Scroll compressor

Abstract

The present invention provides a scroll compressor. The scroll compressor includes: a housing; the driving motor is arranged in the shell; a rotating shaft rotatably coupled to the driving motor and having a first eccentric portion and a second eccentric portion formed spaced apart from each other; a first compression part including a first orbiting scroll coupled to the first eccentric part so as to be capable of orbiting, and a first fixed scroll engaged with the first orbiting scroll to form a first compression chamber; a second compression part including a second orbiting scroll coupled to the second eccentric part so as to be capable of orbiting, and a second fixed scroll engaged with the second orbiting scroll to form a second compression chamber; and a main frame disposed between the first compression portion and the second compression portion and supporting the first compression portion and the second compression portion. A thrust plate is coupled to the inner periphery of either the first fixed scroll or the second fixed scroll, and the thrust plate supports one end of a rotating shaft to form a thrust surface.

Description

Technical Field

[0001] The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having a structure capable of reducing surface pressure by increasing a supported area inside a fixed scroll. Background Art

[0002] In a scroll compressor, an orbiting scroll and a non-orbiting scroll are meshed with each other, and the orbiting scroll orbits relative to the non-orbiting scroll to form a pair of compression chambers.

[0003] The compression chamber includes: a suction pressure chamber formed in the outer contour; an intermediate pressure chamber whose volume gradually decreases from the suction pressure chamber toward the center and is continuously formed; and a discharge pressure chamber that is continuous with the center side of the intermediate pressure chamber. Usually, the suction pressure chamber is formed by penetrating the side of the non-orbiting scroll, the intermediate pressure chamber is sealed, and the discharge pressure chamber is formed by penetrating the end plate of the non-orbiting scroll.

[0004] Scroll compressors can be divided into low-pressure and high-pressure types according to the path of the inhaled refrigerant. The low-pressure type refers to a method in which the refrigerant suction pipe is connected to the internal space of the shell, so that the low-temperature inhaled refrigerant is guided to the suction pressure chamber after passing through the internal space of the shell, and the high-pressure type refers to a method in which the refrigerant suction pipe is directly connected to the suction pressure chamber, and the refrigerant is directly guided to the suction pressure chamber without passing through the internal space of the shell.

[0005] Patent document 1 (Korean Publication Patent No. 10-2017-0122015 (2017.11.03)) discloses a scroll compressor as a bottom compression type. In the scroll compressor of Patent document 1, a compression part is provided on the lower side of the electric part. In addition, an eccentric part of the rotating shaft is inserted into the rotating shaft coupling part of the orbiting scroll plate, and the eccentric part can overlap and couple with the orbiting scroll or the fixed scroll along the radial direction of the compressor. Thus, the following example is disclosed, in which during compression, the repulsive force of the refrigerant is applied to the fixed scroll and the orbiting scroll, and as a reaction force thereto, a compression force is applied between the rotating shaft coupling part and the eccentric part.

[0006] In the case of the scroll compressor of Patent Document 1, there is a problem that when the thrust surface inside the fixed scroll is damaged due to the structure of the shaft support part represented by the eccentric part, the compression part is directly damaged, thereby causing the compressor to be damaged. In addition, in the vertical direction of the Z axis, the compression part may be damaged at the lower part of the shaft support part, and the bearing part may be damaged at the upper part of the shaft support part.

[0007] A scroll compressor is disclosed in Patent Document 2 (Korean Publication Patent No. 10-2016-0020190 (2016.02.23)), and the following scroll compressor is disclosed: it includes: a first scroll plate having a discharge port; a second scroll plate engaged with the first scroll plate to form a first compression chamber and a second compression chamber; and a rotating shaft having an eccentric portion eccentrically coupled to the first scroll plate or the second scroll plate, the eccentric portion radially overlapping with the compression chamber; the discharge port has a discharge inlet and a discharge outlet, the discharge inlet is formed in plurality, and the plurality of discharge inlets can be formed to have different areas, and by allowing the refrigerant in each compression chamber to be discharged smoothly, over-compression loss caused by discharge delay can be suppressed.

[0008] Patent document 3 (International Patent WO2019-039575A1 (2019.02.28)) discloses a double rotating scroll type compressor, wherein the scroll type compressor of Patent document 3 has a driving side scroll and a driven side scroll that rotates synchronously with the driving side scroll, and the driving shaft and the driven shaft are rotated in the same direction at the same angular velocity by offsetting the driven shaft that rotates the driving side scroll by an amount equivalent to the gyration radius. In addition, Patent document 3 discloses a feature of constraining the z direction by a pin & ring anti-rotation structure and the application of a ball bearing.

[0009] In addition, in the case of the conventional scroll compressor, although a part of the portion supported inside the compression part (supporting portion) is removed, the disadvantage caused by supporting the rotating shaft with the eccentric portion is not improved.

[0010] In more detail, the shaft support portion of the prior art has the following disadvantages and problems.

[0011] First, due to the use of an eccentric part, there is a problem of small support area. If a local area is supported in this way, the problem of increased surface pressure will arise. Second, problems arise because the rotation center is not supported. When eccentric support is used, the rotation radius becomes larger, thereby increasing the linear speed. The problems of increased surface pressure and increased linear speed caused by the aforementioned insufficient area overlap. Therefore, problems of heat generation, sintering, and increased mechanical losses may arise.

[0012] In addition, the support area is chamfered due to the bearing press-fitting, etc., instead of contacting with the entire area, so there is a possibility that the shaft will get stuck when moving in the z-axis direction.

[0013] Therefore, it is necessary to develop a compressor having a structure capable of preventing thrust damage from occurring at a portion where a shaft is supported inside a fixed scroll and preventing damage to a compression portion caused by the thrust damage. Summary of the invention

[0014] Problems to be solved by the invention

[0015] The present invention has been made to solve the above-mentioned problem, and an object of the present invention is to provide a scroll compressor having a structure capable of reducing surface pressure by increasing an area supported inside a fixed scroll.

[0016] In addition, another object of the present invention is to provide a scroll compressor that can solve the problems of increased surface pressure, increased linear speed, heat generation, sintering, and increased mechanical losses caused by the existing eccentric support.

[0017] Still another object of the present invention is to provide a scroll compressor having a structure capable of solving problems such as shaft seizure caused by movement in the Z-axis direction.

[0018] Still another object of the present invention is to provide a scroll compressor having a structure that can be applied to a twin scroll compressor while compensating for the disadvantages of the shaft support portion of the conventional shaft-through scroll compressor.

[0019] More specifically, another object of the present invention is to provide a scroll compressor having a structure that prevents damage to a compression part by preventing a thrust surface of a rotating shaft from coming into contact with the compression part.

[0020] Technical solutions to the problem

[0021] In order to solve the above problems, the scroll compressor of the present invention includes: a shell; a driving motor, which is arranged inside the shell; a rotating shaft, which is rotatably connected to the driving motor and has a first eccentric part and a second eccentric part formed separately from each other; a first compression part, including a first orbiting scroll plate which is rotatably connected to the first eccentric part and a first fixed scroll plate which engages with the first orbiting scroll plate to form a first compression chamber; a second compression part, including a second orbiting scroll plate which is rotatably connected to the second eccentric part and a second fixed scroll plate which engages with the second orbiting scroll plate to form a second compression chamber; and a main frame which is arranged between the first compression part and the second compression part and supports the first compression part and the second compression part; a thrust plate is connected to the inner periphery of either the first fixed scroll plate and the second fixed scroll plate, and the thrust plate supports one side end of the rotating shaft to form a thrust surface.

[0022] With such a structure, the support area becomes larger than the existing structure using the eccentric part of the rotating shaft for support. In addition, since the thrust surface is formed at the rotation center of the rotating shaft, the problem of the existing eccentric support that the linear speed increases as the rotation radius increases, thereby generating heat, sintering and increased mechanical loss on the thrust surface is reduced.

[0023] The first compression part is arranged on the opposite side of the driving motor across the second compression part, the inner periphery of the first fixed scroll accommodates one end portion of the rotating shaft, and the thrust plate can support the lower end of the rotating shaft at the inner periphery of the first fixed scroll and be coupled to the lower end of the rotating shaft.

[0024] In addition, in the present invention, since the thrust surface is formed at the lower end of the rotating shaft 125 and not at the compression portion, it is possible to prevent the compression portion from being damaged.

[0025] The thrust plate may be press-fitted and coupled to an inner circumference of the first fixed scroll.

[0026] The thrust plate may be pressed into the inner circumference of the first fixed scroll by a muffler hot pressing method, so that the thrust plate is more firmly combined with the inner circumference of the first fixed scroll.

[0027] A coupling groove formed along a circumferential direction may be provided on an inner periphery of the first fixed scroll so that an outer periphery of the thrust plate can be inserted and coupled.

[0028] Therefore, damage to the inner circumference of the first fixed scroll caused by the thrust plate can be minimized, and the thrust plate can be stably supported by the engaging groove.

[0029] A chamfered portion may be formed at a lower end of an inner circumference of the first fixed scroll so that the thrust plate can be introduced into the inner circumference of the first fixed scroll when the thrust plate is press-fitted.

[0030] By using the chamfered portion, when the thrust plate is press-fitted and coupled, interference between the inner periphery of the first fixed scroll and the thrust plate can be minimized, and stable coupling can be achieved.

[0031] An oil supply hole may be formed in the axial and radial directions inside the rotating shaft to supply oil to the outer periphery of the rotating shaft, and the oil supply hole is connected with the oil absorber to supply oil to the oil supply hole. An oil supply connecting hole may be formed in the central part of the thrust plate, and the oil supply connecting hole can connect the oil absorber and the oil supply hole.

[0032] By forming the oil supply communication hole in the thrust plate, the oil flowing through the oil absorber can be supplied to the oil supply hole of the rotating shaft, so that the oil can be smoothly supplied to the sliding part.

[0033] The thrust plate may have a radial oil supply groove formed in a radial direction between the oil supply communication hole and an edge of the thrust plate to communicate with the oil supply hole.

[0034] A plurality of radial oil supply grooves may be provided spaced apart from each other along the circumferential direction.

[0035] The radial oil supply groove may be formed on a surface that contacts the thrust surface of the lower end of the rotating shaft, so that oil can be supplied to the oil supply hole of the rotating shaft more smoothly.

[0036] The thrust plate may have a circular oil supply groove formed along a circumferential direction at an outer side of the oil supply hole so that the circular oil supply groove communicates with the oil supply hole.

[0037] Therefore, the oil supplied through the oil sucker can be smoothly supplied toward the thrust surface of the thrust plate in the circumferential direction, and the oil can be more smoothly supplied to the oil supply hole of the rotating shaft.

[0038] A coupling ring may be coupled to an inner circumference of the first fixed scroll to press and support the thrust plate on an opposite surface of the thrust surface.

[0039] As the coupling ring is disposed on the opposite side of the thrust surface of the thrust plate, the coupling ring is pressed upward and supported on the bottom surface of the thrust plate, so that the thrust plate can be more firmly coupled to the inner circumference of the first fixed scroll.

[0040] The axial ends of the first eccentric portion can be arranged between the inner end of the first fixed scroll and one side of the main frame, and the axial ends of the second eccentric portion can be arranged between the inner end of the second fixed scroll and the other side of the main frame, separated from the inner end of the second fixed scroll and the other side of the main frame.

[0041] The axial distance of the first eccentric portion may be greater than the axial distance of the second eccentric portion so that the second eccentric portion is spaced apart from the inner end of the second fixed scroll and the other surface of the main frame when the first eccentric portion is restricted from upward movement by the main frame.

[0042] As described above, when the upper end of the first eccentric portion is in contact with the lower end of the main frame, the upper and lower ends of the second eccentric portion are also separated between the second fixed scroll plate and the main frame and will not contact each other, thereby preventing the compression portion from being damaged and providing a clear reference point for the up and down movement of the rotating shaft.

[0043] The first fixed scroll plate may have a first bearing protrusion, which is formed by protruding from the central portion of the first fixed scroll plate toward the lower end, and the rotating shaft is inserted into and accommodated in the inner periphery of the first bearing protrusion. The scroll compressor of the present invention may also include a discharge cover, which has a connecting end portion connected to the lower end of the first bearing protrusion, and the discharge cover accommodates and discharges the refrigerant discharged from the first compression chamber. The connecting end portion may have a thrust support portion, which is arranged at the upper end of the connecting end portion and supports the thrust plate.

[0044] With such a structure, the thrust plate is used as a reference, and the reference for the lowermost end surface of the rotating shaft 125 is ensured, and a portion that accepts the tolerance for the upper portion is ensured.

[0045] In addition, since the center portion of the rotating shaft is supported by the thrust plate, a linear speed lower than that of the prior art can be ensured.

[0046] A first bearing may be provided on an outer periphery of the rotating shaft disposed at an inner periphery of the first fixed scroll, and an edge of a thrust surface of the thrust plate may be in contact with the first bearing.

[0047] A structure contact-supported by the first bearing is formed at a side portion of the thrust plate, so that the thrust plate can prevent deformation of a portion supported at the lower end of the rotation shaft and can be stably supported.

[0048] Effects of the Invention

[0049] In the present invention, since the thrust plate supports one side end of the rotating shaft to form a thrust surface, the supporting area becomes larger than that of the existing structure that uses the eccentric portion of the rotating shaft for support. In addition, since the thrust surface is formed at the rotation center of the rotating shaft, the problem of the existing eccentric support that as the rotation radius increases, the linear speed increases, thereby generating heat, sintering, and increased mechanical loss on the thrust surface is reduced.

[0050] In addition, in the present invention, as the thrust plate has the radial oil supply groove, the oil supplied by the oil absorber can be smoothly supplied to the thrust surface of the thrust plate in the radial direction, and the oil can be more smoothly supplied to the oil supply hole of the rotating shaft.

[0051] In addition, in the present invention, as the thrust plate has the circular oil supply groove, the oil supplied by the oil absorber can be smoothly supplied in the circumferential direction toward the thrust surface of the thrust plate, and the oil can be more smoothly supplied to the oil supply hole of the rotating shaft.

[0052] Furthermore, in the present invention, the central portion of the rotating shaft is supported by the thrust plate, so that a linear speed smaller than that of the prior art can be ensured.

[0053] In addition, in the present invention, a structure in which the thrust plate is contact-supported by the first bearing is formed at the side of the thrust plate, so that the thrust plate can prevent deformation of the portion supported at the lower end of the rotating shaft and can be stably supported.

[0054] In addition, in the present invention, when the upper end of the first eccentric portion contacts the lower end of the main frame, the upper and lower ends of the second eccentric portion are also separated between the second fixed scroll plate and the main frame and will not contact each other, thereby preventing the compression portion from being damaged and providing a clear reference point for the up and down movement of the rotating shaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0055] Figure 1 It is a cross-sectional view showing a compound scroll compressor according to the present invention.

[0056] Figure 2 This is an exploded perspective view of the first compression unit, the second compression unit, and the main frame of the present invention, which are decomposed and viewed from the upper side.

[0057] Figure 3 This is an exploded perspective view of the first compression unit, the second compression unit, and the main frame of the present invention, which are decomposed and viewed from the bottom.

[0058] Figure 4 This is a cross-sectional view showing the first compression part, the second compression part, and the main frame in an enlarged manner according to the present invention.

[0059] Figure 5 It is an exploded perspective view showing an example in which a thrust plate is provided at the lower end of a rotating shaft on the inner periphery of a first fixed scroll.

[0060] Figure 6 is a perspective view showing a thrust plate having an oil supply hole, a radial oil supply groove, and a circular oil supply groove. DETAILED DESCRIPTION

[0061] Hereinafter, the scroll compressor 100 of the present invention will be described in detail with reference to the drawings.

[0062] In this specification, even in different embodiments, the same or similar components are denoted by the same or similar reference numerals, and repeated description thereof is omitted.

[0063] Furthermore, even if the embodiments are different from each other, as long as there is no contradiction in structure and function, the structure applied to one embodiment can be similarly applied to another embodiment.

[0064] Unless the context clearly indicates otherwise, an expression in the singular includes an expression in the plural.

[0065] When describing the embodiments disclosed in this specification, if it is determined that the detailed description of the related known technology may make the gist of the embodiments disclosed in this specification unclear, the detailed description will be omitted.

[0066] It should be understood that the drawings are only used to facilitate the understanding of the embodiments disclosed in this specification, and the technical ideas disclosed in this specification are not limited to the drawings, including all changes, equivalents and substitutes made within the ideas and technical scope of the present invention.

[0067] Figure 1 is a cross-sectional view showing a compound scroll compressor 100 of the present invention, Figure 2 This is an exploded perspective view in which the first compression unit C1, the second compression unit C2, and the main frame 130 of the present invention are decomposed and viewed from the upper side.

[0068] in addition, Figure 3 This is an exploded perspective view of the first compression unit C1, the second compression unit C2, and the main frame 130 of the present invention, which is observed from the bottom. Figure 4 This is a cross-sectional view showing the first compression part C1, the second compression part C2, and the main frame 130 of the present invention in an enlarged manner.

[0069] Figure 5 1 is an exploded perspective view showing an example in which the thrust plate 180 is provided at the lower end of the rotating shaft 125 on the inner periphery of the first fixed scroll 141 . Figure 6 18 is a perspective view showing the thrust plate 180 having the oil supply hole 126 , the radial oil supply groove 183 , and the circular oil supply groove 185 .

[0070] Hereinafter, a scroll compressor 100 according to the present embodiment will be described in detail based on one embodiment shown in the drawings.

[0071] The scroll compressor 100 of the present invention includes a housing 110 , a driving motor 120 , a rotating shaft 125 , a first compression part C1 , a second compression part C2 , and a main frame 130 .

[0072] The driving motor 120 is disposed inside the housing 110 .

[0073] The rotating shaft 125 is rotatably coupled to the driving motor 120. The rotating shaft 125 has a first eccentric portion 1255 and a second eccentric portion 1256 formed to be spaced apart from each other. The first eccentric portion 1255 and the second eccentric portion 1256 can respectively orbit a first orbiting scroll 151 and a second orbiting scroll 152 described later.

[0074] The first compression portion C1 includes a first orbiting scroll 151 and a first fixed scroll 141 .

[0075] The first orbiting scroll 151 is orbitably coupled to the first eccentric portion 1255. The first fixed scroll 141 and the first orbiting scroll 151 mesh with each other to form a first compression chamber V1.

[0076] The second compression portion C2 includes a second orbiting scroll 152 and a second fixed scroll 142 .

[0077] The second orbiting scroll 152 is orbitably coupled to the second eccentric portion 1256. The second fixed scroll 142 and the second orbiting scroll 152 mesh with each other to form a second compression chamber V2.

[0078] The main frame 130 is disposed between the first compression part C1 and the second compression part C2 and supports the first compression part C1 and the second compression part C2.

[0079] The first compression portion C1 is disposed on the opposite side of the drive motor 120 across the second compression portion C2. At this time, one end portion of the rotary shaft 125 is accommodated in the inner circumference of the first fixed scroll 141.

[0080] A thrust plate 180 is coupled to the inner circumference of the first fixed scroll 141 . The thrust plate 180 supports one end of the rotary shaft 125 to form a thrust surface.

[0081] The thrust surface formed by the thrust plate 180 mainly described in the present invention can be understood as Figure 1 and Figure 4 In the figure, the contact surface between the lower end of the rotating shaft 125 and the top surface of the thrust plate 180.

[0082] The detailed structures of the first compression part C1, the second compression part C2, the main frame 130, and the rotating shaft 125 will be described later.

[0083] On the other hand, in the present invention, the scroll compressor 100 may be a compound scroll compressor 100 including a first compression part C1 and a second compression part C2.

[0084] In the compound scroll compressor 100 (hereinafter referred to as the scroll compressor 100 for explanation) of the present 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, a main frame 130 and a second compression part C2 are respectively provided on one side of the driving motor 120.

[0085] 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 coupled to the lower end of the rotating shaft 125 in sequence. Thus, the compressor forms the aforementioned lower compression type structure, and the first compression part C1 and the second compression part C2 are coupled to the driving motor 120 via a rotating shaft 125, so as to operate at the same speed.

[0086] Reference Figure 1 The housing 110 of this embodiment may include a cylindrical shell 111, an upper shell 112, and a lower shell 113. The cylindrical shell 111 is a cylindrical shape with upper and lower ends opened, the upper shell 112 is combined in a manner of covering the upper end of the cylindrical shell 111, and the lower shell 113 is combined in a manner of covering the lower end of the cylindrical shell 111. As a result, the internal space 110a of the housing 110 is sealed, and the internal space 110a of the sealed housing 110 is divided into a lower space S1 and an upper space S2 based on the driving motor 120.

[0087] 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 .

[0088] 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 mixed oil mixed with liquid refrigerant. The discharge space S12 is a space formed between the top surface of the compression part C and the bottom surface of the drive motor 120, forming a space for the refrigerant compressed in the compression part C or the mixed refrigerant mixed with oil to be discharged.

[0089] The upper space S2 is a space formed above the drive 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.

[0090] The lower space S1 and the upper space S2 may be communicated through an internal passage penetrating the internal space 110 a of the housing 110 , or may be communicated through an external passage passing through the outside of the housing 110 .

[0091] A main frame 130 is disposed between the first compression part C1 and the second compression part C2 . The main frame 130 is fixed to the inner circumference of the housing 110 , and has a structure that supports the first compression part C1 and the second compression part C2 on the bottom and top surfaces of the main frame 130 , respectively.

[0092] The refrigerant suction pipe 115 penetrates and is coupled to the side surface of the cylindrical shell 111. Thus, the refrigerant suction pipe 115 penetrates and is coupled to the cylindrical shell 111 constituting the housing 110 in the radial direction.

[0093] The refrigerant suction pipe 115 may be formed in an F shape having one inlet and two outlets.

[0094] For example, refer to Figures 1 to 4, one end of the refrigerant suction pipe 115 forming an 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 an 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. Thus, the refrigerant is directly sucked into the first compression chamber V1 and the second compression chamber V2 through the first suction pipe 1151 and the second suction pipe 1152, respectively.

[0095] The inner end of the refrigerant discharge pipe 116 penetrates and is coupled to the upper portion of the upper shell 112 to communicate with the internal space 110 a of the housing 110 , specifically, communicate with the upper space S2 formed on the upper side of the driving motor 120 .

[0096] One end of the oil circulation pipe (not shown) may be radially penetrated and coupled to the lower half of the lower housing 113. Both ends of the oil circulation pipe may be open, and the other end of the oil circulation pipe may be penetrated and coupled to the refrigerant suction pipe 115. An oil circulation valve (not shown) may be provided in the middle of the oil circulation pipe.

[0097] Reference Figure 1 The driving motor 120 of this embodiment includes a stator 121 and a rotor 122. The stator 121 is inserted and fixed to the inner circumference of the cylindrical shell 111, and the rotor 122 is rotatably disposed inside the stator 121.

[0098] The stator 121 includes a stator core 1211 and a stator coil 1212 .

[0099] The stator core 1211 is formed into an annular or hollow cylindrical shape and is fixed to the inner circumference of the cylindrical housing 111 by heat pressing. The outer circumference of the stator core 1211 is cut or recessed into a half-moon (D-cut) shape along the axial direction, so that the oil separated in the upper space S2 can be recovered to the oil storage space S11.

[0100] The stator coil 1212 is wound around the stator core 1211 and is electrically connected to an external power source by penetrating a power line 1141 coupled to the housing 110. A refrigerant passage (not marked with a reference numeral) is formed between the stator core 1211 and the stator coil 1212 to move the refrigerant discharged from the first compression unit C1 to the upper space S2.

[0101] The rotor 122 includes a rotor core 1221 and permanent magnets 1222 .

[0102] The rotor core 1221 is formed in a cylindrical shape and is rotatably accommodated in the center of the stator core 1211 with a predetermined air gap therebetween. Thus, the air gap between the stator core 1211 and the rotor core 1221 forms a refrigerant channel (not indicated by a reference numeral).

[0103] 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. Thus, the rotating shaft 125 can transmit the rotational force of the driving motor 120 to the first orbiting scroll 151 and the second orbiting scroll 152 constituting the compression part C while rotating together with the rotor 122.

[0104] 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 with respect to the axis O of the rotating shaft 125.

[0105] like Figure 1 and Figure 4 As shown, an example is shown in which a first bearing 1252a is provided between the outer periphery of the first bearing portion 1252 and the first bearing protrusion 1413 of the first fixed scroll 141, a second bearing 1253a is provided between the second bearing portion 1253 and the second bearing protrusion 1423 of the second fixed scroll 142, a third bearing 1255a is provided between the first eccentric portion 1255 and the inner periphery of the first orbiting scroll 151, and a fourth bearing 1256a is provided between the second eccentric portion 1256 and the inner periphery of the second orbiting scroll 152. The first to fourth bearings 1252a, 1253a, 1255a, 1256a may be bearing members formed of journal bearings, bushing bearings, ball bearings, or the like.

[0106] The first eccentric portion 1255 is inserted into the inner circumference of the first orbiting scroll 151 , and may be formed to protrude in the radial direction between the first fixed scroll 141 and the main frame 130 .

[0107] For example, the first eccentric portion 1255 may be formed to protrude in the radial direction between a top surface (a surface facing the first compression chamber V1 ) of the first end plate portion 1411 of the first fixed scroll 141 and a bottom surface of the main frame 130 .

[0108] The lower end of the first eccentric portion 1255 is spaced a predetermined distance from the first fixed scroll 141. In addition, the upper end of the first eccentric portion 1255 is spaced a predetermined distance from the bottom surface of the main frame 130, and its upper movement is restricted by the bottom surface of the main frame 130.

[0109] The second eccentric portion 1256 is inserted into the inner circumference of the second orbiting scroll 152 , and may be formed to protrude in the radial direction between the second fixed scroll 142 and the main frame 130 .

[0110] As an example, the second eccentric portion 1256 may be formed to protrude in the radial direction between a bottom surface (a surface facing the second compression chamber V2 ) of the second end plate portion 1421 of the second fixed scroll 142 and a bottom surface of the main frame 130 .

[0111] The upper end of the second eccentric portion 1256 is spaced apart from the second fixed scroll 142 by a predetermined interval. In addition, the lower end of the second eccentric portion 1256 is spaced apart from the top surface of the main frame 130 by a predetermined interval.

[0112] That is, the axial ends of the first eccentric portion 1255 are arranged between the inner end of the first fixed scroll 141 and one surface of the main frame 130 , and the axial ends of the second eccentric portion 1256 are arranged between the inner end of the second fixed scroll 142 and the other surface of the main frame 130 .

[0113] At this time, when the axial upper end of the first eccentric portion 1255 contacts the lower end of the main frame 130, the axial ends of the second eccentric portion 1256 can be separated from the inner end of the second fixed scroll plate 142 and the other surface of the main frame 130 and configured between the inner end of the second fixed scroll plate 142 and the other surface of the main frame 130.

[0114] As described above, when the upper end of the first eccentric portion 1255 is in contact with the lower end of the main frame 130, the upper and lower ends of the second eccentric portion 1256 are also separated from the second fixed scroll plate 142 and the main frame 130 and will not contact them, thereby preventing the compression portion from being damaged and providing a clear reference point for the up and down movement of the rotating shaft 125.

[0115] On the other hand, refer to Figure 4 The axial distance d1 of the first eccentric portion 1255 may be greater than the axial distance d2 of the second eccentric portion 1256 , so that when the first eccentric portion 1255 is restricted from moving upward by the main frame 130 , the second eccentric portion 1256 is separated from the inner end of the second fixed scroll plate 142 and the other side of the main frame 130 .

[0116] Therefore, when the first eccentric portion 1255 is restricted from moving up and down by the main frame 130, the upper and lower ends of the second eccentric portion 1256 can also be separated from the second fixed scroll plate 142 and the main frame 130, respectively, thereby preventing the compression portion C from being damaged and providing a clear reference point for the up and down movement of the rotating shaft 125.

[0117] On the other hand, the main shaft portion 1251 constitutes the upper end portion of the rotating shaft 125 and is press-fitted to the rotor 122. The main shaft portion 1251 extends in the axial direction so as to be coaxial with the rotor 122. Thus, the main shaft portion 1251 rotates concentrically with the rotor 122.

[0118] 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. Thus, the first bearing portion 1252 can be inserted into the first fixed scroll 141 described later and supported radially, and the second bearing portion 1253 can be inserted into the second fixed scroll 142 described later and supported radially.

[0119] 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. Thus, the first eccentric portion 1255 and the second eccentric portion 1256 rotate at the same speed as the main shaft portion 1251.

[0120] The first eccentric portion 1255 and the second eccentric portion 1256 may be formed on the same axis or on different axes. In other words, the first eccentric portion 1255 and the second eccentric portion 1256 may be formed to be eccentric with the same eccentricity at the same rotation angle or 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. Thus, with the main frame 130 as a reference, the first orbiting scroll 151 coupled to the first eccentric portion 1255 and the second orbiting scroll 152 coupled to the second eccentric portion 1256 are symmetrically subjected to back pressure, so that the first orbiting scroll 151 and the second orbiting scroll 152 can move stably.

[0121] In addition, since the first eccentric portion 1255 and the second eccentric portion 1256 are formed to be axially symmetrical with the main frame 130 interposed therebetween, the scroll compressor 100 of the present invention has a structure that prevents the rotating shaft 125 from jumping in the z-axis direction (axial direction).

[0122] In addition, a hollow oil supply passage 126 is formed inside the rotating shaft 125. The oil supply passage 126 may penetrate the inside of the rotating shaft 125 or be recessed to a preset height. In the present embodiment, the lower end of the rotating shaft 125 may be recessed to an intermediate height, for example, recessed to the first bearing portion 1252. An oil sucker 127 for pumping the oil filled in the oil storage space S11 may be combined at the lower end of the rotating shaft 125. Thus, 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 sucker 127 and the oil supply passage 126, and lubricates the sliding portion.

[0123] The oil absorber 127 may include a cover member 1272 and a suction pipe 1271 .

[0124] As an example, Figure 1 As shown, in the case where the scroll compressor 100 of the present invention is a high-pressure type, due to the application of a pressure differential oil supply system, even if the oil absorber does not have a trochoid gear, etc., the pressure difference between the oil storage space and the compression part can be used to suck the oil in the oil storage space upward, and oil can be supplied to the outer peripheral surface of the rotating shaft 125 or the compression part.

[0125] The oil supply passage 126 may be formed along the axial direction, or may be formed inclined at a predetermined angle. This embodiment shows an example in which the oil supply passage 126 is formed inclined.

[0126] Thus, the oil pumped by the oil sucker 127 is sucked upward by the centrifugal force in the oil supply passage 126, and can be smoothly supplied to the sliding portion.

[0127] The oil supply passage 126 is formed with an oil supply hole 126 penetrating the outer peripheral surface of the rotating shaft 125. A plurality of oil supply holes 126 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 first bearing portion 1252, a second oil supply hole 126b may be formed in the first eccentric portion 1255, a third oil supply hole 126c may be formed in the second eccentric portion 1256, and a fourth oil supply hole 126d may be formed in the second bearing portion 1253. Thus, the oil pumped through the oil supply passage 126 may be smoothly supplied to each bearing surface through each oil supply hole 126.

[0128] Reference Figures 1 to 3 The compression part C of this embodiment includes a first compression part C1 and a second compression part C2.

[0129] In addition, a main frame 130 is disposed between the first compression part C1 and the second compression part C2. The main frame 130 is fixed to the inner circumference of the housing 110, and the bottom surface and the top surface of the main frame 130 support the first compression part C1 and the second compression part C2 respectively.

[0130] An Oldham Ring 160 may be provided between the bottom surface of the main frame 130 and the first compression part C1 to prevent the first orbiting scroll 151 from rotating.

[0131] In addition, an Oldham ring 160 may be provided between the main frame 130 and the top surface and the second compression portion C2 to prevent the second orbiting scroll 152 from rotating.

[0132] Reference Figures 1 to 4 The main frame 130 may form a symmetrical structure in which the top and bottom surfaces have the same structure, so as to be able to support the first compression part C1 and the second compression part C2 on the top and bottom surfaces respectively.

[0133] That is, as described later, a structure is formed on the top surface of the main frame 130 to fixedly support the second fixed scroll 142 , support the second orbiting scroll 152 to be able to orbit, and form a back pressure chamber between the second fixed scroll 142 and the second orbiting scroll 152 .

[0134] Similar to the top surface of the main frame, a back pressure chamber may be formed in the circumferential direction on the bottom surface of the main frame 130 at a side portion between the first fixed scroll 141 and the first orbiting scroll 151 .

[0135] Reference Figure 1 and Figure 4 The main frame 130 forms a first back pressure chamber 137a between the side of the top surface and the second orbiting scroll 152 and the second fixed scroll 142. The first back pressure chamber may be formed in an annular structure along a circumferential direction at the side of the main frame 130.

[0136] The main frame 130 forms a first back pressure chamber 171 between the side of the bottom surface and the first orbiting scroll 150 and the first fixed scroll 141. The first back pressure chambers 137a, 171 may be formed in a ring structure at the side of the main frame 130 along a circumferential direction.

[0137] In addition, scroll fixing portions 136 that can fixably support the fixed scroll 140 may be formed on both surfaces of the main frame 130. In addition, the scroll fixing portions 136 may have fastening holes 136a that can fix the fixed scroll 140.

[0138] The scroll fixing portion 136 may be formed into a side wall structure protruding upward and downward along the circumferential direction on both sides of the main frame 130 .

[0139] In addition, the top surface and the bottom surface of the main frame 130 each have a swirl space portion 133 and a swirl support surface 132, and the swirl space portion 133 is a space formed on the inner side so that the first swirl scroll 151 and the second swirl scroll 152 can be accommodated for swirl movement, and the swirl support surface 132 is arranged around the swirl space portion 133, and is formed on the top surface of the main frame 130 to have a predetermined width, supporting the first swirl scroll 151 and the second swirl scroll 152 so that they can swirl and rotate.

[0140] The main frame 130 is provided with a first back pressure chamber 137 a as a space for accommodating the gas exhausted from the compression chamber V.

[0141] For example, the first back pressure chamber 137 a may be provided between a top surface of the main frame 130 , a lower side portion of the orbiting scroll 150 , and a bottom surface of the fixed scroll 140 .

[0142] Figure 2 FIG. 1 a shows an example in which the first back pressure chamber 137 a is provided between the left and right top surfaces of the main frame 130 , the left and right side portions of the orbiting scroll 150 , and the bottom surfaces of the fixed scroll 140 .

[0143] exist Figure 1 It is shown in the figure that the first back pressure chamber 137a is arranged on the left and right sides, but it can be understood that the first back pressure chamber 137a is a space formed along the circumferential direction between the main frame 130, the orbiting scroll 150 and the fixed scroll 140.

[0144] In addition, Oldham rings 160 may be provided on the bottom and top surfaces of the main frame 130 , respectively, and the Oldham rings 160 prevent the first orbiting scroll 151 and the second orbiting scroll 152 from rotating.

[0145] The first compression part C1 and the second compression part C2 are respectively arranged on both sides of the axial direction with respect to the main frame 130. Hereinafter, the compression part C located at the lower side of the main frame 130 is defined as the first compression part C1, and the compression part located at the upper side of the main frame 130 is defined as the second compression part C2 and described.

[0146] The first compression portion C1 of the present embodiment includes a first fixed scroll 141 and a first orbiting scroll 151 .

[0147] 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 on the top surface of the first fixed scroll 141. Thus, two pairs of first compression chambers V1 are formed between the first fixed scroll 141 and the first orbiting scroll 151 constituting the first compression portion C1.

[0148] The first fixed scroll 141 may have a first bearing protrusion 1413. Figure 3 The first bearing protrusion 1413 is formed to protrude from the central portion of the first fixed scroll 141 to the lower end, and the rotating shaft 125 is inserted into and accommodated in the inner periphery of the first bearing protrusion 1413 .

[0149] The first bearing protrusion 1413 may be formed extending axially from the center of the first fixed scroll 141 toward the lower housing 113. A cylindrical first bearing hole 1413a may be formed axially through the center of the first bearing protrusion 1413, and the first bearing portion 1252 of the rotating shaft 125 may be inserted and radially supported in the first bearing hole 1413a.

[0150] On the other hand, the scroll compressor 100 of the present invention may further include a discharge cover 145 .

[0151] The discharge cover 145 may include a coupling end portion 145a coupled to a lower end of the first bearing protrusion 1413. The discharge cover 145 is coupled to a lower end of the first fixed scroll 141 to accommodate compressed refrigerant discharged from the first compression chamber V1.

[0152] Then, the refrigerant discharged from the first compression chamber V1 to the discharge space 1451 of the discharge cap 145 is mixed with the refrigerant discharged from the second compression chamber V2 to the internal space 110 a of the housing 110 , and after passing through the drive motor 120 , oil is separated in the upper space S2 .

[0153] As an example, the discharge cap 145 may include a coupling end portion 145 a and a thrust support portion 145 b .

[0154] The inner side of the coupling end portion 145 a may be coupled to the lower end of the first bearing protrusion 1413 .

[0155] The coupling end portion 145a may be provided at a central portion of the discharge cover 145. In addition, the coupling end portion 145a may be formed with a receiving groove portion 145e which is extended in a circumferential direction and receives the lower end of the first bearing protrusion 1413 therein.

[0156] The coupling end portion 145 a may further be formed with a sealing groove portion 145 c , and a sealing member capable of achieving sealing between the coupling end portion 145 a and the first bearing protrusion 1413 is provided in the sealing groove portion 145 c .

[0157] The thrust support portion 145 b may be disposed at an upper portion of the coupling end portion 145 a and support the thrust plate 180 .

[0158] A through hole 145d coupled to the upper portion of the oil absorber 127 may be formed at the inner periphery of the coupling end portion 145a.

[0159] A coupling ring 187 described below may be coupled between the thrust support portion 145b and the thrust plate 180. For example, the coupling ring 187 may be coupled to a surface of the thrust plate 180 located opposite to the thrust surface inside the first bearing protrusion 1413 of the first fixed scroll 141 to press and support the thrust plate 180.

[0160] As the coupling ring 187 is disposed on the opposite surface of the thrust surface of the thrust plate 180 , the thrust plate 180 may be more firmly coupled to the inner circumference of the first fixed scroll 141 .

[0161] As an example, the coupling ring 187 may be a C-shaped ring. Figure 5 2 shows an example in which the coupling ring 187 is a C-shaped ring. The coupling ring 187 has an elastic opening 187 c and is elastically deformable so as to be elastically coupled to the inner circumference of the first fixed scroll 141 .

[0162] With such a structure, the reference of the lowermost end surface of the rotating shaft 125 is ensured with the thrust plate 180 as a reference, and a portion that accepts the upper tolerance is ensured.

[0163] In addition, since the center portion of the rotating shaft 125 is supported by the thrust plate 180 , a linear velocity smaller than that of the related art can be ensured.

[0164] The first fixed scroll 141 of the present embodiment may further include a first fixed end plate portion 1411 , a first fixed side wall portion 1412 , a first bearing protrusion 1413 and a first fixed scroll 1414 .

[0165] The first fixed end plate portion 1411 is formed in a disk shape, and a first bearing hole 1413 a constituting a first bearing protrusion 1413 described later is formed through the center thereof in the axial direction.

[0166] A first discharge port 1411a is formed around a first bearing hole 1413a described later, and the first discharge port 1411a is formed to open toward a discharge space 1451 of a discharge cover 145 fixed to a second side surface (bottom surface) of the first fixed end plate portion 1411. Thus, the refrigerant compressed in the first compression chamber V1 is discharged into the discharge space 1451 of the discharge cover 145 through the first discharge port 1411a.

[0167] The first fixed side wall portion 1412 may be formed into a ring shape by axially extending from the first side (top) edge of the first fixed end plate portion 1411 toward the first orbiting end plate portion 1511 of the first orbiting scroll 151. Thus, the first orbiting end plate portion 1511 may be axially supported by the first fixed side wall portion 1412 in an axial manner.

[0168] The first fixed side wall portion 1412 is provided with a first suction port 1412a which penetrates the first fixed side wall portion 1412 in a radial direction. As described above, the end of the first suction pipe 1151 which penetrates the cylindrical shell 111 is inserted and coupled to the first suction port 1412a. Thus, a part 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.

[0169] The first bearing protrusion 1413 is formed to extend axially from the center of the first fixed end plate 1411 toward the lower housing 113. A cylindrical first bearing hole 1413a may be formed axially through the center of the first bearing protrusion 1413, and the first bearing portion 1252 of the rotating shaft 125 may be inserted and radially supported in the first bearing hole 1413a.

[0170] As mentioned above, the inner circumference of the first fixed scroll 141 accommodates one end of the rotating shaft 125. In addition, the inner circumference of the first fixed scroll 141 is coupled with a thrust plate 180 that supports one end of the rotating shaft 125 and forms a thrust surface.

[0171] In the present invention, since the thrust plate 180 supports one side end of the rotating shaft 125 to form a thrust surface, the support area becomes larger compared to the existing structure that uses the eccentric portion of the rotating shaft 125 for support. In addition, since the thrust surface is formed at the rotation center of the rotating shaft 125, the problem of the existing eccentric support that the linear speed increases as the rotation radius increases, thereby generating heat, sintering, and increased mechanical loss on the thrust surface is reduced.

[0172] In addition, in the present invention, since the thrust surface is formed at the lower end of the rotating shaft 125 and not at the compression portion, it is possible to prevent the compression portion from being damaged.

[0173] like Figure 4 14 shows an example in which the lower end of the first bearing portion of the rotary shaft 125 is accommodated in the inner periphery of the first bearing hole 1413 a at the center of the first bearing protrusion 1413 of the first fixed scroll 141 .

[0174] In addition, an example is shown in which the thrust plate 180 is coupled to the inner circumference of the first bearing hole 1413a and supports the lower end of the first bearing portion of the rotating shaft 125, and a thrust surface is formed between the lower end of the first bearing portion of the rotating shaft 125 and the top surface of the thrust plate 180.

[0175] The thrust plate 180 may be pressed into the inner circumference of the first fixed scroll 141. Figure 4 and Figure 5 As shown, the thrust plate 180 may be pressed into the inner circumference of the first bearing hole 1413 a coupled to the first bearing protrusion 1413 .

[0176] In addition, a coupling groove 1413 b may be provided at the inner circumference of the first fixed scroll 141 so that the outer circumference of the thrust plate 180 can be inserted and coupled.

[0177] A chamfered portion 1413 b may be formed at a lower end of the inner circumference of the first fixed scroll 141 so that the thrust plate 180 can be introduced into the inner circumference of the first fixed scroll 141 when being press-fitted.

[0178] In addition, an oil supply connecting hole 181 is formed in the thrust plate 180 . The oil supply connecting hole 181 can connect the oil absorber and the oil supply hole 126 inside the rotating shaft 125 , and the oil in the oil storage space can be supplied to the oil supply hole 126 through the oil absorber 127 via the oil supply connecting hole 181 .

[0179] The oil supply communication hole 181 may be formed at the center of the thrust plate 180. In addition, the oil supply communication hole 181 may be formed through the thrust plate 180.

[0180] The thrust plate 180 may further include a radial oil supply groove 183. The radial oil supply groove 183 may be formed in a radial direction between the oil supply communication hole 181 and an edge of the thrust plate 180 to communicate with the oil supply hole 126.

[0181] Since the radial oil supply groove 183 may be formed on the surface in contact with the lower end of the rotating shaft 125 , oil may be supplied to the oil supply hole 126 of the rotating shaft 125 more smoothly.

[0182] A plurality of radial oil supply grooves 183 may be provided spaced apart from each other along the circumferential direction.

[0183] exist Figure 6 , an example is shown in which three radial oil supply grooves 183 are arranged at equal intervals from each other in the circumferential direction.

[0184] The thrust plate 180 may have a circular oil supply groove 185 .

[0185] A circular oil supply groove 185 may be formed along a circumferential direction at an outer side of the oil supply hole 126 to communicate with the oil supply hole 126 .

[0186] As the thrust plate 180 has the radial oil supply groove 183 , the oil supplied through the oil absorber may be smoothly supplied to the thrust surface of the thrust plate 180 in the radial direction, and the oil may be more smoothly supplied to the oil supply hole 126 of the rotating shaft 125 .

[0187] In addition, as the thrust plate 180 has the circular oil supply groove 185 , the oil supplied through the oil absorber may be smoothly supplied in the circumferential direction to the thrust surface of the thrust plate 180 , and the oil may be more smoothly supplied to the oil supply hole 126 of the rotating shaft 125 .

[0188] In addition, refer to Figure 4 , the first bearing 1252 a may contact an edge of the thrust surface of the thrust plate 180 .

[0189] A structure contact-supported by the first bearing 1252 a is formed at a side of the thrust plate 180 , so that the thrust plate 180 can prevent deformation of a portion supported at the lower end of the rotation shaft 125 and can be stably supported.

[0190] On the other hand, a coupling ring 187 may be coupled to the inner circumference of the first fixed scroll 141 to press and support the thrust plate 180 on the opposite side of the thrust surface. For example, the coupling ring 187 may be coupled to the surface of the thrust plate 180 located on the opposite side of the thrust surface inside the first bearing protrusion 1413 of the first fixed scroll 141 to press and support the thrust plate 180.

[0191] As the coupling ring 187 is disposed on the opposite surface of the thrust surface of the thrust plate 180 , the thrust plate 180 may be more firmly coupled to the inner circumference of the first fixed scroll 141 .

[0192] As an example, the coupling ring 187 may be a C-shaped ring.

[0193] The first bearing hole 1413 a and the second bearing hole 1423 a described later are formed on the same axis. The first bearing described above may be provided on the inner circumference of the first bearing hole 1413 a to support the first bearing portion 1252 of the rotating shaft 125 .

[0194] The first fixed scroll 1414 may be formed on the top surface of the first fixed end plate 1411 and extend axially toward the first orbiting scroll 151. The first fixed scroll 1414 engages with a first orbiting scroll 1512 described later to form a pair of first compression chambers V1.

[0195] The first fixed wrap 1414 may be formed in an involute shape. However, the first fixed wrap 1414 may be formed in various shapes other than an involute shape together with the first orbiting wrap 1512 .

[0196] For example, the first fixed scroll 1414 may have a shape of connecting a plurality of arcs having different diameters and origins, and the outermost curve may be formed into a substantially elliptical shape having a major axis and a minor axis. The first orbiting scroll 1512 may also be formed into an involute shape, and may also be formed into a circular arc connection shape other than an involute.

[0197] Reference Figures 1 to 3 In this embodiment, the first orbiting scroll 151 may include a first orbiting end plate portion 1511 , a first orbiting scroll 1512 , and a first rotation shaft coupling portion 1513 .

[0198] 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 bottom surface. The bottom edge of the first orbiting end plate 1511 is axially supported on the top 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 on the first fixed scroll 141 and performs an orbiting motion.

[0199] In addition, an annular back pressure chamber 171 may be formed between the first orbiting end plate 1511 and the main frame 130 facing it. Thus, the first orbiting end plate 1511 is axially supported by the main frame 130 in the direction toward the first fixed scroll 141, thereby effectively suppressing leakage between compression chambers in the first compression chamber V1.

[0200] A back pressure chamber 137a may also be formed between the second rotating end plate and the main frame 130 facing therefrom, and the description of this is replaced by the description of the back pressure chamber 170 between the first rotating end plate 1511 and the main frame 130 facing therefrom.

[0201] Specifically, first sealing grooves 1511 e are formed at predetermined intervals in the radial direction on the back surface of the first revolving end plate portion 1511 , and a sealing member is inserted into the first sealing groove 1511 e .

[0202] Therefore, a back pressure chamber is formed outside the sealing member inserted into the first sealing groove 1511 e , between the main frame 130 and the side and upper portion of the first orbiting scroll 151 .

[0203] The first orbiting wrap 1512 may be formed to extend from the second side surface (bottom 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.

[0204] The first orbiting scroll 1512 is formed to correspond to the shape of the first fixed scroll 1414 described above, and may be formed in an involute shape similarly to the first fixed scroll 1414 , or may be formed in an arc shape.

[0205] However, the inner end of the first orbiting scroll 1512 may be formed in the central portion of the first orbiting end plate portion 1511 , and the first rotating shaft coupling portion 1513 may be formed axially penetrating the central portion of the first orbiting end plate portion 1511 .

[0206] 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, and during the compression process, it forms the first compression chamber V1 together with the first fixed scroll 1414.

[0207] 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 overlapping with the first eccentric portion 1255 of the rotating shaft 125 on the same plane with the first swirling scroll 1512. Thus, 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 tilt of the first swirling scroll 151 caused by the action of the compressive force and the repulsive force.

[0208] Re-reference Figures 1 to 3 The second compression part C2 of this embodiment is disposed on the upper side of the main frame 130 , and the second compression part C2 is formed symmetrically with the first compression part C1 . For example, the second compression part C2 includes a second fixed scroll 142 and a second orbiting scroll 152 .

[0209] On the other hand, as described above, the first compression part C1 is provided at the lower side of the main frame 130 .

[0210] The second fixed scroll 142 is fixed to the inner circumferential surface of the cylindrical housing 111 on the upper side of the main frame 130, and the second orbiting scroll 152 can be rotatably supported in the axial direction on the back side of the second fixed scroll 142. Thus, two pairs of second compression chambers V2 are formed between the second fixed scroll 142 and the second orbiting scroll 152 constituting the second compression portion C2.

[0211] The second fixed scroll 142 of the present embodiment may include a second fixed end plate portion 1421 , a second fixed sidewall portion 1422 , a second bearing protrusion 1423 , and a second fixed scroll 1424 .

[0212] The second fixed end plate 1421 is formed in a disc shape, and a second bearing hole 1423a constituting a second bearing protrusion 1423 described later is formed through the center thereof in the axial direction. 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.

[0213] The second discharge port 1421a is formed to communicate between the second compression chamber V2 and the internal space 110a of the housing 110. Thus, 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.

[0214] The second fixed side wall 1422 may be formed into a ring shape by axially extending from the first side (bottom) edge of the second fixed end plate 1421 toward the second orbiting end plate 1521 of the second orbiting scroll 152 described later. Thus, the second orbiting end plate 1521 may be rotatably supported by the second fixed side wall 1422 in the axial direction.

[0215] 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.

[0216] As described above, the end of the second suction pipe 1152 penetrating the cylindrical housing 111 is inserted and coupled to the second suction port 1422a. Thus, part 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.

[0217] The second bearing protrusion 1423 is formed at the center of the second fixed end plate 1421 and extends axially toward the drive motor 120. A cylindrical second bearing hole 1423a can be formed in the center of the second bearing protrusion 1423 along the axial direction, and the second bearing portion 1253 of the rotating shaft 125 can be inserted and radially supported in the second bearing hole 1423a.

[0218] 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 such as a bushing bearing or a ball bearing is provided on the inner circumference of the second bearing hole 1423a to support the second bearing portion 1253 of the rotating shaft 125.

[0219] The second fixed scroll 1424 may be formed on the bottom surface of the second fixed end plate 1421 and extend axially 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.

[0220] 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 of 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. The second orbiting scroll 1522 may also be formed in the same manner.

[0221] In addition, the second fixed scroll 1424 is formed symmetrically with the aforementioned first fixed scroll 1414. In other words, the second fixed scroll 1424 is formed to be identical to the first fixed scroll 1414 when projected in the axial direction (or along the axial direction). Thus, 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.

[0222] Re-reference Figures 1 to 4 The second orbiting scroll 152 of the present embodiment includes a second orbiting end plate portion 1521 , a second orbiting scroll 1522 and a second rotating shaft coupling portion 1523 .

[0223] The second orbiting wrap 1522 is formed extending from the second side surface (top 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 scroll 1424 to form a second compression chamber V2.

[0224] Since the second orbiting scroll 1522 is formed corresponding to the shape of the aforementioned second fixed scroll 1424, 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 the second rotating shaft coupling portion 1523 can be formed in the central part of the second orbiting end plate 1521 along the axial direction.

[0225] In addition, the second swirling scroll 1522 is formed symmetrically with the aforementioned first swirling scroll 1512. In other words, as the first eccentric portion 1255 and the second eccentric portion 1256 of the rotating shaft 125 are formed on the same axis, the second swirling scroll 1522 is formed axially identically with the first swirling scroll 1512. Thus, 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.

[0226] 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, and during the compression process, it plays a role in forming a second compression chamber V2 together with the second fixed scroll 1424.

[0227] The second rotating shaft coupling portion 1523 may be formed at a height overlapping the second orbiting scroll 1522 on the same plane. That is, the second rotating shaft coupling portion 1523 may be arranged at a height overlapping the second eccentric portion 1256 of the rotating shaft 125 and the second orbiting scroll 1522 on the same plane. Thus, 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.

[0228] The scroll compressor 100 of the present embodiment as described above operates as follows.

[0229] That is, if power is applied to the drive motor 120, the drive motor 120 generates a rotational force, so that the rotor 122 rotates. Then, 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 is supported by the main frame 130 and orbits relative to the first fixed scroll 141. At the same time, the second orbiting scroll 152 coupled to the second eccentric portion 1256 of the rotating shaft 125 is supported by the main frame 130 and orbits relative to the second fixed scroll 142.

[0230] Therefore, the volume of the first compression chamber V1 and the second compression chamber V2 gradually decreases as they approach the intermediate pressure chambers (not marked with figure marks) formed continuously toward the center side and the discharge pressure chambers (not marked with figure marks) formed on the center side from the suction pressure chambers (not marked with figure marks) formed on the outside of the first compression chamber V1 and the second compression chamber V2.

[0231] Then, the refrigerant having passed through the refrigeration cycle device is sucked into the first suction pressure chamber side constituting the first compression chamber V1 and the second suction pressure chamber side constituting the second compression chamber V2 through the first suction pipe 1151 and the second suction pipe 1152 of the refrigerant suction pipe 115, respectively.

[0232] Therefore, the refrigerant sucked into each suction pressure chamber moves along the moving trajectory of the first compression chamber V1 and the second compression chamber V2, passes through each intermediate pressure chamber and is compressed while moving to each discharge pressure chamber. 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.

[0233] Then, the refrigerant discharged from the first compression chamber V1 to the discharge space 1451 of the discharge cap 145 is mixed with the refrigerant discharged from the second compression chamber V2 to the internal space 110a of the casing 110, and is oil-separated in the upper space S2 after passing through the drive motor 120.

[0234] Then, 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 to the oil storage space S11 which is the lower space S1 of the shell 110. The oil repeatedly performs a series of processes in which the oil is supplied to each bearing surface (not marked with a reference numeral) through the oil supply passage 126 and a part of the oil is supplied to the compression chamber V.

[0235] At this time, a portion of the oil pumped through the oil supply channel 126 is supplied to the outer periphery of the rotating shaft 125 (the first bearing portion 1252, the second bearing portion 1253, the first eccentric portion 1255 and the second eccentric portion 1256) and between the first to fourth bearings 1252a, 1253a, 1255a, 1256a through the respective oil supply holes 126a to 126d.

[0236] In addition, the pumped oil can be supplied to the oil supply hole 126 of the rotating shaft 125 through the oil supply communication hole 181. At this time, the thrust surface between the rotating shaft 125 and the thrust plate 180 promotes the flow of oil through the circular oil supply groove 185 and the radial oil supply groove 183.

[0237] On the other hand, when the first orbiting scroll 151 and the second orbiting scroll 152 are rotated by the rotation of the rotating shaft 125, since the thrust plate 180 is arranged at the lower end of the rotating shaft 125, and no thrust surface like the shaft support part of the existing rotating shaft 125 is arranged inside the first fixed scroll 141 and the second fixed scroll 142, the area supported by the thrust surface becomes larger, which can reduce the increase in surface pressure and linear velocity.

[0238] In addition, since the thrust surface is located at the lower end of the rotating shaft 125, the thrust surface of the shaft does not come into contact with the compression part, thereby preventing the compression part from being damaged.

[0239] The scroll compressor 100 described above is not limited to the configuration and method of the above-described embodiment, and various modifications may be made by selectively combining all or part of each embodiment.

[0240] It is obvious to those skilled in the art that the present invention can be embodied in other specific ways without departing from the spirit and essential features of the present invention. Therefore, the detailed description described above should not be interpreted as restrictive in all aspects, but should be understood as exemplary. The scope of the present invention should be determined by the reasonable interpretation of the attached claims, and all changes within the equivalent scope of the present invention fall within the scope of the present invention.

[0241] Industrial Applicability

[0242] The present invention can be utilized in a scroll compressor having a structure capable of reducing surface pressure by increasing a supported area inside a fixed scroll.

Claims

1. A scroll compressor, wherein: include: case; A driving motor is arranged inside the housing; a rotating shaft rotatably coupled to the driving motor and having a first eccentric portion and a second eccentric portion formed to be spaced apart from each other; A first compression portion includes a first orbiting scroll orbitally coupled to the first eccentric portion and a first fixed scroll meshed with the first orbiting scroll to form a first compression chamber; A second compression portion includes a second orbiting scroll orbitally coupled to the second eccentric portion and a second fixed scroll meshed with the second orbiting scroll to form a second compression chamber; as well as A main frame, disposed between the first compression part and the second compression part and supporting the first compression part and the second compression part; A thrust plate is coupled to an inner periphery of one of the first fixed scroll and the second fixed scroll. The thrust plate supports one end of the rotary shaft to form a thrust surface.

2. The scroll compressor according to claim 1, wherein: The first compression part is arranged on the opposite side of the driving motor across the second compression part, and the inner periphery of the first fixed scroll accommodates one end portion of the rotating shaft; The thrust plate supports and is coupled to a lower end of the rotating shaft at an inner circumference of the first fixed scroll.

3. The scroll compressor according to claim 2, wherein: The thrust plate is press-fitted and coupled to the inner circumference of the first fixed scroll.

4. The scroll compressor according to claim 3, wherein: A coupling groove formed along a circumferential direction is provided on the inner periphery of the first fixed scroll so that the outer periphery of the thrust plate can be inserted and coupled.

5. The scroll compressor according to claim 3, wherein: A chamfered portion is formed at a lower end of an inner circumference of the first fixed scroll so that the thrust plate can be introduced into the inner circumference of the first fixed scroll when the thrust plate is press-fitted.

6. The scroll compressor according to claim 1, wherein: An oil supply hole is formed inside the rotating shaft in the axial direction and the radial direction to supply oil to the outer periphery of the rotating shaft, and the oil supply hole is communicated with the oil absorber to be able to supply oil to the oil supply hole; An oil supply communication hole is formed at a central portion of the thrust plate, and the oil supply communication hole enables the oil absorber to communicate with the oil supply hole.

7. The scroll compressor according to claim 6, wherein: The thrust plate has a radial oil supply groove formed in a radial direction between the oil supply communication hole and an edge of the thrust plate to communicate with the oil supply hole.

8. The scroll compressor according to claim 7, wherein: A plurality of radial oil supply grooves are arranged spaced apart from each other along the circumferential direction.

9. The scroll compressor according to claim 6, wherein: The thrust plate has a circular oil supply groove formed along a circumferential direction at an outer side of the oil supply hole so that the circular oil supply groove is communicated with the oil supply hole.

10. The scroll compressor according to claim 1, wherein: A coupling ring is coupled to an inner circumference of the first fixed scroll to press and support the thrust plate on a surface opposite to the thrust surface.

11. The scroll compressor according to claim 2, wherein: The axial ends of the first eccentric portion are arranged between the inner end of the first fixed scroll and one surface of the main frame; Both axial ends of the second eccentric portion are disposed between the inner end of the second fixed scroll and the other surface of the main frame and spaced apart from the inner end of the second fixed scroll and the other surface of the main frame.

12. The scroll compressor according to claim 11, wherein: The axial distance of the first eccentric portion is greater than the axial distance of the second eccentric portion so that the second eccentric portion is spaced apart from the inner end of the second fixed scroll and the other surface of the main frame when the first eccentric portion is restricted from upward movement by the main frame.

13. The scroll compressor according to claim 2, wherein: The first fixed scroll has a first bearing protrusion, which is formed protruding from the center of the first fixed scroll toward the lower end, and the rotating shaft is inserted into and accommodated in the inner periphery of the first bearing protrusion; The scroll compressor further includes a discharge cover having a coupling end coupled to a lower end of the first bearing protrusion, the discharge cover accommodating and discharging refrigerant discharged from the first compression chamber; The coupling end portion has a thrust support portion which is provided at an upper end of the coupling end portion and supports the thrust plate.

14. The scroll compressor according to claim 2 or 13, wherein: A first bearing is provided on the outer periphery of the rotating shaft disposed on the inner periphery of the first fixed scroll; An edge of the thrust surface of the thrust plate contacts the first bearing.

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