Scroll compressor

Abstract

In the scroll compressor of the present invention, a plurality of mutually separated fixing protrusions may be provided on the key constituting the Oldham ring, and a plurality of mutually separated fixing grooves may be provided on the orbiting scroll or the ring body of the Oldham ring coupled with the key, so that the plurality of fixing protrusions are respectively inserted and fixed. Thus, the motor efficiency can be improved by reducing the weight of the Oldham ring, and at the same time, the key constituting the Oldham ring can be prevented from being separated from the orbiting scroll or the ring body due to the difference in thermal deformation rate.

Description

Technical Field

[0001] The invention relates to a cross ring and a scroll compressor having the same. Background Art

[0002] A scroll compressor is a compressor in which one or two scrolls facing each other form a compression chamber that moves continuously while rotating. The scroll compressor may have an anti-rotation member that prevents a scroll (e.g., an orbiting scroll) that receives the rotational force of a drive motor from rotating relative to another scroll (e.g., a fixed scroll) or a fixed frame that faces it.

[0003] As a self-rotation prevention member, a cross ring (Oldham ring) or a pin and ring (pin & ring) is well known. Compared with the pin and ring, the cross ring is more advantageous in terms of assembly. Recently, a technology has been introduced that ensures the required rigidity while reducing the weight by making the ring body (ring body) and the key (key) constituting the cross ring different in material.

[0004] Patent document 1 (U.S. Patent Publication 2017 / 0234313A1) discloses a technique for reducing the weight of the cross ring while improving the wear resistance by forming the ring body and the key with different materials and pressing or engaging the key with the protrusion of the ring body. In Patent document 1, the key may be detached from the ring body during the operation of the compressor due to the reduction of mechanical reliability of the joint between the ring body and the key or due to the difference in thermal deformation rate between the ring body and the key.

[0005] On the other hand, there is also a technique in which the Oldham ring is formed of a single component and a wear-preventing member is provided between the key of the Oldham ring and the keyway of the scroll (or the frame).

[0006] Patent document 2 (Japanese Patent Publication No. 2017-133466) discloses a technique for suppressing wear between a keyway and a key by providing an anti-wear member between the keyway and the key. In Patent document 2, due to the difference in thermal expansion coefficient between the anti-wear member and the scroll plate (or fixed frame), during the operation of the compressor, the anti-wear member may be detached or the press rod may be loosened, resulting in vibration noise. Summary of the invention

[0007] Problems to be solved by the invention

[0008] An object of the present invention is to provide a scroll compressor capable of improving motor efficiency by reducing the weight of an Oldham ring as an anti-rotation mechanism.

[0009] Furthermore, an object of the present invention is to provide a scroll compressor in which a portion of an Oldham ring is formed of the same material as that of an orbiting scroll, thereby reducing the weight of the Oldham ring and reducing friction loss between the orbiting scroll and the Oldham ring.

[0010] Another object of the present invention is to provide a scroll compressor capable of suppressing the key from coming off due to a change in ambient temperature during operation by increasing the bonding force between the key constituting the Oldham ring and a member fixing the key.

[0011] Another object of the present invention is to provide a scroll compressor capable of improving the reliability of an Oldham ring by ensuring high support rigidity of a key constituting the Oldham ring and a member for fixing the key.

[0012] In addition, another object of the present invention is to provide a scroll compressor in which the entire Oldham ring can be formed of a lightweight material and the friction loss can be reduced.

[0013] Another object of the present invention is to provide a scroll compressor in which a wear preventing member can be inserted into an orbiting scroll or a main frame slidably coupled to a key of an Oldham ring and in which detachment of the wear preventing member is suppressed.

[0014] Another object of the present invention is to provide a scroll compressor capable of easily inserting an anti-wear member into an orbiting scroll or a main frame while effectively suppressing the anti-wear member from coming out.

[0015] Technical solutions to the problem

[0016] In order to achieve the purpose of the present invention, a scroll compressor can be provided, which includes a plurality of scrolls and a cross ring that limits the rotational motion of at least one of the plurality of scrolls. The plurality of scrolls are engaged with each other and can include a revolving scroll, which is at least one of the plurality of scrolls that is coupled to a rotating shaft and performs a revolving motion. The cross ring can be slidably coupled to the revolving scroll to guide the revolving motion of the revolving scroll. A key groove can be formed on one of the revolving scroll and the cross ring, and a key that is slidably inserted into the key groove can be formed on the other. The key can be provided with a plurality of fixed protrusions separated from each other, and the revolving scroll or the cross ring can be provided with a plurality of fixed grooves separated from each other for the plurality of fixed protrusions to be respectively inserted and fixed. As a result, the inside of the key is formed into a hollow shape, so that the weight of the key is reduced, and therefore, the motor efficiency can be improved by reducing the weight of the cross ring. At the same time, the key can be pressed into the plurality of press-fit surfaces, so that it is possible to suppress the key from being separated from the orbiting scroll or the ring body due to the difference in thermal deformation rate, thereby improving reliability.

[0017] As an example, a keyway may be formed in the Oldham ring, and a plurality of the fixing grooves may be formed on a side of the orbiting scroll facing the keyway. The plurality of fixing grooves are spaced apart from each other in the circumferential direction or radial direction, and may be in close contact with at least one side of the outer side and the inner side of the fixing protrusion. Thus, even if the ambient temperature conditions of the orbiting scroll or the Oldham ring change during operation, the reliability can be improved by suppressing the key from detaching from the orbiting scroll or the Oldham ring.

[0018] Specifically, the plurality of fixing protrusions and the plurality of fixing grooves may be paired one by one and spaced apart from each other in at least one of the circumferential direction and the radial direction, thereby suppressing key disengagement during thermal expansion and thermal contraction, thereby improving reliability.

[0019] As another example, the fixed protrusions may extend axially from the circumferential sides of the key. Thus, the weight of the key can be reduced while the anti-rotation function of the orbiting scroll is smoothly performed, and the radial ends of the key are open, thereby improving the oil supply effect on the key and the keyway.

[0020] As another example, a plurality of the fixing protrusions may be connected to form a ring. A plurality of the fixing grooves may be connected to form a ring. Thus, the key can be effectively prevented from being disengaged due to thermal deformation while reducing the weight of the key, and the support rigidity can be improved by ensuring the cross-sectional area of ​​the key.

[0021] As another example, the plurality of fixing protrusions may be formed to be spaced apart and parallel to each other. The plurality of fixing grooves may be formed to be spaced apart and parallel to each other. Thus, the key is fixed uniformly along the length direction, thereby being able to further effectively suppress separation caused by thermal deformation.

[0022] Specifically, the key may include a circumferential side surface and a radial side surface. The circumferential side surface may be respectively arranged on both sides of the circumference at a preset interval. The radial side surface may be respectively arranged on both sides of the radial direction at a preset interval, connecting the circumferential side surfaces on both sides to each other. A hollow portion may be formed between the inner side surfaces of the circumferential side surfaces on both sides and the inner side surfaces of the radial side surfaces on both sides, and one end of the circumferential side surface and one end of the radial side surface may form the fixing protrusion. Thus, the key can be effectively prevented from detaching due to thermal deformation while reducing its weight, and the support stiffness can be improved by ensuring the cross-sectional area of ​​the key.

[0023] In addition, the key may further include an axial side surface, the axial side surface connecting the circumferential side surfaces on both sides and the radial side surfaces on both sides. Thus, the reliability of the key can be improved by ensuring the rigidity of the circumferential side surfaces and the radial side surfaces.

[0024] Furthermore, a through hole may be formed in the axial side surface, the through hole having a cross-sectional area smaller than that of the hollow portion. Thus, a predetermined amount of oil is stored while preventing the refrigerant from filling the inside of the key, thereby reducing friction loss during restart.

[0025] As another example, the key may include a circumferential side surface and an axial side surface. The circumferential side surfaces may be arranged on both sides of the circumference at a preset interval. The axial side surface may connect the circumferential side surfaces on both sides. A hollow portion may be formed between the inner side surfaces of the circumferential side surfaces on both sides and the inner side surfaces of the axial side surfaces, and one end of the circumferential side surface may form the fixing protrusion. Thus, the support stiffness of the circumferential side surface of the key that substantially constitutes the cross ring can be ensured while removing the radial side surface.

[0026] As another example, the key may include a circumferential side surface. The circumferential side surfaces may be arranged on both sides of the circumference at a predetermined interval. The fixing protrusions may be formed by extending from the circumferential side surfaces on both sides toward the fixing groove. The circumferential side surface and the fixing protrusion may be formed on the same axis. Thus, the support stiffness can be improved by ensuring the cross-sectional area of ​​the key.

[0027] As another example, the key may include a circumferential side surface and a hollow portion. The circumferential side surfaces may be arranged on both sides of the circumference at a predetermined interval. The hollow portion may be arranged between the circumferential side surfaces on both sides. An oil supply groove may be formed on at least one outer side surface of the circumferential side surfaces on both sides, or an oil supply hole may be formed that passes through the outer side surface and the inner side surface. Thus, friction loss can be reduced by smoothly supplying a predetermined amount of oil between the key and the keyway.

[0028] As another example, the key may include a circumferential side surface and a hollow portion. The circumferential side surfaces may be arranged on both sides of the circumference at a predetermined interval. The hollow portion may be arranged between the circumferential side surfaces on both sides. An oil supply groove may be formed on the circumferential inner side surface of the keyway facing the circumferential side surface. Thus, friction loss can be reduced by smoothly supplying a predetermined amount of oil between the key and the keyway.

[0029] Here, the Oldham ring may be formed of the same material as the orbiting scroll, thereby reducing the weight of the Oldham ring and improving the motor efficiency.

[0030] In addition, the scroll compressor may further include a frame, the frame being formed of a different material from the orbiting scroll and being slidably arranged relative to the cross ring. A keyway may be formed in the frame. The cross ring may include: a ring body formed in a ring shape; and a key extending from the ring body and the ring body as a whole and inserted into the keyway of the frame. Thus, the ring body and a portion of the key of the cross ring may be formed of a lightweight material, thereby being able to improve the motor efficiency by reducing the weight of the cross ring.

[0031] In order to achieve the purpose of the present invention, a scroll compressor can be provided, which includes a plurality of scroll plates and a cross ring that limits the rotational movement of at least one of the plurality of scroll plates. The plurality of scroll plates can be engaged with each other, including a revolving scroll plate, which is at least one of the plurality of scroll plates that is coupled to a rotating shaft and performs a revolving movement. The cross ring can be slidably coupled to the revolving scroll plate to guide the revolving movement of the revolving scroll plate. A keyway can be formed in one of the revolving scroll plate and the cross ring. The cross ring can include: a ring body formed in an annular shape; and a key extending from the ring body and inserted into the keyway. A liner can be inserted into the keyway. A liner fixing groove can be formed on one circumferential side or both circumferential sides of the keyway, and the liner fixing groove can be formed to be separated from the keyway, and at least a portion of the liner fixing groove overlaps with the keyway in the circumferential direction. A gasket fixing platform may be formed between the keyway and the gasket fixing groove. Thus, the Oldham ring is formed of a single material, thereby further reducing the weight of the Oldham ring and improving reliability by inhibiting the gasket disposed between the Oldham ring and the orbiting scroll from being separated.

[0032] As an example, the gasket may include a gasket body, a gasket extension, and a gasket fixing portion. The gasket body may be inserted into the keyway, and the key may be slidably inserted into the gasket body. The gasket extension may extend circumferentially from the gasket body. The gasket fixing portion may extend axially from the gasket extension and be inserted into the gasket fixing groove. The gasket body and the gasket fixing portion may be formed to overlap circumferentially with the side surface of the gasket fixing platform. Thus, it is possible to effectively prevent the gasket from detaching due to the difference in thermal deformation rate between the orbiting scroll and the gasket.

[0033] In addition, a gasket insertion groove recessed in the axial direction to a preset depth may be formed in the axial cross section of the gasket fixing platform for the gasket extension to be inserted into. Thus, the gasket is hidden in the orbiting scroll, which can prevent the orbiting scroll from colliding with adjacent components when the orbiting scroll is in orbiting motion, so that the movement of the orbiting scroll becomes stable.

[0034] In addition, an oil supply groove extending in the radial direction may be formed on the inner side surface of the gasket body, so that a predetermined amount of oil is supplied between the gasket and the key, thereby preventing friction loss and wear between the gasket and the key in advance.

[0035] Here, the ring body and the key may be formed of the same material. The gasket may be formed of a material different from that of the cross ring. Thus, the weight of the cross ring can be reduced while suppressing friction loss and wear between the cross ring and the gasket.

[0036] Effects of the Invention

[0037] In the scroll compressor of the present invention, a plurality of mutually separated fixing protrusions may be provided on the key constituting the Oldham ring, and a plurality of mutually separated fixing grooves may be provided on the orbiting scroll or the ring body of the Oldham ring coupled with the key, so that the plurality of fixing protrusions are respectively inserted and fixed. Thus, the motor efficiency can be improved by reducing the weight of the Oldham ring, and at the same time, the key constituting the Oldham ring can be prevented from being separated from the orbiting scroll or the ring body due to the difference in thermal deformation rate.

[0038] In the scroll compressor of the present invention, the plurality of fixing protrusions and the plurality of fixing grooves can be paired one by one and spaced from each other in at least one of the circumferential direction and the radial direction. Thus, even if the ambient temperature conditions of the orbiting scroll or the Oldham ring change during operation, the reliability can be improved by suppressing the key from being separated from the orbiting scroll or the Oldham ring.

[0039] In the scroll compressor of the present invention, the fixed protrusions can extend axially from the circumferential sides of the key, thereby smoothly performing the anti-rotation function of the orbiting scroll and reducing the weight of the key, while the radial ends of the key are open, thereby improving the oil supply effect on the key and the keyway.

[0040] In the scroll compressor of the present invention, a plurality of fixing protrusions can be connected to each other to form a ring shape, and a plurality of fixing grooves can be connected to each other to form a ring shape. Thus, the weight of the key can be reduced and the key can be effectively prevented from being disengaged due to thermal deformation, while the support rigidity can be improved by ensuring the cross-sectional area of ​​the key.

[0041] In the scroll compressor of the present invention, the plurality of fixing protrusions can be formed to be spaced apart and parallel to each other, and the plurality of fixing grooves can be formed to be spaced apart and parallel to each other. Thus, the key is fixed uniformly along the length direction, thereby further effectively suppressing separation caused by thermal deformation.

[0042] In the scroll compressor of the present invention, a hollow portion may be formed between the inner side surfaces of the circumferential side surfaces on both sides and the inner side surfaces of the radial side surfaces on both sides, and a fixing convex portion may be formed at one end of the circumferential side surface and one end of the radial side surface. Thus, the weight of the key can be reduced and the key can be effectively prevented from being disengaged due to thermal deformation, while the support rigidity can be improved by ensuring the cross-sectional area of ​​the key.

[0043] The scroll compressor of the present invention may further include an axial side surface, the axial side surface connecting the circumferential side surfaces on both sides and the radial side surfaces on both sides, thereby improving the reliability of the key by ensuring the rigidity of the circumferential side surfaces and the radial side surfaces.

[0044] In the scroll compressor of the present invention, a through hole may be formed on the axial side surface, and the through hole has a cross-sectional area smaller than that of the hollow portion, thereby preventing the refrigerant from filling the inside of the key and storing a predetermined amount of oil, thereby reducing friction loss during restart.

[0045] In the scroll compressor of the present invention, the circumferential side surface and the fixing protrusion can be formed on the same axis. Thus, the support rigidity can be improved by ensuring the cross-sectional area of ​​the key.

[0046] In the scroll compressor of the present invention, at least one of the circumferential side surfaces on both sides may be formed with an oil supply groove or an oil supply hole that passes through the outer side surface and the inner side surface, thereby reducing friction loss by smoothly supplying a predetermined amount of oil between the key and the keyway.

[0047] In the scroll compressor of the present invention, an oil supply groove may be formed on the circumferential inner side surface of the keyway facing the circumferential side surface of the key, thereby reducing friction loss by smoothly supplying a predetermined amount of oil between the key and the keyway.

[0048] In the scroll compressor of the present invention, a keyway may be formed on one of the orbiting scroll and the Oldham ring, a liner may be inserted into the keyway, a liner fixing groove may be formed on one circumferential side or both circumferential sides of the keyway, the liner fixing groove may be formed to be separated from the keyway, at least a portion of the liner fixing groove overlaps the keyway in the circumferential direction, and a liner fixing platform may be formed between the keyway and the liner fixing groove. Thus, the Oldham ring is formed of a single material, thereby further reducing the weight of the Oldham ring, and at the same time, the reliability can be improved by suppressing the detachment of the liner provided between the Oldham ring and the orbiting scroll.

[0049] In the scroll compressor of the present invention, the gasket body and the gasket fixing portion constituting a part of the gasket can overlap with the side surface of the gasket fixing platform in the circumferential direction, thereby effectively preventing the gasket from detaching due to the difference in thermal deformation rate between the orbiting scroll and the gasket.

[0050] In the scroll compressor of the present invention, a gasket insertion groove that is recessed in the axial direction to a predetermined depth can be formed in the axial cross section of the gasket fixing platform for the gasket extension to be inserted into. As a result, the gasket is hidden in the orbiting scroll, which can prevent the orbiting scroll from colliding with adjacent components when the orbiting scroll performs an orbiting motion, thereby stabilizing the movement of the orbiting scroll.

[0051] In the scroll compressor of the present invention, an oil supply groove extending in the radial direction may be formed on the inner side surface of the liner body, so that a predetermined amount of oil is supplied between the liner and the key, thereby preventing friction loss and wear between the liner and the key in advance. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] Figure 1 1 is a cross-sectional view showing the scroll compressor of the present embodiment.

[0053] Figure 2 It is shown Figure 1 An exploded perspective view of a portion of the compression portion of the .

[0054] Figure 3 It is shown Figure 2 An exploded perspective view showing the state in which the second key is separated from the orbiting scroll.

[0055] Figure 4 It is shown Figure 3 A perspective view showing the state in which the second key is assembled to the orbiting scroll.

[0056] Figure 5 yes Figure 4 “Ⅳ-Ⅳ” line cross-sectional view.

[0057] Figure 6 This is a front view shown to explain another embodiment of the second key.

[0058] Figure 7 yes Figure 6 “VI-VI” line cross-sectional view.

[0059] Figure 8 and Fig. 9 yes Figure 5 The "V-V" line cross-sectional view is a cross-sectional view shown to illustrate the process of fixing the second bond as the temperature changes.

[0060] Fig.10 It is an exploded perspective view shown to explain still another embodiment of the second key.

[0061] Fig.11 It is an exploded perspective view shown to explain still another embodiment of the second key.

[0062] Fig.12It is an exploded perspective view shown to explain still another embodiment of the second key.

[0063] Fig.13 It is to illustrate Figure 1 An exploded perspective view of a portion of the compression portion is shown to illustrate another embodiment of the assembly position of the second key in the compression portion.

[0064] Fig.14 It is shown Figure 1 An exploded perspective view of the second keyway and the anti-wear member (liner) of the intermediate orbiting scroll.

[0065] Fig.15 It is shown Fig.14 A perspective view of another embodiment of the anti-wear component.

[0066] Fig.16 yes Fig.14 Assembly stereogram of .

[0067] Fig.17 and Fig.18 yes Fig.16 The cross-sectional view taken along the line "VII-VII" is a cross-sectional view shown to explain the process in which the wear-preventing member is fixed as the temperature changes. DETAILED DESCRIPTION

[0068] Hereinafter, a scroll compressor according to the present invention will be described in detail based on one embodiment shown in the accompanying drawings.

[0069] Depending on whether the drive motor and the compression part are arranged together in the internal space of the housing, the scroll compressor can be divided into a closed type and an open type. In the closed type, the drive motor and the compression part are arranged together in the internal space of the housing, and in the open type, the drive motor (or drive source) is arranged outside the housing. The present embodiment is described with a closed scroll compressor as a representative example. However, it can also be applied to an open scroll compressor.

[0070] In addition, scroll compressors can be divided into fixed scroll compressors and mobile scroll compressors. Fixed scroll compressors are usually used for building air conditioning, and mobile scroll compressors are used for vehicle air conditioning. This embodiment is described using a fixed scroll compressor as a representative example. However, it can also be applied to mobile scroll compressors.

[0071] In addition, according to the pressure of the refrigerant filled in the internal space of the shell, the scroll compressor can be divided into a low-pressure type and a high-pressure type. In the low-pressure type, the internal space of the shell is filled with the refrigerant of the suction pressure, and in the high-pressure type, the internal space of the shell is filled with the refrigerant of the discharge pressure. In this embodiment, a high-pressure scroll compressor is used as a representative example for explanation. However, it can also be applied to a low-pressure scroll compressor.

[0072] In addition, according to the setting position of the compression part, the scroll compressor can be divided into an upper compression type and a lower compression type. In the upper compression type, the compression part is arranged on the upper side than the driving motor, and in the lower compression type, the compression part is arranged on the lower side than the driving motor. In this embodiment, the upper compression type scroll compressor is used as a representative example for explanation. However, it can also be applied to the lower compression type scroll compressor.

[0073] In addition, depending on whether the scroll disk rotates, the scroll compressor can be divided into a deflected scroll compressor and an inter-rotating scroll compressor. The deflected scroll compressor is configured such that the scroll disk on one side is fixed or its rotational motion is restricted, while the scroll disk on the other side performs a swirling motion, and the inter-rotating scroll compressor is configured such that the scroll disks on both sides rotate. In this embodiment, the deflected scroll compressor is used as a representative example for explanation. However, it can also be applied to an inter-rotating scroll compressor.

[0074] In addition, the scroll compressor of this embodiment can also be applied to all scroll compressors using a cross ring.

[0075] Figure 1 1 is a cross-sectional view showing the scroll compressor of the present embodiment.

[0076] Reference Figure 1 In the scroll compressor of this embodiment, a driving motor 120 may be provided at the lower half of the housing 110, and a main frame 130 may be provided on the upper side of the driving motor 120. A compression unit is provided on the upper side of the main frame 130. The compression unit includes a fixed scroll 140 and an orbiting scroll 150, and depending on the situation, the main frame 130 may also be included in the compression unit for illustration.

[0077] The shell 110 of this embodiment may include a cylindrical shell 111, an upper cover 112, and a lower cover 113. Thus, the internal space 110a of the shell 110 may be divided into an upper space 110b provided inside the upper cover 112, an intermediate space 110c provided inside the cylindrical shell 111, and a lower space 110d provided inside the lower cover 113 based on the flow order of the refrigerant. Hereinafter, the upper space 110b may be defined as a discharge space, the intermediate space 110c may be defined as an oil separation space, and the lower space 110d may be defined as an oil storage space.

[0078] The cylindrical shell 111 has a cylindrical shape with upper and lower ends opened. The driving motor 120 is pressed into and fixed to the lower half of the inner circumference of the cylindrical shell 111 , and the main frame 130 is pressed into and fixed to the upper half of the inner circumference of the cylindrical shell 111 .

[0079] The middle space 110c of the cylindrical shell 111, specifically, the refrigerant discharge pipe 116 is connected through between the drive motor 120 and the main frame 130. The refrigerant discharge pipe 116 can be directly inserted into the cylindrical shell 111 and welded, but usually, an intermediate connecting pipe (collar pipe) (not shown) formed of the same material as the cylindrical shell 111 is inserted and welded to the cylindrical shell 111, and the refrigerant discharge pipe 116 formed of a copper pipe can be inserted and welded to the intermediate connecting pipe.

[0080] The upper cover 112 is coupled to the cylindrical shell 111 in a manner covering the upper end of the opening of the cylindrical shell 111. A refrigerant suction pipe 115 is coupled to the upper cover 112 through the upper space 110b of the shell 110 and is directly connected to a suction chamber (not shown) of a compression unit described later. Thus, refrigerant can be supplied to the suction chamber through the refrigerant suction pipe 115.

[0081] The lower cover 113 is combined with the cylindrical shell 111 in a manner covering the lower end of the opening of the cylindrical shell 111. The lower space 110d of the lower cover 113 forms an oil storage space, and a preset amount of oil can be stored in the oil storage space. The lower space 110d constituting the oil storage space can be connected to the upper space 110b and the middle space 110c of the shell 110 through an oil recovery passage (not marked). Thus, the oil separated from the refrigerant in the upper space 110b and the middle space 110c and the oil recovered after being supplied to the compression part can be recovered to the lower space 110d constituting the oil storage space through the oil recovery passage and stored.

[0082] Reference Figure 1 The driving motor 120 of this embodiment is disposed in the lower half of the intermediate space 110c forming the high-pressure portion in the internal space 110a of the housing 110, and includes a stator 121 and a rotor 122. The stator 121 is fixed to the inner wall surface of the cylindrical housing 111 by hot pressing, and the rotor 122 is rotatably disposed inside the stator 121.

[0083] The stator 121 includes a stator core 1211 and a stator coil 1212 .

[0084] The stator core 1211 is formed into a cylindrical shape and is fixed by heat pressing to the inner peripheral surface of the cylindrical housing 111. The stator coil 121a is wound around the stator core 1211 and is electrically connected to an external power source via terminals (not shown) penetrating and coupled to the housing 110.

[0085] The rotor 122 includes a rotor core 1221 and permanent magnets 1222 .

[0086] The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the stator core 1211 at a predetermined air gap interval. The permanent magnets 1222 are buried in the rotor core 1221 at predetermined intervals in the circumferential direction.

[0087] The rotating shaft 125 is press-fitted and coupled to the rotor 122. The rotating shaft 125 has an eccentric portion at its upper end and is rotatably supported radially by a main frame 130 described later. The rotating shaft 125 has a lower end rotatably supported radially and axially by a subframe 118.

[0088] In addition, an oil supply hole 1255 penetrating between both ends of the rotating shaft 125 may be formed inside the rotating shaft 125. The oil supply hole 1255 may be formed to penetrate from the lower end of the rotating shaft 125 to the bottom surface of the eccentric portion 1251. Thus, the oil stored in the lower space 110d constituting the oil storage space can be supplied to the inside of the eccentric portion 1251 through the oil supply hole 1255.

[0089] In addition, an oil absorber 126 may be provided at the lower end of the rotating shaft 125, more precisely, at the lower end of the oil supply hole 1255. The oil absorber 126 may be provided so as to be immersed in the oil stored in the oil storage space 110d. Thus, the oil stored in the oil storage space 110d is pumped by the oil absorber 126 and can be sucked upward through the oil supply hole 1255.

[0090] Reference Figure 1 The main frame 130 of this embodiment is disposed on the upper side of the driving motor 120 and is fixed by hot pressing or welding to the inner wall surface of the cylindrical shell 111. Therefore, the main frame 130 is usually formed of cast iron.

[0091] The main frame 130 includes a main flange portion 131 and a shaft supporting protrusion 132 .

[0092] The main flange portion 131 is formed in an annular shape and is accommodated in the middle space 110c of the cylindrical shell 111. For example, the outer peripheral surface of the main flange portion 131 may be formed in a circular shape and closely attached to the inner peripheral surface of the cylindrical shell 111. In this case, at least one axially penetrating oil recovery hole (not shown) may be formed between the outer peripheral surface and the inner peripheral surface of the main flange portion 131.

[0093] In addition, at least one frame fixing protrusion (not marked) may be formed extending radially on the outer peripheral surface of the main flange portion 131. The outer peripheral surface of the frame fixing protrusion may be tightly fixed to the inner peripheral surface of the cylindrical shell 111. In this case, the frame fixing protrusion may be formed with a second discharge channel groove 1421 spaced apart in the circumferential direction, and the second discharge channel groove 1421 passes through the axial side surfaces of the main flange portion 131. The second discharge channel groove 1421 may be formed to be connected to each other on the same axis as the first discharge channel groove 1421 described later. As a result, the upper space 110b and the middle space 110c are connected to each other, so that the refrigerant discharged from the compression portion to the upper space 110b moves to the middle space 110c and can be discharged to the condenser through the refrigerant discharge pipe 116.

[0094] In addition, an Oldham ring receiving portion (not shown) may be formed on the top surface of the main flange portion 131, and a first key groove (not shown) may be formed in the Oldham ring receiving portion. Two first key grooves may be formed with a phase difference of about 180 degrees in the circumferential direction.

[0095] The first key 162 of the cross ring 160 described later may be inserted into the first key groove in a radially slidable manner. In this case, a liner constituting an anti-wear member may be inserted into the first key groove, or the first key 162 of the cross ring 160 inserted into the first key groove may be formed of a different material (different material) from the ring body 161 of the cross ring 160.

[0096] For example, in the case where the main frame 130 is formed of the same material (material) as the first key 162 of the cross ring 160, a gasket formed of a different material from the main frame 130 or the cross ring 160 may be provided to suppress wear between the main frame 130 and the cross ring 160. Alternatively, the first key 162 may be assembled to the ring body 161 constituting the cross ring 160, and the first key 162 is formed of a different material from the main frame 130. However, as shown in the present embodiment, in the case where the main frame 130 and the ring body 161 of the cross ring 160 are formed of different materials from each other (for example, the main frame is cast iron and the first key of the cross ring is aluminum), there is no need to provide an additional gasket in the first keyway.

[0097] The shaft support protrusion 132 extends from the center of the main flange portion 131 toward the drive motor 120, and a shaft support hole 1321 is formed inside the shaft support protrusion 132. The shaft support hole 1321 can be formed through both axial sides of the main flange portion 131. Thus, the main flange portion 131 can be formed in a ring shape.

[0098] Reference Figure 1 The fixed scroll 140 of the present embodiment may include a fixed end plate portion 141 , a fixed sidewall portion 142 and a fixed scroll portion 143 .

[0099] The fixed end plate portion 141 may be formed in a circular plate shape. The outer peripheral surface of the fixed end plate portion 141 may be formed to be in close contact with the inner peripheral surface of the upper cover 112 constituting the upper space 110 b or to be spaced apart from the inner peripheral surface of the upper cover 112 .

[0100] In addition, a suction port 1411 that penetrates in the axial direction and communicates with a suction chamber (not shown) may be formed at the edge of the fixed end plate portion 141, and a refrigerant suction pipe 115 that penetrates the upper cover 112 of the shell 110 may be inserted and connected to the suction port 1411. Thus, the refrigerant suction pipe 115 may be directly connected to the suction port 1411 of the fixed scroll 140 through the upper space 110b of the shell 110.

[0101] In addition, a discharge port 1412 and a bypass hole (not shown) may be formed in the center of the fixed end plate 141, and a discharge valve 145 for opening and closing the discharge port 1412 and a bypass valve (not shown) for opening and closing the bypass hole may be provided on the top surface of the fixed end plate 141. Thus, the refrigerant compressed in the compression chamber V is discharged from the upper side of the fixed scroll 140 to the upper space 110b formed in the upper cover 112.

[0102] The fixed side wall portion 142 may extend in a ring shape from the edge of the fixed end plate portion 141 toward the main frame 130. Thus, the bottom surface of the fixed side wall portion 142 may be closely attached to the top surface of the main frame 130, ie, the top surface of the main flange portion 131, and be bolted.

[0103] At least one first discharge channel groove 1421 may be formed on the outer peripheral surface of the fixed side wall portion 142. The first discharge channel groove 1421 may be formed to be recessed from the outer peripheral surface of the fixed scroll 140, and communicate between the axial side surfaces of the fixed scroll 140. For example, the first discharge channel groove 1421 may be formed to communicate from the top surface of the fixed end plate portion 141 to the bottom surface of the fixed side wall portion 142. Thus, the upper end of the first discharge channel groove 1421 may be communicated with the upper space 110b, and the lower end of the first discharge channel groove 1421 may be communicated with the upper ends of the second discharge channel grooves 1421, 1311 provided on the main frame 130.

[0104] The fixed scroll portion 143 may extend from the bottom surface of the fixed end plate portion 141 toward the orbiting scroll 150. The fixed scroll portion 143 may be formed in various shapes such as an involute curve. The fixed scroll portion 143 may mesh with the orbiting scroll portion 153 described later to form two pairs of compression chambers V.

[0105] Reference Figure 1 The orbiting scroll 150 of the present embodiment may include an orbiting end plate portion 151 , a rotating shaft coupling portion 152 and an orbiting scroll portion 153 .

[0106] The orbiting end plate portion 151 is formed in a circular plate shape, is supported by the main frame 130 in the axial direction, and orbits between the main frame 130 and the fixed scroll 140 .

[0107] A second key 163 constituting a part of the later-described Oldham ring 160 may be provided on one side surface of the orbiting end plate portion 151, that is, on the side surface opposite to the orbiting scroll portion 153. The second key 163 may be provided with a phase difference of about 180 degrees in the circumferential direction.

[0108] The second key 163 may extend axially toward the Oldham ring 160 so as to be radially slidably inserted into a second key groove 1612 of the Oldham ring 160 described later. The second key 163 will be described again later together with the Oldham ring.

[0109] The rotating shaft coupling portion 152 may extend from the geometric center of the orbiting scroll 150 toward the eccentric portion 1251 of the rotating shaft 125. The rotating shaft coupling portion 152 may be rotatably inserted into the eccentric portion 1251 of the rotating shaft 125. Thus, the orbiting scroll 150 performs an orbiting motion through the eccentric portion 1251 of the rotating shaft 125 and the rotating shaft coupling portion 152.

[0110] The orbiting scroll portion 153 may extend from the top surface of the orbiting end plate portion 151 toward the fixed scroll 140. The orbiting scroll portion 153 may be formed in various shapes such as an involute curve to correspond to the fixed scroll portion 143.

[0111] The Oldham ring 160 may be disposed between the main frame 130 and the orbiting scroll 150. However, depending on circumstances, the Oldham ring 160 may also be disposed at the fixed scroll 140 and the orbiting scroll 150. In this embodiment, the Oldham ring 160 is disposed between the main frame 130 and the orbiting scroll 150.

[0112] For example, the Oldham ring 160 may be slidably coupled to the main frame 130 and the orbiting scroll 150. Thus, the Oldham ring 160 restricts the rotation of the orbiting scroll 150 so that the orbiting scroll 150 orbits relative to the main frame 130. The Oldham ring 160 will be described again later.

[0113] The scroll compressor of the present embodiment described above has the following effects.

[0114] That is, when power is applied to the driving motor 120 to generate a rotational force, the orbiting scroll 150 eccentrically coupled to the rotating shaft 125 orbits relative to the fixed scroll 140 via the Oldham ring 160. At this time, two pairs of compression chambers V are formed between the fixed scroll 140 and the orbiting scroll 150, which move continuously.

[0115] Then, while the orbiting scroll 150 is orbiting, the volume of the compression chamber V gradually narrows as it moves from the suction port (or suction chamber) 1411 to the discharge port (or discharge chamber) 1412 side.

[0116] Then, the refrigerant flows into the compression chamber V through the refrigerant suction pipe 115 via the suction port 1411 of the fixed scroll 140, and the refrigerant is compressed while moving toward the final compression chamber through the orbiting scroll 150. The refrigerant is discharged from the final compression chamber to the upper space 110b of the shell 110 through the discharge port 1412 of the fixed scroll 140, and moves to the middle space 110c and / or the lower space 110d of the shell 110 through the refrigerant guide channel composed of the first discharge channel groove 1421 and the second discharge channel groove 1311.

[0117] Then, the following series of processes are repeated: as the refrigerant circulates in the internal space 110a of the shell 110, the oil is separated from the refrigerant, and the oil separated from the refrigerant moves to the oil storage space constituting the lower space 110d of the shell 110 and is stored, and then is supplied to the compression part through the oil suction device 126 and the oil supply hole 1255 of the rotating shaft 125, and the refrigerant separated from the oil is discharged to the outside of the shell 110 through the refrigerant discharge pipe 116.

[0118] On the other hand, as mentioned above, the orbiting scroll is slidably coupled to the Oldham ring and orbits relative to the fixed scroll and / or the main frame. Therefore, forming the orbiting scroll and the Oldham ring with as light a material as possible is beneficial to improving the motor efficiency.

[0119] Therefore, in the prior art, it is known that the orbiting scroll and the Oldham ring are made of aluminum alloy material (hereinafter referred to as aluminum). In this case, the ring body and the second key of the Oldham ring are made of different materials from each other. The ring body can be made of aluminum material, which is the same material as the orbiting scroll, and the second key can be made of iron-based materials such as cast iron, which is a different material from the orbiting scroll.

[0120] However, as shown in Patent Document 1, when the ring body is formed with a fixing protrusion and the second key is inserted, not only the thickness of the fixing protrusion becomes thinner and the mechanical reliability is reduced, but also the key may be detached due to the difference in thermal deformation rate between the ring body and the second key. As shown in Patent Document 2, when the gasket is inserted into the second keyway of the orbiting scroll, the gasket may also be detached due to the difference in thermal deformation rate between the orbiting scroll and the gasket.

[0121] Therefore, in this embodiment, the ring body and the key of the cross ring can be formed of different materials and assembled later, or a wear-resistant coating layer can be formed on the key and assembled later, and double or multiple press-fit surfaces can be formed between the ring body and the key. In this way, while ensuring the rigidity of the part where the ring body and the key of the cross ring are combined, the detachment of the key caused by the difference in thermal deformation rate between the ring body and the key can be suppressed in advance. The following is mainly explained with the example that the ring body and the key constituting the cross ring are formed of different materials.

[0122] Figure 2 It is shown Figure 1 An exploded perspective view of a portion of the compression section in FIG. Figure 3 It is shown Figure 2 An exploded perspective view of the state in which the second key and the orbiting scroll are separated. Figure 4 It is shown Figure 3 A perspective view of the state in which the second key is assembled to the orbiting scroll. Figure 5 yes Figure 4 The "Ⅳ-Ⅳ" line cross-sectional view, Figure 6 is a front view for explaining another embodiment of the second key, Figure 7 yes Figure 6 “VI-VI” line cross-sectional view.

[0123] Reference Figures 2 to 5 The cross ring 160 of this embodiment may include a ring body 161 , a first key 162 and a second key 163 .

[0124] The first key 162 and the second key 163 may each be formed of a different material from the ring body 161, and either one of the first key 162 and the second key 163 may be formed of the same material as the ring body 161, and the other may be formed of a different material from the ring body 161. This embodiment is described mainly by taking the example that the first key 162 is formed of the same material as the ring body 161, and the second key 163 is formed of a different material from the ring body 161.

[0125] Specifically, the ring body 161 can be formed of the same material as the orbiting scroll 150, that is, aluminum. The specific gravity of cast iron used in the main frame 130 or the fixed scroll 140 is about 785, and the specific gravity of aluminum alloy is about 28. Therefore, when the ring body 161 of the Oldham ring 160 is formed of aluminum material, the increase of vibration noise caused by the reciprocating motion of the Oldham ring 160 during high-speed operation can be suppressed by reducing the weight of the Oldham ring 160, while the manufacturing cost of the Oldham ring 160 can be reduced.

[0126] The ring body 161 may be formed in a ring shape. The ring body 161 may be formed in a circular shape, or may be formed in an elliptical shape according to circumstances. This embodiment is described mainly with the example that the ring body 161 is formed in a circular shape.

[0127] The ring body 161 may be formed in a circular shape, and may form an expansion portion 1611 at an appropriate position along the circumferential direction. The expansion portion 1611 may be a portion where the Oldham ring 160 is coupled to the main frame 130 and the orbiting scroll 150, and may be formed at intervals of about 90 degrees.

[0128] The expansion portion 1611 may extend radially. For example, the expansion portion 1611 may extend radially from the outer circumference of the ring body 161, and may also extend radially from the inner circumference of the ring body 161 according to circumstances. Of course, the expansion portion 1611 may also extend radially from the outer circumference and the inner circumference of the ring body 161, respectively. This embodiment is described with the example that the expansion portion 1611 extends radially from the outer circumference of the ring body 161 as the center.

[0129] The expansion portion 1611 may be extended long in the radial direction to ensure the radial length of the first key 162 and / or the second key 163. Thus, while ensuring the radial length of the first key 162 and the second key 163 to the extent that the orbiting scroll 150 can be suppressed, the radial width of the ring body 161 can be minimized, thereby suppressing the increase in the weight of the Oldham ring 160.

[0130] The expansion portion 1611 may also extend in the axial direction. For example, the expansion portion 1611 may extend in the axial direction from one or both axial sides of the ring body 161 to a preset height. Thus, the ring body 161 is formed such that the axial height (thickness) of the expansion portion 1611 is greater than the axial height (thickness) of the portion outside the expansion portion 1611, and the axial side of the portion constituting the expansion portion 1611 is in contact with the main frame 130 or the orbiting scroll 150, so that it can be supported in the axial direction. Thus, the cross ring 160 can be slidably arranged between the main frame 130 and the orbiting scroll 150, while reducing the weight of the cross ring 160.

[0131] In addition, the first key 162 and the second key 163 may be integrally extended from the axial side of the expansion portion 1611 or assembled to the axial side of the expansion portion 1611. For example, the expansion portion 1611 may be formed by two first expansion portions 1611a and two second expansion portions 1611b, and the two first expansion portions 1611a and the two second expansion portions 1611b may be alternately formed along the circumferential direction.

[0132] The axial side surfaces of both sides of the first expansion portion 1611a are respectively formed flat, and the first key 162 can extend from one side surface (bottom surface) of the first expansion portion 1611a in the axial direction toward the first key groove of the main frame 130, and is formed integrally with the first expansion portion 1611a. Therefore, the first expansion portion 1611a constituting a part of the ring body 161 can be formed of the same material as the first key 162.

[0133] The axial side surfaces of the second expansion portion 1611b are flatly formed, and the second expansion portion 1611b may be formed with a second key groove 1612 that passes from one side surface (top surface) to the other side surface (bottom surface) of the second expansion portion 1611b. The second key 163 provided on the orbiting scroll 150 may be inserted into the second key groove 1612 in a radially slidable manner.

[0134] The second keyway 1612 may be formed long in the radial direction. For example, the second keyway 1612 may be formed in a rectangular shape that is long in the radial direction. The second keyway 1612 may be formed in a long hole shape in which both circumferential side surfaces are closed and both radial side surfaces are closed. However, depending on the situation, both circumferential side surfaces of the second keyway 1612 may be blocked, while one of the radial side surfaces may be opened. In this case, oil is smoothly supplied to the second keyway 1612, thereby reducing friction loss and wear.

[0135] As described above, the first key 162 may extend downward from one side of the first expansion portion 1611a constituting the ring body 161 toward the first key groove. Thus, the first key 162 may be formed of an aluminum material, which is the same material as the ring body 161. This is applicable when the main frame 130, into which the first key 162 is slidably inserted, is formed of a different material from that of the cross ring 160, such as cast iron. If the main frame 130 is formed of the same material as the cross ring 160, i.e., an aluminum material, the first key 162 may be assembled to the main frame 130 later, similarly to the second key 163 described later. In this case, first key grooves (not shown) are provided on both circumferential sides of the second key groove 1612 in the ring body 161, respectively, so that the first key 162 may be slidably coupled to the first key groove in the radial direction.

[0136] The second key 163 may be formed in a rectangular box shape as a whole, and one end facing a fixing groove 1511 described later may be opened so as to be inserted into the fixing groove 1511 .

[0137] As mentioned above, the fixing groove 1511 may be formed on one side of the rotating end plate 151, in other words, on the bottom surface of the rotating end plate 151 facing the cross ring 160, so that one end of the second key 163 can be inserted. The fixing groove 1511 may be formed corresponding to the fixing protrusion 1635.

[0138] Specifically, the fixing groove 1511 can be recessed to a predetermined depth so as to be inserted into the fixing protrusion 1635 of the second key 163 described later. For example, the fixing groove 1511 can be recessed so that one side of the fixing groove 1511 facing the fixing protrusion 1635 of the second key 163 is open, while the other side is closed.

[0139] Preferably, the depth of the fixing groove 1511 is formed as deep as possible so as to stably support the second key 163. For example, the axial depth of the fixing groove 1511 can be formed to be less than the axial height of the second key 163 and less than the axial thickness of the revolving end plate 151. Preferably, the axial depth of the fixing groove 1511 is formed to be more than about 1 / 2 of the axial thickness of the revolving end plate 151.

[0140] A plurality of fixing grooves 1511 may be formed in the revolving end plate 151. For example, the fixing groove 1511 may be formed of a plurality of circumferential fixing grooves 1612a and a plurality of radial fixing grooves 1612b.

[0141] The circumferential fixing groove portion 1612a and the radial fixing groove portion 1612b may also be formed to have the same length as each other. However, the circumferential fixing groove portion 1612a and the radial fixing groove portion 1612b may also be formed to be different from each other. For example, the circumferential side surface 1631 of the second key 163 is in sliding contact with the circumferential side surface 1631 of the first key groove, thereby preventing the rotational movement of the orbiting scroll 150. Therefore, the circumferential side surface 1631 of the second key 163 is subjected to a greater load than the radial side surface 1632, so the second key 163 may be formed so that the length of the circumferential fixing protrusion 1635 described later is longer than the length of the radial fixing protrusion 1635. Thus, the fixing groove portion 1511 may also be formed so that the length of the circumferential fixing groove portion 1612a is longer than the length of the radial fixing groove portion 1612b.

[0142] In addition, the plurality of circumferential fixing groove portions 1612a may be spaced apart from each other at predetermined intervals in the circumferential direction, and the plurality of radial fixing groove portions 1612b may be spaced apart from each other at predetermined intervals in the radial direction.

[0143] The plurality of circumferential fixing grooves 1612a and the plurality of radial fixing grooves 1612b are separated from each other and independently configured, but depending on the situation, both ends of the circumferential fixing groove 1612a and both ends of the radial fixing groove 1612b may be connected to each other to form an annular shape, for example, Figure 5 As shown, when projected axially, it can also be formed into a "mouth" cross-section shape.

[0144] On the other hand, as described above, the second key 163 may be formed to be inserted into and fixed to the fixing groove portion 1511, and thus the fixing protrusion 1635 constituting a part of the second key 163 may be formed to correspond to the shape of the fixing groove portion 1511. For example, the second key 163 may include a circumferential side surface 1631, a radial side surface 1632, an axial side surface 1633, a hollow portion 1634, and a fixing protrusion 1635.

[0145] The circumferential side surface 1631 can be formed into a pair of left and right sides to be inserted into the aforementioned circumferential fixing groove portion 1612a, and be spaced apart by a predetermined interval in the circumferential direction and parallel to each other. The outer side surface and the inner side surface of the circumferential side surface 1631 can be formed flat respectively. Thus, the circumferential side surface 1631 can be slidably combined in the radial direction while being supported in the circumferential direction relative to the circumferential inner side surface 1612a of the second key groove 1612.

[0146] In the circumferential side surface 1631 of the second key 163, the circumferential side surfaces 1631 on the left and right sides can be formed to have the same thickness. Thus, the production of the second key 163 including the circumferential side surface 1631 can be facilitated. However, depending on the situation, the thickness of the circumferential side surfaces 1631 on both sides can also be formed differently. In this case, the thickness of the circumferential side surface 1631 on the side in contact with the first key groove can be formed thicker. Thus, the rigidity of the second key 163 and the reliability against wear can be improved.

[0147] In addition, the circumferential side surface 1631 can be formed to have the same thickness as the radial side surface 1632 and / or the axial side surface 1633. Thus, the production of the second key 163 including the circumferential side surface 1631, the radial side surface 1632 and the axial side surface 1633 can be facilitated. However, depending on the situation, the thickness of the circumferential side surface 1631 can also be formed thicker than the thickness of the radial side surface 1632 and / or the axial side surface 1633. Thus, the rigidity and wear resistance of the circumferential side surface 1631 that substantially constitutes the friction surface can be improved, thereby improving the rigidity and reliability against wear of the second key 163.

[0148] In addition, the circumferential side surface 1631 may be formed into a closed shape. Thus, the wear of the circumferential side surface 1631 of the second key 163 can be suppressed by reducing the surface pressure at the circumferential side surface 1631. However, depending on the situation, a portion of the circumferential side surface 1631 may also be formed into an open or groove shape. For example, Figure 6 and Figure 7As shown, an oil supply groove 1631a may be formed on the circumferential side surface 1631 of the second key 163 facing the circumferential inner side surface 1515a of the second key groove 1515. The oil supply groove 1631a may be formed to radially cross between the two ends of the circumferential side surface 1631 at the middle height of the circumferential side surface 1631. In this case, oil can smoothly flow between the circumferential side surface 1631 of the second key 163 and the circumferential inner side surface 1612a of the second key groove 1612 facing it.

[0149] Although not shown, an oil supply groove (not shown) may also be formed on the circumferential inner side surface 11612a of the second key groove 1612. In this case, the circumferential side surface 1631 of the second key 163 is formed into a closed shape, thereby improving the wear resistance of the circumferential side surface 1631 of the second key 163.

[0150] The radial side surface 1632 can be formed by a pair of inner and outer sides to be inserted into the aforementioned radial fixing groove portion 1612b, and be parallel to each other with a predetermined interval in the radial direction. The inner circumferential radial side surface 1632 can connect the inner ends of the circumferential side surface 1631 to each other, and the outer circumferential radial side surface 1632 can connect the outer ends of the circumferential side surface 1631 to each other. Thus, as described above, the fixing protrusion 1635 of the second key 163 described later can be formed into a shape corresponding to the fixing groove portion 1511, that is, as Figure 5 As shown, it can be formed into a "mouth" cross-section shape when projected axially.

[0151] The radial side surface 1632 may be formed into a closed shape, or may be formed into a shape with at least a portion of the opening depending on the situation. When the radial side surface 1632 is formed into a closed shape, the circumferential side surface 1631 may be more firmly supported. The shape of the opening of the radial side surface 1632 will be described later in another embodiment.

[0152] The axial side surface 1633 is formed at the opposite end of the fixing protrusion 1635 described later in the axial ends of the second key 163, and the other end of the circumferential side surface 1631 and the other end of the radial side surface 1632 can be connected to each other by the axial side surface 1633. Thus, the circumferential side surface 1631 of the second key 163 can be circumferentially supported by the radial side surface 1632 of the second key 163 and the axial side surface 1633 of the second key 163. Thus, even if the circumferential side surface 1631 of the second key 163 is in sliding contact with the circumferential inner side surface 1612a of the second key groove 1612 and receives a circumferential load, the circumferential side surface 1631 of the second key 163 can maintain rigidity without deformation.

[0153] The axial side surface 1633 may be formed in a closed shape or in a partially open shape. The partially open shape of the axial side surface 1633 will be described later in another embodiment.

[0154] The hollow portion 1634 may be formed between the inner side surface of the circumferential side surface 1631, the inner side surface of the radial side surface 1632, and the inner side surface of the axial side surface 1633. The volume of the hollow portion 1634 is inversely proportional to the weight of the second key 163. Therefore, preferably, the volume of the hollow portion 1634 is formed as large as possible, so that the weight of the second key 163, that is, the cross ring 160, can be reduced.

[0155] Although not shown, the hollow portion 1634 may be removed or formed to be minimal even if the hollow portion 1634 is present. For example, in the present embodiment, the circumferential side surface 1631, the radial side surface 1632, and the axial side surface 1633 may be formed to have the same thickness as each other, but depending on the situation, at least one of the circumferential side surface 1631 and the radial side surface 1632 may be formed to be thinner or thicker than the other side surface. Thus, the hollow portion 1634 may also be formed to be larger or smaller than the hollow space provided inside the fixing protrusion 1635 described later.

[0156] The fixing protrusion 1635 may be formed at one end of the circumferential side surface 1631 and one end of the radial side surface 1632. In other words, the fixing protrusion 1635 may include: a circumferential fixing protrusion 1635a, which is provided at the end on the opposite side of the axial side surface 1633 in the circumferential side surface 1631; and a radial fixing protrusion 1635b, which is provided at the end on the opposite side of the axial side surface 1633 in the radial side surface 1632.

[0157] As described above, the fixing protrusion 1635 may be formed corresponding to the fixing groove 1511. Figure 5 As shown, the plurality of circumferential fixing protrusions 1635a and the plurality of radial fixing protrusions 1635b can be connected to each other, forming a "mouth" cross-sectional shape when projected in the axial direction. Thus, when the fixing protrusion 1635 is inserted into the fixing groove 1511, the outer side surface of the fixing protrusion 1635 can be configured to face the outer side surface of the fixing groove 1511, and the inner side surface of the fixing protrusion 1635 can be configured to face the inner side surface of the fixing groove 1511.

[0158] The circumferential fixing protrusion 1635a may extend flatly with the same thickness as the circumferential side surface 1631, and the radial fixing protrusion 1635b may extend flatly with the same thickness as the radial side surface 1632. In other words, the circumferential fixing protrusion 1635a may be formed flatly without forming a step on the same axis as the circumferential side surface 1631, and the radial fixing protrusion 1635b may be formed flatly without forming a step on the same axis as the radial side surface 1632. Thus, the cross-sectional area of ​​the fixing protrusion 1635 composed of the circumferential fixing protrusion 1635a and the radial fixing protrusion 1635b is increased, so that the rigidity of the fixing protrusion 1635 can be ensured while forming a hollow space inside the fixing protrusion 1635.

[0159] Although not shown, the circumferential fixing protrusion 1635a may be formed to protrude more circumferentially than the circumferential side surface 1631 and / or the radial fixing protrusion 1635b may be formed to protrude more radially than the radial side surface 1632. In this case, the cross-sectional area of ​​the circumferential fixing protrusion 1635a and / or the radial fixing protrusion 1635b is increased, so that the rigidity and wear resistance of the fixing protrusion 1635 can be further improved.

[0160] As described above, the fixing protrusion 1635 of the second key 163 of the present embodiment can be pressed into and fixed to the fixing groove 1511 of the revolving end plate 151. In other words, the fixing groove 1511 and the fixing protrusion 1635 are respectively formed into a "mouth" cross-sectional shape, so that when the compressor is stopped, the outer side surface of the fixing protrusion 1635 can be kept in a state of being almost or completely in contact with the outer side surface of the fixing groove 1511 and pressed in, and the inner side surface of the fixing protrusion 1635 can be kept in a state of being almost or completely in contact with the inner side surface of the fixing groove 1511 and pressed in.

[0161] On the other hand, during the operation of the compressor, the orbiting scroll 150 thermally expands or contracts according to the ambient temperature conditions, and the thermal deformation of the orbiting end plate 151 is greater than the thermal deformation of the second key 163, so that the orbiting end plate 151 and the second key 163 are opened, so that the second key 163 can be separated from the orbiting end plate 151. However, as shown in this embodiment, since the second key 163 has a plurality of pressing surfaces, during the operation of the compressor, the second key 163 can also remain in a state of being closely attached to the orbiting end plate 151, thereby preventing the second key 163 from being separated from the orbiting end plate 151.

[0162] Figure 8 and Fig. 9 yes Figure 5 The "V-V" line cross-sectional view is a cross-sectional view shown to illustrate the process of fixing the second bond as the temperature changes.

[0163] Reference Figure 8 , under high temperature conditions, the revolving end plate portion 151 thermally expands more than the second key 163. At this time, as shown in the prior art (Patent Document 1), if the ring body (corresponding to the revolving end plate portion of this embodiment) and the second key are formed in a column shape and have a press-fit surface, the ring body and the second key open due to the difference in thermal expansion, and the second key 163 may be detached.

[0164] However, in this embodiment, the fixed groove 1511 of the revolving end plate 151 and the fixed protrusion 1635 of the second key 163 are respectively formed in an annular shape, and a plurality of press-fit surfaces are formed between the fixed groove 1511 of the revolving end plate 151 and the fixed protrusion 1635 of the second key 163. As a result, the outer side surface of the fixed groove 1511 with a large thermal expansion amount expands more than the outer side surface of the fixed protrusion 1635 with a small thermal expansion amount, so that a gap may be generated between the outer side surface of the fixed groove 1511 and the outer side surface of the fixed protrusion 1635 facing it. On the other hand, the inner side surface of the fixed groove 1511 with a large thermal expansion amount expands more than the inner side surface of the fixed protrusion 1635 with a small thermal expansion amount, so that the inner side surface of the fixed groove 1511 is tightly attached to the inner side surface of the fixed protrusion 1635.

[0165] In other words, the outer side surface 1511a1 of the circumferential fixing groove 1511a expands from the outer side surface 1635a1 of the circumferential fixing protrusion 1635 due to thermal expansion, but the inner side surface 1511a2 of the circumferential fixing groove 1511a may be more closely attached to the inner side surface 1635a2 of the circumferential fixing protrusion 1635 due to thermal expansion. This phenomenon also occurs in the radial fixing groove 1511b and the radial fixing protrusion 1635b. Thus, even if the revolving end plate 151 and the second key 163 are formed of different materials with different thermal deformation rates, the second key 163 can be effectively prevented from detaching from the revolving end plate 151 when operating under high temperature.

[0166] On the other hand, in the low temperature state, the opposite phenomenon to the above-mentioned high temperature state occurs, so that the second key 163 can be kept fixed to the revolving end plate portion 151. Fig. 9 , under low temperature conditions, the revolving end plate portion 151 having a relatively large thermal deformation rate shrinks more than the second key 163 having a relatively small thermal deformation rate.

[0167] For example, the inner side surface 1511a2 of the circumferential fixing groove 1511a opens from the inner side surface 1635a2 of the circumferential fixing protrusion 1635 due to heat shrinkage, but the outer side surface 1511a1 of the circumferential fixing groove 1511a may be more closely attached to the outer side surface 1635a1 of the circumferential fixing protrusion 1635a due to heat shrinkage. This phenomenon also occurs in the radial fixing groove 1511b and the radial fixing protrusion 1635b. Thus, even if the revolving end plate 151 and the second key 163 are formed of different materials with different thermal deformation rates, the second key 163 can be effectively prevented from detaching from the revolving end plate 151 when operating in a low temperature state.

[0168] In this way, when the orbiting scroll and the Cross ring are formed of the same material, the ring body of the Cross ring is formed of the same material as the orbiting scroll, thereby reducing the weight of the Cross ring. On the other hand, the second key is formed of a different material from the ring body, thereby being able to suppress the friction loss between the orbiting scroll and the Cross ring.

[0169] In addition, when the orbiting scroll and the Cross ring are formed of the same material, the second key made of a different material from the ring body of the Cross ring is fixed to the orbiting scroll, and a double pressing surface is formed between the second key and the orbiting scroll, so that it can be fixed to the orbiting scroll. Thus, even if the thermal deformation rate of the orbiting scroll is greater than that of the second key, the reliability can be improved by effectively preventing the second key from detaching from the orbiting scroll during operation.

[0170] Furthermore, the second key made of a different material can be easily assembled to the orbiting scroll while ensuring the cross-sectional area of ​​the second key, thereby improving reliability by reinforcing the support rigidity of the second key at the portion coupled to the orbiting scroll.

[0171] On the other hand, another embodiment of the cross ring is as follows.

[0172] That is, in the aforementioned embodiment, the hollow portion 1634 of the second key 163 is formed in a closed shape, but depending on circumstances, a through hole may be formed in at least one of the plurality of side surfaces constituting the second key 163 .

[0173] Fig.10 It is an exploded perspective view shown to explain still another embodiment of the second key.

[0174] Reference Fig.10 , the second key 163 of this embodiment may include a circumferential side surface 1631, a radial side surface 1632, and an axial side surface 1633. The second key 163 including the circumferential side surface 1631 and the radial side surface 1632 may be formed almost the same as the aforementioned embodiment. Thus, the revolving end plate portion 151 and the fixing groove portion 1511 provided on the revolving end plate portion 151 are formed the same as the aforementioned embodiment, and the effects thereof are the same as the aforementioned embodiment, so the description of the aforementioned embodiment is used to replace the description thereof.

[0175] However, in this embodiment, at least one through hole 1633a may be formed on the axial side surface 1633. The through hole 1633a may be formed to be smaller than the area of ​​the axial side surface 1633 at the center portion of the axial side surface 1633, for example, less than about 1 / 2 of the area of ​​the axial side surface 1633.

[0176] The through hole 1633a may be formed in a circular shape, but may be formed in an elongated hole shape depending on the situation. When the through hole 1633a is formed in an elongated hole shape, forming it long in the radial direction may be advantageous for reliability.

[0177] Although not shown, in addition to the axial side surface 1633, the through hole can also be formed on the radial side surface 1632 or on the circumferential side surface 1631. The radial side surface 1632 does not form a bearing surface for the second key groove 1612, and thus can be formed on the inner circumferential side radial side surface 1632 or the outer circumferential side radial side surface 1632, respectively. The circumferential side surface 1631 forms a bearing surface for the second key groove 1612, and the side surface on the rotation direction side of the rotating shaft 125 can also be in closer contact with the second key groove 1612. Therefore, through holes (not shown) can also be formed on the circumferential side surfaces 1631 on both sides, respectively. In the case where a through hole (not shown) is formed on one circumferential side surface 1631, it may be advantageous to form a through hole on the side surface on the opposite side of the rotation direction of the rotating shaft 125.

[0178] As described above, when the through hole 1633a is formed on the axial side surface (or the other side surface) 1633 of the second key 163, even if refrigerant or air flows into the hollow portion 1634 of the second key 163, the refrigerant or air can be quickly discharged from the hollow portion 1634 through the through hole 1633a. Thus, it is possible to suppress the second key 163 from being separated from the orbiting scroll 150 due to the refrigerant or air filling the inside of the hollow portion 1634 and expanding and pushing the second key 163 from the orbiting scroll 150.

[0179] In addition, the oil around the Oldham ring 160 can flow into and be stored in the hollow portion 1634 through the through hole 1633a. The oil is stored in the hollow portion 1634, and lubricates the Oldham ring 160 and the orbiting scroll 150 when the compressor is restarted, thereby reducing friction loss and wear that may occur during restart.

[0180] On the other hand, another embodiment of the Oldham ring is as follows.

[0181] That is, in the aforementioned embodiment, the axial side surface 1633 of the second key 163 is closed or opened by more than half, but depending on the situation, the axial side surface 1633 of the second key 163 may be removed or the opening may be less than half of the cross-sectional area of ​​the second key 163.

[0182] Fig.11 It is an exploded perspective view shown to explain still another embodiment of the second key.

[0183] Reference Fig.11, the second key 163 of this embodiment may include a circumferential side surface 1631, a radial side surface 1632, and an axial side surface 1633. The second key 163 including the circumferential side surface 1631 and the radial side surface 1632 may be formed almost the same as the aforementioned embodiment. Thus, the fixed groove portion 1511 provided on the orbiting scroll 150 is formed the same as the aforementioned embodiment, and its function and effect are the same as the aforementioned embodiment, so the description of the aforementioned embodiment is used to replace the description thereof.

[0184] However, the second key 163 of this embodiment can remove the axial side surface 1633 or be formed so that the axial side surface 1633 is much smaller than the cross-sectional area of ​​the second key 163. In this embodiment, the case where the axial side surface 1633 is removed is shown. Thus, the axial side surfaces 1633 on both sides of the second key 163 are open, and the second key 163 can be formed by the circumferential side surface 1631 and the radial side surface 1632.

[0185] As mentioned above, in the second key 163 of the Cross ring 160, the circumferential side surface 1631 that is in sliding contact with the second key groove 1612 of the ring body 161 forms a bearing surface. Even if the radial side surface 1632 and the axial side surface 1633 are separated from the components facing them, it will not have a substantial impact on the anti-rotation function of the Cross ring 160.

[0186] Therefore, as shown in the present embodiment, even if the axial side surface 1633 on the opposite side of the fixed protrusion 1635 is removed, the Oldham ring 160 can slide smoothly relative to the orbiting scroll 150, thereby suppressing the rotational movement of the orbiting scroll 150. On the contrary, as shown in the present embodiment, since the axial side surface 1633 on the opposite side of the fixed protrusion 1635 is removed, the weight of the second key 163 having a relatively large specific gravity may be reduced. As a result, the overall weight of the Oldham ring 160 is reduced, thereby improving the motor efficiency.

[0187] On the other hand, the situation regarding still another embodiment of the Oldham ring is as follows.

[0188] That is, in the aforementioned embodiment, the radial side surface 1632 of the second key 163 is formed by extending from the circumferential side surface 1631 and the axial side surface 1633 , but depending on circumstances, the radial side surface 1632 may be removed or opened to less than half.

[0189] Fig.12 It is an exploded perspective view shown to explain still another embodiment of the second key.

[0190] Reference Fig.12 The second key 163 of this embodiment may include a circumferential side surface 1631, a radial side surface 1632, and an axial side surface 1633. The second key 163 including the circumferential side surface 1631 and the axial side surface 1633 may be connected to the aforementioned Figure 3In other words, the circumferential side surfaces 1631 on both sides may be connected to each other by the axial side surface 1633 at the upper end.

[0191] However, the radial side surface 1632 may be removed from the second key 163 of this embodiment. Therefore, the fixed groove portion 1511 provided in the orbiting scroll 150 may be formed differently from the above-mentioned embodiment.

[0192] Specifically, the fixing groove 1511 can be formed by removing the radial fixing grooves 1612b on both sides and only the circumferential fixing grooves 1612a on both sides. The circumferential fixing grooves 1612a on both sides can be formed to extend radially and be parallel to each other at a predetermined interval in the circumferential direction, that is, the circumferential width of the second key 163.

[0193] As shown in the present embodiment, even if the radial side surface 1632 is removed from the second key 163, the second key 163 can be stably fixed to the fixing groove portion 1511 of the revolving end plate portion 151. As described in the aforementioned embodiment, under high temperature conditions, the inner side surface 1635a1 of the circumferential fixing protrusion 1635a constituting one end of the second key 163 is tightly fixed to the inner side surface 1612a2 of the circumferential fixing groove portion 1612a provided in the revolving end plate portion 151, and under low temperature conditions, the outer side surface of the circumferential fixing protrusion 1635a constituting one end of the second key 163 can be tightly fixed to the outer side surface of the circumferential fixing groove portion 1612a provided in the revolving end plate portion 151.

[0194] In addition, even if the radial side surface 1632 is removed from the second key 163, the Oldham ring 160 of this embodiment can smoothly perform the function of preventing the orbiting scroll 150 from rotating, as in the above-mentioned embodiment. On the contrary, as shown in this embodiment, since the radial side surface 1632 is removed, the weight of the second key 163 with a relatively large specific gravity can be reduced. Therefore, the motor efficiency can be improved by reducing the overall weight of the Oldham ring 160.

[0195] Although not shown, the radial side surface 1632 may be formed to connect the circumferential side surfaces 1631 on both sides, that is, the middle of the circumferential side surfaces 1631 on both sides and the axial side surface 1633 to each other. Thus, the combination of the circumferential side surfaces 1631 on both sides and the radial side surface 1632 may also be formed into an "H" cross-sectional shape when projected axially. In this case, the radial side surface 1632 is reduced to one, thereby reducing the weight of the key, and at the same time, the reliability of the second key 163 can be ensured by improving the rigidity of the circumferential side surface 1631.

[0196] On the other hand, another embodiment of the Oldham ring is as follows.

[0197] That is, in the aforementioned embodiment, the second key 163 is fixedly coupled to the orbiting scroll 150 and slidably inserted into the ring body 161 of the Cross ring 160, but depending on the circumstances, the second key may also be fixedly coupled to the ring body 161 of the Cross ring 160 and slidably inserted into the orbiting scroll 150.

[0198] Fig.13 It is to illustrate Figure 1 An exploded perspective view of a portion of the compression portion is shown to illustrate another embodiment of the assembly position of the second key in the compression portion.

[0199] Reference Fig.13 The cross ring 160 may include a ring body 161, a first key 162, and a second key 163. The basic shapes and functions of the ring body 161, the first key 162, and the second key 163 are similar to those of the aforementioned embodiment, so the description of the aforementioned embodiment is used instead of the description thereof.

[0200] However, in this embodiment, the fixing groove 1613 is formed in the ring body 161, so that the fixing protrusion 1635 in one end of the second key 163 can be pressed into and combined with the ring body 161. In this case, the other end of the second key 163 can be inserted into the second key groove 1515 provided in the revolving end plate 151 in a radially slidable manner.

[0201] As described above, when the second key 163 is pressed into and coupled to the ring body 161 of the cross ring 160, the fixing protrusion 1635 and the fixing groove 1613 are also provided in plural numbers, and the plural fixing protrusions 1635 and the plural fixing grooves 1613 can be formed to be spaced apart from each other. Thus, the second key 163 forms a double pressing surface and is pressed into the ring body 161, so that even if the thermal deformation rate of the ring body 161 is greater than that of the second key 163, the second key 163 can be stably fixed.

[0202] On the other hand, still another embodiment of the wear preventing member is as follows.

[0203] That is, in the aforementioned embodiment, the ring body 161 and at least one key 162, 163 constituting the cross ring 160 are formed of different materials, but depending on the situation, the ring body 161 and the keys 162, 163 constituting the cross ring 160 are formed of the same material, and an additional anti-wear member (liner, gasket) 170 can be inserted into the second key groove 1515 provided in the orbiting scroll (or / and the fixed frame or the fixed scroll 150). In this case, the anti-wear member 170 can form a double or multiple press-fit surfaces with the second key groove 1515. The following description is centered on the example of the anti-wear member 170 being inserted into the second key groove 1515 of the orbiting scroll 150.

[0204] Fig.14 It is shown Figure 1 An exploded perspective view of the second keyway and the anti-wear member (liner) of the intermediate orbiting scroll, Fig.15 It is shown Fig.14 A perspective view of another embodiment of the anti-wear component, Fig.16 yes Fig.14 Assembly stereogram of Fig.17 and Fig.18 yes Fig.16 The "VII-VII" line cross-sectional view is a cross-sectional view shown to explain the process of fixing the wear-resistant component as the temperature changes.

[0205] Refer again Figure 1 The scroll compressor of this embodiment may be provided with a cross ring 160 as an anti-rotation member between the main frame 130 and the orbiting scroll 150. Therefore, the orbiting scroll 150 may form a compression chamber V between the fixed scroll 140 while performing an orbiting motion relative to the main frame 130.

[0206] The Oldham ring 160 is provided with a first key 162 and a second key 163 on both axial sides, respectively. The first key 162 can be slidably inserted into a first key slot provided on the main frame 130, and the second key 163 can be slidably inserted into a second key slot 1515 provided on the orbiting scroll 150. Thus, when the rotating shaft 125 rotates, the Oldham ring 160 reciprocates in four directions between the main frame 130 and the orbiting scroll 150, while limiting the rotation of the orbiting scroll 150 eccentrically coupled to the rotating shaft 125.

[0207] As described above, the Oldham ring 160 is attached to the driving motor 120 that generates a rotating force, and generates a centrifugal force with reciprocating motion, which affects the efficiency of the driving motor 120. Therefore, making the Oldham ring 160 as light as possible is beneficial to the motor efficiency.

[0208] In the Cross ring 160 of the aforementioned embodiment, the ring body 161 and the key may be formed of different materials from each other, but in the Cross ring 160 of the present embodiment, the first key 162 and the second key 163 may be formed of the same material as the ring body 161. Thus, the motor loss caused by the centrifugal force of the Cross ring 160 can be further reduced by further reducing the weight of the Cross ring 160. However, in the case where the Cross ring 160 is formed of the same material as the orbiting scroll 150, the friction loss on the Cross ring 160 and the orbiting scroll 150 may increase. Therefore, in the present embodiment, the Cross ring 160 may be formed of a single material, and the second key groove 1515 of the orbiting scroll 150 may be provided with an anti-wear member 170 of a different material from the Cross ring 160.

[0209] Reference Figures 14 to 16 The orbiting scroll 150 of this embodiment may include an orbiting end plate portion 151, a rotating shaft coupling portion 152, and an orbiting scroll portion 153. The basic structures and effects of the orbiting end plate portion 151, the rotating shaft coupling portion 152, and the orbiting scroll portion 153 are almost the same as those of the aforementioned embodiment, so the description of the aforementioned embodiment is used instead of the specific description thereof.

[0210] However, in the revolving end plate 151 of the present embodiment, a liner 170 as an anti-wear component is inserted into the second keyway 1515, and a liner fixing groove 1516 described later may be provided around the second keyway 1515 to fix the liner 170 by a plurality of press-fit surfaces.

[0211] Specifically, the second key groove 1515 may be extended long in the radial direction and formed into a "U" cross-sectional shape with an outer peripheral side open and an inner peripheral side closed. The second key groove 1515 may be formed so that the intervals between the inner side surfaces on both sides in the circumferential direction are substantially the same.

[0212] A gasket fixing groove 1516 may be formed on both sides of the second key groove 1515 in the circumferential direction. Although the gasket fixing grooves 1516 on both sides may be formed asymmetrically with the second key groove 1515 as the center, the gasket fixing grooves 1516 on both sides of the present embodiment may be formed symmetrically with the second key groove 1515 as the center. Thus, the gasket 170 receives a uniform supporting force in the circumferential direction, and thus may be stably fixed. Hereinafter, the gasket fixing groove 1516 on one side centered on the second key groove 1515 is described as a representative example.

[0213] The gasket fixing groove 1516 may be formed so that at least a portion overlaps the second key groove 1515 in the circumferential direction. For example, the gasket fixing groove 1516 may also be formed deeper than or equal to the second key groove 1515. In this case, the gasket fixing portion 173 described later may be pressed more tightly, so that the gasket 170 may be fixed more stably. However, considering the thickness of the revolving end plate portion 151, the gasket fixing groove 1516 may also be formed shallower than or equal to the second key groove 1515.

[0214] A gasket fixing platform 1517 may be formed between the gasket fixing groove 1516 and the second key groove 1515 . Thus, the second key groove 1515 may be separated from the gasket fixing groove 1516 by the gasket fixing platform 1517 .

[0215] The gasket fixing groove 1516 may be formed to be parallel to the second key groove 1515. For example, like the second key groove 1515, the gasket fixing groove 1516 may be formed to be long in the radial direction, and may be shorter than or equal to the second key groove 1515.

[0216] The gasket fixing platform 1517 may be formed to be smaller than or equal to the circumferential width of the second keyway 1515 or the circumferential width of the gasket fixing groove 1516. Thus, the gasket fixing groove 1516 is formed close to the second keyway 1515, so that the length of the gasket extension portion 172 described later can be minimized. Thus, the weight increase of the orbiting scroll 150 caused by the gasket 170 can be suppressed by minimizing the weight of the gasket 170.

[0217] A gasket insertion groove 1518 recessed in the axial direction to a predetermined depth may be formed in the axial cross section of the gasket fixing platform 1517. The gasket insertion groove 1518 is a portion for inserting the gasket extension portion 172, and may preferably be formed to a depth that prevents the gasket extension portion 172 from being exposed to the outside of the revolving end plate portion 151. For example, the depth of the gasket insertion groove 1518 is greater than or equal to the thickness of the gasket extension portion 172.

[0218] Although not shown, the gasket fixing groove 1516 and the gasket fixing platform 1517 may be formed only on one circumferential side of the second key groove 1515. In this case, the effect may be similar to that of the aforementioned embodiment, i.e., the gasket fixing groove 1516 and the gasket fixing platform 1517 are formed on both circumferential sides. However, compared with the case where the gasket fixing groove 1516 and the gasket fixing platform 1517 are formed on one circumferential side of the second key groove 1515, the manufacturing and assembly process of the gasket 170 can be simplified.

[0219] Reference Fig.14 and Fig.15 The gasket 170 of the present embodiment can be formed by cutting a material having higher rigidity than the orbiting scroll 150 made of aluminum, such as cast iron, or by die processing such as powder metallurgy. Thus, the gasket 170 can be formed to have the same thickness, but each part can also be formed to have different thicknesses as needed.

[0220] Specifically, the pad 170 may include a pad body 171, a pad extension 172, and a pad fixing portion 173. The pad body 171, the pad extension 172, and the pad fixing portion 173 may be formed by extending a single body, or at least a portion thereof may be assembled later. This embodiment shows an example in which the pad body 171, the pad extension 172, and the pad fixing portion 173 are formed by a single body.

[0221] The gasket body 171 can be inserted into the second key groove 1515 so that the second key 163 can be slidably inserted. The gasket body 171 can be formed into a long slit shape in the radial direction when projected in the axial direction, and can be formed into a "U" shaped cross-sectional shape when projected in the radial direction. Thus, the circumferential side surface 1631 of the second key 163 inserted into the gasket body 171 can be slidably coupled with the inner side surface (circumferential side surface) of the gasket body 171.

[0222] The inner side surface of the pad body 171 may be formed flat. However, depending on the situation, the inner side surface of the pad body 171 may also be formed concavely. For example, Fig.15 As shown, the oil supply groove 171a may be formed long in the radial direction on the inner side of the gasket body. In this case, the oil supply groove 171a may extend in the radial direction of the gasket body 171 to the outer peripheral side opening end.

[0223] As described above, when the oil supply groove 171a is formed on the inner side of the gasket body 171, the second key 163 can generate a pumping effect while reciprocating inside the gasket body 171. Then, the oil around the cross ring 160 flows into the inside of the gasket body 171 through the oil supply groove 171a due to the pumping effect, thereby lubricating the second key 163 and the gasket body 171. Although not shown in the figure, the oil supply groove can also extend in the axial direction.

[0224] The gasket extension portion 172 may further extend in the circumferential direction from both circumferential ends of the gasket body portion 171. The gasket extension portion 172 may be bent in the lateral direction and extend flatly from the end of the gasket body portion 171. The gasket extension portion 172 is inserted into the gasket insertion groove 1518 of the aforementioned orbiting scroll 150 and is hidden, and may be supported by the gasket fixing platform 1517 in the axial direction.

[0225] The gasket fixing portion 173 may be bent and extended in the axial direction from the gasket extension portion 172. The gasket fixing portion 173 may be formed to have a length inserted into the gasket fixing groove 1516, for example, the gasket fixing portion 173 may be formed to have a length overlapping with the gasket body portion 171 in the circumferential direction. Thus, the gasket fixing portion 173 may overlap with the side wall surface of the gasket fixing stage 1517 provided on one circumferential side of the second keyway 1515 in the circumferential direction.

[0226] As described above, the gasket fixing groove 1516 is formed on both circumferential sides of the second key groove 1515 separated by the gasket fixing platform 1517, so that the gasket fixing portion 173 inserted into the gasket fixing groove 1516 is independent of the thermal deformation of the orbiting scroll plate 150, and at least one side surface of the gasket fixing portion 173 can be pressed and fixed to the gasket fixing groove 1516.

[0227] Fig.17is a cross-sectional view showing the relationship between the liner and the orbiting scroll when the orbiting scroll thermally expands. Fig.18 2 is a cross-sectional view showing the relationship between the spacer and the orbiting scroll when the orbiting scroll is thermally contracted.

[0228] like Fig.17 As shown, during thermal expansion, the orbiting scroll 150 having a relatively large thermal deformation rate deforms in a direction opening around the second keyway 1515. At this time, the outer side surface 1516a of the gasket fixing groove 1516 expands more in the circumferential direction than the gasket fixing portion 173 having a relatively small thermal deformation rate. Then, a gap may be generated between the outer side surface 1516a of the gasket fixing groove 1516 and the outer side surface 173a of the gasket fixing portion 173.

[0229] However, the gasket fixing base 1517 constituting the inner side surface 1516b of the gasket fixing groove 1516 is thermally expanded more than the inner side surface 173b of the gasket fixing portion 173. Then, the gasket fixing base 1517 constituting the inner side surface 1516b of the gasket fixing groove 1516 is in close contact with the inner side surface 173b of the gasket fixing portion 173, thereby applying pressure and supporting in the direction of opening the gasket 170 (the direction away from the second key groove). This phenomenon also occurs in the opposite side gasket fixing portion 173, so that the gasket fixing portion 173 can be fixed by opening the gasket fixing bases 1517 on both sides in directions opposite to each other.

[0230] On the other hand, Fig.18 As shown, during thermal contraction, the opposite phenomenon to the aforementioned thermal expansion occurs, and the gasket 170 can be fixed. That is, during thermal contraction of the orbiting scroll 150, the orbiting scroll 150 having a relatively large thermal deformation rate deforms in a concave direction with the second keyway 1515 as the center. At this time, the gasket fixing platform 1517 constituting the inner side surface 1516b of the gasket fixing groove 1516 shrinks more in the circumferential direction than the gasket fixing portion 173 having a relatively small thermal deformation rate. Then, a gap may be generated between the gasket fixing platform 1517 constituting the inner side surface of the gasket fixing groove 1516 and the inner side surface 173b of the gasket fixing portion 173.

[0231] However, the outer side surface 1516a of the gasket fixing groove 1516 shrinks more than the outer side surface 173a of the gasket fixing portion 173. Then, the outer side surface 1516a of the gasket fixing groove 1516 and the outer side surface 173a of the gasket fixing portion 173 are closely attached to each other, so that the gasket 170 is pressed and supported in the concave direction (the direction close to the second key groove). This phenomenon also occurs in the opposite side gasket fixing portion 173, and the gasket fixing portion 173 can be fixed by concavely moving the gasket fixing grooves 1516 on both sides in opposite directions.

[0232] As such, in a case where the gasket 170 is inserted into the second key groove 1515 , the gasket 170 may be stably fixed to the second key groove 1515 without an additional fixing member.

[0233] In addition, in this embodiment, the ring body 161 and the key constituting the cross ring 160 are formed of a single material, thereby facilitating the manufacture of the cross ring 160 and enabling the entire cross ring 160 to be replaced with a thin material such as aluminum, thereby reducing the weight of the cross ring 160 accordingly, thereby improving the motor efficiency.

[0234] On the other hand, in the aforementioned embodiment, the main frame 130 is described mainly by an example in which the main frame 130 is formed of a different material from that of the Oldham ring 160 or the orbiting scroll 150, but depending on the situation, the main frame 130 may be formed of the same material as that of the Oldham ring 160 or the orbiting scroll 150. In this case, the first key 162 of the Oldham ring 160 may be coupled to the main frame 130 in the same manner as the aforementioned second key 163, and may be slidably coupled to the Oldham ring 160. The description of the aforementioned embodiment replaces the specific description thereof.

[0235] In addition, when the Oldham ring 160 is integrally formed, the aforementioned gasket 170 may be inserted into the first key groove (not shown) of the main frame 130. The detailed description thereof will be replaced by the description of the aforementioned embodiment.

Claims

1. A scroll compressor, wherein: include: A plurality of scrolls meshing with each other, including a revolving scroll, wherein the revolving scroll is at least one scroll among the plurality of scrolls that is coupled to the rotating shaft to perform a revolving motion; and A cross ring is slidably coupled to the orbiting scroll to guide the orbiting motion of the orbiting scroll. A key groove is formed on one of the orbiting scroll and the Oldham ring, and a key that is slidably inserted into the key groove is formed on the other. The key is provided with a plurality of fixing protrusions, and the orbiting scroll or the Oldham ring is provided with a plurality of fixing grooves for the plurality of fixing protrusions to be inserted and fixed respectively. The plurality of fixing protrusions are connected to each other to form a ring shape, and the plurality of fixing grooves are connected to each other to form a ring shape. The keys include: The circumferential side surfaces are respectively arranged on both sides of the circumference at a preset interval; as well as The radial side surfaces are arranged at both sides of the radial direction at a predetermined interval, connecting the circumferential side surfaces at both sides to each other. A hollow portion is formed between inner side surfaces of the circumferential side surfaces on both sides and inner side surfaces of the radial side surfaces on both sides, and one end portion of the circumferential side surface and one end portion of the radial side surface form the fixing protrusion.

2. The scroll compressor according to claim 1, wherein: A keyway is formed in the cross ring. A plurality of the fixing grooves are formed on a side surface of the orbiting scroll facing the key groove. The plurality of fixing grooves are spaced apart from each other in the circumferential direction or the radial direction and are in close contact with at least one of the outer side surface and the inner side surface of the fixing protrusion.

3. The scroll compressor according to claim 1, wherein: The plurality of fixing protrusions and the plurality of fixing grooves are paired one by one and are spaced apart from each other in at least one of a circumferential direction and a radial direction.

4. The scroll compressor according to claim 1, wherein: The fixing protrusions extend in the axial direction from both circumferential side surfaces of the key.

5. The scroll compressor according to claim 1, wherein: The key further includes an axial side surface connecting the circumferential side surfaces on both sides and the radial side surfaces on both sides.

6. The scroll compressor according to claim 5, wherein: A through hole is formed in the axial side surface, and the through hole has a smaller cross-sectional area than a cross-sectional area of ​​the hollow portion.

7. The scroll compressor according to claim 1, wherein: An oil supply groove is formed on the outer side surface of at least one of the circumferential side surfaces on both sides, or an oil supply hole is formed that passes through the outer side surface and the inner side surface.

8. The scroll compressor according to claim 1, wherein: An oil supply groove is formed on a circumferential inner side surface of the key groove facing the circumferential side surface.

9. The scroll compressor according to any one of claims 1 to 8, wherein: The Oldham ring is formed of the same material as that of the orbiting scroll.

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