Scroll compressor

Abstract

A scroll compressor is disclosed. The scroll compressor includes an Oldham ring having a plurality of orbiting-side keys on one side surface of a ring body thereof facing an orbiting scroll, wherein the plurality of orbiting-side keys may include an orbiting-side main key formed on a center line passing through the center of the ring body, and an orbiting-side sub-key provided on one side or both sides of the plurality of orbiting-side keys in the circumferential direction. As such, as the key area of the orbiting-side keys increases, the surface pressure between the orbiting-side keys and orbiting-side key recesses is reduced, thereby effectively restraining abrasion of an Oldham ring key.

Description

scroll compressor

[0001] The present invention relates to an oldham ring and a scroll compressor having the same.

[0002] A scroll compressor is a compressor in which one or two opposing scrolls form a compression chamber in which they continuously move while rotating. A scroll compressor may be equipped with an anti-rotation member to prevent a scroll (e.g., an orbiting scroll) receiving the rotational power of a driving motor from rotating relative to another opposing scroll (e.g., a fixed scroll) or a fixed frame. Commonly known anti-rotation members include Oldham rings and pin-and-rings.

[0003] Typically, the Oldham ring has keys formed on both axial sides of the ring body so that it can be slidably connected to the main frame and the orbiting scroll, respectively, or multiple keys formed on one axial side of the ring body so that it can be slidably connected to the fixed scroll and the orbiting scroll, respectively.

[0004] In these cases, the rotational force of the rotating shaft is transmitted to the Oldham ring through the orbiting scroll, and the key of the Oldham ring and the keyway of the orbiting scroll that accommodates the keyway and the keyway of the main frame (or fixed scroll) come into contact in the circumferential direction, thereby inducing the orbiting motion of the orbiting scroll.

[0005] However, in the case of a conventional scroll compressor, when the compression capacity increases and the force acting on the key of the Oldham ring increases, the surface pressure acting on the key of the Oldham ring increases, and the wear of the key of the Oldham ring may increase under the same lubrication conditions.

[0006] Taking this into consideration, the surface pressure acting on the Oldham ring key can be lowered by increasing the height of the Oldham ring or by forming the key longer to expand the key area. However, if the height of the Oldham ring is increased, the depth of the keyway of the orbiting scroll and / or main frame (or fixed scroll) in which the key of the Oldham ring is accommodated may also increase. In particular, in the case of the orbiting scroll, the thickness of the orbiting plate must be formed thicker as the depth of the keyway increases. This increases the weight of the orbiting scroll, which may lower the motor efficiency as the centrifugal force and moment increase during the orbiting motion of the orbiting scroll.

[0007] On the other hand, when the key length is increased, the outer diameter of the orbiting plate increases, which not only increases the centrifugal force and moment during the orbiting motion of the orbiting scroll, but also increases the weight of the Oldham ring, which may cause abnormal noise during compressor operation. In addition, the outer diameter of the main frame (or fixed scroll) increases, which may be detrimental to the miniaturization of the compressor.

[0008] The purpose of the present invention is to provide a scroll compressor capable of reducing the surface pressure and / or wear between the key of an oldham ring and the keyway of an orbiting scroll and / or a main frame (or fixed scroll) that accommodates the key.

[0009] Another object of the present invention is to provide a scroll compressor capable of suppressing an increase in the weight of an orbiting scroll by maintaining or lowering the height of the key of the Oldham ring while reducing the surface pressure acting on the key of the Oldham ring.

[0010] Another object of the present invention is to provide a scroll compressor capable of suppressing abnormal noise generated by an Oldham ring during operation of the compressor by maintaining or reducing the outer diameter of the Oldham ring while reducing the surface pressure between the key and the keyway.

[0011] To achieve the object of the present invention, a scroll compressor including a plurality of scrolls and an Oldham ring may be provided. The plurality of scrolls may be interlocked with each other, and may include an orbiting scroll in which at least one scroll is coupled to a rotational shaft and performs an orbiting motion. The Oldham ring may have a plurality of orbiting keys provided at predetermined intervals along a circumferential direction on one side of a ring body facing the orbiting scroll, and the plurality of orbiting keys may be slidably engaged with a plurality of orbiting key grooves provided on the orbiting scroll, respectively. The plurality of orbiting keys may include a orbiting main key formed on a centerline passing through the center of the ring body, and orbiting sub-keys provided on one or both circumferential sides of the plurality of orbiting main keys. As a result, the key area of ​​the orbiting key increases, thereby reducing the surface pressure between the key and the orbiting key groove, thereby effectively suppressing wear of the Oldham ring key.

[0012] For example, the pivot-side main key and the pivot-side sub-key may each be provided in multiple numbers. The multiple pivot-side sub-keys may be formed on the same side in the circumferential direction with respect to the multiple pivot-side main keys. This allows the key area of ​​the pivot-side key to increase while uniformly transmitting force to the pivot scroll, thereby stabilizing the behavior of the pivot scroll.

[0013] For example, the plurality of pivot-side sub-keys may be spaced apart from the plurality of pivot-side main keys by the same distance in the circumferential direction. This allows the positions of the Oldham ring keys to be formed symmetrically, thereby uniformly transmitting force to the pivot scroll, thereby further reducing wear on the Oldham ring keys.

[0014] Specifically, the circumferential gaps between the plurality of pivot keys and the plurality of pivot keyways can be formed to be identical to each other. This allows the key area to be maintained constant regardless of the direction of rotational force applied to the Oldham ring, while minimizing the surface pressure between the pivot keys and the pivot keyway.

[0015] In addition, the gap between the plurality of turning-side main keys and the plurality of turning-side sub-keys may be formed to be 0.13 to 0.2 times the outer diameter of the ring body, respectively. Through this, the total surface pressure generated between the turning-side keys and the turning-side keyway can be minimized, thereby significantly reducing the wear of the Oldham ring keys.

[0016] In addition, the length of each of the plurality of pivot-side sub-keys may be formed to be smaller than the length of each of the plurality of pivot-side main keys. This allows the total length of the Oldham ring key to be increased without increasing the outer diameter of the Oldham ring and / or the main frame, thereby increasing the key area as much as possible and further reducing the surface pressure.

[0017] In addition, the width of each of the plurality of pivot-side sub-keys may be formed to be the same as the width of each of the plurality of pivot-side main keys. Through this, the key area of ​​the Oldham ring key is expanded while the rigidity of the pivot-side key is secured, thereby improving the reliability of the Oldham ring.

[0018] In addition, the width of the plurality of pivot-side sub-keys may be formed to be smaller or larger than the width of the plurality of pivot-side main keys. Through this, the weight of the Oldham ring can be reduced while the rigidity of the pivot plate can be secured, or the key area for the pivot-side keys can be further expanded to maximize the surface pressure.

[0019] In order to achieve the object of the present invention, a scroll compressor including a plurality of scrolls and an Oldham ring may be provided. The plurality of scrolls may be interlocked with each other, and may include an orbiting scroll in which at least one scroll is coupled to a rotational shaft and performs an orbiting motion. The Oldham ring may have a plurality of orbiting keys provided at predetermined intervals along a circumferential direction on one side of a ring body facing the orbiting scroll, and the plurality of orbiting keys may be slidably engaged with a plurality of orbiting keyways provided on the orbiting scroll, respectively. The plurality of orbiting keys may be formed in at least four numbers, and the respective circumferential gaps between the plurality of orbiting keys and the plurality of orbiting keyways may be formed to be the same. Through this, the key area may be maintained constant regardless of the direction of application of a rotational force applied to the Oldham ring, while the surface pressure between the orbiting keys and the orbiting keyways may be reduced to a minimum.

[0020] For example, a plurality of non-rotating keys may be provided at predetermined intervals along the circumference of the ring body on the other side of the ring body facing away from one side of the ring body. The ring body may include a plurality of main pivot keys positioned on a centerline passing through the center of the ring body, and a plurality of sub-keys provided on one or both sides of the main pivot keys in the circumference. Through this, the key area of ​​the pivot keys may be increased while uniformly transmitting force to the pivot scroll, thereby stabilizing the behavior of the pivot scroll.

[0021] For example, the plurality of pivot-side sub-keys may be spaced apart from the plurality of pivot-side main keys by the same distance in the circumferential direction. This allows the positions of the Oldham ring keys to be formed symmetrically, thereby uniformly transmitting force to the pivot scroll, thereby further reducing wear on the Oldham ring keys.

[0022] In addition, the plurality of pivot keys may be spaced apart from the center line passing through the center of the ring body by a predetermined distance in both circumferential directions. This allows the center of gravity of the Oldham ring to coincide with the center of the ring body, thereby reducing the surface pressure while effectively suppressing abnormal behavior of the Oldham ring during compressor operation.

[0023] Specifically, the plurality of pivot keys may be formed in parallel and spaced apart from the center line in the circumferential direction by equal intervals. This allows the positions of the Oldham ring keys to be formed symmetrically, thereby uniformly transmitting force to the pivot scroll, thereby further reducing wear on the Oldham ring keys.

[0024] Specifically, the plurality of pivot keys may be formed to have the same length or width. This allows the key area of ​​the Oldham ring key to be expanded while ensuring the rigidity of the pivot key, thereby enhancing the reliability of the Oldham ring.

[0025] Specifically, the spacing between the plurality of pivot keys provided on both sides in the circumferential direction around the center line may be formed to be 0.13 to 0.2 times the outer diameter of the ring body. Through this, the total surface pressure generated between the pivot key and the pivot keyway can be minimized, thereby significantly reducing the wear amount of the Oldham ring key.

[0026] A scroll compressor according to the present invention comprises a plurality of pivot keys on one side of a ring body facing an orbiting scroll, wherein the plurality of pivot keys may include a pivot main key formed on a centerline passing through the center of the ring body, and pivot sub keys provided on one or both sides of the pivot keys in the circumferential direction. Through this, as the key area of ​​the pivot key increases, the surface pressure between the key and the pivot keyway decreases, thereby effectively suppressing wear of the Oldham ring key.

[0027] In addition, in the scroll compressor according to the present invention, a plurality of pivot-side sub-keys can be formed on the same side in the circumferential direction with respect to a plurality of pivot-side main keys. This allows the key area of ​​the pivot-side key to be increased while uniformly transmitting force to the pivot scroll, thereby stabilizing the behavior of the pivot scroll.

[0028] In addition, in the scroll compressor according to the present invention, the circumferential gaps between the plurality of pivot keys and the plurality of pivot keyways can be formed to be identical to each other. This allows the key area to be maintained constant regardless of the direction of rotational force applied to the Oldham ring, while minimizing the surface pressure between the pivot keys and the pivot keyways.

[0029] In addition, the scroll compressor according to the present invention can be formed so that the gap between the plurality of pivot-side main keys and the plurality of pivot-side sub-keys is 0.13 to 0.2 times the outer diameter of the ring body, respectively. This minimizes the total surface pressure generated between the pivot-side keys and the pivot-side keyway, thereby significantly reducing the wear of the Oldham ring keys.

[0030] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0031] Fig. 2 is a perspective view showing the rotary scroll and old ring in disassembly according to the present embodiment.

[0032] Figure 3 is a plan view showing the assembled rotary scroll and old ring of Figure 2.

[0033] Figure 4 is a cross-sectional view taken along line Ⅳ-Ⅳ" of Figure 3.

[0034] Fig. 5 is a plan view showing the old ring according to Fig. 2.

[0035] Fig. 6 is a graph showing the change in surface pressure with respect to the change in the spacing of the turning keys in the old ring according to the present embodiment.

[0036] Figure 7 is a perspective view showing another embodiment of an old ring separated from a rotating scroll.

[0037] Fig. 8 is a plan view showing the old ring according to Fig. 7.

[0038] Figure 9 is a perspective view showing another embodiment of an old ring separated from a rotating scroll.

[0039] Fig. 10 is a plan view showing the old ring according to Fig. 9.

[0040] Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment illustrated in the attached drawings.

[0041] Scroll compressors can be classified as sealed or open types, depending on whether the drive motor and compression unit are installed together within the internal space of the casing. In sealed types, the drive motor and compression unit are installed together within the internal space of the casing, while in open types, the drive motor (or drive source) is installed outside the casing. This embodiment describes a sealed scroll compressor as a representative example. However, the same principles can be applied to open scroll compressors.

[0042] Scroll compressors can also be categorized into fixed scroll compressors and mobile scroll compressors. Fixed scroll compressors are typically used for building air conditioning, while mobile scroll compressors are used for vehicle air conditioning. This embodiment uses a fixed scroll compressor as a representative example. However, the same principles can be applied to mobile scroll compressors.

[0043] Scroll compressors can also be categorized as low-pressure or high-pressure depending on the pressure of the refrigerant filled within the internal space of the casing. In a low-pressure type, the internal space of the casing is filled with refrigerant at suction pressure, while in a high-pressure type, the internal space of the casing is filled with refrigerant at discharge pressure. This embodiment uses a high-pressure scroll compressor as a representative example. However, the same principles can be applied to low-pressure scroll compressors.

[0044] Additionally, scroll compressors can be categorized into upper compression types and lower compression types depending on the installation location of the compression unit. In the upper compression type, the compression unit is installed above the driving motor, and in the lower compression type, the compression unit is installed below the driving motor. This embodiment describes an upper compression type scroll compressor as a representative example. However, the same principles can be applied to a lower compression type scroll compressor.

[0045] In addition, scroll compressors can be classified into single-rotating scroll compressors and reciprocating scroll compressors depending on whether the scrolls rotate. Single-rotating scroll compressors are configured such that one scroll is fixed or has limited rotational movement while the other scroll rotates, while reciprocating scroll compressors are configured such that both scrolls rotate. This embodiment will be described using a single-rotating scroll compressor as a representative example. However, the same principles can be applied to reciprocating scroll compressors.

[0046] In addition, the scroll compressor is applied with an Oldham ring, which is an anti-rotation mechanism of the orbiting scroll. The Oldham ring may be slidably coupled between the orbiting scroll and the main frame, or may be slidably coupled between the orbiting scroll and the fixed scroll (or non-orbiting scroll). This embodiment is described using an example in which the Oldham ring is provided between the orbiting scroll and the main frame as a representative example. However, the Oldham ring may be equally applied to an example in which the Oldham ring is provided between the orbiting scroll and the fixed scroll.

[0047] In addition, the scroll compressor according to the present embodiment can be applied equally to all scroll compressors to which Oldham ring is applied.

[0048] Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.

[0049] Referring to FIG. 1, a scroll compressor according to the present embodiment may have a drive motor (120) installed in the lower half of a casing (110), and a main frame (130) installed above the drive motor (120). A compression unit may be installed above the main frame (130). The compression unit includes a fixed scroll (140) and an orbiting scroll (150), but in some cases, the main frame (130) may also be described as being included in the compression unit.

[0050] The casing (110) according to the present embodiment may include a cylindrical shell (111), an upper cap (112), and a lower cap (113). Accordingly, the internal space (110a) of the casing (110) may be divided into an upper space (110b) provided on the inside of the upper cap (112), an intermediate space (110c) provided on the inside of the cylindrical shell (111), and a lower space (110d) provided on the inside of the lower cap (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) as an oil separation space, and the lower space (110d) as an oil storage space, respectively.

[0051] The cylindrical shell (111) has a cylindrical shape with both upper and lower ends open, and a drive motor (120) can be press-fitted and fixed to the lower half and a main frame (130) can be press-fitted and fixed to the upper half of the inner surface of the cylindrical shell (111).

[0052] A refrigerant discharge pipe (116) may be connected by penetrating the intermediate space (110c) of the cylindrical shell (111), specifically between the driving motor (120) and the main frame (130). The refrigerant discharge pipe (116) may be directly inserted into the cylindrical shell (111) and welded thereto, but typically, a collar pipe (not shown) made of the same material as the cylindrical shell (111) may be inserted into the cylindrical shell (111) and welded thereto, and a refrigerant discharge pipe (116) made of a copper pipe may be inserted into the collar pipe and welded thereto.

[0053] The upper cap (112) can be coupled to cover the open upper portion of the cylindrical shell (111). A refrigerant suction pipe (115) is coupled to the upper cap (112) by passing through it, and the refrigerant suction pipe (115) can pass through the upper space (110b) of the casing (110) and be directly connected to the suction chamber (not shown) of the compression unit to be described later. Accordingly, the refrigerant can be supplied to the suction chamber through the refrigerant suction pipe (115).

[0054] The lower cap (113) can be coupled to cover the opened lower end of the cylindrical shell (111). The lower space (110d) of the lower cap (113) forms a storage space, and a preset amount of oil can be stored in the storage space. The lower space (110d) forming the storage space can be connected to the upper space (110b) and the intermediate space (110c) of the casing (110) through an oil return passage (not shown). Accordingly, the oil separated from the refrigerant in the upper space (110b) and the intermediate space (110c) and the oil supplied to the compression unit and then recovered can be recovered and stored in the lower space (110d) forming the storage space through the oil return passage.

[0055] Referring to FIG. 1, the driving motor (120) according to the present embodiment is installed in the lower half of the intermediate space (110c) forming the high-pressure section in the internal space (110a) of the casing (110), and may include a stator (121) and a rotor (122). The stator (121) is fixed to the inner wall surface of the cylindrical shell (111) by hot pressing, and the rotor (122) may be rotatably provided inside the stator (121).

[0056] The stator (121) may include a stator core (1211) and a stator coil (1212).

[0057] The stator core (1211) is formed in a cylindrical shape and can be fixed to the inner surface of the cylindrical shell (111) by hot pressing. The stator coil (121a) is wound around the stator core (1211) and can be electrically connected to an external power source through a terminal (not shown) that is penetrated and connected to the casing (110).

[0058] The rotor (122) may include a rotor core (1221) and a permanent magnet (1222).

[0059] The rotor core (1221) is formed in a cylindrical shape and can be rotatably inserted into the interior of the stator core (1211) at a predetermined gap interval. The permanent magnet (1222) can be embedded in the interior of the rotor core (1221) at a predetermined gap interval along the circumference.

[0060] The rotation shaft (125) can be press-fitted and coupled to the rotor (122). The upper end of the rotation shaft (125) is provided with an eccentric portion (1251) and is rotatably supported radially on a main frame (130) to be described later, and the lower end of the rotation shaft (125) can be rotatably supported radially and axially on a subframe (118).

[0061] In addition, an oil supply hole (1255) may be formed inside the rotating shaft (125) by penetrating between the two ends of the rotating shaft (125). The oil supply hole (1255) may be formed by penetrating from the lower end of the rotating shaft (125) to the bottom surface of the eccentric portion (1251). Accordingly, oil stored in the lower space (110d) forming the oil storage space may be supplied to the inside of the eccentric portion (1251) through the oil supply hole (1255).

[0062] Additionally, an oil pickup (126) may be installed at the bottom of the rotating shaft (125), more precisely, at the bottom of the oil supply hole (1255). The oil pickup (126) may be installed so as to be immersed in the oil stored in the oil storage space (110d). Accordingly, the oil stored in the oil storage space (110d) may be pumped by the oil pickup (126) and sucked up through the oil supply hole (1255).

[0063] Referring to Fig. 1, the main frame (130) according to the present embodiment is installed on the upper side of the driving motor (120) and can be fixed by hot pressing or welding to the inner wall surface of the cylindrical shell (111). Accordingly, the main frame (130) can be typically formed of cast iron.

[0064] The main frame (130) may include a main flange portion (131), a shaft support portion (132), and an old ring receiving portion (133).

[0065] The main flange portion (131) is formed in an annular shape and can be accommodated in the intermediate space (110c) of the cylindrical shell (111). For example, the outer surface of the main flange portion (131) can be formed in a circular shape and can be in close contact with the inner surface of the cylindrical shell (111). In this case, at least one oil recovery groove (not shown) penetrating in the axial direction can be formed on the outer surface of the main flange portion (131).

[0066] In addition, the upper surface of the main flange portion (131) may be formed flat, but may be formed with a step with the Oldham ring receiving portion (133) described later therebetween. For example, the inner circumference of the Oldham ring receiving portion (133) may be formed such that the thrust surface (1311) on which the orbiting scroll (150) is axially supported protrudes from the bottom surface of the Oldham ring receiving portion (133) by a preset height, and the outer circumference of the Oldham ring receiving portion (133) may be formed such that the scroll fixing surface (1312) on which the fixed scroll (140) is axially supported protrudes from the bottom surface of the Oldham ring receiving portion (133) by a preset height. Accordingly, the upper surface of the main flange portion (131) is formed so that the inner side forming the thrust surface (1311) is lower than the outer side forming the scroll fixing surface (1312), so that the orbiting scroll (150) described later can be provided to be able to rotate between the main frame (130) and the fixed scroll (140).

[0067] The shaft support protrusion (132) extends from the main flange portion (131) toward the driving motor (120), and a shaft support hole (1321) may be formed on the inside of the shaft support protrusion (132). The shaft support hole (1321) may be formed by penetrating both axial side surfaces from the center of the main flange portion (131), that is, the center of the thrust surface (1311). Accordingly, the main flange portion (131) may be formed in an annular shape.

[0068] The Oldham ring receiving portion (133) can be formed in an annular shape by being sunken to a preset depth between the upper surface of the main flange portion (131), that is, the thrust surface (1311) and the scroll fixing surface (1312). Accordingly, the Oldham ring receiving portion (133) forms a predetermined space between the thrust surface (1311) and the scroll fixing surface (1312), and this space can form a kind of back pressure space (S) by storing oil sucked through the oil supply hole (1255) of the rotating shaft (125).

[0069] In addition, a frame-side keyway (1331) may be formed in the Oldham ring receiving portion (133) into which a frame-side key (162) of an Oldham ring (160), which will be described later, is slidably inserted in the radial direction. For example, the frame-side keyway (1331) may be formed to extend radially from the bottom surface of the Oldham ring receiving portion (133). Two frame-side keyway (1331) may be formed with a phase difference of approximately 180° along the circumferential direction.

[0070] Referring to FIG. 1, the fixed scroll (140) according to the present embodiment may include a fixed plate portion (141), a fixed side wall portion (142), and a fixed wrap (143).

[0071] The fixed plate portion (141) may be formed in a circular shape. The outer surface of the fixed plate portion (141) may be formed to be in close contact with the inner surface of the upper cap (112) forming the upper space (110b), or may be formed to be spaced apart from the inner surface of the upper cap (112).

[0072] In addition, a suction port (not shown) that penetrates axially and is connected to a suction chamber (not shown) is formed at the edge of the fixed plate portion (141), and a refrigerant suction pipe (115) that penetrates the upper cap (112) of the casing (110) can be inserted and connected to the suction port. Accordingly, the refrigerant suction pipe (115) can pass through the upper space (110b) of the casing (110) and be directly connected to the suction port of the fixed scroll (140).

[0073] In addition, a discharge port (1412) and a bypass hole (not shown) are formed in the center of the fixed plate portion (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 installed on the upper surface of the fixed plate portion (141). Accordingly, the refrigerant compressed in the compression chamber (V) can be discharged from the upper side of the fixed scroll (140) to the upper space (110b) formed in the upper cap (112).

[0074] The fixed side wall portion (142) can extend in a ring shape from the edge of the fixed plate portion (141) toward the main frame (130). Accordingly, the fixed side wall portion (142) can be bolt-fastened so that its lower surface is in close contact with the upper surface of the main frame (130), i.e., the scroll fixing surface (1312) of the main flange portion (131).

[0075] The fixed wrap (143) can extend from the lower surface of the fixed plate portion (141) toward the orbiting scroll (150). The fixed wrap (143) can be formed in various shapes such as an involute. The fixed wrap (143) can be interlocked with the orbiting wrap (153) described later to form a pair of compression chambers (V).

[0076] Referring to FIG. 1, the rotary scroll (150) according to the present embodiment may include a rotary plate portion (151), a rotary shaft insert portion (152), and a rotary wrap (153).

[0077] The pivot plate (151) is provided between the main frame (130) and the fixed scroll (140) and can be axially supported by the main frame (130). Accordingly, the pivot plate (151) can perform a pivoting movement between the main frame (130) and the fixed scroll (140).

[0078] The pivot plate (151) may be formed in a circular shape. For example, the outer surface of the pivot plate (151) may be formed in a circular shape so as to correspond to the outer surface of the Oldham ring receiving portion (133), that is, the inner surface of the scroll fixing surface (1312). In this case, the outer diameter of the pivot plate (151) may be formed smaller than the inner diameter of the scroll fixing surface (1312). Accordingly, the pivot scroll (150) can smoothly pivot within the Oldham ring receiving portion (133) without the outer surface of the pivot plate (151) interfering with the inner surface of the scroll fixing surface (1312).

[0079] A turning wrap (153) to be described later may be formed on one side of the turning plate (151), and a turning-side keyway (1511) into which a turning-side key (163) of an oldham ring (160) to be described later may be slidably inserted may be formed on the other side of the turning plate (151), that is, on the opposite side facing away from the turning wrap (153). The turning-side keyway (1511) may be formed with a phase difference of approximately 180° along the circumferential direction. However, since the turning-side keyway (1511) according to the present embodiment is formed in four pairs of two each, corresponding turning-side keyway (1511) are formed with a phase difference of approximately 180° as described above, but the interval between turning-side keyway (1511) adjacent to each other in the circumferential direction may be formed to be less than 180°.

[0080] For example, a turning-side keyway (1511) may have a turning-side main keyway (or a turning-side first keyway) (1515) formed on both sides thereof, and a turning-side sub-keyway (or a turning-side second keyway) (1516) formed on one circumferential side of the turning-side main keyway (1515). The turning-side main keyway (1515) may be formed with a phase difference of approximately 180° along the circumferential direction between the turning-side main keyway (1515) and the turning-side sub-keyway (1516) may be formed with a phase difference of approximately 180° along the circumferential direction between the turning-side main keyway (1515) and the turning-side sub-keyway (1516) may be formed with a phase difference of approximately 180° along the circumferential direction. In this case, the turning-side main keyway (1515) and the turning-side sub-keyway (1516) may be formed in parallel. Accordingly, the pivot key (163) of the Oldham ring (160) to be described later is slidably inserted into the pivot key groove (1511) of the pivot scroll (150), thereby dispersing the force transmitted between the pivot key (163) and the pivot key groove (1511), thereby reducing the surface pressure between the pivot key (163) and the pivot key groove (1511). The pivot key groove (1511) will be described again later together with the pivot key (163) of the Oldham ring (160).

[0081] The rotary shaft insertion portion (152) can extend from the geometric center of the orbiting scroll (150) toward the eccentric portion (1251) of the rotary shaft (125). The rotary shaft insertion portion (152) can be rotatably inserted into the eccentric portion (1251) of the rotary shaft (125). Accordingly, the orbiting scroll (150) is rotated by the eccentric portion (1251) of the rotary shaft (125) and the rotary shaft insertion portion (152).

[0082] The pivoting wrap (153) can extend from one side of the pivoting plate (151) toward the fixed scroll (140). The pivoting wrap (153) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (143).

[0083] Referring to FIG. 1, the Oldham ring (160) according to the present embodiment may be installed between the main frame (130) and the orbiting scroll (150). However, in some cases, the Oldham ring (160) may be installed on the fixed scroll (140) and the orbiting scroll (150). This embodiment will be described focusing on an example in which the Oldham ring (160) is installed between the main frame (130) and the orbiting scroll (150).

[0084] The Oldham ring (160) may include a ring body (161), a frame-side key (162), and a pivot-side key (163). The ring body (161) is provided between the main frame (130) and the pivot scroll (150), and the frame-side key (162) may be slidably inserted into a frame-side key groove (1331) provided in the main frame (130), and the pivot-side key (163) may be slidably inserted into a pivot-side key groove (1511) provided in the pivot scroll (150). Accordingly, the Oldham ring (160) restricts the rotational motion of the pivot scroll (150) so that the pivot scroll (150) pivots with respect to the main frame (130).

[0085] The ring body (161) is formed in an annular shape to correspond to the Oldham ring receiving portion (133), the frame-side key (162) is formed to correspond to the frame-side keyway (1331), and the pivot-side key (163) can be formed in parallel to correspond to the pivot-side keyway (1511). The Oldham ring (160) including the pivot-side key (163) will be described again later together with the main frame (130) and the pivot scroll (150).

[0086] The operational effects of the scroll compressor according to the present embodiment as described above are as follows.

[0087] That is, when power is applied to the driving motor (120) and rotational force is generated, the orbiting scroll (150) eccentrically coupled to the rotation shaft (125) rotates relative to the fixed scroll (140) by the Oldham ring (160). At this time, two pairs of compression chambers (V) that move continuously are formed between the fixed scroll (140) and the orbiting scroll (150).

[0088] Then, the compression chamber (V) gradually becomes narrower in volume as it moves from the suction port (or suction chamber) toward the discharge port (or discharge chamber) (1412) while the orbiting scroll (150) rotates.

[0089] Then, the refrigerant is introduced into the compression chamber (V) through the refrigerant suction pipe (115) and the suction port of the fixed scroll (140), and the refrigerant is compressed while moving toward the final compression chamber by the orbiting scroll (150). The refrigerant is discharged from the final compression chamber to the upper space (110b) of the casing (110) through the discharge port (1412) of the fixed scroll (140), and then moves to the intermediate space (110c) or / and the lower space (110d) of the casing (110) through the refrigerant guide passage provided in the fixed scroll and the main frame.

[0090] Then, the refrigerant circulates through the internal space (110a) of the casing (110), and oil is separated from the refrigerant. The oil separated from the refrigerant moves to the oil storage space forming the lower space (110d) of the casing (110), is stored, and is then supplied to the compression unit through the oil pickup (126) and the oil supply hole (1255) of the rotating shaft (125), while the refrigerant from which the oil is separated is discharged to the outside of the casing (110) through the refrigerant discharge pipe (116), repeating a series of processes.

[0091] At this time, the frame-side key (162) of the Oldham ring (160) is slidably inserted into the frame-side key groove (1331) of the main frame (130), and the pivot-side key (163) of the Oldham ring (160) is slidably inserted into the pivot-side key groove (1511) of the pivot scroll (150), thereby suppressing rotation of the pivot scroll (150). Accordingly, contact force (hereinafter collectively referred to as surface pressure) is generated between the circumferential side surface of the frame-side key groove (1331) and both circumferential side surfaces of the frame-side key (162) facing it, and between the circumferential side surface of the pivot-side key groove (1511) and both circumferential side surfaces of the pivot-side key (163) facing it. This surface pressure corresponds to the value obtained by dividing the force acting on the key (162)(163) of the Oldham ring (160) by the area (hereinafter, key area) that the key (162)(163) of the Oldham ring (160) contacts in the circumferential direction with the pivot-side keyway (1511) of the pivot scroll (150) or the frame-side keyway (1331) of the main frame (130). The amount of wear on the key (162)(163) of the Oldham ring (160) can be determined according to the surface pressure. In other words, when the surface pressure is high, the amount of wear on the Oldham ring (160) (e.g., the amount of wear on the key) increases, and when the surface pressure is low, the amount of wear on the Oldham ring (160) decreases. Therefore, as the capacity of the compressor increases, the force acting on the Oldham ring (160) increases, so expanding the key area of ​​the Oldham ring (160) can be advantageous in reducing the wear on the keys (162)(163) of the Oldham ring (160) and extending the life of the Oldham ring (160) and / or the compressor. This may be especially necessary in the case of the pivot-side key (163), which forms a free end and is relatively far from the Oldham ring receiving portion (133) and may thus be vulnerable to lubrication, to expand the key area and lower the surface pressure. Hereinafter, an example of expanding the key area of ​​the pivot-side key (163) will be described. However, the key area of ​​the frame-side key (162) can also be expanded in the same way as the pivot-side key (163).

[0092] As previously explained, the key area of ​​the pivot key (163) can be increased by increasing the height or length of the pivot key (163). However, when the height of the pivot key (163) is increased, the depth of the keyway (1511) of the pivot scroll (150) in which the pivot key (163) is accommodated also becomes deeper. Then, the thickness of the pivot plate (151) must be increased in proportion to the increased depth of the keyway (1511). This may cause an increase in the weight of the pivot scroll (150), which may lead to an increase in centrifugal force and moment during the pivoting motion of the pivot scroll (150), which may lower motor efficiency.

[0093] In addition, when the length of the pivot key (163) is increased, the outer diameter of the pivot plate (151) increases, which also causes an increase in the weight of the pivot scroll (150), and as the centrifugal force and moment increase during the pivoting movement of the pivot scroll (150) as described above, not only does this cause a decrease in motor efficiency, but also causes an increase in the weight of the old ring (160), which may cause abnormal noise during compressor operation.

[0094] Accordingly, in the present embodiment, the total key area for the pivot key (163) of the Oldham ring (160) can be expanded by increasing the number of pivot keys (163). For example, even if the height of the pivot key (163) of the Oldham ring (160) is maintained or lowered, the total key area for the entire pivot key (163) can be expanded by increasing the number of pivot keys (163). Accordingly, while expanding the key area for the pivot key (163) of the Oldham ring (160), the thickness of the pivot plate portion (151) into which the pivot key (163) is inserted can be maintained or reduced. This lowers the contact pressure of the Oldham ring against the pivot key (162), thereby reducing the amount of wear on the Oldham ring (e.g., the pivot key) (160), thereby extending the life of the Oldham ring (160) and / or the compressor.

[0095] In addition, by lowering the surface pressure on the pivot key (163) of the Oldham ring (160) and suppressing an increase in the weight of the pivot scroll (150), the motor efficiency can be increased, and by suppressing abnormal noise generated by the Oldham ring (160) during operation of the compressor, the reliability of the compressor can be increased.

[0096] FIG. 2 is a perspective view showing an exploded view of a turning scroll and an Oldham ring according to the present embodiment, FIG. 3 is a plan view showing the assembled turning scroll and the Oldham ring of FIG. 2, FIG. 4 is a cross-sectional view taken along line IV-IV" of FIG. 3, FIG. 5 is a plan view showing an Oldham ring according to FIG. 2, and FIG. 6 is a graph showing changes in surface pressure with respect to changes in the spacing of turning keys in an Oldham ring according to the present embodiment.

[0097] Referring to FIGS. 2 to 5, the Oldham ring (160) according to the present embodiment may include a ring body (161), a frame-side key (162), and a pivot-side key (163) as described above. The frame-side key (162) and the pivot-side key (163) may be formed as a single body on each of the axial sides of the ring body (161), or may be manufactured separately and then assembled post-manufactured. In the former case, the Oldham ring (160) can be manufactured easily, and in the latter case, the ring body (161) and the pivot-side key (162) can be manufactured from different materials to reduce the weight of the ring body (161) or reduce the wear of the pivot-side key (162). The present embodiment will be described with reference to an example in which the pivot-side key (163) is formed as a single body on one side of the ring body (161). However, the same can be applied even when the pivot key (163) is post-assembled to the ring body (161).

[0098] The ring body (161) according to the present embodiment may be formed in an annular shape. For example, the inner circumference of the ring body (161) may be formed in a circular shape, and the outer circumference of the ring body (161) may be formed in an annular shape overall, but the portion where the frame-side key (162) and the pivot-side key (163) are formed may be formed in a non-circular shape. Accordingly, the ring body (161) may be inserted into the old ring receiving portion (133) of the main frame (130) and may reciprocate in both directions along the frame-side key groove (1331).

[0099] Specifically, the ring body (161) has a main body portion (1611) formed in a ring shape, and a plurality of bearing surfaces (1612a) (1612b) can be formed in steps at predetermined intervals along the circumferential direction on both axial sides of the main body portion (1611).

[0100] The frame-side keys (162) and pivot-side keys (163) described above may be alternately formed on a plurality of bearing surfaces (1612a) (1612b). For example, a first bearing surface (1612a) provided with a frame-side key (162) may be formed on a first center line (CL1) passing through the center (or the axis center of the rotation axis) (Or) of the ring body (161), and a second bearing surface (1612b) provided with a pivot-side key (163) may be formed on a second center line (CL2) passing through the center (or the axis center of the rotation axis) (Or) of the ring body and perpendicular to the first center line (CL1).

[0101] In this case, the inner surface of the first bearing surface portion (1612a) and the inner surface of the second bearing surface portion (1612b) are formed into a circle having the same curvature as the inner surface of the main body portion (1611), and the outer surface of the first bearing surface portion (1612a) and the outer surface of the second bearing surface portion (1612b) can be formed into a protrusion shape by extending radially from the outer surface of the main body portion (1611). Accordingly, the length of the frame-side key (162) and the length of the pivot-side key (163), which will be described later, can be formed to be long in the radial direction or in the direction of the second center line (CL2), thereby expanding the key area.

[0102] In addition, in this case, the first bearing surface portion (1612a) and the second bearing surface portion (1612b) can be formed in a tapered shape whose cross-sectional area becomes narrower the farther away from the outer surface of the main body portion (1611) when projected in the axial direction. Accordingly, among the slewing-side keys (163) formed on the second bearing surface portion (1612b), the length (L21) of the slewing-side main key (1631) to be described later can be formed longer than the length (L22) of the slewing-side sub-key (1632), so that the total length of the slewing-side keys (163) can be formed as long as possible. Through this, the total length of the Oldham ring key can be increased without increasing the outer diameter of the Oldham ring (160) and / or the main frame (130), thereby increasing the key area as much as possible and further lowering the surface pressure.

[0103] The frame-side key (162) according to the present embodiment may be formed to protrude from one side of the ring body (161), that is, the lower surface of the first bearing surface portion (1612a) facing the main frame (130), by a predetermined height toward the frame-side key groove (1331) of the main frame (130). In this case, the height (not shown) of the frame-side key (162) may be formed to be the same as the height (H1) of the turning-side key (1633) described later, for example, the turning-side main key (1631), or may be formed to be higher than the height (H2) of the turning-side main key (1631). In the former case, the main frame (130) and / or the old ring (160) can be easily processed, and in the latter case, as the contact area between the frame-side keyway (1331) and the frame-side key (162) is expanded, the key area of ​​the frame-side key (162) is increased accordingly, so that the surface pressure on the frame-side key (162) can be reduced. However, as described above, the frame-side keyway (1331) and the frame-side key (162) are immersed in oil contained in the old ring receiving portion (133), so that even if the height (unsigned) of the frame-side key (162) is formed to be the same as the height (H1) of the turning-side main key (1631) as in the former, the surface pressure may not increase significantly compared to the turning-side key (163).

[0104] In addition, referring to FIGS. 3 to 5, the frame-side keys (162) may be formed one each on the left and right sides based on the center (Or) of the ring body (161) on the first center line (CL1) passing through the center (or the axis center of the rotation axis) (Oc) of the ring body (161). Accordingly, the frame-side keys (162) on both sides may be formed with a phase difference of approximately 180° along the circumferential direction.

[0105] In addition, the frame-side key (162) may be formed into a hexahedral shape that is symmetrical left and right with respect to the first center line (CL1). In this case, the frame-side keyway (1331) of the main frame (130) may also be formed into a rectangular parallelepiped shape that is elongated in the direction of the first center line (CL1) when projected in the axial direction. Accordingly, the contact surfaces of the frame-side keyway (1331) and the frame-side key (162) may be formed flat, and the contact area between the frame-side keyway (1331) and the frame-side key (162) may be formed as wide as possible. Through this, the surface pressure between the frame-side keyway (1331) and the frame-side key (162) may be reduced to a minimum.

[0106] Although not shown in the drawing, the frame-side key (162) is formed in a hexahedral shape when projected in the axial direction, but may be formed in a sunken torepan shape with oil supply grooves (not shown) on both sides that contact the frame-side keyway (1331). In this case, the contact area between the frame-side key (162) and the frame-side keyway (1331) is reduced, but the actual surface pressure can be lowered as oil flows between the two contact surfaces through the oil supply grooves (not shown). These oil supply grooves may be formed in the frame-side keyway (1331) or may be formed in each of the frame-side key (162) and the frame-side keyway (1331).

[0107] Although not shown in the drawing, the frame-side key (162) may be rotatably coupled to the ring body. In this case, when the frame-side key (162) rotates in the direction in which the force is applied to the frame-side keyway (1331), the frame-side key (162) maintains surface contact with the frame-side keyway (1331), thereby suppressing frictional loss and wear between the frame-side key (162) and / or the frame-side keyway (1331). In addition, by increasing the tolerance for the ring body (161) and the frame-side key (162), it is possible to easily manufacture the Oldham ring, thereby reducing the manufacturing cost for the Oldham ring (160), and by forming a part of the Oldham ring (160) out of a lightweight material to reduce the weight of the Oldham ring (160), it is possible to improve motor efficiency.

[0108] Also, in this case, the circumferential gaps (G) on both sides between the frame-side keyway (1331) and the frame-side key (162) can be formed to be identical to each other. For example, in the initial state where the center (Or) of the ring body (161) and the axial center (Oc) of the rotational shaft (125) are aligned, the circumferential gaps (G) between the circumferential sides of the frame-side keyway (1331) and the circumferential sides of the frame-side keyway (162) facing each other can be formed to be identical to each other. Accordingly, the contact area between the frame-side keyway (1331) of the main frame (130) and the frame-side key (162) of the Oldham ring (160) is maintained constant regardless of the direction of the rotational force applied to the Oldham ring (160), and the surface pressure between the frame-side keyway (1331) and the frame-side key (162) can be reduced to a minimum.

[0109] Referring to FIGS. 3 to 5, the pivot-side key (163) according to the present embodiment may be formed to protrude a predetermined height from the other side of the ring body (161), that is, the upper surface of the second bearing surface portion (1612b) facing the pivot scroll (150), toward the pivot-side key groove (1511) of the pivot scroll (150). In this case, the height of the pivot-side key (163) may be formed to be the same as the height (unsigned) of the frame-side key (162) described above, or may be formed to be lower than the height of the frame-side key (162). In the former case, the pivot scroll (150) and / or the Oldham ring (160) can be easily processed, and in the latter case, the pivot plate portion (151) can be formed thin, thereby reducing the weight of the pivot scroll (150) and improving motor efficiency.

[0110] In addition, the pivot key (163) may be formed in two numbers on each of the left and right sides based on the first center line (CL1) passing through the center (or the axis center of the rotation axis) (Or) of the ring body (161). For example, the pivot key (163) may include a pivot main key (1631) and a pivot sub key (1632) formed on each of the left and right sides based on the first center line (CL1).

[0111] According to the present embodiment, the pivot-side main keys (1631) can be formed one each on the left and right sides of the first center line (CL1) on the second center line (CL2) perpendicular to the first center line (CL1) at the center (or the axis center of the rotation axis) (Or) of the ring body (161). Accordingly, the pivot-side main keys (1631) on both sides can be formed with a phase difference of approximately 180° along the circumferential direction.

[0112] In addition, the pivot-side main key (1631) may be formed in a hexahedral shape. For example, the pivot-side main key (1631) may be formed in a rectangular parallelepiped shape that is symmetrical about the second center line (CL2) when projected in the axial direction and is elongated in the direction of the second center line (CL2). In this case, the pivot-side main key groove (1515) of the pivot scroll (150) may be formed in a shape corresponding to the pivot-side main key (1631), that is, in a rectangular parallelepiped shape that is symmetrical about the second center line (CL2) when projected in the axial direction and is elongated in the direction of the second center line (CL2). Accordingly, the contact area between the pivot-side main key groove (1515) and the pivot-side main key (1631) is formed as wide as possible, and the surface pressure between the pivot-side main key groove (1515) and the pivot-side main key (1631) can be reduced to a minimum.

[0113] In addition, the turning-side main key (1631) can be formed to have the same circumferential gap between it and the turning-side main key home (1515). For example, in the initial state where the center (Or) of the ring body (161) and the axial center (Oc) of the rotation axis (125) are aligned, the two circumferential side surfaces (1631a) of the turning-side main key (1631) can be formed to have the same circumferential gap (G1) (G2) between them and the circumferential side surfaces (1515a) of the turning-side main key home (1515) facing them. Accordingly, the contact area between the pivot-side main key home (1515) of the pivot scroll (150) and the pivot-side main key (1631) of the Oldham ring (160) is maintained constant regardless of the direction of rotational force applied to the Oldham ring (160), and the surface pressure between the pivot-side main key home (1515) and the pivot-side main key (1631) can be reduced to a minimum.

[0114] In addition, the turning-side main key (1631) may be formed longer than the turning-side sub-key (1632) to be described later. For example, when the length of the turning-side main key (1631) in the direction perpendicular to the first center line (CL1) is referred to as the key length, the length (L21) of the turning-side main key (1631) may be formed to be longer than the length (L22) of the turning-side sub-key (1632). Accordingly, the key area of ​​the turning-side main key (1631), which has a relatively large load, is expanded, thereby effectively reducing the surface pressure.

[0115] Although not shown in the drawing, the length (L21) of the turning-side main key (1631) may be formed to be shorter than or equal to the length (L22) of the turning-side sub-key (1632) described later. In these cases, as the outer end of the turning-side main key (1631) is shortened, the outer diameter of the ring body (161) is reduced, thereby reducing the weight of the old ring (160).

[0116] In addition, the width (W1) of the turning-side main key (1631) may be formed to be the same as the width (W2) of the turning-side sub-key (1632) to be described later. For example, when the length of the turning-side main key (1631) in the direction in which the first center line (CL1) extends is referred to as the key width, the width (W1) of the turning-side main key (1631) may be formed to be the same as the width (W2) of the turning-side sub-key (1631). Accordingly, while the key area of ​​the Oldham ring key is expanded, the rigidity of the turning-side key (163) is secured, so that the reliability of the Oldham ring (160) can be improved.

[0117] Although not shown in the drawing, the width (W1) of the main key (1631) on the turning side may be formed to be smaller or larger than the width (W2) of the sub-key (1632) on the turning side, which will be described later. In the former case, the weight of the old ring (160) is reduced, and the width (unsigned) of the keyway (1511) on the turning side is also reduced, so that the rigidity of the turning plate (151) can be secured accordingly. In the latter case, the key area for the key (163) on the turning side is expanded, so that the surface pressure can be expanded as much as possible.

[0118] In addition, the height (H1) of the pivot-side main key (1631) can be formed to be the same as the height (H2) of the pivot-side sub-key (1632) to be described later. In this case, the key area of ​​the pivot-side key (163) can be expanded to effectively lower the surface pressure on the pivot-side key (163).

[0119] Although not shown in the drawing, the height (H1) of the main key (1631) on the turning side may be formed to be lower or higher than the height (H2) of the sub-key (1632) on the turning side, which will be described later. In the former case, the weight of the old ring (160) is reduced, and the depth (unsigned) of the keyway (1511) on the turning side is also reduced, thereby securing the rigidity of the turning plate (151) to that extent. In the latter case, the key area for the key (163) on the turning side is expanded, thereby increasing the surface pressure as much as possible.

[0120] Meanwhile, the turning-side main key (1631) according to the present embodiment may be formed in a torepan shape. For example, the turning-side main key (1631) is formed in a hexahedral shape when projected in the axial direction, but oil supply grooves (not shown) may be formed sunken on both sides that contact the turning-side main key groove (1515). In this case, the contact area between the turning-side main key (1631) and the turning-side main key groove (1515) is reduced, but the actual surface pressure can be lowered as oil flows between the two contact surfaces through the oil supply groove. Such oil supply grooves may be formed on the turning-side main key (1631) and / or the turning-side main key groove (1515).

[0121] In addition, the turning-side main key (1631) according to the present embodiment may be rotatably coupled to the ring body (161). For example, a key receiving portion (not shown) may be formed on the ring body (161), and a key rotation projection (not shown) that is rotatably coupled to the key receiving portion of the ring body (161) may be formed on the turning-side key (163). In this case, the turning-side main key (1631) rotates in the direction in which force is applied from the turning-side main key home (1515) and maintains surface contact with the turning-side main key home (1515). This can suppress friction loss and wear between the turning-side main key (1631) and / or the turning-side main key home (1515). In addition, by increasing the tolerance for the ring body (161) and the turning-side main key (1631) to facilitate the manufacture of the Oldham ring (160), the manufacturing cost for the Oldham ring (160) can be reduced, and by forming the ring body (161) and / or the turning-side main key (1631) with a light material to reduce the weight of the Oldham ring (160), the motor efficiency can be improved.

[0122] The turning-side sub-keys (1632) according to the present embodiment may be formed parallel to the turning-side main key (1631) on one circumferential side of the turning-side main key (1631) described above. For example, each turning-side sub-key (1632) may be formed with a predetermined interval in the same circumferential direction, that is, in the counterclockwise direction, with respect to each turning-side main key (1631). Accordingly, the turning-side sub-keys (1632) on both sides may be formed with a phase difference of approximately 180° along the circumferential direction.

[0123] In addition, the pivot-side sub-key (1632) according to the present embodiment may be formed in a hexahedron, for example, a rectangular parallelepiped, like the pivot-side main key (1631). In this case, the pivot-side sub-key groove (1516) of the pivot scroll (150) may also be formed in a rectangular parallelepiped shape, like the pivot-side main key groove (1515), when projected in the axial direction. Accordingly, the contact area between the pivot-side sub-key groove (1516) and the pivot-side sub-key (1632) is formed as wide as possible, while the surface pressure between the pivot-side sub-key groove (1516) and the pivot-side sub-key (1632) can be reduced to a minimum.

[0124] In addition, the pivot-side sub-key (1632) may be formed to have the same circumferential gap between it and the pivot-side sub-key groove (1516). For example, in the initial state where the center (Or) of the ring body (161) and the axial center (Oc) of the rotation axis (125) are aligned, the two circumferential side surfaces (1632a) of the pivot-side sub-key (1632) may be formed to have the same circumferential gap (G1) (G2) between them and the circumferential side surface (1516a) of the pivot-side sub-key groove (1516) facing them. Accordingly, the contact area between the pivot-side sub-key home (1516) of the pivot scroll (150) and the pivot-side sub-key (1632) of the Oldham ring (160) is maintained constant regardless of the direction of rotational force applied to the Oldham ring (160), and the surface pressure between the pivot-side sub-key home (1516) and the pivot-side sub-key (1632) can be reduced to a minimum.

[0125] In addition, in this case, the circumferential gap (G1)(G2) between the pivot-side sub-key (1632) and the pivot-side sub-keyway (1516) can be formed to be identical to the circumferential gap (G1)(G2) between the pivot-side main key (1631) and the pivot-side main keyway (1515) described above. Accordingly, the contact area between the pivot-side keyway (1511) of the pivoting scroll (150) and the pivot-side key (163) of the Oldham ring (160) is maintained constant regardless of the direction of the rotational force applied to the Oldham ring (160), and the surface pressure between the pivot-side keyway (1511) and the pivot-side key (163) can be reduced to a minimum.

[0126] Although not illustrated in the drawing, the pivot-side sub-key (1632) may be formed in the same torepan shape as the pivot-side main key (1631) or may be rotatably coupled to the ring body (161). In these cases, the description of the pivot-side main key (1631) described above will be used instead.

[0127] Meanwhile, the gap between the turning-side main key (1631) and the turning-side sub-key (1632), that is, the gap between the center of the turning-side main key (1631) and the center of the turning-side sub-key (1632) (hereinafter, key gap) (L) can be formed to be approximately 0.13 to 0.2 times the diameter of the virtual circle (C) connecting the outer ends of the turning-side main keys (1631) on both sides (hereinafter, outer diameter of the ring body) (D).

[0128] This can also be seen from Fig. 6. Referring to Fig. 6, it can be seen that the surface pressure is substantially minimum when the key spacing (L) is between 0.13 and 0.2 times. Of course, as can be seen from Fig. 6, the surface pressure decreases as the key spacing (L) becomes narrower. However, when the key spacing (L) is less than 0.13 times, for example, less than 0.1 times, the partition between the main keyway (1515) on the turning side and the sub-keyway (1516) on the turning side becomes too thin, which may make processing difficult or may cause damage to the partition during operation. Therefore, it may be desirable to form the minimum key spacing (L) to be 0.1 times or more, preferably 0.13 times or more, in order to lower the surface pressure. Accordingly, the total surface pressure generated between the turning-side main key (1631) and the turning-side main key home (1515) and between the turning-side sub-key (1632) and the turning-side sub-key home (1516) can be minimized, thereby significantly reducing the amount of wear of the turning-side main key (1631) and / or the turning-side sub-key (1632) of the old ring (160).

[0129] Meanwhile, there are other examples of Oldham Rings, as follows:

[0130] That is, in the above-described embodiment, the turning-side sub-key is provided on one circumferential side of the turning-side main key, but in some cases, the turning-side sub-key may be provided on each circumferential side of the turning-side main key.

[0131] Fig. 7 is a perspective view showing another embodiment of an old ring separated from a rotating scroll, and Fig. 8 is a plan view showing an old ring according to Fig. 7.

[0132] Referring again to FIG. 1, the basic configuration and the resulting operational effects of the old ring (160) and the main frame (130) and the rotating scroll (150) to which the old ring (160) is coupled according to the present embodiment are similar to those of the above-described embodiment.

[0133] For example, an Oldham ring receiving portion (133) into which an Oldham ring (160) can be movably inserted may be formed on the upper surface of the main frame (130), and a frame-side key groove (1331) into which a frame-side key (162) of the Oldham ring (160) can be slidably inserted may be formed in the Oldham ring receiving portion (133).

[0134] Also in this case, the turning scroll (150) is provided with a circular turning plate (151), and a turning-side keyway (1511) into which a turning-side key (163) of an old ring (160) is slidably inserted may be formed on the lower surface of the turning plate (151). The turning-side keyway (1511) may be formed to be long in a direction perpendicular to the frame-side keyway (1331) described above.

[0135] Also in this case, the old ring (160) can be formed with a frame-side key (162) and a pivot-side key (163) oriented perpendicular to each other on both axial sides of the ring body (161). In this case, the frame-side key (162) and the pivot-side key (163) can be formed in a hexahedral shape or a torepan shape.

[0136] Also in this case, the frame side key (162) and the pivot side key (163) may be formed as a single body in the ring body (161) or may be rotatably coupled to the ring body (161).

[0137] However, the pivot key (163) of the old ring (160) according to the present embodiment may have pivot sub-keys (1632) formed on both sides of the pivot main key (1631) in the circumferential direction. Accordingly, the key area of ​​the pivot key (163) may be further expanded.

[0138] Specifically, referring to FIGS. 7 and 8, the turning-side key (163) according to the present embodiment may have turning-side sub-keys (1632) formed on both sides of the circumference of the turning-side main key (1631) located on the second center line (CL2). In other words, in the above-described embodiment, the turning-side main key (1631) is formed on the second center line (CL2), and the turning-side sub-keys (1632) are formed on only one side of the circumference of the turning-side main key (1631), but in the present embodiment, the turning-side main key (1631) may be provided on the second center line (CL2), and at least one turning-side sub-key (1632) may be provided on both sides of the circumference of the turning-side main key (1631). In this case, a pivot key groove (1511) may be formed on the pivot plate (151) of the pivot scroll (150) to correspond to the pivot key (163) described above. Accordingly, in the Oldham ring (160) according to the present embodiment, the number of pivot keys (163) increases compared to the Oldham ring (160) in the above-described embodiment illustrated in FIG. 2, and the key area is expanded, so that the surface pressure between the pivot key (163) and the pivot key groove (1511) can be further reduced.

[0139] Also in this case, both circumferential gaps (see Fig. 3) (G1) (G2) between the turning-side key (163) and the turning-side keyway (1511) facing it can be formed identically. Accordingly, the total contact area between the turning-side key (163) and the turning-side keyway (1511) is expanded, and the surface pressure at the turning-side key (163) can be reduced to a minimum.

[0140] Also in this case, the width (W1), height (H1) and length (L21) of the turning-side main key (and the turning-side main keyway) (1631) and the width (W2), height (H2) and length (L22) of the turning-side sub-key (and the turning-side sub-keyway) (1632) may be formed to be the same as each other, or the width (W1), height (H1) and length (L21) of the turning-side main key (and the turning-side main keyway) (1631) may be formed to be larger or smaller than the width (W2), height (H2) and length (L22) of the turning-side sub-key (and the turning-side sub-keyway) (1632). Since the operational effects for each of these embodiments are almost the same as those in the above-described embodiments, the description thereof will be replaced with the above-described embodiments.

[0141] Also in this case, the key spacing (L) on both sides between the turning-side main key (1631) and the turning-side sub-keys (1632) on both sides can be formed to be the same. For example, the key spacing (L) on both sides can be formed to be approximately 0.13 to 0.2 times the outer diameter (D) of the ring body (161), as in the above-described embodiment. Accordingly, the total surface pressure generated between the turning-side main key (1631) and the turning-side main key home (1515) and between the turning-side sub-key (1632) and the turning-side sub-key home (1516) can be minimized, thereby significantly reducing the wear amount of the turning-side main key (1631) and / or the turning-side sub-key (1632) of the Oldham ring (160).

[0142] As described above, when the pivot-side sub-key (1632) is formed on each side of the pivot-side main key (1631), the total key area of ​​the pivot-side sub-key (1632) further increases, so that the size of the pivot-side main key (1631) and / or the pivot-side sub-key (1632) can be further reduced, thereby further reducing the size of the pivot-side main key groove (1515) and / or the pivot-side sub-key groove (1516) of the pivot scroll (150). This can be advantageous in reducing the thickness of the pivot plate portion (151) or securing the rigidity of the pivot plate portion (151).

[0143] Meanwhile, another example of Oldhamling is as follows.

[0144] That is, in the embodiments described above, some of the Oldham ring keys are formed on the second center line, but in some cases, all of the Oldham ring keys may be formed to be spaced apart from the second center line.

[0145] Fig. 9 is a perspective view showing another embodiment of an old ring separated from a turning scroll, and Fig. 10 is a plan view showing an old ring according to Fig. 9.

[0146] Referring again to FIG. 1, the basic configuration and the resulting operational effects of the old ring (160) and the main frame (130) and the rotating scroll (150) to which the old ring (160) is coupled according to the present embodiment are similar to those of the above-described embodiment.

[0147] For example, an Oldham ring receiving portion (133) into which an Oldham ring (160) can be movably inserted may be formed on the upper surface of the main frame (130), and a frame-side key groove (1331) into which a frame-side key (162) of the Oldham ring (160) can be slidably inserted may be formed in the Oldham ring receiving portion (133).

[0148] In addition, the turning scroll (150) is provided with a circular turning plate (151), and a turning-side keyway (1511) into which a turning-side key (163) of an old ring (160) is slidably inserted may be formed on the lower surface of the turning plate (151). The turning-side keyway (1511) may be formed to be long in a direction perpendicular to the frame-side keyway (1331) described above.

[0149] In addition, the Oldham ring (160) may be formed with a frame-side key (162) and a pivot-side key (163) oriented perpendicular to each other on both axial sides of the ring body (161). In this case, the frame-side key (162) and the pivot-side key (163) may be formed in a hexahedral shape or a torepan shape.

[0150] Additionally, the frame-side key (162) and the pivot-side key (163) may be formed as a single body in the ring body (161) or may be rotatably coupled to the ring body (161).

[0151] However, in the present embodiment, the pivot key (163) of the Oldham ring (160) may be formed at an equal distance from the center (Or) of the ring body (161). Accordingly, the center of gravity (Om) of the Oldham ring (160) may be aligned with the center (Or) of the ring body (161) as much as possible, thereby suppressing abnormal behavior of the Oldham ring (160).

[0152] Specifically, referring to FIGS. 9 and 10, the pivot-side keys (163) according to the present embodiment may be formed spaced apart from each other by a preset distance on both the left and right sides with respect to the second center line (CL2). For example, a plurality of first pivot-side keyways (1511a) and second pivot-side keyways (1511b) may be formed on the pivot scroll (150), and a plurality of first pivot-side keys (163) inserted into a plurality of first pivot-side keyways (1511a) and a plurality of second pivot-side keys (163b) inserted into a plurality of second pivot-side keyways (1511b) may be formed on the old ring (160).

[0153] In this case, a plurality of first turning-side keys (163a) may be formed on a second-first center line (CL2-1) parallel to the second center line (CL2) at a position spaced apart from the second center line (CL2) by a preset interval to the left of the drawing, and a plurality of second turning-side keys (163b) may be formed on a second-second center line (CL2-2) parallel to the second center line (CL2) at a position spaced apart from the second center line (CL2) by a preset interval to the right of the drawing. In this case, the first turning-side keys (163a) and the second turning-side keys (163b) may be spaced apart from the second center line (CL2) by the same interval or may be spaced apart from each other by different intervals. In the former case, the radial distance from the center (Or) of the ring body (161) to each pivot key (163a) (163b) is formed to be the same, so that the surface pressure is maintained uniformly, thereby minimizing the wear on the Oldham ring keys, whereas in the latter case, the positions of each pivot keyway (1511a) (1511b) and each pivot key (163a) (163b) are appropriately adjusted according to the eccentric mass of the pivot scroll (150), thereby further stabilizing the behavior of the pivot scroll (150). This embodiment illustrates an example in the former case, that is, a plurality of first pivot keys (163a) and a plurality of second pivot keys (163b) are spaced apart from the second center line (CL2) by the same distance and arranged in parallel to each other.

[0154] Also in this case, both circumferential gaps (see Fig. 3) (G1) (G2) between the turning-side key (163) and the turning-side keyway (1511) facing it can be formed identically. Accordingly, the total contact area between the turning-side key (163) and the turning-side keyway (1511) is expanded, and the surface pressure at the turning-side key (163) can be reduced to a minimum.

[0155] Also in this case, the width (W1), height (H1) and length (L21) of the first turning-side key (and the first turning-side keyway) (163a) and the width (W2), height (H2) and length (L22) of the first turning-side key (and the second turning-side keyway) (163b) may be formed to be the same, or the width (W1), height (H1) and length (L21) of the first turning-side key (and the first turning-side keyway) (163a) may be formed to be larger or smaller than the width (W2), height (H2) and length (L22) of the second turning-side key (and the second turning-side keyway) (163b). Since the operational effects for each of these embodiments are almost the same as those in the above-described embodiments, the description thereof will be replaced with the above-described embodiments.

[0156] Also in this case, the key gap (L) between the first turning-side key (163a) and the second turning-side key (163b) can be formed to be approximately 0.13 to 0.2 times the outer diameter (D) of the ring body (161) as in the above-described embodiment. Accordingly, the total surface pressure generated between the first turning-side key (163a) and the second turning-side keyway (1511a) and between the second turning-side key (163b) and the second turning-side keyway (1511b) can be minimized, thereby significantly reducing the wear amount of the first turning-side key (163a) and / or the second turning-side key (163b) of the Oldham ring (160).

[0157] As described above, when the first turning side key (163a) and the second turning side key (163b) are spaced apart by a preset distance on both sides of the second center line (CL2), the center of gravity (Om) of the Oldham ring (160) coincides with the center (Or) of the ring body (161), so that the surface pressure is reduced due to the expansion of the key area, while the abnormal behavior of the Oldham ring (160) can be effectively suppressed during operation of the compressor.

[0158] Meanwhile, in the above-described embodiments, the explanation was centered on the example in which the keys of the Oldham ring were slidably inserted into the main frame and the orbiting scroll, respectively. However, in some cases, the same may be applied to the case in which the keys of the Oldham ring are slidably inserted into the non-orbiting scroll (fixed scroll) and the orbiting scroll, respectively. In this case, the non-orbiting side key of the Oldham ring inserted into the non-orbiting scroll is formed in the same manner as the frame side key described above, and therefore, the explanation thereof will be replaced with the explanation of the above-described embodiments.

Claims

1. A plurality of scrolls including a pivoting scroll which are interlocked with each other and at least one of the scrolls is coupled to a rotational axis and pivots; and A plurality of pivot keys are provided at predetermined intervals along the circumferential direction on one side of the ring body facing the pivot scroll, and the plurality of pivot keys include an Oldham ring that is slidably engaged with a plurality of pivot key grooves provided in the pivot scroll, respectively. The above plurality of pivot keys are, A pivot-side main key formed on a center line passing through the center of the ring body; and A scroll compressor including a pivot-side sub-key provided on one or both circumferential sides of the plurality of pivot-side main keys.

2. In paragraph 1, The above turning side main key and the above turning side sub key are each provided in multiples, The above plurality of pivot-side sub-keys are, A scroll compressor formed on the same side in the circumferential direction for each of the plurality of pivot-side main keys.

3. In paragraph 2, Each of the above plurality of pivot-side sub-keys is A scroll compressor having the plurality of main keys on the pivot side spaced apart from each other by equal intervals in the circumferential direction.

4. In paragraph 2, Each circumferential gap between the plurality of pivot-side keys and the plurality of pivot-side keyways is Scroll compressors that are formed identically to each other.

5. In paragraph 2, The intervals between the plurality of turning-side main keys and the plurality of turning-side sub keys are respectively: A scroll compressor formed to be 0.13 to 0.2 times the outer diameter of the above ring body.

6. In paragraph 2, The lengths of the above plurality of pivot-side sub-keys are respectively: A scroll compressor formed to be shorter than the length of the plurality of main keys on the pivot side.

7. In paragraph 2, The width of each of the above plurality of pivot-side sub-keys is A scroll compressor formed with the same width as the plurality of main keys on the above-mentioned turning sides.

8. In paragraph 2, The width of the above plurality of pivot-side sub-keys is A scroll compressor formed to be smaller or larger than the width of the plurality of main keys on the above-mentioned turning sides.

9. A plurality of scrolls, including a pivoting scroll, which are interlocked with each other and at least one of the scrolls is coupled to a rotational axis and pivots; and A plurality of pivot keys are provided at predetermined intervals along the circumferential direction on one side of the ring body facing the pivot scroll, and the plurality of pivot keys include an Oldham ring that is slidably engaged with a plurality of pivot key grooves provided in the pivot scroll, respectively. The above plurality of pivot keys are, A scroll compressor having at least four or more keys, wherein the circumferential gaps between the plurality of pivot-side keys and the plurality of pivot-side keyways are formed to be identical to each other.

10. In paragraph 9, On the other side of the ring body facing away from one side of the ring body, a plurality of non-rotating keys are provided at preset intervals along the circumferential direction of the ring body. The above plurality of pivot keys are, A plurality of pivot-side main keys positioned on a center line passing through the center of the ring body; and A scroll compressor including a plurality of pivot-side sub-keys each provided on one or both sides of the circumferential direction of the plurality of pivot-side main keys.

11. In paragraph 10, Each of the above plurality of pivot-side sub-keys is A scroll compressor having the plurality of main keys on the pivot side spaced apart from each other by equal intervals in the circumferential direction.

12. In paragraph 9, Each of the above plurality of turning keys is A scroll compressor spaced apart from the center line passing through the center of the above ring body by a predetermined distance in both circumferential directions.

13. In paragraph 12, Each of the above plurality of turning keys is A scroll compressor formed in parallel and spaced equally apart in the circumferential direction from the center line.

14. In paragraph 12, Each of the above plurality of turning keys is A scroll compressor in which the length or width is formed to be identical to each other.

15. In paragraph 12, The spacing between the plurality of pivot keys provided on both sides of the circumference around the center line is A scroll compressor formed to be 0.13 to 0.2 times the outer diameter of the above ring body.

Images