Scroll compressor

Abstract

The invention provides a scroll compressor. The scroll compressor includes: a first orbiting scroll coupled to a first eccentric portion of a rotating shaft to form a first compression chamber; a second orbiting scroll coupled to a second eccentric portion of the rotating shaft to form a second compression chamber; and a back pressure chamber provided between the back surface of the first orbiting scroll and the back surface of the second orbiting scroll facing the first orbiting scroll, the back pressure chamber supporting the first orbiting scroll and the second orbiting scroll in the axial direction, respectively. As a result, the number of components can be reduced and the size of the compressor can be reduced by excluding a main frame in the twin scroll compressor.

Description

Technical Field

[0001] The invention relates to a scroll compressor, in particular to a double scroll compressor. Background Art

[0002] In a scroll compressor, a fixed scroll (or non-orbiting scroll) and an orbiting scroll that form a compression section engage with each other to form a pair of compression chambers. Since this scroll compressor continuously inhales, compresses, and discharges during the orbiting of the orbiting scroll, the number of components is small and high-speed rotation can be achieved. In addition, since the torque required for compression varies less and inhalation and compression occur continuously, noise and vibration are small. Therefore, scroll compressors are widely used in air conditioners.

[0003] Scroll compressors can be divided into single scroll compressors and twin scroll compressors according to the number of compression parts. A single scroll compressor has one compression part, while a twin scroll compressor has multiple compression parts.

[0004] Patent document 1 (US Patent Publication US2006 / 0204378A1) is a method in which a driving motor is arranged in the middle, and a first compression part and a second compression part are respectively arranged at both ends of a rotating shaft coupled to a rotor of the driving motor. In Patent document 1, since the compression parts on both sides are spaced apart from each other, it is difficult to share components, which increases manufacturing costs and increases the size of the compressor.

[0005] In the conventional scroll compressor as described above, since the first compression section and the second compression section are spaced apart from each other and have a driving motor therebetween, even if an abnormal operation occurs in the compression section on either side, it is difficult to solve the problem quickly and easily, and the manufacturing cost may increase accordingly. For example, if the pressure in the back pressure chamber for supporting the orbiting scroll toward the fixed scroll side rises excessively, causing the orbiting scroll to be in excessively close contact with the fixed scroll, in order to solve this problem, valves must be provided in the compression sections on both sides, respectively, which may not only delay the overpressure release operation, but also increase the manufacturing cost. Summary of the invention

[0006] Problem to be solved

[0007] An object of the present invention is to provide a scroll compressor capable of reducing manufacturing costs by reducing the number of components in a twin scroll compressor.

[0008] Furthermore, an object of the present invention is to provide a scroll compressor that can eliminate a main frame in a twin scroll compressor and stably support compression parts on both sides, thereby reducing manufacturing costs and achieving miniaturization.

[0009] Furthermore, an object of the present invention is to provide a scroll compressor that can use one Oldham coupling ring in a twin scroll compressor and drive compression parts on both sides, thereby reducing manufacturing costs.

[0010] Furthermore, an object of the present invention is to provide a scroll compressor capable of reducing the number of back pressure seal members in a twin scroll compressor and stably supporting compression parts on both sides, thereby reducing manufacturing costs.

[0011] Technical solutions to problems

[0012] In order to achieve the purpose of the present invention, a scroll compressor may include a housing, a drive motor, a rotating shaft, a first compression part, a second compression part and a back pressure chamber. The drive motor may be arranged inside the housing. The rotating shaft may be combined with the rotor of the drive motor and have a first eccentric part and a second eccentric part spaced apart in the axial direction. The first compression part may include a first orbiting scroll plate that is combined with the first eccentric part of the rotating shaft to perform an orbiting motion, and a first fixed scroll plate that is engaged with the first orbiting scroll plate to form a first compression chamber. The second compression part may include a second orbiting scroll plate that is combined with the second eccentric part of the rotating shaft to perform an orbiting motion, and a second fixed scroll plate that is engaged with the second orbiting scroll plate to form a second compression chamber. The back pressure chamber may be arranged between the back side of the first orbiting scroll plate and the back side of the second orbiting scroll plate facing it, and the first orbiting scroll plate and the second orbiting scroll plate are supported in the axial direction respectively. Thus, the main frame can be excluded in the twin scroll compressor to reduce the number of components and miniaturize the compressor.

[0013] As an example, a back pressure sealing member forming the back pressure chamber may be provided on at least one of the back side of the first orbiting scroll and the back side of the second orbiting scroll facing the first orbiting scroll. Thus, the main frame can be eliminated and the first orbiting scroll and the second orbiting scroll can be stably supported, thereby effectively suppressing leakage between the compression chambers.

[0014] Specifically, an annularly recessed back pressure groove can be formed on at least one of the back side of the first orbiting scroll and the back side of the second orbiting scroll facing the first orbiting scroll. The back pressure sealing component can be respectively arranged on the inner circumference and the outer circumference of the back pressure groove. Thus, a back pressure chamber can be stably formed between the first orbiting scroll and the second orbiting scroll as movable components.

[0015] As another example, a cross ring for suppressing the self-rotation of the first and second orbiting scrolls may be provided between the back side of the first orbiting scroll and the back side of the second orbiting scroll facing the first orbiting scroll. Thus, the cross ring can be applied to the twin scroll compressor to simplify the structure of the anti-self-rotation mechanism and facilitate processing. In addition, the miniaturization of the compressor can be achieved by suppressing the increase in the outer diameter of the compression part. In addition, the manufacturing cost can be reduced by reducing the number of cross rings in the twin scroll compressor.

[0016] Specifically, the cross ring may include a ring body, a fixed key, a first swing key, and a second swing key. The ring body may be formed in an annular shape and arranged between the first swing scroll and the second swing scroll. The fixed key may extend axially from the ring body and be slidably inserted into the first fixed scroll or the second fixed scroll. The first swing key may extend from the ring body along a first axial direction and be slidably inserted into the first swing scroll. The second swing key may extend from the ring body along a second axial direction and be slidably inserted into the second swing scroll. Thus, a cross ring can be used in a double scroll compressor to effectively limit the rotation of the swing scrolls on both sides.

[0017] More specifically, the axial length of the fixed key can be formed to be longer than the axial length of the first and second swirl keys. Thus, the cross ring is located between the first and second swirl scrolls and the fixed key of the cross ring is slidably coupled to the fixed scroll, so that the rotation of the swirl scrolls on both sides can be effectively restricted by one cross ring.

[0018] Alternatively, the first and second orbiting keys may be formed symmetrically with respect to the ring body. Thus, the rotation of the orbiting scrolls on both sides can be effectively restricted by using one Oldham ring in the twin scroll compressor.

[0019] Alternatively, the first keyway protrusion may extend radially on the outer peripheral surface of the first orbiting scroll, and the first keyway protrusion may be formed with a first orbiting keyway into which the first orbiting key is slidably inserted radially. The second keyway protrusion may extend radially on the outer peripheral surface of the second orbiting scroll, and the second keyway protrusion may be formed with a second orbiting keyway into which the second orbiting key is slidably inserted radially. The first orbiting keyway and the second orbiting keyway may be formed on the same axis. Thus, a cross ring can be used in a double scroll compressor to effectively limit the rotation of the orbiting scrolls on both sides.

[0020] Specifically, a stepped cross-ring accommodation surface that is lower than the back side of the first orbiting scroll or the back side of the second orbiting scroll can be formed on at least one of the side surfaces of the first keyway protrusion and the side surfaces of the second keyway protrusion facing the first keyway protrusion. The ring body of the cross-ring can be inserted into the cross-ring accommodation surface from the back side of at least one of the first orbiting scroll and the second orbiting scroll. Thus, a cross-ring can be used in a twin-scroll compressor to effectively limit the rotation of the orbiting scrolls on both sides, and ensure the reliability of the cross-ring.

[0021] More specifically, a stepped first cross ring accommodating surface may be formed on one side of the first keyway protrusion, and a second cross ring accommodating surface may be formed on one side of the second keyway protrusion facing the first cross ring accommodating surface. The ring body of the cross ring may be inserted into the first orbiting scroll and the second orbiting scroll, respectively. Thus, the rigidity of the cross ring can be ensured by keeping the axial length of the fixing key and / or the orbiting key of the cross ring as short as possible in the twin scroll compressor.

[0022] In addition, at least one of the first and second orbiting key grooves may be open in the axial direction, thereby enabling oil to be smoothly supplied between the orbiting key groove and the orbiting key, thereby reducing friction loss between the Oldham ring and the orbiting scroll and improving reliability.

[0023] In addition, in at least one of the first and second swirl keyways, at least a portion of the other surfaces except the surface facing the Cross ring in the axial direction can be formed into a closed shape. As a result, a portion of the oil supplied between the swirl keyway and the swirl key will remain between the swirl keyway and the swirl key, thereby further reducing the friction loss between the Cross ring and the swirl scroll and further improving reliability. Furthermore, since the bottom surfaces of the swirl keyways on both sides of the swirl key are connected to each other, the rigidity of the swirl keyway can be improved.

[0024] As another example, a first cross ring may be provided between the first orbiting scroll and the first fixed scroll facing the first orbiting scroll, and a second cross ring may be provided between the second orbiting scroll and the second fixed scroll facing the first orbiting scroll. Thus, the main frame can be eliminated in the twin scroll compressor and the load applied to the cross ring can be reduced to improve the reliability of the cross ring.

[0025] Specifically, the first Oldham ring may include a first ring body, a first fixed key, and a first swing key. The first ring body may be formed in an annular shape and disposed between the first orbiting scroll and the first fixed scroll. The first fixed key may extend from the first ring body along a first axial direction and be slidably inserted into the first fixed scroll. The first swing key may extend from the first ring body along a second axial direction and be slidably inserted into the first orbiting scroll. The second Oldham ring may include a second ring body, a second fixed key, and a second swing key. The second ring body may be formed in an annular shape and disposed between the second orbiting scroll and the second fixed scroll. The second fixed key may extend from the second ring body along a second axial direction and be slidably inserted into the second fixed scroll. The second swing key may extend from the second ring body along a first axial direction and be slidably inserted into the second orbiting scroll. Thus, since each Oldham ring is provided in each compression portion of the twin scroll compressor, the load applied to the Oldham ring can be dispersed, thereby improving the reliability of the Oldham ring.

[0026] As another example, the first eccentric portion and the second eccentric portion may be formed to be located on the same axis. Thus, the first orbiting scroll and the second orbiting scroll are subjected to the same back pressure at the same position and perform an orbiting motion, so that the orbiting scrolls on both sides operate stably, thereby effectively suppressing leakage between the compression chambers to improve compression efficiency.

[0027] As another example, the first eccentric portion and the second eccentric portion may be formed to be located on different axes, thereby making it possible to cancel out the centrifugal forces generated by the eccentric portions on both sides to reduce the vibration of the compressor.

[0028] Effects of the Invention

[0029] According to the scroll compressor of the present invention, the scroll compressor may include: a first swirling scroll plate, which is combined with the first eccentric portion of the rotating shaft to form a first compression chamber; a second swirling scroll plate, which is combined with the second eccentric portion of the rotating shaft to form a second compression chamber; and a swirling scroll plate arranged between the back side of the first swirling scroll plate and the back side of the second swirling scroll plate facing the first swirling scroll plate, respectively supporting the first swirling scroll plate and the second swirling scroll plate in the axial direction. Thus, the main frame can be eliminated in the double scroll compressor to reduce the number of components and miniaturize the compressor.

[0030] According to the scroll compressor of the present invention, a back pressure sealing component forming a back pressure chamber can be provided on at least one of the back side of the first orbiting scroll plate and the back side of the second orbiting scroll plate facing the first orbiting scroll plate. Thus, the main frame can be eliminated and the first orbiting scroll plate and the second orbiting scroll plate can be stably supported, thereby effectively suppressing leakage between the compression chambers.

[0031] According to the scroll compressor of the present invention, a cross ring for suppressing the self-rotation of the first and second orbiting scroll plates can be provided between the back side of the first orbiting scroll plate and the back side of the second orbiting scroll plate facing the first orbiting scroll plate. Thus, the cross ring can be applied to the twin scroll compressor to simplify the structure of the anti-self-rotation mechanism and make the processing easier. In addition, the miniaturization of the compressor can be achieved by suppressing the increase in the outer diameter of the compression part. In addition, the manufacturing cost can be reduced by reducing the number of cross rings in the twin scroll compressor.

[0032] According to the scroll compressor of the present invention, the first and second orbiting keys may be formed symmetrically with the ring body as the center, thereby effectively restricting the rotation of the orbiting scrolls on both sides in the twin scroll compressor by using one Oldham ring.

[0033] According to the scroll compressor of the present invention, the ring body of the cross ring can be inserted into the receiving surface of the cross ring from the back side of at least one of the first and second orbiting scroll plates. Thus, a cross ring can be used in a double scroll compressor to effectively limit the rotation of the orbiting scroll plates on both sides and ensure the reliability of the cross ring.

[0034] According to the scroll compressor of the present invention, a first cross ring can be provided between the first orbiting scroll and the first fixed scroll facing the first orbiting scroll, and a second cross ring can be provided between the second orbiting scroll and the second fixed scroll facing the second orbiting scroll. Thus, the reliability of the cross ring can be improved by eliminating the main frame in the twin scroll compressor and reducing the load applied to the cross ring.

[0035] According to the scroll compressor of the present invention, the first eccentric portion and the second eccentric portion can be formed to be located on the same axis. As a result, the first orbiting scroll and the second orbiting scroll are subjected to the same back pressure at the same position and perform an orbiting motion, so that the orbiting scrolls on both sides operate stably, thereby effectively suppressing leakage between the compression chambers to improve the compression efficiency.

[0036] According to the scroll compressor of the present invention, the first eccentric portion and the second eccentric portion may be formed to be located on different axes, thereby making it possible to cancel out the centrifugal forces generated by the eccentric portions on both sides and reduce the vibration of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] Figure 1 1 is a longitudinal sectional view showing the scroll compressor according to the present embodiment.

[0038] Figure 2 It is decomposition Figure 1 A stereoscopic view of the compression section in FIG. 1 and shown from the top.

[0039] Figure 3It is decomposition Figure 1 A stereoscopic view of the compression section in FIG. 1 and shown from the bottom.

[0040] Figure 4 Yes Assembly Figure 2 and Figure 3 A portion of the diagram is shown in a stereoscopic view.

[0041] Figure 5 Is separation Figure 4 A portion of the diagram is shown in a stereoscopic view.

[0042] Figure 6 Is magnification Figure 5 The "A" portion is shown in a stereoscopic view.

[0043] Figure 7 yes Figure 6 "IX-IX" line cross-sectional view.

[0044] Figure 8 It shows that Figure 7 A perspective view of another embodiment of the "A" portion.

[0045] Fig. 9 It is decomposed for Figure 1 Another embodiment of the compression part in FIG. 1 is shown in a perspective view from the top.

[0046] Fig.10 yes Fig. 9 "XX" line sectional view.

[0047] Fig.11 Yes Assembly Fig. 9 and a cross-sectional view shown.

[0048] Fig.12 It is decomposed for Figure 1 A stereoscopic view of another embodiment of the compression portion in FIG. 1 and shown from the top.

[0049] Fig.13 Yes Assembly Fig.12 The compressed portion is shown in a cross-sectional view. DETAILED DESCRIPTION

[0050] Hereinafter, the scroll compressor according to the present invention will be described in detail based on the drawings. In the following description, in order to clarify the features of the present invention, the description of some components may be omitted.

[0051] In addition, the "upper side" used in the following description refers to the direction away from the support surface supporting the scroll compressor according to the embodiment of the present invention, that is, the drive part (electric part or drive motor) side represents the upper side when viewed from the center of the drive part (electric part or drive motor) and the compression part. The "lower side" refers to the direction close to the support surface, that is, the compression part side represents the lower side when viewed from the center of the drive part (electric part or drive motor) and the compression part.

[0052] In addition, the term "axial direction" used in the following description refers to the length direction of the rotation axis. "Axial direction" can be understood as the direction of the upper and lower sides. "Radial direction" refers to the direction intersecting the rotation axis.

[0053] In addition, in the following description, the case where the scroll compressor is a closed scroll compressor having a drive unit (electric unit or drive motor) and a compression unit in the housing is used as an example for description. However, the same may also be applied to an open compressor in which the drive unit (electric unit or drive motor) is arranged outside the housing and connected to the compression unit arranged inside the housing.

[0054] In addition, in the following description, the following scroll compressor is taken as an example for description, and the scroll compressor is a vertical scroll compressor in which the electric part and the compression part are arranged along the vertical axial direction, and is a lower compression scroll compressor in which the compression part is located at a lower side position than the driving part (electric part or driving motor). However, it can also be applied to a horizontal scroll compressor in which the driving part (electric part or driving motor) and the compression part are arranged left and right, and an upper compression scroll compressor in which the compression part is located at an upper side position than the driving part (electric part or driving motor).

[0055] Figure 1 is a longitudinal sectional view showing a scroll compressor according to the present embodiment, Figure 2 It is decomposition Figure 1 The compression part in the figure is shown in a perspective view from the top, Figure 3 It is decomposition Figure 1 A stereoscopic view of the compression section in FIG. 1 and shown from the bottom.

[0056] Reference Figure 1 According to the twin scroll compressor (hereinafter referred to as scroll compressor) of this embodiment, a driving motor 120 forming an electric part is provided in the upper half of the shell 110, and a first compression part C1 and a second compression part C2 are respectively provided on one side of the driving motor 120.

[0057] The driving motor 120 forming the electric part is coupled to the upper end of the rotating shaft 125 described later, and the first compression part C1 and the second compression part C2 are sequentially coupled to the lower end of the rotating shaft 125. Therefore, the compressor forms the above-mentioned lower compression type structure, and the first compression part C1 and the second compression part C2 are coupled to the driving motor 120 through one rotating shaft 125, so as to operate at the same speed.

[0058] Reference Figure 1 According to the present embodiment, the housing 110 may include a cylindrical housing 111, an upper housing 112, and a lower housing 113. The cylindrical housing 111 is in the shape of a cylinder with upper and lower ends opened, the upper housing 112 is combined in a manner of covering the upper end of the cylindrical housing 111, and the lower housing 113 is combined in a manner of covering the lower end of the cylindrical housing 111. Therefore, the internal space 110a of the housing 110 is closed, and the internal space 110a of the closed housing 110 is divided into a lower space S1 and an upper space S2 based on the driving motor 120.

[0059] The lower space S1 is a space formed at the lower side of the driving motor 120 , and the lower space S1 may be further divided into an oil storage space S11 and a discharge space S12 based on the compression part C including the first compression part C1 and the second compression part C2 .

[0060] The oil storage space S11 is a space formed at the lower side of the compression part C, forming a space for storing oil or a mixed oil mixed with liquid refrigerant. The discharge space S12 is a space formed between the upper surface of the compression part C and the lower surface of the drive motor 120, forming a space for discharging the refrigerant compressed in the compression part C or the mixed refrigerant mixed with oil.

[0061] The upper space S2 is a space formed above the driving motor 120 and forms an oil separation space where oil is separated from the refrigerant discharged from the compressed portion C. The refrigerant discharge pipe 116 communicates with the upper space S2.

[0062] The lower space S1 and the upper space S2 may be communicated through an internal passage that penetrates the internal space 110a of the shell 110, or may be communicated through an external passage that passes through the outside of the shell 110. In the present embodiment, since the main frame is excluded between the first compression section C1 and the second compression section C2 described later, the lower space S1 and the upper space S2 of the shell 110 may be communicated through an external passage (not shown). However, the lower space S1 and the upper space S2 of the shell 110 do not necessarily have to be communicated through an external passage (not shown). For example, a communication portion (not shown) may also be formed between the first fixed scroll 141 and the second fixed scroll 142 described later, so that the lower space S1 and the upper space S2 of the shell 110 are communicated through an internal passage (not shown).

[0063] The refrigerant suction pipe 115 penetrates and is coupled to the side of the cylindrical shell 111. Therefore, the refrigerant suction pipe 115 penetrates and is coupled to the cylindrical shell 111 forming the shell 110 in a radial direction.

[0064] The refrigerant suction pipe 115 may be formed in an F shape having one inlet and two outlets. For example, one end of the refrigerant suction pipe 115 forming the inlet is connected to a refrigerant pipe (not shown) extending from an evaporator (not shown), and the other end of the refrigerant suction pipe 115 forming the outlet is divided into a first suction pipe 1151 and a second suction pipe 1152, the first suction pipe 1151 is connected to a first suction port 1412a described later, and the second suction pipe 1152 is connected to a second suction port 1422a described later. Therefore, the refrigerant is directly sucked into the first compression chamber V1 through the first suction pipe 1151, and is directly sucked into the second compression chamber V2 through the second suction pipe 1152.

[0065] The inner end of the refrigerant discharge pipe 116 passes through and is coupled to the upper portion of the upper shell 112 so as to communicate with the internal space 110 a of the shell 110 (specifically, the upper space S2 formed on the upper side of the driving motor 120 ).

[0066] One end of the oil circulation pipe (not shown) may penetrate radially and be coupled to the lower half of the lower shell 113. Both ends of the oil circulation pipe may be open, and the other end of the oil circulation pipe may penetrate and be coupled to the refrigerant suction pipe 115. An oil circulation valve (not shown) may be provided in the middle of the oil circulation pipe.

[0067] Reference Figure 1 The driving motor 120 according to the present embodiment includes a stator 121 and a rotor 122. The stator 121 is inserted into and fixed to the inner circumference of the cylindrical housing 111, and the rotor 122 is rotatably disposed inside the stator 121.

[0068] The stator 121 includes a stator core 1211 and a stator coil 1212 .

[0069] The stator core 1211 is formed into an annular or hollow cylindrical shape and is hot-pressed and fixed to the inner circumference of the cylindrical housing 111. The outer circumference of the stator core 1211 is cut or recessed into a D-cut shape in the axial direction so that the oil separated from the upper space S2 can be recovered to the oil storage space S11.

[0070] The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source through a power cable 1141 that penetrates and is combined with the housing 110. A refrigerant channel (not marked) is formed between the stator core 1211 and the stator coil 1212 to move the refrigerant discharged from the first compression part C1 to the upper space S2.

[0071] The rotor 122 includes a rotor core 1221 and permanent magnets 1222 .

[0072] The rotor core 1221 is formed in a cylindrical shape and is rotatably accommodated in the central portion of the stator core 1211 via a predetermined gap. Therefore, the gap between the stator core 1211 and the rotor core 1221 forms a refrigerant passage (not indicated by a symbol).

[0073] The permanent magnet 1222 is embedded along the edge of the rotor core 1221, and the upper end of the rotating shaft 125 is coupled to the center of the rotor core 1221. Therefore, the rotating shaft 125 rotates together with the rotor 122, and transmits the rotational force of the driving motor 120 to the first and second orbiting scrolls 151 and 152 forming the compression part C.

[0074] The rotating shaft 125 includes a main shaft portion 1251, a first bearing portion 1252, a second bearing portion 1253, an extension portion 1254, a first eccentric portion 1255, and a second eccentric portion 1256. The first bearing portion 1252, the second bearing portion 1253, and the axis alignment portion 1254 are formed on the same axis as the main shaft portion 1251, and the first eccentric portion 1255 and the second eccentric portion 1256 are formed on different axes from the main shaft portion 1251. Therefore, when the rotating shaft 125 rotates, the first eccentric portion 1255 and the second eccentric portion 1256 rotate eccentrically relative to the axis O of the rotating shaft 125.

[0075] The main shaft portion 1251 forms the upper end portion of the rotating shaft 125 and is press-fitted and coupled to the rotor 122. The main shaft portion 1251 extends in the axial direction so as to be coaxial with the rotor 122. Therefore, the main shaft portion 1251 rotates concentrically with the rotor 122.

[0076] The first bearing portion 1252 is formed between the main shaft portion 1251 and the first eccentric portion 1255, and the second bearing portion 1253 is formed between the second eccentric portion 1256 and the lower end of the rotating shaft 125. Therefore, the first bearing portion 1252 can be inserted into the first fixed scroll 141 described later and radially supported, and the second bearing portion 1253 can be inserted into the second fixed scroll 142 described later and radially supported.

[0077] The first eccentric portion 1255 and the second eccentric portion 1256 extend from the main shaft portion 1251 to form the lower half of the rotating shaft 125, and are inserted and coupled to the compression portion. For example, the first eccentric portion 1255 is coupled to the first compression portion C1 described later, and the second eccentric portion 1256 is coupled to the second compression portion C2 described later. Therefore, the first eccentric portion 1255 and the second eccentric portion 1256 rotate at the same speed as the main shaft portion 1251.

[0078] The first eccentric portion 1255 and the second eccentric portion 1256 can be formed on the same axis or on different axes. In other words, the first eccentric portion 1255 and the second eccentric portion 1256 can be formed to be eccentric with the same eccentricity at the same rotation angle, or can be formed to be eccentric with different eccentricities at different rotation angles. In the present embodiment, an example is shown in which the first eccentric portion 1255 and the second eccentric portion 1256 are formed on the same axis, so that the first eccentric portion 1255 and the second eccentric portion 1256 are axially symmetrical. Therefore, the first orbiting scroll 151 combined with the first eccentric portion 1255 and the second orbiting scroll 152 combined with the second eccentric portion 1256 are symmetrically subjected to back pressure, so that the operation of the first orbiting scroll and the second orbiting scroll can be stabilized.

[0079] In addition, a hollow oil supply channel 126 is formed inside the rotating shaft 125. The oil supply channel 126 can penetrate the inside of the rotating shaft 125 or form a groove dug to a predetermined height. In the present embodiment, a groove can be formed from the lower end of the rotating shaft 125 to an intermediate height (for example, to the first bearing portion 1252). An oil pickup 127 for sucking the oil filled in the oil storage space S11 can be coupled to the lower end of the rotating shaft 125. Therefore, when the rotating shaft 125 rotates, the oil filled in the oil storage space S11 is sucked to the upper end of the rotating shaft 125 through the oil pickup 127 and the oil supply channel 126, thereby lubricating the sliding portion.

[0080] The oil supply passage 126 may be formed along the axial direction or may be formed obliquely at a predetermined angle. This embodiment shows an example in which the oil supply passage 126 is formed obliquely. Therefore, the oil sucked by the oil picker 127 is sucked by the centrifugal force in the oil supply passage 126, so that it can be smoothly supplied to the sliding portion.

[0081] An oil supply hole penetrating the outer peripheral surface of the rotating shaft 125 is formed in the oil supply passage 126. A plurality of oil supply holes may be formed at predetermined intervals between the lower end and the upper end of the oil supply passage 126. For example, a first oil supply hole 126a may be formed in the second bearing portion 1253, a second oil supply hole 126b may be formed in the second eccentric portion 1256, a third oil supply hole 126c may be formed in the first eccentric portion 1255, and a fourth oil supply hole 126d may be formed in the first bearing portion 1252. Therefore, the oil sucked through the oil supply passage 126 may be smoothly supplied to the respective bearing surfaces through the respective oil supply holes.

[0082] Reference Figures 1 to 3According to the present embodiment, the compression part C includes a first compression part C1, a second compression part C2, and a cross ring 160 shared by the first compression part C1 and the second compression part C2. The first compression part C1 and the second compression part C2 are respectively arranged on both sides of the axial direction with the cross ring 160 as a reference. In the following, the compression part located on the lower side of the cross ring 160 is defined as the first compression part C1, and the compression part located on the upper side of the cross ring 160 is defined as the second compression part C2 for explanation.

[0083] The first compression portion C1 according to the present embodiment includes a first fixed scroll 141 and a first orbiting scroll 151 .

[0084] The first fixed scroll 141 may be fixed to the inner circumferential surface of the cylindrical housing 111, and the first orbiting scroll 151 may be rotatably supported in the axial direction by the upper surface of the first fixed scroll 141. Therefore, two pairs of first compression chambers V1 are formed between the first fixed scroll 141 and the first orbiting scroll 151 forming the first compression portion C1.

[0085] The first fixed scroll 141 according to the present embodiment may include a first fixed end plate portion 1411 , a first fixed sidewall portion 1412 , a first bearing protrusion 1413 , and a first fixed wrap 1414 .

[0086] The first fixed end plate portion 1411 is formed in a disk shape, and a first bearing hole 1413 a penetrating in the axial direction and forming a first bearing protrusion 1413 described later is formed at the center thereof.

[0087] A first discharge port 1411a is formed around the first bearing hole 1413a described later, and the first discharge port 1411a is formed to open toward the discharge space 1451 of the discharge cover 145 fixed to the second side surface (lower surface) of the first fixed end plate portion 1411. Therefore, the refrigerant compressed in the first compression chamber V1 is discharged to the discharge space 1451 of the discharge cover 145 through the first discharge port 1411a.

[0088] The first fixed side wall portion 1412 may be formed into an annular shape by axially extending from the first side (upper surface) edge of the first fixed end plate portion 1411 toward the first orbiting end plate portion 1511 of the first orbiting scroll 151. Therefore, the first orbiting end plate portion 1511 may be supported axially by the first fixed side wall portion 1412 in an axially rotatable manner.

[0089] The first fixed side wall portion 1412 is provided with a first suction port 1421 that radially penetrates the first fixed side wall portion 1412. As described above, the end of the first suction pipe 1151 that penetrates the cylindrical shell 111 is inserted into and coupled to the first suction port 1421. Therefore, a portion of the refrigerant discharged from the evaporator is sucked into the first compression chamber V1 through the first suction pipe 1151 of the refrigerant suction pipe 115 and the first suction port 1421a.

[0090] A fixed keyway 1412b is formed on the upper surface of the first fixed side wall portion 1412. The fixed keyway 1412b is formed long in the radial direction on both sides with a phase difference of 180 degrees in the circumferential direction. Therefore, the fixed key 160b of the later-described Oldham ring 160 is slidably inserted into the fixed keyway 1412b in the radial direction, thereby guiding the orbiting motion of the first orbiting scroll 151 and the second orbiting scroll 152.

[0091] Although not shown in the drawings, the fixed key groove 1412 b may be formed in the second fixed side wall portion 1422 of the second fixed scroll 142 , or may be formed in the first fixed side wall portion 1412 and the second fixed side wall portion 1422 , respectively.

[0092] The first bearing protrusion 1413 is formed to extend axially from the center of the first fixed end plate portion 1411 toward the lower housing 113. A first cylindrical bearing hole 1413a penetrating in the axial direction may be formed at the center of the first bearing protrusion 1413, and the first bearing portion 1252 of the rotating shaft 125 may be inserted into the first bearing hole 1413a and radially supported.

[0093] The first bearing hole 1413a and the second bearing hole 1423a described later are formed on the same axis. A bearing member made of a bushing bearing or a ball bearing may be provided on the inner circumference of the first bearing hole 1413a to support the first bearing portion 1252 of the rotating shaft 125.

[0094] The first fixed wrap 1414 may be formed to extend axially from the upper surface of the first fixed end plate portion 1411 toward the first orbiting scroll 151. The first fixed wrap 1414 meshes with a first orbiting wrap 1512 described later to form a pair of first compression chambers V1.

[0095] The first fixed scroll 1414 may be formed in an involute shape. However, the first fixed scroll 1414 may be formed in various shapes other than an involute together with the first orbiting scroll 1512. For example, the first fixed scroll 1414 may have a shape connecting a plurality of arcs having different diameters and origins, and the outermost curve may be formed in a substantially elliptical shape having a major axis and a minor axis. This may also be formed in the first orbiting scroll 1512 in the same manner.

[0096] Figure 4 Yes Assembly Figure 2 and Figure 3 A portion of the stereogram is shown, Figure 5 Is separation Figure 4 A portion of the stereogram is shown, Figure 6 Is magnification Figure 5 The "A" portion and the perspective view shown, Figure 7 yes Figure 6 The "IX-IX" line section view, Figure 8 It shows that Figure 7 A perspective view of another embodiment of the "A" portion.

[0097] Reference Figures 4 to 8 According to the present embodiment, the first orbiting scroll 151 includes a first orbiting end plate portion 1511 , a first orbiting scroll 1512 and a first rotation shaft coupling portion 1513 .

[0098] The first orbiting end plate 1511 is formed in a disc shape, and a first orbiting scroll 1512 is formed in the center of its lower surface. The lower surface edge of the first orbiting end plate 1511 is axially supported by the upper surface of the first fixed scroll 141. Therefore, when the first orbiting scroll 1512 is engaged with the first fixed scroll 1414, the first orbiting end plate 1511 is supported by the first fixed scroll 141 and performs an orbiting motion.

[0099] The first revolving keyway 1511b is formed to extend radially from the outer peripheral surface of the first revolving end plate 1511. Like the fixed keyway 1412b, the first revolving keyway 1511b is formed on both sides with a phase difference of 180° in the circumferential direction, and has a phase difference of 90° with the fixed keyway 1412b. Therefore, the first revolving key 160c of the later-described Cross ring 160 can be slidably inserted into the first revolving keyway 1511b, so that the first revolving scroll 151 revolves relative to the first fixed scroll 141.

[0100] Specifically, a first keyway protrusion 1511a extending in the radial direction is formed on the outer peripheral surface of the first rotary end plate portion 1511, and the first rotary keyway 1511b is formed to cross the center of the first keyway protrusion 1511a in the radial direction. In other words, the first rotary keyway 1511b is formed in a substantially rectangular shape extending in the radial direction when projected in the axial direction. Therefore, the first rotary key 160c to be described later inserted into the first rotary keyway 1511b is supported by the first rotary keyway 1511b on both sides in the circumferential direction and can slide in the radial direction.

[0101] A stepped first cross ring accommodation surface 1511c is formed on the upper surface of the first keyway protrusion 1511a. In other words, the upper surface of the first keyway protrusion 1511a is formed to be lower than the back surface of the first revolving end plate 1511. Therefore, a part of the ring body 160a of the later-described cross ring 160, that is, the lower half of the ring body 160a, can be inserted into the outer peripheral surface of the first revolving end plate 1511 until the first cross ring accommodation surface 1511c. Thus, the cross ring 160 is arranged between the back surface of the first revolving end plate 1511 and the back surface of the second revolving end plate 1521, and the back surfaces of the revolving end plates 1511 and 1521 on both sides can slide in contact with each other. In addition, since the outer diameter of the portion of the first revolving end plate 1511 other than the first keyway protrusion 1511a is not increased as a whole, the weight of the first revolving scroll 151 can be reduced to improve the efficiency of the compressor.

[0102] Although not shown, the first Cross-ring accommodating surface 1511c may be excluded. In this case, the second Cross-ring accommodating surface 1521c may be formed only in the second orbiting scroll 152, so that the ring body 160a of the Cross-ring 160 described later is only inserted into the second orbiting scroll 152. This is also the same in the second orbiting scroll 152. That is, the second Cross-ring accommodating surface 1521c may be excluded and only the first Cross-ring accommodating surface 1511c may be provided, so that the ring body 160a of the Cross-ring 160 is only inserted into the first orbiting scroll 151. In these cases, the processing of the Cross-ring accommodating surface can be simplified by reducing the number of times the Cross-ring accommodating surface is processed.

[0103] The first rotary keyway 1511b can be formed into a shape with an open outer circumferential surface, or can be formed into a shape with a closed outer circumferential surface. When the outer circumferential surface of the first rotary keyway 1511b is open, oil can be smoothly supplied between the first rotary keyway 1511b and the first rotary key 160c. On the contrary, when the outer circumferential surface of the first rotary keyway 1511b is closed, the two ends of the first rotary keyway 1511b are connected to each other, so that the rigidity in the first rotary keyway 1511b can be improved. In this embodiment, an example in which the outer circumferential surface of the first rotary keyway 1511b is open is shown.

[0104] In addition, the first rotary keyway 1511b can be formed to be through-through in the axial direction, or can be formed to be a structure with one side surface closed. Figure 6 and Figure 7 As shown, the side surfaces on both axial sides of the first rotary key groove 1511b can be formed to be open. In this case, the bearing surface between the first rotary key groove 1511b and the first rotary key 160c is exposed on both axial sides, so that oil can be supplied to either side of the axial direction, and thus oil can be smoothly supplied to the bearing surface between the first rotary key groove 1511b and the first rotary key 160c.

[0105] However, the first swing key groove 1511b may also be formed in a shape in which at least a portion of the side surfaces other than the upper surface into which the first swing key 160c of the cross ring 160 is inserted is closed. Figure 8 As shown, a keyway connection surface 1511d may be formed on the lower surface and the outer side surface of the first rotary keyway 1511b, respectively. Therefore, the axial lower end and the radial outer end of the first rotary keyway 1511b may be connected to each other through the keyway connection surface 1511d.

[0106] As described above, if the lower surface of the first rotary key groove 1511b is connected to the outer side surface through the key groove connecting surface 1511d, the oil flowing into the upper surface of the first rotary key groove 1511b can be stored in the first rotary key groove 1511b through the key groove connecting surface 1511d. In this way, the oil can be smoothly supplied between the first rotary key groove 1511b and the first rotary key 160c not only at the initial startup of the compressor but also during operation, thereby suppressing friction loss or wear.

[0107] In addition, since the lower surface of the first rotary key groove 1511b is connected to the outer side surface through the key groove connecting surface 1511d, the rigidity of the first key groove protrusion 1511a including the first rotary key groove 1511b can be improved. In other words, even if the first key groove protrusion 1511a including the first rotary key groove 1511b is formed in a cantilever shape, since the first key groove protrusions 1511a are connected to each other around the first rotary key groove 1511b, the rigidity of the first key groove protrusion 1511a including the first rotary key groove 1511b can be improved.

[0108] Although not shown, the keyway connection surface 1511d may be formed only on one side of the lower surface or the outer side surface of the first rotary keyway 1511b. For example, when the keyway connection surface 1511d is formed on the lower surface of the first rotary keyway 1511b, it may be advantageous in terms of oil supply and rigidity, and when the keyway connection surface 1511d is formed on the outer side surface of the first rotary keyway 1511b, it may be advantageous in terms of rigidity.

[0109] In addition, an annular back pressure chamber 170 is formed between the first orbiting end plate 1511 and the second orbiting end plate 1521 opposite thereto. Therefore, the first orbiting end plate 1511 is axially supported relative to the second orbiting end plate 1521 in the direction toward the first fixed scroll 141, thereby effectively suppressing leakage between compression chambers in the first compression chamber V1.

[0110] Specifically, a first sealing groove 1511e and a second sealing groove 1511f are formed at a predetermined interval in the radial direction on the back side of the first rotating end plate 1511, and a back pressure groove 1511g recessed to a predetermined depth is formed between the first sealing groove 1511e and the second sealing groove 1511f. Since the first sealing groove 1511e and the second sealing groove 1511f are formed in an annular shape, the back pressure groove 1511g is also formed in an annular shape.

[0111] The first back pressure sealing member 155 is inserted into the first sealing groove 1511e, and the second back pressure sealing member 156 is inserted into the second sealing groove 1511f. The first back pressure sealing member 155 contacts the back side of the first rotating end plate 1511 and the back side of the second rotating end plate 1521 to seal the inner peripheral side of the back pressure groove 1511g, and the second back pressure sealing member 156 contacts the back side of the first rotating end plate 1511 and the back side of the second rotating end plate 1521 to seal the outer peripheral side of the back pressure groove 1511g. Therefore, the back pressure groove 1511g is radially sealed by the first back pressure sealing member 155 and the second back pressure sealing member 156, and is axially sealed by the back side of the first rotating end plate 1511 and the back side of the second rotating end plate 1521, thereby forming the above-mentioned annular back pressure chamber 170.

[0112] The back pressure chamber 170 communicates with the oil supply passage 126 and the first bearing hole 1413 a forming the discharge pressure, so that the inner back pressure chamber 171 forms a discharge pressure space and the outer back pressure chamber 172 forms an intermediate pressure space via the first back pressure seal member 155 .

[0113] As described above, the back pressure chamber 170 is formed in an annular shape, and the discharge ports 1411a and 1421a in this embodiment are arranged eccentrically from the axis, so the back pressure chamber 170 can also be formed eccentrically in the direction in which the discharge ports 1411a and 1421a are eccentric. Therefore, the first orbiting scroll 151 and the second orbiting scroll 152 can be supported more stably.

[0114] The first orbiting wrap 1512 may be formed to extend from the second side surface (lower surface) of the first orbiting end plate portion 1511 toward the first fixed scroll 141. The first orbiting wrap 1512 meshes with the first fixed scroll 1414 to form a first compression chamber V1.

[0115] Since the first orbiting scroll 1512 is formed corresponding to the shape of the first fixed scroll 1414, the description of the first orbiting scroll 1512 is replaced by the description of the first fixed scroll 1414. However, the inner end of the first orbiting scroll 1512 can be formed in the central part of the first orbiting end plate 1511, and a first rotating shaft coupling portion 1513 that penetrates axially can be formed in the central part of the first orbiting end plate 1511.

[0116] The first eccentric portion 1255 of the rotating shaft 125 is rotatably inserted and coupled to the first rotating shaft coupling portion 1513. The outer periphery of the first rotating shaft coupling portion 1513 is connected to the first orbiting scroll 1512, thereby forming a first compression chamber V1 together with the first fixed scroll 1414 during compression.

[0117] The first rotating shaft coupling portion 1513 may be formed at a height overlapping with the first swirling scroll 1512 on the same plane. That is, the first rotating shaft coupling portion 1513 may be arranged at a height where the first eccentric portion 1255 of the rotating shaft 125 overlaps with the first swirling scroll 1512 on the same plane. Therefore, the repulsive force and the compressive force of the refrigerant are offset by each other based on the first swirling end plate portion 1511 applied to the same plane, thereby suppressing the tilting of the first swirling scroll 151 caused by the action of the compressive force and the repulsive force.

[0118] Refer again Figures 1 to 3 According to the present embodiment, the second compression portion C2 is disposed on the upper side of the later-described Oldham ring 160 , and is formed symmetrically with the first compression portion C1 . For example, the second compression portion C2 includes a second fixed scroll 142 and a second orbiting scroll 152 .

[0119] The second fixed scroll 142 is fixed to the inner circumferential surface of the cylindrical housing 111 from the upper side of the Oldham ring 160, and the second orbiting scroll 152 can be rotatably supported in the axial direction by the back surface of the second orbiting scroll 152. Therefore, two pairs of second compression chambers V2 are formed between the second fixed scroll 142 and the second orbiting scroll 152 forming the second compression portion C2.

[0120] The second fixed scroll 142 according to the present embodiment includes a second fixed end plate portion 1421 , a second fixed side wall portion 1422 , a second bearing protrusion 1423 , and a second fixed wrap 1424 .

[0121] The second fixed end plate 1421 is formed in a disc shape, and a second bearing hole 1423a is formed in the center thereof, which passes through in the axial direction and forms a second bearing protrusion 1423 described later. A second discharge port 1421a is formed around the second bearing hole 1423a. The second discharge port 1421a is formed to be located on the same axis as the first discharge port 1411a, in other words, at the same rotation angle.

[0122] The second discharge port 1421a is formed to communicate between the second compression chamber V2 and the internal space 110a of the housing 110. Therefore, the refrigerant compressed in the second compression chamber V2 is discharged to the internal space 110a of the housing 110 through the second discharge port 1421a.

[0123] The second fixed side wall portion 1422 can be formed into an annular shape by axially extending from the first side (lower surface) edge of the second fixed end plate portion 1421 toward the second orbiting end plate portion 1521 of the second orbiting scroll 152 described later. Therefore, the second orbiting end plate portion 1521 can be supported axially by the second fixed side wall portion 1422 in a rotatable manner.

[0124] The second fixed side wall portion 1422 is provided with a second suction port 1422a that radially penetrates the second fixed side wall portion 1422. The second suction port 1422a is formed to be coaxial with the first suction port 1412a, in other words, to be located at the same rotation angle.

[0125] As described above, the end of the second suction pipe 1152 penetrating the cylindrical shell 111 is inserted and coupled to the second suction port 1422a. Therefore, a portion of the refrigerant discharged from the evaporator is sucked into the second compression chamber V2 through the second suction pipe 1152 of the refrigerant suction pipe 115 and the second suction port 1422a.

[0126] Although not shown, a fixed key groove 1412b may be formed on the lower surface of the second fixed side wall portion 1422. In this case, the fixed key groove 1412b is formed long in the radial direction on both sides with a phase difference of 180° along the circumferential direction, so that the fixed key (not shown) of the cross ring 160 can be slidably inserted into the fixed key groove 1412b in the radial direction.

[0127] The second bearing protrusion 1423 is formed to extend axially from the center of the second fixed end plate portion 1421 toward the drive motor 120. A second cylindrical bearing hole 1423a penetrating in the axial direction may be formed at the center of the second bearing protrusion 1423, and the second bearing portion 1253 of the rotating shaft 125 may be inserted into the second bearing hole 1423a and radially supported.

[0128] The second bearing hole 1423a is formed on the same axis as the shaft receiving portion 133 of the main frame 130 and the first bearing hole 1413a. A bearing member made of a bushing bearing or a ball bearing may be provided on the inner circumference of the second bearing hole 1423a to support the second bearing portion 1253 of the rotating shaft 125.

[0129] The second fixed scroll 1424 may be formed to extend axially from the lower surface of the second fixed end plate portion 1421 toward the second orbiting scroll 152. The second fixed scroll 1424 engages with a second orbiting scroll 1522 described later to form a pair of second compression chambers V2.

[0130] The second fixed scroll 1424 may be formed in an involute shape. However, the second fixed scroll 1424 may be formed in various shapes other than an involute together with the second orbiting scroll 1522. For example, the second fixed scroll 1424 may have a shape connecting a plurality of arcs having different diameters and origins, and the outermost curve may be formed in a substantially elliptical shape having a major axis and a minor axis. This may also be formed in the second orbiting scroll 1522 in the same manner.

[0131] In addition, the second fixed scroll 1424 is formed to be symmetrical with the above-mentioned first fixed scroll 1414. In other words, the second fixed scroll 1424 is formed to be the same as the first fixed scroll 1414 when projected in the axial direction (or along the axial direction). Therefore, the second suction port 1422a can be formed on the same axis as the first suction port 1412a, and the second discharge port 1421a can be formed on the same axis as the first discharge port 1411a, in other words, they can be formed at the same rotation angle.

[0132] Refer again Figure 4 and Figure 5 According to the present embodiment, the second orbiting scroll 152 includes a second orbiting end plate portion 1521 , a second orbiting scroll 1522 , and a second rotation shaft coupling portion 1523 .

[0133] The second rotating end plate portion 1521 is formed in a disc shape and is configured to face the back side of the first rotating end plate portion 1511. In other words, the back side (lower surface) of the second rotating end plate portion 1521 and the back side (upper surface) of the first rotating end plate portion 1511 are in slidable contact with each other, so that each other can be axially supported. Therefore, a back pressure chamber 170 sealed by the above-mentioned first back pressure sealing member 155 and the second back pressure sealing member 156 is formed between the back side of the second rotating end plate portion 1521 and the back side of the first rotating end plate portion 1511 facing it, so that the above-mentioned second rotating end plate portion 1521 can be supported by the first rotating end plate portion 1511 in the axial direction.

[0134] Specifically, a second keyway protrusion 1521a extending in the radial direction is formed on the outer peripheral surface of the second revolving end plate 1521, and the second revolving keyway 1521b is formed to cross the center of the second keyway protrusion 1521a in the radial direction. In other words, the second revolving keyway 1521b is formed in a substantially rectangular shape extending in the radial direction when projected in the axial direction. Therefore, the second revolving key 160d to be described later inserted into the second revolving keyway 1521b is supported by the first revolving keyway 1511b on both sides in the circumferential direction and can slide in the radial direction.

[0135] A stepped second cross ring accommodation surface 1521c is formed on the lower surface of the second keyway protrusion 1521a. In other words, the lower surface of the second keyway protrusion 1521a is formed at a position higher than the back of the second revolving end plate 1521. Therefore, the other part of the ring body 160a of the cross ring 160 described later, that is, the upper half of the ring body 160a, can be inserted into the outer peripheral surface of the second revolving end plate 1521 until the second cross ring accommodation surface 1521c. Thus, the cross ring 160 is arranged between the back of the first revolving end plate 1511 and the back of the second revolving end plate 1521, and the backs of the revolving end plates 1511 and 1521 on both sides can slide in contact with each other. In addition, since the outer diameter of the second revolving end plate 1521 except the second keyway protrusion 1521a is not increased as a whole, the weight of the second revolving scroll 152 can be reduced to improve the efficiency of the compressor.

[0136] The second rotary keyway 1521b can be formed in a shape with an open outer circumferential surface, or can be formed in a shape with a closed outer circumferential surface. When the outer circumferential surface of the second rotary keyway 1521b is open, oil can be smoothly supplied between the second rotary keyway 1521b and the second rotary key 160c. On the contrary, when the outer circumferential surface of the second rotary keyway 1521b is closed, the two ends of the second rotary keyway 1521b are connected to each other, so that the rigidity in the second rotary keyway 1521b can be improved. In this embodiment, an example in which the outer circumferential surface of the second rotary keyway 1521b is open is shown.

[0137] In addition, the second rotary keyway 1521b can be formed into a structure that is axially through or has a closed surface on one side. For example, the side surfaces on both axial sides of the second rotary keyway 1521b can be formed to be open. In this case, the bearing surface between the second rotary keyway 1521b and the second rotary key 160d is exposed on both axial sides, so that oil can be supplied to either side of the axial direction, and thus oil can be smoothly supplied to the bearing surface between the second rotary keyway 1521b and the second rotary key 160d.

[0138] However, the axial side surface and / or radial outer side surface of the second rotary key groove 1521b can also be formed into a closed structure. In this case, the side surfaces on both sides of the circumferential direction of the second rotary key groove 1521b are connected to each other, thereby improving the rigidity of the second rotary key groove 1521b.

[0139] On the other hand, the above-mentioned back pressure chamber 170 is formed between the back side of the second revolving end plate portion 1521 and the first revolving end plate portion 1511. The back pressure chamber 170 may also be formed by a first back pressure sealing member 155 and a second back pressure sealing member 156 disposed on the back side of the first revolving end plate portion 1511. However, depending on the circumstances, at least one of the first back pressure sealing member 155 and the second back pressure sealing member 156 may also be disposed on the back side of the second revolving end plate portion 1521. However, as shown in the present embodiment, in the case where the second revolving scroll is disposed on the upper side of the first revolving scroll 151, it may be advantageous for the first back pressure sealing member 155 and the second back pressure sealing member 156 to be disposed at the first revolving scroll 151 disposed on the lower side.

[0140] The second orbiting wrap 1522 is formed to extend from the second side surface (upper surface) of the second orbiting end plate portion 1521 toward the second fixed scroll 142. The second orbiting wrap 1522 meshes with the second fixed wrap 1424 to form a second compression chamber V2.

[0141] The second orbiting scroll 1522 is formed to correspond to the shape of the second fixed scroll 1424, so the description of the second orbiting scroll 1522 is replaced by the description of the second fixed scroll 1424. However, the inner end of the second orbiting scroll 1522 can be formed in the central part of the second orbiting end plate 1521, and a second rotating shaft coupling portion 1523 that penetrates axially can be formed in the central part of the second orbiting end plate 1521.

[0142] In addition, the second orbiting scroll 1522 is formed to be symmetrical with the above-mentioned first orbiting scroll 1512. In other words, the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 are formed on the same axis, so that the second orbiting scroll 1522 is formed to be axially identical to the first orbiting scroll 1512. Therefore, the second suction port 1422a can be formed on the same axis as the first suction port 1412a, and the second discharge port 1421a can be formed on the same axis as the first discharge port 1411a, in other words, each can be formed at the same rotation angle.

[0143] The second eccentric portion 1256 of the rotating shaft 125 is rotatably inserted and coupled to the second rotating shaft coupling portion 1523. The outer periphery of the second rotating shaft coupling portion 1523 is connected to the second orbiting scroll 1522, thereby playing a role in forming a second compression chamber V2 together with the second fixed scroll 1424 during compression.

[0144] The second rotating shaft coupling portion 1523 may be formed at a height overlapping with the second orbiting scroll 1522 on the same plane. That is, the second rotating shaft coupling portion 1523 may be arranged at a height where the second eccentric portion 1256 of the rotating shaft 125 overlaps with the second orbiting scroll 1522 on the same plane. Therefore, the repulsive force and the compressive force of the refrigerant are offset by each other based on the second orbiting end plate portion 1521 applied to the same plane, thereby suppressing the tilt of the second orbiting scroll 152 caused by the action of the compressive force and the repulsive force.

[0145] On the other hand, refer to Figure 4 and Figure 5 The cross ring 160 is disposed between the first compression part C1 and the second compression part C2 (specifically, between the first orbiting scroll 151 and the second orbiting scroll 152), and is respectively combined with the first orbiting scroll 151 and the second orbiting scroll 152. Therefore, the first orbiting scroll 151 and the second orbiting scroll 152 in the scroll compressor according to the present embodiment can each perform an orbiting motion through one cross ring 160.

[0146] The cross ring 160 includes a ring body 160a, a fixed key 160b, a first rotating key 160c and a second rotating key 160d. The ring body 160a is located at the periphery of the first rotating end plate 1511 and / or the second rotating end plate 1521, the fixed key 160b can be slidably inserted into the fixed key 160b groove 1412b of the first rotating end plate 1511, the first rotating key 160c can be slidably inserted into the first rotating key groove 1511b of the first rotating scroll 151, and the second rotating key 160d can be slidably inserted into the second rotating key groove 1521b of the second rotating scroll 152. Therefore, as described above, the first rotating scroll 151 and the second rotating scroll 152 are combined with a cross ring 160 so that their respective rotational movements are restricted.

[0147] The ring body 160a is formed in an annular shape and inserted into the outside of the first rotating end plate 1511 and / or the outside of the second rotating end plate 1521. Therefore, the inner diameter of the ring body 160a is formed to be larger than the outer diameter of the first rotating end plate 1511 and / or the outer diameter of the second rotating end plate 1521.

[0148] For example, the ring body 160a may also be configured to surround the outer peripheral surface of the first rotary end plate portion 1511 or to surround the outer peripheral surface of the second rotary end plate portion 1521. However, the ring body 160a may also be configured to surround a portion of the outer peripheral surface of the first rotary end plate portion 1511 and a portion of the outer peripheral surface of the second rotary end plate portion 1521 at the same time. The present embodiment shows an example in which the ring body 160a surrounds a portion of the outer peripheral surface of the first rotary end plate portion 1511 and a portion of the outer peripheral surface of the second rotary end plate portion 1521 at the same time. Therefore, the first rotary key 160c and the second rotary key 160d described later may be formed to have the same axial length.

[0149] The fixing key 160b extends axially from the lower surface (first side surface) of the ring body 160a. Two fixing keys 160b are formed in the circumferential direction with a phase difference of 180 degrees corresponding to the above-mentioned fixing key grooves 1412b. Therefore, each fixing key 160b is slidably inserted into the fixing key grooves 1412b in the radial direction.

[0150] The fixed key 160b goes over the first orbiting end plate 1511 and is coupled to the first fixed scroll 141, so the fixed key 160b is formed to have an axial length greater than (longer than) the axial length of the first orbiting scroll 1512 and / or the second orbiting scroll 1522. Therefore, the fixed key 160b can be formed to have a circumferential length greater than the circumferential length of the first orbiting scroll 1512 and / or the second orbiting scroll 1522. Thus, the fixed key 160b can be formed to have a longer axial length and ensure rigidity.

[0151] The first rotary key 160c extends axially from the lower surface (first side surface) of the ring body 160a. In other words, since the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 are formed symmetrically, the first rotary key 160c can extend axially between the inner circumference and the outer circumference of the ring body 160a. Therefore, the first rotary key 160c does not protrude from the ring body 160a in the radial direction, but extends in the same axial direction as the fixed key 160b.

[0152] The first swing key 160c may be formed into a rectangular or square cross-sectional shape when projected in the axial direction. Therefore, the first swing key 160c contacts the first swing key groove 1511b in the circumferential direction, thereby improving the reliability in the circumferential direction.

[0153] Two first rotary keys 160c are formed in the circumferential direction corresponding to the first rotary key grooves 1511b with a phase difference of 180°. Therefore, the first rotary key 160c and the fixed key 160b have a phase difference of 90° in the circumferential direction.

[0154] The first rotary key 160c is inserted into the first rotary key groove 1511b of the adjacent first rotary end plate portion 1511, so the axial length of the first rotary key 160c is formed to be shorter than the axial length of the fixed key 160b. Therefore, even if the circumferential length of the first rotary key 160c is formed to be smaller than the circumferential length of the fixed key 160b, the rigidity of the first rotary key 160c can be ensured.

[0155] The second rotary key 160d extends axially from the upper surface (second side surface) of the ring body 160a. In other words, since the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 are formed symmetrically, the second rotary key 160d can extend axially between the inner circumference and the outer circumference of the ring body 160a. Therefore, the second rotary key 160d does not protrude from the ring body 160a in the radial direction, but extends axially on the side opposite to the fixed key 160b.

[0156] The second rotary key 160d may be formed into a rectangular or square cross-sectional shape when projected in the axial direction. Therefore, the second rotary key 160d is in contact with the second rotary key groove 1521b in the circumferential direction, thereby improving the reliability in the circumferential direction.

[0157] Two second rotary keys 160d are formed corresponding to the second rotary key grooves 1521b in the circumferential direction with a phase difference of 180°. Therefore, the second rotary key 160d and the fixed key 160b have a phase difference of 90° in the circumferential direction, so that the second rotary key 160d and the first rotary key 160c are formed on both sides of the axial direction at the same angle in the circumferential direction.

[0158] The second rotary key 160d is inserted into the second rotary key groove 1521b of the adjacent second rotary end plate portion 1521, so the axial length of the second rotary key 160d is formed to be shorter than the axial length of the fixed key 160b. Therefore, the circumferential length of the second rotary key 160d can be formed to be smaller than the circumferential length of the fixed key 160b. In other words, the axial length and circumferential length of the second rotary key 160d can be formed to be the same as the axial length and circumferential length of the first rotary key 160c.

[0159] The scroll compressor according to the present embodiment as described above operates as follows.

[0160] That is, if power is applied to the drive motor 120, the drive motor 120 generates a rotational force to rotate the rotor 122. In this way, the rotating shaft 125 coupled to the rotor 122 rotates, and the first orbiting scroll 151 coupled to the first eccentric portion 1255 of the rotating shaft 125 orbits relative to the first fixed scroll 141 through the Oldham ring 160. At the same time, the second orbiting scroll 152 coupled to the second eccentric portion 1256 of the rotating shaft 125 orbits relative to the second fixed scroll 142 through the Oldham ring 160.

[0161] In this way, the volumes of the first compression chamber V1 and the second compression chamber V2 gradually decrease as they approach the respective intermediate pressure chambers (unmarked with symbols) and the respective discharge pressure chambers (unmarked with symbols) formed continuously toward the center side from the respective suction pressure chambers (unmarked with symbols) formed on the outside of the compression chambers V1 and V2.

[0162] In this way, the refrigerant passing through the refrigeration cycle device is sucked into the first suction pressure chamber side forming the first compression chamber V1 through the first suction pipe 1151 of the refrigerant suction pipe 115, and is sucked into the second suction pressure chamber side forming the second compression chamber V2 through the second suction pipe 1152.

[0163] In this way, the refrigerant sucked into the respective suction pressure chambers moves along the moving trajectory of the first compression chamber V1 and the second compression chamber V2, passes through the respective intermediate pressure chambers and is compressed while moving to the respective discharge pressure chambers. The refrigerant compressed in the first compression chamber V1 is discharged to the discharge space 1451 of the discharge cover 145 through the first discharge port 1411a, and the refrigerant compressed in the second compression chamber V2 is discharged to the internal space 110a of the shell 110 through the second discharge port 1421a.

[0164] In this way, the refrigerant discharged from the first compression chamber V1 to the discharge space 1451 of the discharge cover 145 is mixed with the refrigerant discharged from the second compression chamber V2 to the internal space 110a of the shell 110, and is oil-separated in the upper space S2 after passing through the driving motor 120.

[0165] In this way, the refrigerant from which the oil is separated in the upper space S2 moves toward the condenser of the refrigeration cycle through the refrigerant discharge pipe 116, and the oil separated from the refrigerant in the upper space S2 is recovered in the oil storage space S11 which is the lower space S1 of the shell 110. The oil is repeatedly supplied to the respective bearing surfaces (not marked with a symbol) through the oil supply passage 126, and a part of the oil is supplied to the compression chamber V.

[0166] At this time, a portion of the oil sucked through the oil supply passage 126 is supplied to the back pressure chamber 170 through the respective oil supply holes 126a to 126c. Since the oil forms a discharge pressure, the first back pressure sealing member 155 and the second back pressure sealing member 156 quickly float from the respective sealing grooves 1511e and 1511f due to the pressure and temperature of the oil, thereby sealing the back pressure chamber 170.

[0167] In this way, an appropriate back pressure is formed between the first orbiting scroll 151 and the second orbiting scroll 152 , thereby pushing the first orbiting scroll 151 toward the first fixed scroll 141 and pushing the second orbiting scroll 152 toward the second fixed scroll 142 .

[0168] In this way, the first fixed scroll 141 and the first orbiting scroll 151 are in close contact with each other by the pressure of the back pressure chamber 170, so that the leakage between the compression chambers in the first compression chamber V1 is suppressed, and the compression efficiency in the first compression part C1 is improved. At the same time, the second fixed scroll 142 and the second orbiting scroll 152 are in close contact with each other by the pressure of the back pressure chamber 170, so that the leakage between the compression chambers in the second compression chamber V2 is suppressed, and the compression efficiency in the second compression part C2 is improved.

[0169] In this way, the plurality of compression parts C1 and C2 are driven by one drive motor 120, thereby reducing the number of components for the twin scroll compressor, reducing the manufacturing cost and miniaturizing the compressor.

[0170] In addition, since the plurality of compression parts C1 and C2 are arranged to support each other, the main frame supporting the compression parts C1 and C2 can be eliminated. Thus, the number of components for the main frame in the twin scroll compressor is reduced, the manufacturing cost can be further reduced, and the compressor can be further miniaturized.

[0171] In addition, since one Oldham ring 160 is disposed between the first orbiting scroll 151 and the second orbiting scroll 152 to restrict the rotation of the orbiting scrolls 151 and 152 on both sides, the number of Oldham rings 160 can be reduced. Thus, by reducing the number of components for the Oldham rings 160 in the twin scroll compressor, the manufacturing cost can be further reduced.

[0172] In addition, since the cross ring 160 is used to limit the rotation of the orbiting scrolls 151 and 152 on both sides, the assembly structure becomes simpler than the pin ring structure or the cam structure, and the processing is also easier than the pin ring or the cam, so the manufacturing cost can be reduced. In addition, when the pin ring or the cam is applied, the outer diameter of the fixed scroll 141 and 142 and the orbiting scroll 151 and 152 must be increased, so compared with these structures, miniaturization can be achieved.

[0173] In addition, since a back pressure chamber 170 is formed between the plurality of compression parts to axially support the orbiting scrolls 151 and 152 on both sides, the number of back pressure sealing components 155 and 156 forming the back pressure chamber 170 can be reduced. Thus, by reducing the number of components for the back pressure sealing components 155 and 156 in the twin scroll compressor, the manufacturing cost can be further reduced.

[0174] On the other hand, another embodiment of the scroll compressor is as follows.

[0175] That is, in the above-mentioned embodiment, the first eccentric portion and the second eccentric portion are formed to be axially symmetrical, but depending on the situation, the first eccentric portion and the second eccentric portion can also be formed to be axially asymmetrical. In other words, the first eccentric portion and the second eccentric portion can be formed to have a phase difference of a predetermined rotation angle. The following is an example in which the first eccentric portion and the second eccentric portion are formed with a phase difference of 180°.

[0176] Fig. 9 It is decomposed for Figure 1 Another embodiment of the compression part in FIG. 1 is shown in a perspective view from the upper side, Fig.10 yes Fig. 9 The "XX" line section view, Fig.11 Yes Assembly Fig. 9 and a cross-sectional view shown.

[0177] Reference Figures 9 to 11 The scroll compressor according to the present embodiment forms a twin scroll compressor in which a first compression portion C1 and a second compression portion C2 are arranged in the axial direction, which is the same as the above-mentioned scroll compressor.

[0178] For example, according to the scroll compressor of the present embodiment, the rotating shaft 125 is combined with a driving motor 120, the first eccentric portion 1255 and the second eccentric portion 1256 are eccentrically formed on the rotating shaft 125 in the axial direction, the first compression portion C1 including the first orbiting scroll 151 is combined with the first eccentric portion 1255, and the second compression portion C2 is combined with the second eccentric portion 1256. The first orbiting scroll 151 and the second orbiting scroll 152 are configured to be in sliding contact with each other. Therefore, the main frame is excluded between the first compression portion C1 and the second compression portion C2, so that the number of components in the twin scroll compressor can be reduced and the compressor can be miniaturized.

[0179] In addition, an Oldham ring 160 for preventing the self-rotation of the two-side orbiting scrolls is arranged between the first orbiting scroll 151 and the second orbiting scroll 152. Therefore, the self-rotation of the two-side orbiting scrolls is restricted by the Oldham ring 160, thereby simplifying the anti-self-rotation mechanism and miniaturizing the compressor compared with the pin ring structure or the cam structure. Moreover, the self-rotation of the two-side orbiting scrolls 151 and 152 is prevented by one Oldham ring 160, so the number of components in the twin scroll compressor can be further reduced.

[0180] In addition, the first compression part C1 and the second compression part C2 are connected to one refrigerant suction pipe 115, and the first suction port 1412a of the first fixed scroll 141 and the second suction port 1422a of the second fixed scroll 142 connected to the refrigerant suction pipe 115 can be formed to be located on the same axis, in other words, at the same rotation angle. Therefore, not only is it easy to assemble the refrigerant suction pipe 115, but also the peripheral pipes including the refrigerant suction pipe 115 can be simplified.

[0181] However, in this embodiment, the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 may be formed asymmetrically. For example, the first eccentric portion 1255 and the second eccentric portion 1256 may be formed with a phase difference of approximately 180° based on the rotation angle. Therefore, the centrifugal forces generated in the first eccentric portion 1255 and the second eccentric portion 1256 are symmetrical to each other and offset, thereby suppressing the vibration of the compressor.

[0182] Reference Fig. 9 and Fig.10 According to the present embodiment, the Cross ring 160 includes a ring body 160a, a fixing key 160b, a first swing key 160c and a second swing key 160d. The first swing key 160c or the second swing key 160d may extend radially longer than the outer circumference of the ring body 160a.

[0183] The cross ring 160 can be formed to be generally the same as the above-mentioned embodiment as a whole. For example, the ring body 160a can be formed into a ring shape, and can be formed to be less than or equal to the outer diameter of the first fixed end plate portion 1411 or the second fixed end plate portion 1421, and larger than the outer diameter of the first rotary end plate portion 1511 and / or the second rotary end plate portion 1521. Therefore, the ring body 160a can be inserted into the outer peripheral surface of the first rotary end plate portion 1511 and / or the outer peripheral surface of the second rotary end plate portion 1521. Thus, as shown in the above-mentioned embodiment, the back surface of the first rotary end plate portion 1511 and the back surface of the second rotary end plate portion 1521 can slide in contact with each other across the back pressure chamber 170, so that they can be axially supported.

[0184] In addition, the fixed key 160b can extend on one axial side of the ring body 160a, and the first rotating key 160c and the second rotating key 160d can extend on the axial side surfaces of both sides of the ring body 160a on the same axis. The fixed key 160b can be slidably inserted into the fixed key groove 1412b provided in the first fixed end plate portion (and / or the second fixed end plate portion), the first rotating key 160c can be slidably inserted into the first rotating key groove 1511b of the first rotating end plate portion 1511, and the second rotating key 160d can be slidably inserted into the second rotating key groove 1521b of the second rotating end plate portion 1521. Therefore, in this embodiment, a cross ring 160 can also be used to limit the rotational movement of the first rotating scroll 151 and the second rotating scroll 152.

[0185] In this case, the outer peripheral surface of any one of the first and second rotating keys 160c and 160d (the second rotating key in this embodiment) 160d is formed to extend further outward than the outer peripheral surface of the ring body 160a. Therefore, even if the second rotating scroll 152 performs a rotating motion away from the Oldham ring 160, the second rotating key 160d of the Oldham ring 160 can be prevented from being disengaged from the second rotating key groove 1521b of the second rotating scroll 152.

[0186] In other words, as shown in the above embodiment, when the first eccentric portion 1255 and the second eccentric portion 1256 are formed symmetrically, the outer peripheral surface of the first revolving end plate portion 1511 and the outer peripheral surface of the second revolving end plate portion 1521 are located on the same axis. Therefore, the second revolving key 160d of the Oldham ring 160 slidably coupled to the first fixed scroll 141 will not be disengaged from the second revolving key groove 1521b of the second revolving scroll 152. Therefore, in the above embodiment, the first revolving key 160c and the second revolving key 160d can be formed so as to be located on the same axis as the outer peripheral surface of the ring body 160a.

[0187] On the contrary, as shown in the present embodiment, when the first eccentric portion 1255 and the second eccentric portion 1256 are formed asymmetrically, one side of the outer peripheral surface of the second orbiting end plate portion 1521 may protrude radially more than one side of the outer peripheral surface of the first orbiting end plate portion 1511. Therefore, the second orbiting key 160d of the Cross ring 160 slidably coupled to the first fixed scroll 141 may be disengaged from the second orbiting key groove 1521b of the second orbiting scroll 152. Therefore, in the present embodiment, as Fig.10As shown, the inner circumferential surface of the second swing key 160d can be formed to be located outside the inner circumferential surface of the ring body 160a, and the second swing key 160d can be formed to be located outside the outer circumferential surface of the ring body 160a. Therefore, the second swing key 160d of the Oldham ring 160 slidably coupled to the first fixed scroll 141 can be prevented from being separated from the second swing key groove 1521b of the second swing scroll 152.

[0188] As described above, even when the first eccentric portion 1255 and the second eccentric portion 1256 are formed asymmetrically, the basic structure of the scroll compressor and its effect are almost similar to those of the above-mentioned embodiment. Therefore, the description of the above-mentioned embodiment replaces the specific description thereof. However, in the present embodiment, as described above, the eccentric loads generated by the first eccentric portion 1255 and the second eccentric portion 1256 cancel each other, thereby suppressing the vibration of the compressor. Therefore, the balancing weight can be reduced or deleted, thereby reducing the manufacturing cost and miniaturizing the compressor.

[0189] On the other hand, still another embodiment of the scroll compressor is as follows.

[0190] That is, in the above embodiment, one Oldham ring is used to prevent the first and second orbiting scrolls from rotating. However, depending on the situation, a plurality of Oldham rings may be provided to be coupled to the first and second orbiting scrolls, respectively.

[0191] Fig.12 It is decomposed for Figure 1 A further embodiment of the compression portion in FIG. 1 and a perspective view shown from above, Fig.13 Yes Assembly Fig.12 The compressed portion is shown in a cross-sectional view.

[0192] Reference Fig.12 and Fig.13 The scroll compressor according to the present embodiment forms a twin scroll compressor in which a first compression portion C1 and a second compression portion C2 are arranged in the axial direction, which is the same as the above-mentioned scroll compressor.

[0193] For example, according to the scroll compressor of the present embodiment, the rotating shaft 125 is combined with a driving motor, the first eccentric portion 1255 and the second eccentric portion 1256 are formed eccentrically on the rotating shaft 125 in the axial direction, the first compression portion C1 including the first orbiting scroll 151 is combined with the first eccentric portion 1255, and the second compression portion C2 is combined with the second eccentric portion 1256. The first orbiting scroll 151 and the second orbiting scroll 152 are provided with a back pressure chamber 170 between the orbiting scrolls 151 and 152 on both sides, and are configured to be in sliding contact with each other. Therefore, the main frame is excluded between the first compression portion C1 and the second compression portion C2, so that the number of components in the twin scroll compressor can be reduced and the compressor can be miniaturized.

[0194] In addition, the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 can be formed symmetrically or asymmetrically. In this embodiment, the first eccentric portion 1255 and the second eccentric portion 1256 are described as being formed symmetrically, but in the case of being formed asymmetrically, the basic structure and its effects are the same as described above. Figure 1 The embodiment is similar to that of Figure 1 Instead of a specific description thereof, a description of an embodiment of the present invention will be given.

[0195] However, in this embodiment, respective cross rings 161 and 162 may be provided in the first compression section C1 and the second compression section C2. Therefore, the cross rings 161 and 162 are respectively arranged adjacent to the fixed scrolls 141 and 142 and the orbiting scrolls 151 and 152, so that the length of the fixed keys 161b and 162b and / or the orbiting keys 161c and 162c is reduced. Thus, even if the thickness of the fixed keys 161b and 162b and / or the orbiting keys 161c and 162c is reduced, the rigidity of the cross rings 161 and 162 including the fixed keys 161b and 162b and / or the orbiting keys 161c and 162c can be ensured.

[0196] Specifically, according to the present embodiment, a first Oldham ring 161 may be disposed between the first fixed scroll 141 and the first orbiting scroll 151, and a second Oldham ring 162 may be disposed between the second fixed scroll 142 and the second orbiting scroll 152. Therefore, the first orbiting scroll 151 may be prevented from self-rotation by the first Oldham ring 161, and the second orbiting scroll 152 may be prevented from self-rotation by the second Oldham ring 162.

[0197] The first Cross ring 161 and the second Cross ring 162 may be arranged symmetrically or asymmetrically with each other.

[0198] For example, when the first fixing key 161b of the first cross ring 161 described later and the second fixing key 162b of the second cross ring 162 described later are symmetrically arranged on the same axis, the number of spiral turns (or the rotation angle of the spiral) of the first fixed scroll 1414 and the second fixed scroll 1424 can be formed to be the same, and the first suction port 1412a and the second suction port 1422a can be arranged on the same axis. In this case, the first compression part C1 and the second compression part C2 are connected to one refrigerant suction pipe 115, so it is not only easy to assemble the refrigerant suction pipe 115 but also the surrounding pipes can be simplified.

[0199] On the contrary, when the first fixing key 161b of the first Oldham ring 161 and the second fixing key 162b of the second Oldham ring 162 are symmetrically arranged on different axes, the first eccentric portion 1255 and the second eccentric portion 1256 can be arranged asymmetrically, thereby canceling out the centrifugal force in the first eccentric portion 1255 and the second eccentric portion 1256. Thus, the vibration of the compressor can be reduced.

[0200] The following description will focus on an example in which the first and second cross rings 161 and 162 are arranged symmetrically. In addition, since the basic structures and effects of the first and second cross rings 161 and 162 are similar, the following description will focus on the first cross ring 161.

[0201] A first fixed keyway 1412a is formed on the first fixed scroll 141, a second fixed keyway 1422a is formed on the second fixed scroll 142, a first rotating keyway 1511b is formed on the first orbiting scroll 151, and a second orbiting keyway 1522b is formed on the second orbiting scroll 152. A first keyway protrusion 1511a is formed on the outer circumference of the first orbiting scroll 151, and a stepped first cross ring receiving groove 1511c is formed on the upper surface of the first keyway protrusion 1511a. A second keyway protrusion 1521a is formed on the outer circumference of the second orbiting scroll 152, and a stepped second cross ring receiving groove 1521c is formed on the lower surface of the second keyway protrusion 1521a. Therefore, the first cross ring 161 is inserted and coupled to the first orbiting scroll 151, and the second cross ring 162 is inserted and coupled to the second orbiting scroll 152. Thus, the compressor can be downsized by suppressing an increase in the outer diameters of the first orbiting scroll 151 and the second orbiting scroll 152 .

[0202] In other words, the first cross ring 161 according to the present embodiment includes the first ring body 161a, the first fixed key 161b and the first swing key 161c, and the second cross ring 162 according to the present embodiment includes the second ring body, the second fixed key 162b and the second swing key 162c. The first ring body 161a corresponds to the second ring body 162a, the first fixed key 161b corresponds to the second fixed key 162b, and the first swing key 161c corresponds to the second swing key 162c, so the description of the first ring body 161a replaces the description of the second ring body 162a, the description of the first fixed key 161b replaces the description of the second fixed key 162b, and the description of the first swing key 161c replaces the description of the second swing key 162c.

[0203] The first ring body 161a may be formed in a ring shape and inserted into the outer peripheral surface of the first orbiting scroll 151 as in the above-mentioned embodiment. However, since the first cross ring 161 is combined only with the first fixed scroll 141 and the first orbiting scroll 151, the first ring body 161a may also be inserted into the back side of the first orbiting scroll 151. Therefore, in the case where the first compression section C1 and the second compression section C2 are provided with respective cross rings 161 and 162, the main frame can be excluded between the first orbiting scroll 151 and the second orbiting scroll 152, and the first cross ring 161 can be supported more stably. This is also the same in the second cross ring 162.

[0204] The first fixed key 161b extends from the first side surface of the first ring body 161a to the first fixed key groove 1411 of the first fixed end plate portion 1411, and the first ring body 161a is arranged adjacent to the first fixed scroll 141, so the axial length of the first fixed key 161b can be formed to be substantially the same as the axial length of the first swing key 161c. Therefore, even if the thickness of the first fixed key 161b is not formed thick, the rigidity of the first fixed key 161b can be ensured. This is also the same in the second fixed key 162b inserted into the second fixed key groove 1422b of the second fixed scroll 142.

[0205] The first swing key 161c extends from the second side surface of the first ring body 161a to the first swing key groove 1511b, and the first ring body 161a is disposed adjacent to the first swing scroll 151, so the axial length of the first swing key 161c can be formed to be substantially the same as the axial length of the first fixed key 161b as described above. This is also the case with the second swing key 162c.

[0206] As described above, even when the first cross ring 161 is provided between the first fixed scroll and the first orbiting scroll 151, and the second cross ring 162 is provided between the second fixed scroll 142 and the second orbiting scroll 152, the main frame can be excluded between the first orbiting scroll 151 and the second orbiting scroll 152. Therefore, the manufacturing cost can be reduced by reducing the number of components of the compressor, and miniaturization can be achieved by reducing the axial length of the compressor.

[0207] In addition, in this case, since the first Cross ring 161 is disposed adjacent to the first fixed scroll 141, the length of the first fixed key 161b can be formed to be substantially the same as the length of the first swing key 161c, and since the second Cross ring 162 is disposed adjacent to the second fixed scroll 142, the length of the second fixed key 162b can be formed to be substantially the same as the length of the second swing key 162c. Therefore, the thickness of the first fixed key 161b can be formed to be the same as the thickness of the first swing key 161c, the thickness of the second fixed key 162b can be formed to be the same as the thickness of the second swing key 162c, and the rigidity of the first Cross ring 161 and the second Cross ring 162 can be ensured.

Claims

1. A scroll compressor, wherein: include: case; A driving motor is arranged inside the housing; a rotating shaft, coupled to the rotor of the driving motor, having a first eccentric portion and a second eccentric portion spaced apart in the axial direction; A first compression portion includes a first orbiting scroll engaged with a first eccentric portion of the rotating shaft to perform an orbiting motion and a first fixed scroll engaged with the first orbiting scroll to form a first compression chamber; A second compression portion includes a second orbiting scroll engaged with a second eccentric portion of the rotating shaft to perform an orbiting motion and a second fixed scroll engaged with the second orbiting scroll to form a second compression chamber; as well as The back pressure chamber is provided between the back surface of the first orbiting scroll and the back surface of the second orbiting scroll facing the first orbiting scroll, and supports the first orbiting scroll and the second orbiting scroll respectively in the axial direction.

2. The scroll compressor according to claim 1, wherein: A back pressure seal member that forms the back pressure chamber is provided on at least one of the back surface of the first orbiting scroll and the back surface of the second orbiting scroll facing the first orbiting scroll.

3. The scroll compressor according to claim 2, wherein: An annularly recessed back pressure groove is formed on at least one of the back surface of the first orbiting scroll and the back surface of the second orbiting scroll facing the first orbiting scroll. The back pressure sealing members are respectively provided on the inner peripheral side and the outer peripheral side of the back pressure groove.

4. The scroll compressor according to claim 1, wherein: A single Oldham ring is provided between the back surface of the first orbiting scroll and the back surface of the second orbiting scroll facing the first orbiting scroll to suppress the rotation of the first orbiting scroll and the second orbiting scroll.

5. The scroll compressor according to claim 4, wherein: The cross ring comprises: a ring body formed in a ring shape and arranged between the first orbiting scroll and the second orbiting scroll; a fixed key extending from the ring body in the axial direction and slidably inserted into the first fixed scroll or the second fixed scroll; a first orbiting key extending from the ring body along a first axial direction and slidably inserted into the first orbiting scroll; and The second orbiting key extends from the ring body along a second axial direction and is slidably inserted into the second orbiting scroll.

6. The scroll compressor according to claim 5, wherein: The axial length of the fixed key is formed to be longer than the axial lengths of the first swing key and the second swing key.

7. The scroll compressor according to claim 5, wherein: The first swing bond and the second swing bond are formed symmetrically with respect to the ring body.

8. The scroll compressor according to claim 5, wherein: The first keyway protrusion extends radially on the outer peripheral surface of the first orbiting scroll, and the first keyway protrusion is formed with a first orbiting keyway into which the first orbiting key is slidably inserted in the radial direction. The second keyway protrusion extends radially on the outer peripheral surface of the second orbiting scroll, and a second orbiting keyway is formed on the second keyway protrusion, into which the second orbiting key is slidably inserted in the radial direction. The first revolving keyway and the second revolving keyway are formed on the same axis.

9. The scroll compressor according to claim 8, wherein: A stepped Oldham ring receiving surface is formed on at least one of a side surface of the first keyway protrusion and a side surface of the second keyway protrusion facing the first keyway protrusion, which is lower than the back surface of the first orbiting scroll or the back surface of the second orbiting scroll. The ring body of the Oldham ring is inserted into the Oldham ring accommodation surface from the back surface of at least one of the first orbiting scroll and the second orbiting scroll.

10. The scroll compressor according to claim 9, wherein: A stepped first Oldham ring accommodating surface is formed on one side of the first keyway protrusion, and a second Oldham ring accommodating surface is formed on one side of the second keyway protrusion facing the first Oldham ring accommodating surface. The ring body of the Oldham ring is respectively inserted into the first orbiting scroll and the second orbiting scroll.

11. The scroll compressor according to claim 8, wherein: At least one of the first revolving key groove and the second revolving key groove is open in the axial direction.

12. The scroll compressor according to claim 8, wherein: At least one of the first and second revolving key grooves has at least a portion of a surface other than a surface facing the Oldham ring in the axial direction formed in a closed shape.

13. The scroll compressor according to claim 1, wherein: A first Oldham ring is provided between the first orbiting scroll and the first fixed scroll facing the first orbiting scroll. A second Oldham ring is provided between the second orbiting scroll and the second fixed scroll facing the second orbiting scroll.

14. The scroll compressor according to claim 13, wherein: The first cross ring comprises: a first ring body formed in an annular shape and disposed between the first orbiting scroll and the first fixed scroll; a first fixed key extending from the first ring body along a first axial direction and slidably inserted into the first fixed scroll; and a first orbiting key extending from the first ring body along a second axial direction and slidably inserted into the first orbiting scroll; The second cross ring comprises: a second ring body formed in an annular shape and disposed between the second orbiting scroll and the second fixed scroll; a second fixed key extending from the second ring body along a second axial direction and slidably inserted into the second fixed scroll; and The second orbiting key extends from the second ring body along a first axial direction and is slidably inserted into the second orbiting scroll.

15. The scroll compressor according to any one of claims 1 to 14, wherein: The first eccentric portion and the second eccentric portion are formed to be located on the same axis.

16. The scroll compressor according to any one of claims 1 to 14, wherein: The first eccentric portion and the second eccentric portion are formed to be located on different axes.

Images