Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor comprises a thermal expansion part. The thermal expansion part is disposed between an orbiting scroll and a non-orbiting scroll. The thermal expansion part thermally expands when the temperature of a compression chamber rises, thereby forming a gap between the orbiting scroll and the non-orbiting scroll. Accordingly, during vacuum operation, vacuum pressure or refrigerant compressed in the compression chamber leaks through the gap, thereby inducing idling of a compressor and preventing additional temperature rise of the compression chamber.

Description

scroll compressor

[0001] The present invention relates to a scroll compressor capable of preventing damage to the compressor due to overheating of the compression chamber.

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

[0003] Scroll compressors can be categorized as upper compression or lower compression types based on the location of the drive motor and compression unit, which form the drive or transmission unit, based on examples installed in a vertical or horizontal configuration. An upper compression type has the compression unit positioned above the drive motor, while a lower compression type has the compression unit positioned below the drive motor. When the casing is installed horizontally, the upper side can be conveniently identified as the left side and the lower side as the right side.

[0004] Scroll compressors can be divided into low-pressure scroll compressors in which the internal space of a casing equipped with a compression unit forms suction pressure, and high-pressure scroll compressors in which the internal space of the casing forms discharge pressure.

[0005] The upper compression scroll compressor can be configured as a low-pressure or high-pressure type, but the lower compression scroll compressor is usually configured as a high-pressure scroll compressor considering the location of the refrigerant suction pipe.

[0006] To minimize compression efficiency degradation due to refrigerant leakage, a conventional scroll compressor can be configured so that the height difference between the orbiting and non-orbiting wraps is within a preset range, for example, 1 to 4 μm. Furthermore, the non-orbiting scroll can be configured to be in close contact with the thrust surface of the frame on which it is supported.

[0007] This prevents the refrigerant from leaking through the end of the orbiting wrap, for example, the gap between the orbiting wrap and the plate portion of the non-orbiting scroll.

[0008] However, when installing the air conditioner, moisture may enter the filter, causing ice to form or foreign substances or valve malfunction.

[0009] This can cause the compressor's suction port to become blocked. In this case, the compressor will operate without any refrigerant flowing in, and if recompression is repeated, the compression chamber may become vacuumed.

[0010] During vacuum operation, the temperature at the center of the compression chamber may rise excessively, which may damage heat-sensitive parts such as bearings or back pressure seals.

[0011] The purpose of the present invention is to provide a scroll compressor having a structure capable of solving the above-described problems.

[0012] The first purpose is to provide a scroll compressor having a structure that can prevent overheating of the compression chamber by preventing compression of the refrigerant during vacuum operation.

[0013] The second objective is to provide a scroll compressor having a structure capable of preventing further temperature rise until the operating conditions are normalized and an emergency stop is performed.

[0014] The third purpose is to provide a scroll compressor having a structure capable of separating the wrap tip of an orbiting scroll or a non-orbiting scroll without an external power source.

[0015] The fourth purpose is to provide a scroll compressor having a structure that can prevent damage to heat-vulnerable components.

[0016] As a result of intensive research, the inventors of the present invention have found that the first to fourth objectives of the present invention can be achieved by the following embodiments of the present invention.

[0017] In order to achieve the above-described object, a scroll compressor according to one embodiment of the present invention may include at least one of a casing, a driving motor, a main frame, a non-orbiting scroll, an orbiting scroll, and a thermal expansion member. The driving motor is provided inside the casing. The main frame is disposed on one side of the driving motor. The non-orbiting scroll may be disposed in an opposite direction to the driving motor with respect to the main frame. The orbiting scroll is connected to the driving motor through a rotational shaft. The orbiting scroll is engaged with the non-orbiting scroll so as to be able to orbit with respect to the non-orbiting scroll. The orbiting scroll may form a compression chamber together with the non-orbiting scroll. The thermal expansion member is disposed between the orbiting scroll and the non-orbiting scroll. The thermal expansion member may thermally expand when the temperature of the compression chamber increases to form a gap between the orbiting scroll and the non-orbiting scroll.

[0018] Through this, the vacuum pressure or refrigerant in the compression chamber can leak through the gap during vacuum operation, thereby suppressing overheating in the compression chamber.

[0019] In one embodiment, the thermal expansion member has a larger coefficient of thermal expansion than the orbiting scroll and the non-orbiting scroll. As a result, the thermal expansion member can expand in volume at a preset temperature.

[0020] In one embodiment, the thermal expansion member may be composed of different materials from the orbiting scroll and the non-orbiting scroll. As a result, the thermal expansion member may have a different coefficient of thermal expansion from the orbiting scroll and the non-orbiting scroll.

[0021] In one embodiment, the orbiting scroll and the non-orbiting scroll may be formed of cast iron. The thermal expansion member may be formed of one or a combination of two or more of nickel steel, chromium nickel steel, and manganese steel. As a result, the thermal expansion member may have a higher coefficient of thermal expansion than the orbiting scroll and the non-orbiting scroll.

[0022] According to one embodiment, the thermal expansion member may be installed embedded in the central portion of the orbiting scroll or the non-orbiting scroll. As a result, the thermal expansion member may expand by receiving heat from the central portion of the orbiting scroll or the non-orbiting scroll.

[0023] According to one embodiment, the thermal expansion member may be installed between the edge of the orbiting scroll and the non-orbiting scroll. As a result, the thermal expansion member may expand by receiving heat from the edge of the orbiting scroll or the non-orbiting scroll.

[0024] According to one embodiment, the non-orbiting scroll includes a non-orbiting plate portion; and a non-orbiting wrap protruding from the non-orbiting plate portion toward the main frame. The orbiting scroll includes an orbiting plate portion arranged between the main frame and the non-orbiting plate portion; and an orbiting wrap protruding from the orbiting plate portion toward the non-orbiting plate portion and interlocking with the non-orbiting wrap so as to be capable of orbiting relative to the non-orbiting wrap.

[0025] In another embodiment, the orbital wrap may extend from the radially outer side of the orbital plate portion toward the inner side. A thermal expansion portion receiving groove is formed to be sunken in a radially inner end of the orbital wrap. The thermal expansion portion may be received in the thermal expansion portion receiving groove. The thermal expansion portion may form a gap between the orbital wrap and the non-orbiting plate portion when the temperature of the compression chamber rises, or may form a gap between the non-orbiting wrap and the orbital plate portion.

[0026] Through this, the thermal expansion member is installed embedded in the inner end of the rotating wrap, so that heat can be transferred from the inner end of the rotating wrap when the compression chamber is overheated.

[0027] According to another embodiment, the orbiting scroll may further include a rotation shaft coupling portion provided at the center of the orbiting plate portion and coupled with the rotation shaft. A thermal expansion portion receiving groove may be formed to be sunken in the rotation shaft coupling portion. The thermal expansion portion may be received in the thermal expansion portion receiving groove. The thermal expansion portion may form a gap between the orbiting wrap and the non-orbiting plate portion when the temperature of the compression chamber rises, or may form a gap between the non-orbiting wrap and the orbiting plate portion.

[0028] Through this, the thermal expansion member is embedded in the rotary shaft coupling member, so that heat can be transferred from the rotary shaft coupling member when the compression chamber is overheated.

[0029] According to another embodiment, the orbiting scroll may further include a rotation shaft coupling portion provided at the center of the orbiting plate portion and coupled to the rotation shaft. The rotation shaft coupling portion and the radially inner end of the orbiting wrap are connected to each other. A thermal expansion portion receiving groove may be formed to be sunken between the rotation shaft coupling portion and the radially inner end of the orbiting wrap. The thermal expansion portion may be received in the thermal expansion portion receiving groove.

[0030] Through this, the thermal expansion member is installed embedded between the rotating shaft coupling part and the inner end of the rotating wrap, so that heat can be transferred from the rotating shaft coupling part and the rotating wrap when the compression chamber is overheated.

[0031] According to another embodiment, the non-orbiting scroll may further include a sub-bearing portion provided in the central portion of the non-orbiting plate portion and coupled to the rotational shaft. A thermal expansion portion receiving groove may be formed to be sunken along the circumference of the sub-bearing portion. The thermal expansion portion may be received in the thermal expansion portion receiving groove.

[0032] Through this, the thermal expansion part is installed in the sub-bearing part, which is the central part of the non-rotating scroll, so that heat can be transferred from the sub-bearing part when the compression chamber is overheated.

[0033] According to another embodiment, the non-orbiting scroll may further include a non-orbiting side wall portion formed to protrude toward the main frame from an edge portion of the non-orbiting plate portion. A thrust surface may be arranged at an end portion of the non-orbiting side wall portion to face one axial surface of the orbiting plate portion. A thermal expansion portion receiving groove may be formed to be recessed in the thrust surface. A thermal expansion portion may be received in the thermal expansion portion receiving groove.

[0034] Through this, the thermal expansion member is installed on the thrust surface, which is the edge of the non-rotating scroll, so that heat can be transferred from the thrust surface when the compression chamber is overheated.

[0035] According to another embodiment, the thrust surface may extend circumferentially along the periphery of the non-orbiting side wall portion. The thermal expansion member receiving grooves may be provided in multiple numbers on the thrust surface. The plurality of thermal expansion member receiving grooves may be arranged to be spaced apart from each other in the circumferential direction of the thrust surface. Accordingly, the thermal expansion members are provided in multiple numbers along the periphery of the thrust surface, thereby expanding the thermal contact area with the non-orbiting scroll when the compression chamber is overheated.

[0036] According to an embodiment of the present invention, the following effects can be achieved.

[0037] First, a thermal expansion member having a larger coefficient of thermal expansion than a compression member may be installed embedded in one side of the orbiting scroll or the non-orbiting scroll. For example, the thermal expansion member may be installed in the center of the orbiting scroll. Specifically, the thermal expansion member may be arranged at the rotating shaft coupling portion or the orbiting wrap of the orbiting scroll. Alternatively, the thermal expansion member may be arranged at the connection portion between the rotating shaft coupling portion of the orbiting scroll and the orbiting wrap. The thickness of the connection portion where the rotating shaft coupling portion of the orbiting scroll meets the orbiting wrap may be thicker than the thickness of the rotating shaft coupling portion or the orbiting wrap. A thermal expansion member receiving groove may be formed at the connection portion between the rotating shaft coupling portion of the orbiting scroll and the orbiting wrap. The thermal expansion member may be received in the thermal expansion member receiving groove. The thermal expansion member receiving groove may be formed to be open toward the non-orbiting head plate. The thermal expansion member may be arranged adjacent to the discharge port or the discharge chamber.

[0038] The wrap tip of the rotating wrap is pressed against the non-rotating plate so that the thermal expansion portion receiving groove is covered by the non-rotating plate during normal operation.

[0039] When the temperature of the discharge chamber in the compression chamber rises above the preset temperature due to recompression during vacuum operation, the thermal expansion member is heated by the rise in temperature of the discharge chamber and expands in volume. The thermal expansion member can protrude through the opening of the thermal expansion member receiving groove and pressurize the non-rotating plate member in the axial direction.

[0040] Accordingly, the lap tip of the rotating lap is separated from the non-rotating plate portion, forming a gap. The compressed refrigerant or vacuum pressure in the discharge chamber leaks through the gap, inducing idling of the compressor and preventing further temperature rise in the compression chamber.

[0041] Second, the thermal expansion section can protect the compressor by forcibly separating the rotating wrap and non-rotating plate during vacuum operation, thereby preventing further temperature rise until the operating conditions return to normal or an emergency stop occurs.

[0042] Third, the thermal expansion section can suppress excessive temperature rise in the compression chamber by keeping the wrap tip of the rotating wrap away from the non-rotating plate section even when there is no external power source during vacuum operation.

[0043] FIG. 1 is a conceptual diagram showing a cross-section of a scroll compressor according to one embodiment of the present invention.

[0044] FIG. 2 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to one embodiment by enlarging II in FIG. 1.

[0045] Figure 3 is a conceptual diagram showing a thermal expansion member installed in the rotating scroll in Figure 2.

[0046] Figure 4 is a conceptual diagram showing the operating state of the thermal expansion part before operation (normal operation) and after operation (overheating) by enlarging IV in Figure 2.

[0047] FIG. 5 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to another embodiment of the present invention.

[0048] Figure 6 is a conceptual diagram showing a thermal expansion part installed in the central portion of the non-rotating scroll in Figure 5.

[0049] Figure 7 is a conceptual diagram showing the operating state of the thermal expansion part before operation (normal operation) and after operation (overheating) by enlarging VII in Figure 5.

[0050] FIG. 8 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to another embodiment of the present invention.

[0051] Figure 9 is a conceptual diagram showing a thermal expansion member installed at the edge (thrust surface) of the non-rotating scroll in Figure 8.

[0052] Figure 10 is a conceptual diagram showing the operating state of the thermal expansion part before operation (normal operation) and after operation (overheating) by enlarging X in Figure 8.

[0053] Hereinafter, a scroll compressor according to an embodiment of the present invention will be described in detail with reference to the attached drawings.

[0054] In the following description, descriptions of some components may be omitted to clarify the features of the present invention.

[0055] 1. Definition of Terms

[0056] Terms that include ordinal numbers, such as first, second, etc., may be used to describe various components, but the components are not limited by these terms. These terms are used solely to distinguish one component from another.

[0057] When a component is referred to as being "connected" or "connected" to another component, it should be understood that it may be directly connected or connected to that other component, but that there may be other components intervening. Conversely, when a component is referred to as being "directly connected" or "connected" to another component, it should be understood that there are no other components intervening.

[0058] As used herein, singular expressions include plural expressions unless the context clearly indicates otherwise.

[0059] As used herein, “radial” or “radial” means a shape that extends out in all directions from a central point like spokes of a wheel.

[0060] “Axial” as used in the following description means the longitudinal direction of the axis of rotation.

[0061] As used in the following description, “radial direction” means the longitudinal direction of a line segment from the center of a circle or cylinder to a point on the circumference (circumference).

[0062] As used in the following description, “circumferential” means the direction of the circumference of a circle.

[0063] In addition, in the following description, the scroll compressor is described as a sealed scroll compressor in which the drive unit (electric unit or drive motor) and the compression unit are provided in the casing. However, the same can be applied to an open compressor in which the drive unit (electric unit or drive motor) is provided outside the casing and connected to the compression unit provided inside the casing.

[0064] In addition, the following description will be given as an example a lower compression type scroll compressor in which the drive unit and the compression unit are arranged in the vertical axial direction and the compression unit is located lower than the drive unit (the drive unit or the drive motor). However, the same can be applied to a horizontal scroll compressor in which the drive unit (the drive unit or the drive motor) and the compression unit are arranged left and right, as well as an upper compression type scroll compressor in which the compression unit is located higher than the drive unit (the drive unit or the drive motor).

[0065] In addition, the following description takes as an example a high-pressure scroll compressor having a lower compression type and a refrigerant suction pipe forming a suction passage directly connected to a compression section, and a refrigerant discharge pipe connected to the internal space of the casing so that the internal space of the casing forms a discharge pressure.

[0066] 2. Description of the configuration of a scroll compressor according to one embodiment of the present invention

[0067] FIG. 1 is a conceptual diagram showing a cross-section of a scroll compressor according to one embodiment of the present invention.

[0068] Hereinafter, each configuration of a scroll compressor according to an embodiment of the present invention will be described with reference to the attached drawings.

[0069] (1) Components of a scroll compressor

[0070] A scroll compressor according to the present invention includes a casing (100). The casing (100) forms the exterior or outer periphery of the compressor. An accommodation space is provided within the casing (100) to accommodate components constituting the compressor.

[0071] A drive motor (110) is installed inside the casing (100). The drive motor (110) constitutes an electric part. A compression part is installed on the lower side of the drive motor (110).

[0072] The electric part is coupled to one end (upper end in the drawing) of the rotating shaft (118). The compression part is coupled to the other end (lower end in the drawing) of the rotating shaft (118). The compressor according to the present embodiment has a lower compression type structure.

[0073] Through this, the compression member is connected to the electric part through the rotation shaft (118), and can operate by receiving rotational power from the electric part.

[0074] The casing (100) can be configured to include a cylindrical shell (101), an upper shell (102), and a lower shell (103).

[0075] The cylindrical shell (101) may be formed in a cylindrical shape. Both ends of the cylindrical shell (101) may be opened in the vertical direction. The upper shell (102) is connected to one end (the upper end based on the drawing) of the cylindrical shell (101). The upper shell (102) is configured to cover the upper end of the cylindrical shell (101).

[0076] The lower shell (103) is connected to the other end (bottom based on the drawing) of the cylindrical shell (101). The lower shell (103) is configured to cover the lower end of the cylindrical shell (101).

[0077] Through this, the internal space (104) of the casing (100) can be sealed. The internal space (104) of the casing (100) can be divided into an upper space (S2) and a lower space (S1) based on the driving motor (110).

[0078] The upper space (S2) is formed above the driving motor (110). Oil can be separated from the refrigerant discharged from the compression unit. The upper space (S2) can be called an oil separation space in that the oil is separated from the refrigerant.

[0079] A refrigerant discharge pipe (105) can be formed to be connected to the upper space (S2).

[0080] The lower space (S1) is formed on the lower side of the driving motor (110). The lower space (S1) can be divided into a storage space (S11) and a discharge space (S12) based on the compression section. The discharge space (S12) can be formed on the upper side of the compression section. The storage space (S11) can be formed on the lower side of the compression section.

[0081] A driving motor (110) and a main frame (120) can be accommodated and fixed on the inner surface of the cylindrical shell (101).

[0082] An oil recovery passage may be formed on the outer surface of the drive motor (110) and the outer surface of the main frame (120). The oil recovery passage may be arranged to be spaced apart from the inner surface of the cylindrical shell (101) at a preset interval.

[0083] A refrigerant suction pipe (106) may be connected to penetrate radially through the side surface of the cylindrical shell (101). The inner end of the refrigerant suction pipe (106) may be connected to communicate with the suction port (133) of the non-rotating scroll (130) to be described later. The outer end of the refrigerant suction pipe (106) may be connected to the evaporator, so that the low-pressure gaseous refrigerant evaporated in the evaporator may be delivered to the compressor. The refrigerant suction pipe (106) may be positioned lower than the driving motor (110).

[0084] A refrigerant discharge pipe (105) is provided on the inner upper portion of the upper shell (102). The refrigerant discharge pipe (105) is connected to the inner space (104) of the casing (100) so as to be in communication with it. The inner end of the refrigerant discharge pipe (105) is connected to the upper space (S2) formed on the upper side of the driving motor (110) so as to be in communication with it. The outer end of the refrigerant discharge pipe (105) is connected to a condenser so that compressed refrigerant can be delivered to the condenser.

[0085] An oil circulation pipe may be provided in the lower shell (103). The inner end of the oil circulation pipe may be connected to the oil storage space (S11) of the lower shell (103). The outer end of the oil circulation pipe may be connected to the refrigerant suction pipe (106). An oil circulation valve may be installed in the middle of the oil circulation pipe.

[0086] Through this, the oil flowing in the refrigerant suction pipe (106) can be circulated to the oil storage space (S11) of the lower shell (103) through the oil circulation pipe.

[0087] The driving motor (110) includes a stator (111) and a rotor (115).

[0088] The stator (111) includes a stator core (112) and a stator coil (113). The stator core (112) may be formed in a cylindrical shape. The stator core (112) may be press-fitted and joined to the inner surface of the cylindrical shell (101).

[0089] The stator coil (113) is wound around the stator core (112). The stator coil (113) is electrically connected to an external power source through a power cable, so that the external power source can be applied to the stator coil (113). The power cable can be coupled by passing through the casing (100). An insulator (114) can be provided between the stator core (112) and the stator coil (113). The insulator (114) is composed of an insulating material to electrically insulate the stator core (112) and the stator coil.

[0090] The rotor (115) includes a rotor core (116) and a permanent magnet (117). The rotor core (116) may be formed in a cylindrical shape. The rotor core (116) is installed rotatably with a preset air gap inside the high-frequency magnetic core.

[0091] The permanent magnet (117) can be mounted embedded in the interior of the rotor core (116). The permanent magnets (117) are arranged at predetermined intervals along the circumference of the rotor core (116).

[0092] A rotational shaft (118) may be coupled to the center of the rotor core (116). The upper end of the rotational shaft (118) may be press-fitted and coupled to the rotor (115). The lower end of the rotational shaft (118) may be rotatably coupled to and supported by a main frame (120) to be described later.

[0093] The main frame (120) is equipped with a main bearing to support the lower end of the rotation shaft (118). The main bearing may be implemented as a bush bearing.

[0094] An eccentric portion is formed eccentrically at the lower end of the rotation shaft (118). The eccentric portion can be eccentrically connected to the rotation shaft connection portion (127) of the orbiting scroll (124).

[0095] Through this, the rotation shaft (118) can transmit the rotational power of the driving motor (110) to the rotating scroll (124).

[0096] The rotary scroll (124) can perform a rotary motion around the rotation axis (118).

[0097] An oil passage (1181) may be formed inside the rotating shaft (118). The oil passage (1181) is configured to guide oil stored in the oil storage space (S11) of the casing (100) to a wetted part, for example, a contact part between the orbiting wrap (126) of the orbiting scroll (124) to be described later and the non-orbiting wrap (135) of the non-orbiting scroll (130).

[0098] An oil pickup (119) may be installed at the bottom of the oil passage (1181). The oil pickup (119) is positioned to be submerged in the oil stored in the lower portion of the casing (100). The oil pickup (119) is configured to pump the oil filled in the oil storage space (S11).

[0099] Through this, the oil pickup (119) can suck up oil along the rotation shaft (118) through the oil passage (1181) when the rotation shaft (118) rotates and transmit it to each sliding part.

[0100] The compression unit may include at least one of a main frame (120), a rotating scroll (124), and a non-rotating scroll (130).

[0101] The main frame (120) is fixedly installed on the inner surface of the cylindrical shell (101). The main frame (120) is placed on the lower side of the driving motor (110).

[0102] The main frame (120) may be configured to include at least one of a frame plate portion (121), a frame side wall portion (123), and a main bearing portion (122).

[0103] The main bearing portion (122) may be formed to protrude from the center of the frame plate portion (121) toward the driving motor (110). A shaft through-hole is formed on the inside of the main bearing portion (122). The rotation shaft (118) is rotatably received and coupled to the inside of the main bearing through the shaft through-hole. Through this, the main bearing portion (122) can rotatably support the rotation shaft (118).

[0104] The frame side wall portion (123) may be formed to protrude from the outer periphery of the frame plate portion (121) toward the rotating scroll (124) to be described later. The frame side wall portion (123) may extend in the circumferential direction along the outer periphery of the frame plate portion (121). The frame side wall portion (123) may be joined to the inner periphery of the cylindrical shell (101) together with the frame plate portion (121) by press-fitting or welding, etc.

[0105] The orbiting scroll (124) is coupled to the rotation shaft (118). The orbiting scroll (124) is arranged between the main frame (120) and the non-orbiting scroll (130). An anti-rotation mechanism, an Oldham ring (128), is provided between the main frame (120) and the orbiting scroll (124). Through this, the orbiting scroll (124) is restricted from rotating and can rotate relative to the non-orbiting scroll (130).

[0106] The turning scroll (124) can be configured to include a turning plate portion (125), a turning wrap (126), and a rotating shaft coupling portion (127).

[0107] The pivot plate (125) may be formed in a circular shape. The pivot plate (125) is accommodated between the frame pivot plate (121) and the non-rotating pivot plate (131) described later. The upper surface of the pivot plate (125) may be axially supported on the main frame (120) with a back pressure sealing member interposed therebetween.

[0108] A keyway is formed to be sunken into the upper surface of the pivot plate (125). The keyway may extend radially from the outer circumference of the pivot plate (125). The keyway may be arranged to face the main frame (120).

[0109] The pivot key of the Oldham ring (128) can be slidably coupled to the keyway of the pivot plate (125).

[0110] A first back pressure chamber (129a) may be formed between the frame plate portion (121) and the orbiting plate portion (125) that face each other in the axial direction. The first back pressure chamber (129a) may be arranged on one side (upper side based on the drawing) of the orbiting plate portion (125) facing in the opposite direction of the non-orbiting scroll (130) with respect to the orbiting scroll (124).

[0111] The second back pressure chamber (129b) may be formed between the inner surface of the radially facing frame side wall portion (123) and the outer surface of the pivot plate portion (125). The first back pressure chamber (129a) and the second back pressure chamber (129b) may be axially connected to each other.

[0112] The first back pressure chamber (129a) and the second back pressure chamber (129b) are connected to the compression chamber through back pressure holes, thereby forming an intermediate pressure (back pressure). Through this, the orbiting plate (125) can receive the back pressure of the back pressure chamber and be brought into close contact with the non-orbiting scroll (130). Accordingly, leakage of refrigerant between the compression chambers can be suppressed.

[0113] The orbiting wrap (126) can protrude and extend from the lower surface of the orbiting plate (125) toward the non-orbiting scroll (130). The orbiting wrap (126) is configured to perform a orbiting motion by interlocking with the non-orbiting wrap (135) of the non-orbiting scroll (130) to be described later.

[0114] The orbital wrap (126) may be formed in an involute shape. However, the orbital wrap (126) is not limited thereto and may be formed in various shapes. The orbital wrap (126) is formed to correspond to the non-orbital wrap (135).

[0115] Through this, the rotating lap (126) can be interlocked with the non-rotating lap (135) to form a compression chamber.

[0116] The compression chamber may be composed of a first compression chamber (V1) and a second compression chamber (V2) based on the orbiting scroll (126). The first compression chamber (V1) and the second compression chamber (V2) may each be composed of a suction pressure chamber, an intermediate pressure chamber, and a discharge pressure chamber. The suction pressure chamber, the intermediate pressure chamber, and the discharge pressure chamber are formed continuously from the outer periphery of the non-orbiting scroll (130) toward the center of the non-orbiting scroll (130).

[0117] The first compression chamber (V1) refers to a compression chamber formed between the outer surface of the orbital wrap (126) and the inner surface of the non-orbital wrap (135) facing it.

[0118] The second compression chamber (V2) refers to a compression chamber formed between the inner surface of the orbital wrap (126) and the outer surface of the non-orbital wrap (135) facing it.

[0119] The inner end of the turning wrap (126) can be formed in the central portion of the turning plate (125).

[0120] The rotary shaft coupling portion (127) is formed to penetrate axially through the central portion of the rotary plate portion (125). As a result, the discharge port described later is arranged eccentrically from the center of the rotary scroll (124), i.e., from the rotary shaft coupling portion (127).

[0121] A rotary shaft (118) is rotatably coupled to a rotary shaft coupling portion (127). An eccentric portion of the rotary shaft (118) is coupled to the rotary shaft coupling portion (127). An inner end of a rotating wrap (126) can be connected to an outer circumference of the rotary shaft coupling portion (127).

[0122] The eccentric portion of the pivoting lap (126), the rotating shaft coupling portion (127) and the rotating shaft (118) can be arranged to overlap in the radial direction.

[0123] The non-orbiting scroll (130) is placed at the bottom of the main frame (120) with the orbiting scroll (124) in between.

[0124] A non-orbiting scroll (130) is configured to include at least one of a non-orbiting plate portion (131), a non-orbiting side wall portion (132), a sub-bearing portion (134), and a non-orbiting wrap (135).

[0125] The non-rotating plate portion (131) can be formed in a circular shape. The non-rotating plate portion (131) is arranged axially spaced apart from the lower side of the frame plate portion (121).

[0126] A sub-bearing portion (134) is provided at the center of the non-rotating plate portion (131). A shaft receiving hole is formed to penetrate axially on the inside of the sub-bearing portion (134). A discharge port may be formed around the shaft receiving hole. The discharge ports are connected to the first compression chamber (V1) and the second compression chamber (V2) in a communicative manner. Through this, the compressed refrigerant can be discharged to the muffler space (137) of the discharge cover (136) described later.

[0127] The discharge port is formed at an eccentric position from the center of the non-rotating plate portion (131). As the shaft receiving hole is formed at the center of the non-rotating plate portion (131), the discharge port is formed at an eccentric position from the shaft receiving hole.

[0128] The non-rotating side wall portion (132) is formed to protrude axially from the outer surface of the non-rotating side plate portion (131) toward the frame side plate portion (121). The non-rotating side wall portion (132) can extend circumferentially along the perimeter of the non-rotating side plate portion (131). The non-rotating side wall portion (132) is coupled to the frame side wall portion (123).

[0129] A suction port (133) is formed to penetrate radially on one side of the non-rotating side wall portion (132). The suction port (133) can be communicated with the inner end of the above-described refrigerant suction pipe (106).

[0130] The non-orbiting wrap (135) protrudes axially from the upper surface of the non-orbiting plate portion (131) toward the orbiting scroll (124) by a predetermined height. The non-orbiting wrap (135) extends around the discharge port so as to be wound several times in a spiral manner toward the non-orbiting side wall portion (132).

[0131] The non-rotating wrap (135) can be formed to correspond to the rotating wrap (126). The lengths of the non-rotating wrap (135) and the rotating wrap (126) can be the same. Through this, two pairs of compression chambers can be formed between the non-rotating wrap (135) and the rotating wrap (126).

[0132] The operation process of the scroll compressor according to the present embodiment will be described below.

[0133] When power is applied to the stator coil (113) of the drive motor (110), the rotor (115) rotates relative to the stator (111) due to electromagnetic interaction between the magnetic field formed around the stator coil (113) and the permanent magnet (117) of the rotor (115). The rotation shaft (118) connected to the rotor (115) rotates.

[0134] The orbiting scroll (124) eccentrically coupled to the rotation axis (118) does not rotate by the Oldham ring (128) but orbits the non-orbiting scroll (130).

[0135] At this time, the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually decreases from the outside of the non-rotating scroll (130) toward the center. Through this, the refrigerant is sucked into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (106).

[0136] The refrigerant is compressed as it moves along the movement path of each compression chamber. The compressed refrigerant is discharged into the muffler space (137) of the discharge cover (136) through a discharge port connected to the compression chamber.

[0137] The refrigerant in the muffler space (137) is discharged to the discharge space (S12) between the main frame (120) and the driving motor (110) through the discharge hole provided in the non-rotating scroll (130) and the main frame (120).

[0138] The refrigerant in the above discharge space (S12) passes through the driving motor (110) and moves to the upper space (S2) of the casing (100). The refrigerant is separated into refrigerant and oil in the upper space (S2). The separated refrigerant can be discharged to the outside of the casing (100) through the refrigerant discharge pipe (105).

[0139] Oil separated from the refrigerant can be rotated into the oil storage space (S11) of the casing (100) through the oil recovery passage. The oil is supplied to each wetted part and compression chamber through the oil passage (1181) of the rotating shaft (118) and then returned to the oil storage space (S11) of the casing (100), a process that is repeated.

[0140] 3. Description of the overheating protection structure of a scroll compressor according to one embodiment of the present invention.

[0141] FIG. 2 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to one embodiment by enlarging II in FIG. 1.

[0142] Figure 3 is a conceptual diagram showing a thermal expansion member (139) installed in the rotating scroll (124) in Figure 2.

[0143] Figure 4 is a conceptual diagram showing the operating state of the thermal expansion part (139) before operation (normal operation) and after operation (overheating) by enlarging IV in Figure 2.

[0144] The back pressure chamber can be formed between one side of the rotating plate (125) facing in the opposite direction to the non-rotating scroll (130) and one side of the frame plate (121) with respect to the rotating plate (125). The back pressure chamber is connected to the compression chamber so as to form an intermediate pressure of the refrigerant. The back pressure chamber can pressurize the rotating plate (125) in the axial direction by the intermediate pressure, that is, the back pressure.

[0145] The orbiting plate (125) is pressed toward the non-orbiting scroll (130) by the back pressure, so that during normal operation, the orbiting wrap (126) can be axially pressed against the non-orbiting plate (131) by the back pressure. In addition, during normal operation, the orbiting plate (125) can be axially pressed against the non-orbiting wrap (135) by the back pressure.

[0146] The thickness of the orbital wrap (126) is formed between the outer surface and the inner surface of the orbital wrap (126). Based on the orbital wrap (126), a first compression chamber (V1) and a second compression chamber (V2) can be formed between the outer surface of the orbital wrap (126) and the inner surface of the non-orbital wrap (135) and between the inner surface of the orbital wrap (126) and the outer surface of the non-orbital wrap (135), respectively.

[0147] As the rotating lap (126) and the non-rotating plate (131) are in close contact with each other, and as the rotating plate (125) and the non-rotating lap (135) are in close contact with each other, refrigerant leakage between the first compression chamber (V1) and the second compression chamber (V2) can be suppressed.

[0148] However, the compressor suction port (133) may become blocked due to foreign substances or valve malfunction.

[0149] If the refrigerant is not introduced through the suction port (133), recompression is repeated in a state where there is no refrigerant in the compression chamber, resulting in a vacuum operation state.

[0150] Due to this, a problem may arise where the temperature in the center of the compression chamber rises excessively during vacuum operation.

[0151] To solve these problems, the scroll compressor according to the present invention provides a structure for separating the wrap tips of the orbiting scroll (124) and / or the non-orbiting scroll (130).

[0152] The lap tip refers to the end of the turning lap (126) or the end of the non-turning lap (135). For example, the end of the turning lap (126) refers to the end of the protruding height of the turning lap (126) that protrudes from the turning plate portion (125) toward the non-turning plate portion (131) and is located furthest from the turning plate portion (125).

[0153] The end of the non-rotating wrap (135) means the end of the protruding height of the non-rotating wrap (135) that protrudes from the non-rotating plate portion (131) toward the rotating plate portion (125) and is located furthest from the non-rotating plate portion (131).

[0154] Separating the wrap tip means separating the wrap tip of the rotating wrap (126) from the non-rotating plate part (131) or separating the wrap tip of the non-rotating wrap (135) from the rotating plate part (125).

[0155] To separate the above-mentioned lap tips, a thermal expansion member (139) is provided. The thermal expansion member (139) can be placed between the orbiting scroll (124) and the non-orbiting scroll (130). The thermal expansion member (139) can be mounted on the orbiting scroll (124) or the non-orbiting scroll (130).

[0156] In this embodiment, a thermal expansion member (139) is shown mounted on a rotating scroll (124). The thermal expansion member (139) may be located at the center of the rotating plate member (125). The thermal expansion member (139) may be installed on a rotating shaft coupling member (127) or a rotating wrap (126).

[0157] The inner end of the pivoting wrap (126) can be connected to the outer surface of the rotating shaft coupling portion (127). The thickness of the inner end of the pivoting wrap (126) is thicker than the thickness of the middle portion between the inner end and the outer end of the pivoting wrap (126). The thickness of the pivoting wrap (126) can be formed between the outer surface and the inner surface of the pivoting wrap (126).

[0158] The thickness of the rotation shaft coupling portion (127) can be formed between the outer surface and the inner surface of the rotation shaft coupling portion (127).

[0159] The thickness of the inner end of the pivot wrap (126) and the connecting portion of the rotation shaft coupling portion (127) is thicker than the thickness of the middle portion of the pivot wrap (126) or the thickness of the rotation shaft coupling portion (127).

[0160] A thermal expansion receiving groove (138) may be formed to be sunken in the inner end of the turning wrap (126) and the connecting portion of the rotating shaft coupling portion (127). The thermal expansion receiving groove (138) may be sunken in the axial direction from the wrap tip of the turning wrap (126) toward the turning plate portion (125).

[0161] The thermal expansion part receiving groove (138) is arranged to face the non-rotating plate part (131). The thermal expansion part receiving groove (138) can be formed to penetrate toward the non-rotating plate part (131). The thermal expansion part (139) is received in the thermal expansion part receiving groove (138). The thermal expansion part receiving groove (138) is formed to surround the thermal expansion part (139).

[0162] The thermal expansion member receiving groove (138) may be formed to correspond to the shape of the thermal expansion member (139). In the present embodiment, the thermal expansion member receiving groove (138) may be formed in a cylindrical shape with one side open. The thermal expansion member (139) may be formed in a cylindrical shape.

[0163] The thermal expansion unit receiving groove (138) or thermal expansion unit (139) can be placed close to the discharge chamber with the highest pressure among the compression chambers.

[0164] The depression depth of the thermal expansion receiving groove (138) is smaller than the height of the rotating shaft coupling portion (127) or the height of the rotating wrap (126). The height of the rotating shaft coupling portion (127) or the height of the rotating wrap (126) refers to the protrusion length of the rotating shaft coupling portion (127) or the protrusion length of the rotating wrap (126) that protrudes axially from the rotating plate portion (125) based on the rotating plate portion (125).

[0165] The depth of the recess of the thermal expansion member receiving groove (138) can be configured at a ratio ranging from 1 / 5 to 1 / 2 compared to the height of the rotary shaft coupling portion (127) or the rotary wrap (126). However, the depth of the recess of the thermal expansion member receiving groove (138) is not limited thereto and can be changed in consideration of the size and thermal expansion coefficient of the thermal expansion member (139).

[0166] The thermal expansion coefficient of the thermal expansion portion (139) is different from the thermal expansion coefficient of the compression portion. For example, the thermal expansion coefficient of the thermal expansion portion (139) is greater than the thermal expansion coefficient of the compression portion.

[0167] The coefficient of thermal expansion, or rate of thermal expansion, defines the ratio between the thermal expansion of an object under constant pressure and its temperature. The higher the coefficient of thermal expansion, the greater the change in size (volume) of the object with temperature changes.

[0168] The compression member may be made of cast iron. The thermal expansion member (139) may be formed of one or a combination of two or more of nickel steel, chromium nickel steel, and manganese steel.

[0169] A comparison of the coefficients of thermal expansion of cast iron and nickel steel is shown in Table 1 below.

[0170] [Table 1]

[0171]

[0172] When the temperature at the center of the compression chamber rises during vacuum operation, the change in size (volume) of the thermal expansion portion (139) is relatively much larger than the change in size of the compression portion.

[0173] Accordingly, when the temperature at the center of the compression chamber rises, the thermal expansion portion (139) expands in all directions due to heat. The thermal expansion portion (139) expands in volume through the open side of the thermal expansion portion receiving groove (138). The thermal expansion portion (139) protrudes from the wrap tip of the rotating wrap (126) toward the non-rotating plate portion (131), thereby applying an axial pressure to the non-rotating plate portion (131).

[0174] The wrap tip of the orbiting wrap (126) can be separated from the non-orbiting plate portion (131). A gap is created between the wrap tip of the orbiting wrap (126) and the non-orbiting plate portion (131). During vacuum operation, the compressed refrigerant or vacuum pressure moves through the gap to an adjacent compression chamber, for example, an intermediate pressure chamber. The compressed refrigerant or vacuum pressure may leak through the gap, causing the compression portion to idle.

[0175] Therefore, according to the present invention, a thermal expansion portion (139) having a larger thermal expansion coefficient than the compression portion can be installed embedded in one side of the orbiting scroll (124). For example, the thermal expansion portion (139) can be installed in the center of the orbiting scroll (124). Specifically, the thermal expansion portion (139) can be arranged in the rotational shaft coupling portion (127) or the orbiting wrap (126) of the orbiting scroll (124). Alternatively, the thermal expansion portion (139) can be arranged in the connection portion between the rotational shaft coupling portion (127) of the orbiting scroll (124) and the orbiting wrap (126). The thickness of the connection portion where the rotational shaft coupling portion (127) of the orbiting scroll (124) and the orbiting wrap (126) meet can be thicker than the thickness of the rotational shaft coupling portion (127) or the orbiting wrap (126). A thermal expansion part receiving groove (138) may be formed at the connection portion between the rotary shaft coupling portion (127) of the above-mentioned rotary scroll (124) and the rotary wrap (126). A thermal expansion part (139) may be received in the thermal expansion part receiving groove (138). The thermal expansion part receiving groove (138) may be formed to be open toward the non-rotating plate portion (131). The thermal expansion part (139) may be arranged adjacent to the discharge port or discharge chamber.

[0176] The thermal expansion portion receiving groove (138) is covered by the non-rotating plate portion (131) during normal operation, and the wrap tip of the rotating wrap (126) is in close contact with the non-rotating plate portion (131).

[0177] When the temperature of the discharge chamber in the compression chamber rises above the preset temperature due to recompression during vacuum operation, the thermal expansion portion (139) is heated by the rise in temperature of the discharge chamber and expands in volume. The thermal expansion portion (139) can protrude through the opening of the thermal expansion portion receiving groove (138) and pressurize the non-rotating plate portion (131) in the axial direction.

[0178] Accordingly, the wrap tip of the rotating wrap (126) is separated from the non-rotating plate portion (131) to form a gap. The compressed refrigerant or vacuum pressure in the discharge chamber leaks through the gap, inducing idling of the compressor and preventing further temperature rise in the compression chamber.

[0179] In addition, the thermal expansion part (139) can protect the compressor by forcibly separating the rotating wrap (126) and the non-rotating plate part (131) during vacuum operation, thereby preventing further temperature rise until the operating conditions are normalized or an emergency stop is performed.

[0180] In addition, the thermal expansion part (139) can suppress excessive temperature rise in the compression chamber by keeping the wrap tip of the rotating wrap (126) away from the non-rotating plate part (131) even when there is no external power source during vacuum operation.

[0181] 4. Description of the overheating protection structure of a scroll compressor according to another embodiment of the present invention

[0182] FIG. 5 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to another embodiment of the present invention.

[0183] Figure 6 is a conceptual diagram showing a thermal expansion part (239) installed in the central portion of the non-rotating scroll (230) in Figure 5.

[0184] Figure 7 is a conceptual diagram showing the operating state of the thermal expansion part (239) before operation (normal operation) and after operation (overheating) by enlarging VII in Figure 5.

[0185] This embodiment differs from the embodiments of FIGS. 1 to 4 described above in that the thermal expansion member (239) is installed in the central portion of the non-rotating scroll (230).

[0186] The thermal expansion member receiving groove (238) may be formed to be axially recessed in the center of the non-orbiting scroll (230). The thermal expansion member receiving groove (238) may be arranged to face the rotation shaft coupling portion (127) of the orbiting scroll (224) in the axial direction.

[0187] The sub-bearing part (234) may be provided at the center of the non-rotating scroll (230). An axial receiving hole is formed to penetrate axially on the inside of the sub-bearing part (234). The rotary shaft (118) may be press-fitted to the inner surface of the sub-bearing part (234) through the axial receiving hole. The sub-bearing part (234) is configured to rotatably support the rotary shaft (118).

[0188] The thermal expansion receiving groove (238) can extend circumferentially along the periphery of the sub-bearing portion (234).

[0189] The thermal expansion member receiving groove (238) can be formed in a ring shape. The thermal expansion member receiving groove (238) is formed to be sunken into one surface of the non-rotating plate portion (131) facing the rotating scroll (224).

[0190] The thermal expansion part (239) is accommodated in the thermal expansion part accommodation groove (238).

[0191] During normal operation, the orbiting wrap (126) of the orbiting scroll (224) is pressed against the non-orbiting plate portion (131) by the above-described back pressure, thereby preventing leakage of refrigerant between the first compression chamber (V1) and the second compression chamber (V2).

[0192] When the temperature of the compression chamber rises above a preset temperature during vacuum operation, the thermal expansion portion (239) expands in volume due to the heat of the compression chamber. The expanded thermal expansion portion (239) can axially pressurize the rotary shaft coupling portion (127) of the orbiting scroll (224), thereby separating the orbiting scroll (224) and the non-orbiting scroll (230).

[0193] The wrap tip of the rotating wrap (126) may be separated from the non-rotating plate portion (131), so that a gap may be formed between the wrap tip of the rotating wrap (126) and one surface of the non-rotating plate portion (131). This can prevent the vacuum pressure or refrigerant in the compression chamber from leaking through the gap, thereby preventing the overheating of the compression chamber from continuing.

[0194] Therefore, it is possible to prevent heat-sensitive parts such as bearings and back pressure seals from being damaged due to excessive temperature rise in the compression chamber.

[0195] Since other components are the same or similar to the embodiments of FIGS. 1 to 4 described above, duplicate descriptions will be omitted.

[0196] 5. Description of the overheating protection structure of a scroll compressor according to another embodiment of the present invention.

[0197] FIG. 8 is a conceptual diagram showing an overheating protection structure of a scroll compressor according to another embodiment of the present invention.

[0198] Figure 9 is a conceptual diagram showing a thermal expansion member (339) installed on the edge (thrust surface (340)) of the non-rotating scroll (330) in Figure 8.

[0199] Figure 10 is a conceptual diagram showing the operating state of the thermal expansion part (339) before operation (normal operation) and after operation (overheating) by enlarging X in Figure 8.

[0200] This embodiment differs from the embodiments of FIGS. 1 to 7 described above in that a thermal expansion member (339) is installed on the thrust surface (340) of the non-rotating scroll (330).

[0201] A non-orbiting scroll (330) may include a non-orbiting plate portion (331), a non-orbiting wrap (335), and a non-orbiting side wall portion (332). The non-orbiting wrap (335) protrudes axially from the non-orbiting plate portion (331) toward the orbiting plate portion (325).

[0202] The non-rotating side wall portion (332) can protrude axially from the non-rotating plate portion (331) toward the frame side wall portion (123) of the main frame (120). The non-rotating side wall portion (332) can extend circumferentially along the perimeter of the non-rotating plate portion (331).

[0203] The axial heights of the non-rotating wrap (335) and the non-rotating side wall (332) are the same based on the non-rotating plate (331), so the ends of the non-rotating wrap (335) and the non-rotating side wall (332) are arranged on the same plane.

[0204] A non-orbiting scroll (330) may be provided with a thrust surface (340). The thrust surface (340) may be formed in a flat shape at an end of the non-orbiting side wall portion (332). The thrust surface (340) may form the same flat surface as the end surface of the non-orbiting wrap (335). The thrust surface (340) may extend circumferentially along the periphery of the non-orbiting side wall portion (332).

[0205] A portion of the thrust surface (340) may be in surface contact with an axial surface of the pivot plate portion (325). Another portion of the thrust surface (340) may be in surface contact with an axial surface (thrust surface) of the frame side wall portion (123).

[0206] The thermal expansion receiving groove (338) may be formed to be sunken in a portion of the thrust surface (340) that comes into contact with the pivot plate (325).

[0207] A plurality of thermal expansion member receiving grooves (338) may be provided. A plurality of thermal expansion member receiving grooves (338) may be arranged at equal intervals in the circumferential direction along the periphery of the thrust surface (340).

[0208] The thermal expansion member receiving groove (338) can be arranged to face the pivot plate member (325) in the axial direction.

[0209] A plurality of thermal expansion parts (339) can be accommodated in a plurality of thermal expansion part accommodation grooves (338).

[0210] The thermal expansion portion (339) may be formed in a cylindrical shape. The thermal expansion portion receiving groove (338) may be formed to correspond to the thermal expansion portion (339). The volume of the thermal expansion portion receiving groove (338) may be formed to be larger than the volume of the thermal expansion portion (339) in consideration of the volume expansion of the thermal expansion portion (339).

[0211] According to this configuration, when the temperature of the compression chamber rises excessively during vacuum operation, the thermal expansion portion (339) expands in volume. The expanded thermal expansion portion (339) presses the rotating plate portion (325) in the axial direction.

[0212] The wrap tip of the non-orbiting wrap (335) of the non-orbiting scroll (330) can be axially spaced from the orbiting plate portion (325) of the orbiting scroll (224) due to the volume expansion of the thermal expansion portion (339). The wrap tip of the orbiting wrap (326) of the orbiting scroll (224) can be axially spaced from the non-orbiting plate portion (331) of the non-orbiting scroll (330) due to the volume expansion of the thermal expansion portion (339).

[0213] Accordingly, the refrigerant or vacuum pressure of the overheated compression chamber can be prevented from leaking through the gap between the wrap tip of the non-rotating wrap (335) and the rotating plate part (325) and the gap between the wrap tip of the rotating wrap (326) and the non-rotating plate part (331), thereby preventing the overheating of the compression chamber from continuing.

Claims

1. Casing; A driving motor provided inside the above casing; A main frame arranged on one side of the above driving motor; A non-rotating scroll arranged in the opposite direction to the driving motor based on the main frame; An orbiting scroll connected to the driving motor through a rotating shaft, interlocked with the non-orbiting scroll so as to be capable of orbiting relative to the non-orbiting scroll, and forming a compression chamber together with the non-orbiting scroll; and A scroll compressor including a thermal expansion member arranged between the orbiting scroll and the non-orbiting scroll and thermally expanding when the temperature of the compression chamber rises to form a gap between the orbiting scroll and the non-orbiting scroll.

2. In paragraph 1, A scroll compressor in which the thermal expansion member has a larger thermal expansion coefficient than the orbiting scroll and the non-orbiting scroll.

3. In paragraph 1, A scroll compressor in which the above thermal expansion member is composed of different materials from the above orbiting scroll and the above non-orbiting scroll.

4. In paragraph 1, The above-mentioned orbiting scroll and the above-mentioned non-orbiting scroll are formed of cast iron, A scroll compressor in which the above thermal expansion member is formed of one or a combination of two or more of nickel steel, chromium nickel steel, and manganese steel.

5. In paragraph 1, A scroll compressor in which the above thermal expansion member is installed embedded in the central portion of the above rotating scroll or the above non-rotating scroll.

6. In paragraph 1, A scroll compressor in which the above thermal expansion member is installed between the edge of the above rotating scroll and the above non-rotating scroll.

7. In paragraph 1, The above non-rotating scroll is, Non-rotating plate section; and Including a non-rotating wrap protruding from the non-rotating plate portion toward the main frame, The above rotating scroll is, A rotating plate portion arranged between the main frame and the non-rotating plate portion; and A scroll compressor including a rotating wrap that protrudes from the rotating plate portion toward the non-rotating plate portion and is interlocked with the non-rotating wrap to enable a rotational movement with respect to the non-rotating wrap.

8. In paragraph 7, The above-mentioned turning wrap extends from the radially outer side of the above-mentioned turning plate toward the inner side, A thermal expansion part receiving groove is formed to be sunken in the radially inner end of the above-mentioned turning wrap, and the thermal expansion part is received in the thermal expansion part receiving groove. A scroll compressor in which the thermal expansion member forms a gap between the rotating wrap and the non-rotating plate part when the temperature of the compression chamber rises, or forms a gap between the non-rotating wrap and the rotating plate part.

9. In paragraph 7, The above rotating scroll is, It further includes a rotation shaft coupling part provided in the central part of the above-mentioned pivot plate and coupled with the rotation shaft, A thermal expansion part receiving groove is formed to be sunken in the above rotary shaft joint, and the thermal expansion part is received in the thermal expansion part receiving groove. A scroll compressor in which the thermal expansion member forms a gap between the rotating wrap and the non-rotating plate part when the temperature of the compression chamber rises, or forms a gap between the non-rotating wrap and the rotating plate part.

10. In paragraph 7, The above rotating scroll is, It further includes a rotation shaft coupling part provided in the central part of the above-mentioned pivot plate and coupled with the rotation shaft, A scroll compressor in which the rotating shaft coupling portion and the radially inner end of the rotating wrap are connected, a thermal expansion portion receiving groove is formed to be sunken between the rotating shaft coupling portion and the radially inner end of the rotating wrap, and the thermal expansion portion is received in the thermal expansion portion receiving groove.

11. In paragraph 7, The above non-rotating scroll is, It further includes a sub-bearing part provided in the central part of the non-rotating plate part and coupled with the rotating shaft, A scroll compressor in which a thermal expansion part receiving groove is formed to be sunken along the circumference of the above sub-bearing part, and the thermal expansion part is received in the thermal expansion part receiving groove.

12. In paragraph 7, The above non-rotating scroll is, It further includes a non-rotating side wall portion formed to protrude toward the main frame from the edge of the non-rotating plate portion, A thrust surface is arranged at the end of the above non-rotating side wall portion to face one axial surface of the above-mentioned rotating plate portion, A scroll compressor in which a thermal expansion member receiving groove is formed to be sunken in the thrust surface, and a thermal expansion member is received in the thermal expansion member receiving groove.

13. In paragraph 12, A scroll compressor in which the thrust surface extends circumferentially along the periphery of the non-rotating side wall portion, a plurality of thermal expansion member receiving grooves are provided on the thrust surface, and the plurality of thermal expansion member receiving grooves are arranged to be spaced apart from each other in the circumferential direction of the thrust surface.

Images