the back pressure chamber, causing the pressure in the back pressure chamber to excessively increase, potentially resulting in frictional loss between the fixed scroll and the orbiting scroll. Furthermore, since the back pressure chamber is formed in the main frame in Patent Document 1, the orbiting scroll moves relative to the main frame, which can limit the area of ​​the back pressure chamber. Furthermore, the small volume of the back pressure chamber can result in pulsating pressure.

[0006] Patent Document 2 (US2015 / 0345493 A1) discloses a low-pressure, fixed-back pressure scroll compressor. Scroll compressors like Patent Document 2 advantageously secure a large back pressure chamber area by forming the back pressure chamber on the back surface of a fixed, non-orbiting scroll. However, Patent Document 2 requires the addition of numerous components to form the back pressure chamber on the back surface of the fixed scroll, which may increase manufacturing costs.

[0007] The purpose of the present invention is to provide a scroll compressor that can prevent refrigerant from leaking from the back pressure chamber or high-pressure medium from flowing into the back pressure chamber by increasing the sealing force of the back pressure chamber.

[0008] Another object of the present invention is to provide a scroll compressor capable of stably supporting an orbiting scroll by expanding the area of ​​a back pressure chamber.

[0009] Another object of the present invention is to provide a scroll compressor capable of reducing pulsating pressure within the back pressure chamber by increasing the volume of the back pressure chamber.

[0010] Another object of the present invention is to provide a scroll compressor capable of reducing manufacturing costs by simplifying a back pressure chamber assembly that provides a close contact between an orbiting scroll and a fixed scroll.

[0011] Another object of the present invention is to provide a scroll compressor capable of securing suction volume while increasing wrap strength.

[0012] In order to achieve the object of the present invention, the refrigerant compressor 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 fixed scroll may be coupled to one side of the main frame. The orbiting scroll may be provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll. The back pressure chamber assembly may be provided between the orbiting scroll and the main frame facing it to pressurize the orbiting scroll toward the fixed scroll. The back pressure chamber assembly may be provided on one side of the orbiting scroll facing the main frame. Through this, the back pressure chamber assembly increases the sealing force between the main frame and the orbiting scroll, effectively blocking refrigerant leakage from the back pressure chamber or inflow into the back pressure chamber, thereby suppressing suction loss and / or compression loss. In addition, by securing a large area of ​​the back pressure chamber, the rotating scroll can be supported more securely.

[0013] For example, the pressure relief chamber assembly may include a pressure relief passage, a pressure relief space, and a floating member. The pressure relief passage may pass through the orbiting scroll to communicate with the compression chamber. The pressure relief space may be formed in an annular shape to accommodate the pressure relief passage. The floating member may be slidably coupled to the pressure relief space to form a pressure relief chamber together with the pressure relief space. Through this, the opening side of the pressure relief space may be sealed, thereby sealing the pressure relief chamber more effectively.

[0014] For example, the back pressure space portion may be formed of a plurality of back pressure guides that are radially spaced apart from one side of the rotating scroll facing the main frame and protrude toward the main frame by a preset height. This allows the volume of the back pressure room to be secured as large as possible, thereby reducing the pulsating pressure in the back pressure room.

[0015] In addition, the back pressure space portion may be formed by being sunken to a predetermined depth on one side of the orbiting scroll facing the main frame. Through this, it is possible to form a back pressure space portion in the orbiting scroll while suppressing an increase in the weight of the orbiting scroll, and to further stabilize the behavior of the orbiting scroll by reducing the gap between the orbiting scroll and the main frame facing it.

[0016] In addition, the above-mentioned back pressure space portion can be formed as a single body in the above-mentioned orbiting scroll. Through this, the orbiting scroll can be easily formed while forming the back pressure space portion in the orbiting scroll.

[0017] In addition, the above-mentioned back pressure space portion can be formed by being assembled to the above-mentioned orbiting scroll. Through this, the back pressure space portion can be formed in the orbiting scroll while increasing the degree of freedom in design for the back pressure space portion.

[0018] Specifically, the floating member may be formed of a lighter material than the orbiting scroll. The back pressure space may be formed of a material having a lower hardness than the orbiting scroll. Through this, not only can the weight of the orbiting scroll be suppressed while forming the back pressure space in the orbiting scroll, but also the frictional loss between the back pressure space and the floating member can be reduced.

[0019] In addition, the floating member may include a plurality of first sliding portions and a second sliding portion. The plurality of first sliding portions may be slidably coupled to an inner wall surface of the back pressure space. The second sliding portion may connect the plurality of first sliding portions to form the back pressure room and may be in sliding contact with the main frame. Through this, the back pressure space may be formed in the orbiting scroll while sealing the back pressure space, thereby preventing refrigerant from leaking from the back pressure room or from flowing into the back pressure room.

[0020] Specifically, the height of the plurality of first sliding sections may be formed to be less than or equal to the depth of the back pressure space section. Through this, the cross-section of the first sliding section is separated from the pivot plate section to form a back pressure surface, thereby maximizing the back pressure area within the back pressure chamber.

[0021] Specifically, a sealing member may be provided between the inner walls of both sides of the plurality of first sliding sections and the back pressure space section facing them. This seals the gap between the back pressure space section and the floating member, thereby more effectively sealing the back pressure chamber.

[0022] Specifically, the second sliding member may have a lubrication groove formed on a surface facing the main frame. This allows for smooth lubrication between the main frame and the floating member facing it, thereby suppressing frictional loss between the main frame and the back pressure chamber assembly.

[0023] In another embodiment, the back pressure chamber assembly may include a back pressure passage, a back pressure space, a plurality of sealing grooves, and a plurality of sealing members. The back pressure passage may pass through 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 plurality of sealing grooves may be formed in an annular shape on both radial sides of the back pressure space. The plurality of sealing members may be respectively inserted into the plurality of sealing grooves to form a back pressure chamber inside the back pressure space. Through this, the frictional area between the sealing members and the main frame may be reduced, thereby lowering the frictional loss between the back pressure chamber assembly and the main frame.

[0024] For example, the back pressure space portion may be formed of a plurality of back pressure guides that are spaced apart radially from one side of the orbiting scroll facing the main frame and protrude toward the main frame by a preset height. The sealing groove portion may be formed on each end surface of the plurality of back pressure guides. Through this, the friction area between the sealing member and the main frame can be reduced while ensuring the volume of the back pressure chamber as large as possible, thereby lowering the pulsating pressure in the back pressure chamber.

[0025] In addition, the back pressure space portion may be formed by being sunken to a predetermined depth on one side of the orbiting scroll facing the main frame. The sealing groove portion may be formed on the inner and outer periphery sides of the back pressure space portion, respectively. Through this, the friction area between the sealing member and the main frame can be reduced, while suppressing an increase in the weight of the orbiting scroll, and at the same time reducing the gap between the orbiting scroll and the main frame facing it.

[0026] In another embodiment, the orbiting scroll may include an orbiting plate portion, an orbiting wrap, and a rotating shaft coupling portion. The orbiting plate portion may be provided between the main frame and the fixed scroll. The orbiting wrap may extend from one side of the orbiting plate portion to form a compression chamber together with the fixed wrap of the fixed scroll. The rotating shaft coupling portion may overlap the orbiting wrap and the rotating shaft in a radial direction at the center of the orbiting plate portion and extend in the axial direction of the rotating shaft. A portion of the orbiting wrap may extend to a front end surface of the rotating shaft coupling portion facing the fixed scroll. As a result, the distance between the bearing reaction force and the gas reaction force acting on the orbiting scroll is reduced, thereby reducing the overturning moment for the orbiting scroll, thereby stabilizing the behavior of the orbiting scroll, suppressing leakage between compression chambers, and simultaneously lowering the back pressure, thereby reducing frictional loss between scrolls. At the same time, a compression chamber can be formed in the center of the rotating scroll, thereby increasing the compression ratio and improving the volumetric efficiency.

[0027] For example, the pivoting plate portion may be provided with a pivoting step surface between the outer surface of the pivoting wrap and the inner surface of the pivoting wrap facing it, and the fixed wrap may be provided with a fixed step surface corresponding to the pivoting step surface. The pivoting step surface and the fixed step surface may be spaced apart from each other at the discharge start angle of at least one compression chamber among the two compression chambers. Through this, even if the pivoting step surface and the fixed step surface are spaced apart and leakage occurs between the two compression chambers, the compression loss due to leakage between the compression chambers can be substantially suppressed because the compression chambers are connected to the discharge port.

[0028] 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 back pressure chamber assembly may be provided on one side of the orbiting scroll facing the main frame. Accordingly, the back pressure chamber assembly increases the sealing force between the main frame and the orbiting scroll, effectively preventing refrigerant from leaking from the back pressure chamber or from flowing into the back pressure chamber, thereby suppressing suction loss and / or compression loss. Furthermore, the back pressure chamber area is secured to be larger, thereby more securely supporting the orbiting scroll.

[0029] A scroll compressor according to the present invention comprises a back pressure chamber assembly including a back pressure passage, a back pressure space, and a floating member, wherein the floating member is slidably coupled to the back pressure space to form a back pressure chamber together with the back pressure space. Through this, the opening side of the back pressure space can be sealed, thereby sealing the back pressure chamber more effectively.

[0030] According to the present invention, a scroll compressor comprises a floating member forming a portion of a back pressure chamber assembly, which includes a plurality of first sliding portions and a plurality of second sliding portions, wherein the plurality of first sliding portions are slidably coupled to an inner wall surface of a back pressure chamber, and the second sliding portion can be in sliding contact with a main frame by connecting the plurality of first sliding portions. Through this, a back pressure chamber can be formed in an orbiting scroll while sealing the back pressure chamber, thereby preventing refrigerant from leaking from the back pressure chamber or from flowing into the back pressure chamber.

[0031] A scroll compressor according to the present invention comprises a back pressure chamber assembly including a back pressure passage, a back pressure space, a plurality of sealing grooves, and a plurality of sealing members, wherein the plurality of sealing members are respectively inserted into the plurality of sealing grooves to form a back pressure chamber within the back pressure space. Through this, the frictional area between the sealing members and the main frame can be reduced, thereby lowering the frictional loss between the back pressure chamber assembly and the main frame.

[0032] A scroll compressor according to the present invention comprises an orbiting scroll including an orbiting plate, an orbiting wrap, and a rotating shaft coupling, wherein the rotating shaft coupling extends axially along the rotational axis so as to radially overlap the orbiting wrap at the center of the orbiting plate, and a portion of the orbiting wrap may extend to a front end surface of the rotating shaft coupling facing the fixed scroll. This reduces the distance between the bearing reaction force and the gas reaction force acting on the orbiting scroll, thereby reducing the overturning moment for the orbiting scroll, thereby stabilizing the behavior of the orbiting scroll, suppressing leakage between compression chambers and lowering the back pressure, thereby reducing frictional loss between scrolls. At the same time, a compression chamber is formed up to the center of the orbiting scroll, thereby increasing the compression ratio and improving volumetric efficiency.

[0033] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0034] Figure 2 is a perspective view showing the disassembled back pressure chamber assembly in Figure 1.

[0035] Figure 3 is a plan view showing the assembled pressure chamber assembly in Figure 2.

[0036] Figure 4 is a cross-sectional view taken along the line “Ⅳ-Ⅳ” of Figure 3.

[0037] FIG. 5 and FIG. 6 are cross-sectional views showing the operation of the pressure chamber assembly according to the present embodiment, with FIG. 5 showing the operation during stop and / or start, and FIG. 6 showing the operation during normal operation.

[0038] Figure 7 is an exploded perspective view of another embodiment of the pressure chamber assembly.

[0039] Fig. 8 is a cross-sectional view showing the assembled pressure chamber assembly of Fig. 7.

[0040] Figure 9 is an exploded perspective view of another embodiment of the pressure chamber assembly.

[0041] Fig. 10 is a cross-sectional view showing the assembled pressure chamber assembly of Fig. 9.

[0042] Figure 11 is an exploded perspective view of another embodiment of the pressure chamber assembly.

[0043] Fig. 12 is a cross-sectional view showing the assembled pressure chamber assembly of Fig. 11.

[0044] Figures 13 and 14 are exploded perspective views of further embodiments of the pressure chamber assembly.

[0045] Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0046] 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.

[0047] 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.

[0048] 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.

[0049] 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.

[0050] 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.

[0051] 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.

[0052] Figure 1 is a longitudinal cross-sectional view showing a scroll compressor according to the present invention.

[0053] 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.

[0054] The casing (110) may include a cylindrical shell (111), an upper cap (112), and a lower cap (113).

[0055] 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 (117), 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).

[0056] 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.

[0057] 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.

[0058] 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.

[0059] 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).

[0060] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0061] 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).

[0062] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0063] 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.

[0064] 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).

[0065] 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.

[0066] Referring to FIG. 1, the main frame (130) according to the present embodiment may include a main flange portion (131) and an axial support portion (132).

[0067] 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).

[0068] 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).

[0069] 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).

[0070] 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.

[0071] 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).

[0072] 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.

[0073] The thrust support surface (1313) is a portion where the floating member (163) of the back pressure chamber assembly (160) to be described later is settled and slides, and can be formed flat like the old ring support surface (1312). Accordingly, the floating member (163) of the back pressure chamber assembly (160) to be described later is axially supported on the thrust support surface (1313) and can smoothly rotate.

[0074] In addition, the thrust support surface (1313) may be formed at the same height as the Oldham ring support surface (1312), or may be formed higher or lower than the Oldham ring support surface (1312). This embodiment illustrates an example in which the thrust support surface (1313) is formed higher than the Oldham ring support surface (1312). Accordingly, the axial length of the back pressure guide (1621)(1622) described later can be minimized, thereby reducing the weight of the orbiting scroll (150).

[0075] 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).

[0076] 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).

[0077] 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).

[0078] 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.

[0079] 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.

[0080] 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.

[0081] 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.

[0082] 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).

[0083] 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.

[0084] 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).

[0085] Referring to FIG. 1, 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 the main frame (130) and the fixed scroll (140). Specifically, the orbiting scroll (150) may include a rotation plate portion (151), a rotation wrap (152), and a rotation shaft coupling portion (153).

[0086] 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).

[0087] 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.

[0088] 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).

[0089] 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).

[0090] 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).

[0091] The orbiting wrap (152) can extend from the upper surface (compression surface) of the orbiting plate (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).

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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).

[0096] 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 be provided with an eccentric bearing formed as a bushing bearing on the inner surface. For convenience, the bushing bearing is defined as the inner surface of the rotary shaft coupling portion (153) and explained below. Accordingly, the inner surface of the rotary shaft coupling portion (153) can be understood to substantially refer to the inner surface of the bushing bearing.

[0097] 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).

[0098] FIG. 2 is a perspective view showing the disassembled back pressure chamber assembly of FIG. 1, FIG. 3 is a plan view showing the assembled back pressure chamber assembly of FIG. 2, FIG. 4 is a cross-sectional view taken along line “Ⅳ-Ⅳ” of FIG. 3, and FIGS. 5 and 6 are cross-sectional views showing the operation of the back pressure chamber assembly according to the present embodiment, with FIG. 5 showing the operation during stop and / or start, and FIG. 6 showing the operation during normal operation, respectively.

[0099] Referring to FIGS. 1 to 4, the back pressure chamber assembly (160) according to the present embodiment may be provided on the back surface of the orbiting scroll (150), that is, on one side facing the main frame (130). Accordingly, the back pressure of the back pressure chamber (160a) (more precisely, the force exerted by the back pressure on the back pressure chamber) acts on the orbiting scroll (150). In other words, the orbiting scroll (150) is pushed in the direction toward the fixed scroll (140) by the back pressure to seal between the two compression chambers (V1) (V2).

[0100] Specifically, the back pressure chamber assembly (160) may include a back pressure passage (161), a back pressure space (162), and a floating member (163). The back pressure passage (161) is a passage connecting the compression chamber (V) and the back pressure chamber (160a), the back pressure space (162) is a space forming the back pressure chamber (160a), and the floating member (163) is a member that seals the back pressure chamber (160a). Accordingly, the back pressure chamber assembly (160) may have a variable back pressure chamber volume as the floating member (163) slides depending on the pressure difference between the compression chamber (V) and the back pressure chamber (160a).

[0101] 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.

[0102] 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).

[0103] 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 lowering or suppressing the pulsating pressure in the back pressure chamber (160a).

[0104] The back pressure space (162) may extend from one side of the turning plate (151), that is, from the back surface of the turning plate (151) facing the main frame (130), toward the main frame (130). For example, the back pressure space (162) may be formed of a plurality of back pressure guides (1621)(1622) that extend in an annular shape from the back surface of the turning plate (151) and are spaced apart from each other by a preset interval in the radial direction. Accordingly, the volume of the back pressure room (160a) can be secured as large as possible without increasing the thickness of the turning plate (151), while lowering or suppressing the pulsating pressure in the back pressure room (160a).

[0105] 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 floating member (163) to be described later.

[0106] Among the plurality of back pressure guides (1621)(1622), the inner back pressure guide (1621) may be formed to be spaced apart from the inner surface of the rotation shaft coupling portion (153) provided at the center of the pivot plate portion (151) in the radial direction 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, an oil supply passage (P) 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 through the oil passage (1252) of the rotation shaft (125) may be supplied between the inner surface of the inner back pressure guide (1621) and the outer surface of the rotation shaft (125) to a floating member (163) to be described later and the main frame (130) facing it.

[0107] Among the plurality of back pressure guides (1621)(1622), the outer back pressure guide (1622) may be formed at a position spaced apart from the outer surface of the orbiting plate (151) by a preset distance. Accordingly, the second key groove (151a) described above may be formed between the outer surface of the outer back pressure guide (1622) and the outer surface of the orbiting plate (151). In other words, the outer back pressure guide (1622) may be formed as wide as possible while forming the second key groove (151a) in the orbiting plate (151). Accordingly, when the back pressure room (160a) defined including the outer back pressure guide (1622) is provided in the orbiting scroll (150) that performs the orbiting movement, the actual area of ​​the back pressure room (160a) is secured widely, so that the orbiting scroll (150) can be stably supported.

[0108] A plurality of back pressure guides (1621)(1622), i.e., an inner back pressure guide (1621) and an outer back pressure guide (1622), may extend as a single body from the back surface of the turning plate (151). In this case, the plurality of back pressure guides (1621)(1622) may be formed of the same material as the turning scroll (150), that is, aluminum. Considering that the main frame (130) is usually formed of cast iron, the back pressure guides (1621)(1622) may be formed of a different material from the main frame (130), thereby suppressing damage due to insufficient lubrication between the back pressure guides and the main frame (130).

[0109] In addition, since a plurality of back pressure guides (1621)(1622) are formed as a single body in the turning plate (151), the back pressure guides, that is, the back pressure space (162), can be easily formed. Accordingly, the turning scroll (150) including the back pressure space (162) can be easily manufactured.

[0110] In addition, a plurality of back pressure guides (1621)(1622) may be formed with the same specifications. For example, a plurality of back pressure guides (1621)(1622) may be formed with the same thickness and / or the same height. Accordingly, the reliability of the back pressure guides (1621)(1622) forming the back pressure space (162) can be secured. However, in some cases, the height of the inner back pressure guide (1621) and the thickness and / or height of the outer back pressure guide (1622) may be formed differently. For example, the height of the outer back pressure guide (1622) may be formed lower than the height of the inner back pressure guide (1621). In this case, even when the orbiting scroll (150) is unstable due to an overturning moment, the outer back pressure guide (1622) can be prevented from directly contacting the main frame (130) to a minimum.

[0111] The floating member (163) may be formed in an annular shape. However, the floating member (163) may be formed of a plurality of first sliding parts (1631) spaced apart in the radial direction, and a single second sliding part (1632) in which the lower ends of the plurality of first sliding parts (1631) are connected to each other. Accordingly, the back pressure chamber (160a) may be formed by the back surface of the pivot plate part (151) between the inner back pressure guide (1621) and the outer back pressure guide (1622), the back pressure space part (162) formed by the inner back pressure guide (1621) and the outer back pressure guide (1622), and the floating member (163) formed by the first sliding part (1631) and the second sliding part (1632).

[0112] For example, the first sliding portion (1631) of the floating member (163) may be formed to extend axially so as to come into sliding contact with the outer surface of the inner back pressure guide (1621) and the inner surface of the outer back pressure guide (1622) forming the back pressure space (162), respectively, and the second sliding portion (1632) of the floating member (163) may be formed to extend radially so as to connect the lower end of the inner back pressure guide (1621) and the lower end of the outer back pressure guide (1622) to each other. Accordingly, the floating member (163) may be formed in a cup cross-sectional shape, and a portion of the back pressure room (160a) may be formed therein.

[0113] In addition, the height of the floating member (163), that is, the height of the first sliding member (1631), may be formed to be lower than or equal to the height of the back pressure guide (1621)(1622). For example, the height of the floating member (163) may be formed to be lower than the height of the first sliding member (1631). Accordingly, as the pressure in the back pressure chamber (160a) increases and the upper end of the first sliding member (1631) is separated from the pivot plate member (151) facing it, the upper end of the first sliding member (1631) forms a back pressure surface, so that the overall area of ​​the back pressure chamber (160a) may increase. Through this, a back pressure chamber (160a) is formed between the main frame (130) and the orbiting scroll (150), and the area of ​​the back pressure chamber (160a) is formed as wide as possible to stably support the orbiting scroll (150).

[0114] In addition, the width of the floating member (163), that is, the width of the second sliding member (1632), can be formed to be larger than the width (thickness) of the back pressure guide (1621) (1622). Accordingly, the area of ​​the back pressure chamber (160a) can be formed as wide as possible while stably supporting the orbiting scroll (150).

[0115] In addition, the floating member (163) can be formed of a material lighter than the orbiting scroll (150). Accordingly, the floating member (163) can be supported in close contact with the upper surface of the main frame (130) while moving quickly in the axial direction relative to the back pressure guide (1621)(1622) according to the pressure of the back pressure chamber (160a).

[0116] In addition, the floating member (163) can be formed of a material having a lower hardness than the orbiting scroll (150). Accordingly, processing of the floating member (163), particularly the contact surface with the back pressure guide (1621) (1622) and / or the main frame (130), can be facilitated.

[0117] In addition, a back pressure sealing member (164) may be provided between the first sliding portion (1631) of the floating member (163) and the inner surface of the inner back pressure guide (1621) and the outer back pressure guide (1622) facing it. Accordingly, it is possible to effectively prevent the refrigerant in the back pressure chamber (160a) from leaking into the low pressure portion (110a).

[0118] In the drawing, the unexplained symbol 118 is a subframe, and 171 is the ring body of the Oldham ring.

[0119] The operational effects of the scroll compressor according to the present embodiment as described above are as follows.

[0120] 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).

[0121] 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.

[0122] Then, the refrigerant is sucked into the low pressure section (110a) of the casing (110) through the refrigerant suction pipe (117), 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 sucked into the suction pressure chamber (not shown) together with other refrigerants.

[0123] 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).

[0124] At this time, as shown in FIGS. 5 and 6, a portion of the refrigerant compressed in the compression chamber (V) moves to the back pressure chamber (160a) of the back pressure chamber assembly (160) through the back pressure passage (161). In other words, 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 orbiting scroll (150) and the main frame (130) through the back pressure passage (161) forming the back pressure hole before reaching the discharge port (1411). Accordingly, the back pressure chamber (160a) forms an intermediate pressure and pushes the floating member (163) of the back pressure chamber assembly (160) toward the main frame (130).

[0125] 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.

[0126] In this way, since the back pressure chamber assembly (160) forming the back pressure chamber (160a) in the orbital back pressure method is provided in the orbital scroll (150), the actual area of ​​the back pressure chamber (160a) can be secured as wide as possible. Through this, the back pressure area supporting the orbital scroll (150) is expanded, so that the orbital scroll (150) can be stably supported.

[0127] In addition, since the back pressure chamber assembly (160) is provided on the orbiting scroll (150) and the floating member (163) forming the back pressure chamber assembly (160) is formed to seal the back pressure chamber (160a), even if the movement of the orbiting scroll (150) is unstable, the refrigerant in the back pressure chamber (160a) can be prevented from leaking into the low pressure section (110a) of the casing (110). This prevents the refrigerant in the back pressure chamber (160a) from heating the suction refrigerant in the low pressure section (110a), thereby preventing a decrease in compression efficiency due to suction loss.

[0128] In addition, since the back pressure space portion (162) forming the back pressure chamber assembly (160) is formed as a single body in the orbiting scroll (150), the back pressure chamber assembly (160) can be easily formed. This reduces the number of parts of the back pressure chamber assembly (160) including the floating member (163), thereby increasing the compression efficiency of the low-pressure scroll compressor while lowering the manufacturing cost.

[0129] In addition, since the rotating shaft coupling portion (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).

[0130] Meanwhile, there are other embodiments of the back pressure chamber assembly as follows.

[0131] That is, in the above-described embodiment, the second sliding part of the floating member forming the pressure chamber assembly is formed flat, but in some cases, a fuel supply groove may be formed in the second sliding part of the floating member.

[0132] Fig. 7 is an exploded perspective view of another embodiment of the pressure chamber assembly, and Fig. 8 is a cross-sectional view of the pressure chamber assembly of Fig. 7 assembled.

[0133] Referring to FIGS. 7 and 8, the back pressure chamber assembly (160) according to the present embodiment is provided between the main frame (130) and the orbiting scroll (150), but the basic configuration and the resulting operational effects of the back pressure chamber assembly (160) are almost the same as those of the above-described embodiment. For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so as 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 from the rear surface of the orbiting plate portion (151) facing the main frame (130) toward the main frame (130) or may be formed to be recessed on the rear surface of the orbiting plate portion (151).

[0134] In addition, a floating member (163) is slidably inserted into the inside of the back pressure space (162), and the floating member (163) can form a sealed back pressure chamber (160a) inside the back pressure space (162) by connecting a plurality of first sliding members (1631) forming the side surface by a second sliding member (1632). Accordingly, the back pressure chamber assembly (160) can have a large back pressure area and suppress refrigerant leakage in the back pressure chamber (160a) as in the above-described embodiments. This will be replaced with a description of the above-described embodiments.

[0135] However, in the present embodiment, a refueling groove (1632a) may be formed in the second sliding portion (1632) of the floating member (163) forming part of the pressure relief assembly (160). In other words, a refueling groove having an annular shape and / or a radial shape and / or a combination of annular and radial shapes may be formed on one side of the second sliding portion (1632) of the floating member (163) facing the main frame (130). The present embodiment discloses a refueling groove (1632a) that combines an annular shape and a radial shape.

[0136] In the case where the oil supply groove (1632a) is formed in the second sliding portion (1632) of the floating member (163) facing the main frame (130) as described above, some of the oil that is sucked up through the oil passage (1252) of the rotating shaft (125) and supplied to the oil supply passage (P) can smoothly flow between the main frame (130) and the floating member (163) through the oil supply groove (1632a). Accordingly, even if the second sliding portion (1632) of the floating member (163), which is pushed toward the main frame (130) by the pressure of the back pressure chamber (160a), is in close contact with the thrust support surface (1313) of the main frame (130) to form a thrust surface, oil can be smoothly supplied to the thrust surface through the oil supply groove (1632a). Through this, even if the area of ​​the thrust surface between the rotating scroll (150) and the main frame (130) increases due to the floating member (163), friction loss can be suppressed as the fuel supply to the thrust surface is smoothly performed through the fuel supply groove (1632a) of the floating member (163).

[0137] Although not shown in the drawing, the refueling groove may also be formed on the thrust support surface (1313) of the main frame (130) facing the floating member (163). In this case, refueling to the aforementioned thrust surface can also be smoothly achieved.

[0138] Meanwhile, another embodiment of the pressure chamber assembly is as follows.

[0139] That is, in the above-described embodiments, the back pressure space forming the back pressure chamber assembly extends as a single body from the orbiting scroll, but in some cases, the back pressure space may be assembled to the orbiting scroll. In this case, the back pressure space may be manufactured separately and attached to the orbiting scroll, or, depending on the material of the back pressure space, may be assembled to the orbiting scroll by injection molding.

[0140] Fig. 9 is an exploded perspective view of another embodiment of the back pressure chamber assembly, and Fig. 10 is a cross-sectional view of the back pressure chamber assembly of Fig. 7 assembled.

[0141] Referring to FIGS. 9 and 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 the basic configuration and the resulting operational effects of the back pressure chamber assembly (160) are almost the same as those of the above-described embodiments. For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so as to perform a orbital movement together with the orbiting scroll (150), and a back pressure space portion (162) forming a part of the back pressure chamber assembly (160) may extend from the rear surface of the orbiting plate portion (151) facing the main frame (130) toward the main frame (130).

[0142] In addition, a floating member (163) is slidably inserted into the back pressure space (162), and the floating member (163) can form a sealed back pressure chamber (160a) inside the back pressure space (162) by connecting a plurality of first sliding members (1631) forming the side surfaces thereof to each other by a second sliding member (1632). Accordingly, the back pressure chamber assembly (160) not only has an expanded back pressure area as in the above-described embodiment, but also can effectively suppress refrigerant leakage in the back pressure chamber (160a) as the opening side of the back pressure chamber (160a) is blocked by the floating member (163). This will be replaced with a description of the above-described embodiment.

[0143] However, in the present embodiment, the back pressure space portion (162) forming part of the back pressure chamber assembly (160) may be formed by being assembled to the orbiting scroll (150). For example, a plurality of back pressure guides (1621)(1622) forming the back pressure space portion (162) may be formed by injection molding on the orbiting scroll (150). In this case, the plurality of back pressure guides (1621)(1622) may be connected to each other by a connecting guide (1623) and may be assembled in a form inserted as a single body into the back surface of the orbiting plate portion (151), or the plurality of back pressure guides (1621)(1622) may be separated from each other and may be assembled in a form inserted independently into the back surface of the orbiting plate portion (151). In the former case, the back pressure space (162) can be easily formed, and in the latter case, by separately fixing each back pressure guide (1621)(1622), a plurality of back pressure guides (1621)(1622) can be assembled more firmly. This embodiment illustrates an example of the former case, that is, a plurality of back pressure guides (1621)(1622) are assembled in a single form connected to each other by a connecting guide (1623).

[0144] Specifically, a guide insertion groove (1512) is formed in a circular shape on the back surface of the pivot plate (151), and the upper half of the back pressure guide (1621)(1622) forming the back pressure space (162) can be molded or bonded to be inserted into the guide insertion groove (1512) and fixed. Accordingly, the back pressure space (162) can be easily assembled to the pivot scroll (150).

[0145] In this case, a pressure relief passage hole (1623a) may be formed in the connecting guide (1623) connecting the two pressure relief guides (1621) (1622) to each other so as to be connected to the pressure relief passage (161) penetrating the turning plate (151). Accordingly, while the pressure relief space (162) is assembled to the turning scroll (150), a pressure relief room (160a) communicating with the pressure relief passage (161) may be formed in the pressure relief space (162).

[0146] Although not shown in the drawing, the inner surface of the guide receiving groove (1512) may be formed to be inclined or stepped so that it becomes deeper as it goes toward the back surface of the pivot plate (151). In this case, the back pressure guides (1621)(1622) on both sides can be axially hooked to the guide receiving groove (1512) to be more firmly connected.

[0147] When the back pressure space (162) forming the back pressure chamber assembly (160) as described above is assembled to the orbiting scroll (150), the material of the back pressure space (162) can be changed in various ways. For example, the back pressure guide (1621)(1622) forming the back pressure space (162) can be formed of a material that is lighter and has lower hardness than the orbiting scroll (150) made of aluminum, that is, the same engineering plastic as the floating member (163). Through this, not only can the weight increase of the orbiting scroll (150) due to the back pressure chamber assembly (160) be minimized while adding the back pressure chamber assembly (160) to the orbiting scroll (150), but also the surface roughness of the back pressure guide (1621)(1622) can be made smooth, thereby minimizing the leakage gap with the floating member (163).

[0148] Also in this case, the previously described fuel supply groove (1632a) can be formed in the second sliding portion (1632) of the floating member (163).

[0149] Meanwhile, another embodiment of the pressure chamber assembly is as follows.

[0150] That is, in the above-described embodiments, the back pressure space forming the back pressure chamber assembly extends from the orbiting scroll toward the main frame, but in some cases, the back pressure space may be formed by being sunken into the orbiting scroll.

[0151] Fig. 11 is an exploded perspective view of another embodiment of the back pressure chamber assembly, and Fig. 12 is a cross-sectional view of the back pressure chamber assembly of Fig. 11 assembled.

[0152] Referring to FIGS. 11 and 12, the back pressure chamber assembly (160) according to the present embodiment is provided between the main frame (130) and the orbiting scroll (150), and the basic configuration and the resulting operational effects of the back pressure chamber assembly (160) are similar to those of the above-described embodiment. For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so as to perform a orbital movement together with the orbiting scroll (150), and a back pressure space portion (162) forming a part of the back pressure chamber assembly (160) may be formed on the back surface of the orbiting plate portion (151) facing the main frame (130).

[0153] In addition, a floating member (163) is slidably inserted into the inside of the back pressure space (162), and the floating member (163) can form a sealed back pressure chamber (160a) inside the back pressure space (162) by connecting a plurality of first sliding members (1631) forming the side surface by a second sliding member (1632). Accordingly, the back pressure chamber assembly (160) can have a large back pressure area and suppress refrigerant leakage in the back pressure chamber (160a) as in the above-described embodiments. This will be replaced with a description of the above-described embodiments.

[0154] However, in the present embodiment, the back pressure space portion (162) may be formed to be recessed in a circular shape to a predetermined depth on the back surface of the pivot plate portion (151), and sealing groove portions (1651) (1652) may be formed to be recessed in a circular shape on the inner and outer sides of the back pressure space portion (162), respectively. In these sealing groove portions (1651) (1652), sealing members (1661) (1662) in a circular shape may be inserted to be in close contact in the radial direction and movable in the axial direction, respectively.

[0155] In this case, the second key groove (151a) into which the second key (173) of the old ring (170) is slidably inserted can be formed radially long on the outside of the outer sealing groove (or outer sealing member) (1652). Accordingly, the area of ​​the back pressure space (162) can be formed as wide as possible, thereby increasing the back pressure area and stably supporting the orbiting scroll (150).

[0156] In the case where the back pressure space (162) is formed to be sunken into the back surface of the orbiting scroll (150) as described above, the weight increase of the orbiting scroll (150) due to the back pressure space (162) can be suppressed, thereby reducing the power consumption of the motor compared to the embodiments described above.

[0157] In addition, the gap between the back surface of the orbiting scroll (150) and the main frame (130) facing it can be reduced to further stabilize the behavior of the orbiting scroll (150).

[0158] Meanwhile, another embodiment of the pressure chamber assembly is as follows.

[0159] That is, in the above-described embodiments, a floating member is slidably inserted into the interior of the back pressure space portion forming the back pressure chamber assembly to form the back pressure chamber, but in some cases, a sealing member may be provided on both the inner and outer sides of the back pressure space portion to form the back pressure chamber.

[0160] Figures 13 and 14 are cross-sectional views showing assembled versions of further embodiments of the pressure chamber assembly.

[0161] Referring to FIGS. 13 and 14, the back pressure chamber assembly (160) according to the present embodiment is provided between the main frame (130) and the orbiting scroll (150), but the basic configuration and the resulting operational effects of the back pressure chamber assembly (160) are similar to those of the above-described embodiment. For example, the back pressure chamber assembly (160) is provided on the orbiting scroll (150) so as to perform a rotational movement together with the orbiting scroll (150), and a back pressure space portion (162) forming a part of the back pressure chamber assembly (160) may be formed on the back surface of the orbiting plate portion (151) facing the main frame (130). Accordingly, the back pressure chamber assembly (160) can have a large back pressure area and suppress refrigerant leakage from the back pressure chamber (160a) as in the above-described embodiments. This will be replaced with a description of the above-described embodiments.

[0162] However, in the present embodiment, sealing members (1661)(1662) may be provided on the inner and outer sides of the back pressure space portion (162), respectively, to seal the inside of the back pressure space portion (162) and form a back pressure chamber (160a). For example, the back pressure space portion (162) may be formed by extending the back pressure guide (1621)(1622) as shown in the aforementioned FIGS. 2, 7, and 9, or may be formed by recessing the back surface of the pivot plate portion (151) as shown in FIG. 11.

[0163] Specifically, as shown in Fig. 13, an inner pressure guide (1621) may be extended toward the main frame (130) on the inner side of the pressure relief space (162), and an outer pressure guide (1622) may be extended toward the outer side. An inner sealing groove (1651) may be formed on the leading edge of the inner pressure guide (1621), and an outer sealing groove (1652) may be formed on the leading edge of the outer pressure guide (1622). An inner sealing member (1661) may be slidably inserted into the inner sealing groove (1651), and an outer sealing member (1662) may be slidably inserted into the outer sealing groove (1652), respectively, in the axial direction. The side walls of the inner sealing member (1661) and the outer sealing member (1662) 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 passage (P) and / or the pressure of the back pressure chamber (160a), and the axial side surface of the inner sealing member (1661) and the axial side surface of the outer sealing member (1662) 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.

[0164] In addition, as shown in Fig. 14, the back pressure space portion (162) may be formed in a circular shape that is sunken to a preset depth on the back surface of the pivot plate portion (151). In this case, an inner sealing groove portion (1651) may be formed in a circular shape on the inner circumference of the back pressure space portion (162), and an outer sealing groove portion (1652) may be formed in a circular shape on the outer circumference. The inner sealing member (1661) and the outer sealing member (1662) described in the embodiment of Fig. 13 above may be inserted into these sealing groove portions (1651)(1652) so as to be in close contact in the radial direction and movable in the axial direction, respectively.

[0165] In these cases, the second key groove (151a) into which the second key (173) of the old ring (170) is slidably inserted can be formed radially long on the outside of the outer sealing groove (or outer sealing member) (1662). Accordingly, the area of ​​the back pressure space (162) can be formed as wide as possible, thereby expanding the back pressure area and stably supporting the orbiting scroll (150).

[0166] As described above, when the back pressure space (162) is sealed by a sealing member (1661)(1662) inserted into the sealing groove (1651)(1652), the frictional area between the sealing member (1661)(1662) and the main frame (130) is reduced, thereby reducing the frictional loss between the back pressure room assembly (160) and the main frame (130).

[0167] In addition, the cross-sectional area of ​​the sealing member (1661)(1662) forming part of the back pressure chamber assembly (160) is reduced, so that the sealing member (1661)(1662) can move more quickly and quickly seal the back pressure chamber (160a). This can be more advantageous in the case of a lower compression type in which the compression part is positioned lower than the driving motor (120).

[0168] Meanwhile, the back pressure chamber assembly according to the above-described embodiments has been examined with a focus on an example applied to a low-pressure scroll compressor, but as explained above, the back pressure chamber assembly according to the above-described embodiments can be equally applied to a high-pressure scroll compressor. However, in the low-pressure type, the refrigerant in the back pressure chamber is prevented from leaking into the low-pressure chamber forming the suction space, whereas in the high-pressure type, the refrigerant in the high-pressure part forming the discharge space is prevented from flowing into the back pressure chamber, thereby preventing the pressure in the back pressure chamber from excessively increasing.

Claims

1. Casing; A main frame fixed inside the above casing; A fixed scroll coupled to one side of the above mainframe; A rotating scroll provided between the main frame and the fixed scroll to form a compression chamber between the main frame and the fixed scroll; and It includes a back pressure chamber assembly provided between the above-mentioned orbiting scroll and the main frame facing it, and pressurizing the above-mentioned orbiting scroll toward the above-mentioned fixed scroll. 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.

2. In paragraph 1, 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 A scroll compressor comprising a floating member that is slidably coupled to the above-mentioned back pressure space to form a back pressure chamber together with the back pressure space.

3. In paragraph 2, The above pressure space is, A scroll compressor comprising a plurality of pressure relief guides spaced radially from one side of the rotating scroll facing the main frame and protruding toward the main frame by a preset height.

4. In paragraph 2, The above pressure space is, A scroll compressor formed by recessing one side of the above-mentioned rotating scroll facing the above-mentioned main frame to a preset depth.

5. In paragraph 2, The above pressure space is, A scroll compressor formed as a single body on the above-mentioned rotating scroll.

6. In paragraph 2, The above pressure space is, A scroll compressor formed by being assembled on the above-mentioned rotating scroll.

7. In paragraph 6, The above floating member is formed of a lighter material than the above rotating scroll, The above pressure space is, A scroll compressor formed of a material having a lower hardness than the above-mentioned orbiting scroll.

8. In paragraph 2, The above floating member is, A plurality of first sliding parts slidably coupled to the inner wall surface of the above-mentioned back pressure space; and A scroll compressor comprising a second sliding section that forms the back pressure chamber by connecting the plurality of first sliding sections and is in sliding contact with the main frame.

9. In paragraph 8, The height of the plurality of first sliding parts is, A scroll compressor formed to have a depth less than or equal to the depth of the above-mentioned back pressure space.

10. In paragraph 8, A scroll compressor in which a sealing member is provided between the inner walls of both sides of the plurality of first sliding sections and the back pressure space section facing them.

11. In paragraph 8, The above second sliding part, A scroll compressor having a lubrication groove formed on the surface facing the main frame.

12. In paragraph 1, 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 above pressure relief passage; A plurality of sealing grooves formed in an annular shape on both sides of the radial direction of the above-mentioned back pressure space; and A scroll compressor including a plurality of sealing members each inserted into the plurality of sealing grooves to form a back pressure chamber inside the back pressure space portion.

13. In paragraph 12, The above-mentioned back pressure space portion is formed of a plurality of back pressure guides spaced radially from one side of the rotating scroll facing the main frame and protruding toward the main frame by a preset height. The above sealing home part is, A scroll compressor formed on each end surface of the plurality of back pressure guides.

14. In paragraph 12, The above pressure space is formed by sinking a predetermined depth on one side of the rotating scroll facing the main frame, The above sealing home part is, A scroll compressor formed on the inner and outer sides of the above-mentioned back pressure space.

15. In any one of paragraphs 1 to 14, The above rotating scroll is, A pivot plate provided between the main frame and the fixed scroll; A rotating wrap extending from one side of the above rotating plate portion and forming a compression chamber together with the fixed wrap of the above fixed scroll; and Including a rotating shaft coupling portion that overlaps the rotating wrap and the rotating shaft in the radial direction at the center of the rotating plate portion and extends in the axial direction of the rotating shaft, A scroll compressor in which a portion of the orbiting wrap extends from the front end surface of the rotating shaft coupling portion facing the fixed scroll.

16. In paragraph 15, The above-mentioned turning plate portion has a turning step surface between the outer surface of the turning wrap and the inner surface of the turning wrap facing it, and the above-mentioned fixed wrap has a fixed step surface corresponding to the turning step surface. The above-mentioned pivoting step surface and the above-mentioned fixed step surface are, A scroll compressor in which the discharge start angles of at least one of the above two compression chambers are spaced apart from each other.

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