Compressor

Abstract

The invention relates to a compressor. The present invention may comprise: a housing (10); and electric units (21, 23) that are disposed inside the housing (10) and that rotate a rotating shaft (30). A compression section (C) may be disposed inside the housing (10). The compression section C may include a cylinder barrel (60), a primary bearing (40), and a secondary bearing (50) together forming a compression space (V). At this time, first oil discharge parts (47, 57) that are recessed radially inward from the outer peripheral surface of either the main bearing (40) or the cylinder tube (60) having a relatively small diameter may be included. The hydraulic cylinder further comprises a second oil discharge part (67) which penetrates through the main bearing (40) and the cylinder barrel (60) with the relatively large diameter in the axial direction. The first oil discharge portion (47, 57) and the second oil discharge portion (67) may be connected to each other in the axial direction to form an oil discharge path OP.

Description

Technical Field

[0001] The present invention relates to a compressor. Background Art

[0002] Generally, a compressor refers to a mechanical device used in the generation of high pressure or the conveyance of high-pressure fluid. Among them, a compressor applied to a refrigeration cycle such as a refrigerator or an air conditioner compresses a refrigerant gas and delivers it to a condenser. Such a compressor can be classified into a reciprocating compressor, a rotary compressor, and a scroll compressor according to the way of compressing the refrigerant.

[0003] Among them, the rotary compressor can be classified into a type in which a vane is slidably inserted into a cylinder barrel and contacts a roller, and a type in which a vane is slidably inserted into a roller and contacts a cylinder barrel. Generally, the former is also referred to as a roller eccentric rotary compressor (hereinafter, referred to as a rotary compressor), and the latter is referred to as a vane concentric rotary compressor (hereinafter, referred to as a vane rotary compressor).

[0004] In the vane rotary compressor, when the vane inserted into the roller rotates together with the roller, it is led out toward the cylinder barrel by centrifugal force and back pressure and contacts the inner circumferential surface of the cylinder barrel. In the vane rotary compressor, each rotation of the roller continuously forms a compression chamber corresponding to the number of vanes, and each compression chamber sequentially performs a suction stroke, a compression stroke, and a discharge stroke. Therefore, the vane rotary compressor has a higher compression ratio than the rotary compressor.

[0005] In the rotary compressor, a main bearing and a sub-bearing can be respectively disposed above and below with the cylinder barrel as the center. The main bearing and the sub-bearing together with the cylinder barrel constitute a compression part, and a compression chamber for disposing the roller is formed inside the compression part. The main bearing and the sub-bearing can respectively support a rotating shaft so that each rotating shaft rotates stably.

[0006] Such a rotary compressor uses oil for lubrication of components. After the oil performs the lubrication function of the compression part, it gathers again at the lower part of the compressor. The oil sprayed into the upper space during the compression process in the compression part or the oil contained in the refrigerant in a gaseous state can be recovered by gravity into an oil storage space formed at the lower part of the compressor. In order to recover the oil, an oil discharge hole through which the oil supply passes can penetrate through the main bearing and the like.

[0007] Korean Patent No. 10-2447838 (Prior Patent 1) discloses a structure for recovering oil by forming an oil discharge hole. In Prior Patent 1, an oil discharge hole is formed at the edge of the main bearing, and a cylinder barrel having a diameter smaller than that of the main bearing is disposed below the main bearing. Thus, the oil passing through the oil discharge hole can gather at the lower part of the compressor through the outer surface of the cylinder barrel and the inner surface of the compressor.

[0008] In recent years, there has been a trend to use environmentally friendly refrigerants in compressors. Such environmentally friendly refrigerants have the characteristic of low density. Therefore, in order to achieve the same performance as existing compressors, it is necessary to manufacture a larger compression chamber. If only the internal compression chamber size is increased while maintaining the size of the compressor, the cylinder barrel becomes larger, resulting in the diameters of the main bearing and the sub-bearing becoming similar to that of the cylinder barrel. Therefore, there is a problem that as the gap between the outer circumferential surfaces of the main bearing, the sub-bearing, and the cylinder barrel and the inner circumferential surface of the housing becomes narrower, a sufficient passage for recovering oil cannot be formed.

[0009] In particular, the oil recovery paths respectively formed at the edge portions of the main bearing, the sub-bearing, and the cylinder barrel with similar diameters to each other may interfere with each other. For example, components (main bearing or cylinder barrel) disposed above or below the oil drain hole block the oil drain hole, thereby interfering with the oil recovery path. As described above, if the oil recovery paths interfere with each other, oil cannot smoothly gather downward through the oil recovery path.

[0010] In this way, the oil cannot move downward and may stagnate above the compression part or between the compression part and the housing. If the oil is not recovered, the amount of oil supplied to the compression part decreases, causing problems such as frictional loss or wear of the compression part. In addition, there is also the following problem. If the oil cannot gather again at the lower part of the compressor, the oil mixes into the refrigerant discharged from the compressor and is discharged to the outside of the compressor together with the refrigerant, thereby exacerbating the oil shortage inside the compressor.

[0011] To solve this problem, the oil recovery path can also be arranged on the center side of the compression part instead of the edge of the compression part. Chinese Utility Model Publication CN218816989U (Existing Patent 2), Chinese Utility Model Publication CN214036114U (Existing Patent 3), and US Granted Patent US11454240 (Existing Patent 4) respectively disclose compressors in which an oil recovery path is formed in the components constituting the compression part. The compressors of Existing Patent 2 to Existing Patent 4 have the following structure: an oil recovery path is formed that penetrates the bearing (flange) axially, and the oil is recovered to the lower part again through the oil recovery path.

[0012] However, in these Existing Patent 2 to Existing Patent 4, since the oil recovery path is formed by penetrating the compression part at a position close to the center of the compression part, it is necessary to prevent the oil recovery path from interfering with the compression chamber provided at the center of the compression part. Therefore, there are problems that the size of the compression chamber is limited, resulting in a decrease in compression performance, and the structure of the oil recovery path also becomes complex.

[0013] Prior Art Documents

[0014] Patent Documents

[0015] Korean Granted Patent 10-2447838 (Existing Patent 1)

[0016] Chinese Utility Model Publication CN218816989U (Existing Patent 2)

[0017] Chinese Utility Model Publication CN214036114U (Existing Patent 3)

[0018] U.S. Granted Patent US11454240 (Existing Patent 4). Summary of the Invention

[0019] The present invention is used to solve the problems of the prior art as described above. The object of the present invention is to ensure a wide oil recovery path between the side surface (outer peripheral surface) of the compression part and the inner peripheral surface of the housing even if the outer diameters of the components constituting the compression part are similar to each other.

[0020] Another object of the present invention is to ensure a wide compression chamber while widening the oil recovery path.

[0021] Another object of the present invention is that even if the oil discharge hole formed in the compression part is blocked by other components, the oil can be recovered through the oil recovery path formed between the compression part and the housing.

[0022] Another object of the present invention is to form a passage for recovering oil at the edge of the main bearing or the auxiliary bearing, and to sufficiently ensure an area for installing a muffler on the main bearing or the auxiliary bearing.

[0023] Another object of the present invention is to provide a wide and simple-shaped oil recovery path on the outer peripheral surface of the compression part instead of forming a complex-shaped oil recovery path in the central part of the compression part.

[0024] According to the features of the present invention for achieving the above-mentioned objects, the present invention may include: a housing; and an electric part disposed inside the housing to rotate a rotating shaft. A compression part may be disposed inside the housing. The compression part may include a cylinder barrel, a main bearing, and an auxiliary bearing that together form a compression space. At this time, it may include a first oil discharge part that is recessed radially inward from the outer periphery of either the main bearing or the cylinder barrel with a relatively smaller diameter. It may also include a second oil discharge part that is formed axially through the other of the main bearing and the cylinder barrel with a relatively larger diameter. The first oil discharge part and the second oil discharge part may be connected to each other in the axial direction to form an oil discharge path. Thus, not only can the oil recovery rate be improved through the oil discharge path, but also the lubrication performance and operation reliability can be improved by smoothly lubricating the components inside the compressor with oil.

[0025] The first oil drainage portion may be formed in the main bearing. The first oil drainage portion may form a passage between the outer circumferential surface of the main bearing and the inner circumferential surface of the housing. Thus, since the oil drainage path is formed along the edge of the compression portion which is the outside of the compression chamber, a relatively wide compression chamber can be ensured inside the compression portion.

[0026] The first oil drainage portion may extend from a position axially downwardly spaced from the upper end of the outer circumferential surface of the main bearing to the lower end of the outer circumferential surface of the main bearing. Thus, the top surface of the main bearing can remain circular, and a relatively wide area for arranging other components such as a discharge muffler can be ensured on the top surface of the main bearing.

[0027] The radial width of the passage formed between the inner circumferential surface of the housing and the first oil drainage portion may be greater than the radial width of the second oil drainage portion. Thus, the bottleneck phenomenon can be eliminated during the oil recovery process.

[0028] The surface of the first oil drainage portion may form a continuous plane or curved surface with the surface of the second oil drainage portion. Thus, oil will not stagnate due to a step structure or the like, and the flow of oil can be made smoother.

[0029] The second oil drainage portion may include a first discharge inner surface forming the inner surface of the second oil drainage portion. The second oil drainage portion may include a second discharge inner surface which is spaced apart from and faces the first discharge inner surface and is formed at a position closer to the inner circumferential surface of the housing than the first discharge inner surface. The second oil drainage portion may include a connecting inner surface connecting between the first discharge inner surface and the second discharge inner surface. At this time, the first discharge inner surface may form a continuous plane or curved surface with the first oil drainage portion.

[0030] A flange portion may be formed above the first oil drainage portion which protrudes more radially toward the inner circumferential surface of the housing than the first oil drainage portion.

[0031] The relationship between the radial distance L1 between the flange portion and the inner circumferential surface of the housing, the radial distance L2 between the surface of the first oil drainage portion and the inner circumferential surface of the housing, the radial distance L3 between the second discharge inner surface and the inner circumferential surface of the housing, and the radial distance L4 between the first discharge inner surface and the inner circumferential surface of the housing may be L3 < L1 < L2 = L4.

[0032] A flange portion may be formed above the first oil drainage portion which protrudes more radially toward the inner circumferential surface of the housing than the first oil drainage portion. The relative ratio (OH / BH) of the axial height OH of the first oil drainage portion to the overall axial height BH of the flange portion and the first oil drainage portion may be 0.2 to 0.35.

[0033] Above the first oil drainage part, a flange part that protrudes more radially toward the inner circumferential surface of the housing than the first oil drainage part may be formed. The flange part may be axially spaced upward from the upper end of the second oil drainage part. At this time, the first oil drainage part may be formed between the flange part and the second oil drainage part.

[0034] Above the first oil drainage part, a flange part that protrudes more radially toward the inner circumferential surface of the housing than the first oil drainage part may be formed. The edge of the flange part may be circular, and a discharge muffler may be disposed on the top surface of the flange part.

[0035] A plurality of the first oil drainage parts and a plurality of the second oil drainage parts may be respectively arranged along the circumferential direction of the compression part.

[0036] Main fastening holes for the fastening solid to pass through may be formed in the main bearing and the cylinder barrel respectively along the circumferential direction. The main fastening hole and the cylinder barrel fastening hole may be connected to each other axially. In the circumferential direction, the first oil drainage part may be formed between the main fastening holes, and the second oil drainage part may be formed between the cylinder barrel fastening holes.

[0037] A plurality of main fastening holes for the fastening solid to pass through may penetrate the main bearing along the circumferential direction. The centers of the main fastening holes may be formed radially between the compression space and the first oil drainage part.

[0038] The centers of the main fastening holes and the first oil drainage part may be spaced apart along the circumferential direction of the main bearing.

[0039] The outer circumferential surface of the cylinder barrel may be in close contact with the inner circumferential surface of the housing. The outer circumferential surfaces of the main bearing and the sub-bearing may be spaced apart from the inner circumferential surface of the housing.

[0040] The diameter of the cylinder barrel may be larger than the diameters of the main bearing and the sub-bearing. The first oil drainage part may be formed in both the main bearing and the sub-bearing. The second oil drainage part may be formed in the cylinder barrel.

[0041] The first oil drainage part may be formed by being recessed radially inward from the outer circumferential surface of the main bearing facing the inner circumferential surface of the housing.

[0042] The first oil drainage part may extend continuously from the upper end of the outer circumferential surface of the main bearing to the lower end of the outer circumferential surface of the main bearing.

[0043] The first oil drainage part may have the same cross-sectional shape along the axial direction.

[0044] A flange portion that protrudes more radially toward the inner circumferential surface of the housing than the first oil drainage portion may be formed above the first oil drainage portion. The axial height of the first oil drainage portion may be lower than the axial height of the flange portion.

[0045] The first oil drainage portion may be formed in the main bearing, and the second oil drainage portion may be formed in the cylinder barrel. The oil drainage path may include: a first passage formed between the upper portion of the outer circumferential surface of the main bearing and the inner surface of the housing; a second passage formed by the first oil drainage portion; and a third passage formed by the second oil drainage portion.

[0046] The first oil drainage portion may include: a main oil drainage portion formed in the main bearing; and a sub oil drainage portion formed in the sub bearing. At this time, the main oil drainage portion and the sub oil drainage portion may form the oil drainage path via the second oil drainage portion.

[0047] The sub oil drainage portion may extend from a position axially upwardly spaced from the lower end of the outer circumferential surface of the sub bearing to the upper end of the outer circumferential surface of the sub bearing.

[0048] The sub oil drainage portion may extend from the upper end of the outer circumferential surface of the sub bearing to the lower end.

[0049] The circumferential width of the first oil drainage portion may be the same as the circumferential width of the second oil drainage portion.

[0050] The outer circumferential surface of the main bearing may overlap all or a part of the second oil drainage portion based on the radial direction.

[0051] The top edge of the main bearing or the bottom edge of the sub bearing may be circular, and a discharge muffler may be disposed on the top surface of the main bearing or the bottom surface of the sub bearing.

[0052] The oil drainage path may include: a first path formed between the outer circumferential surface of the main bearing and the inner circumferential surface of the housing; a second path formed axially through the cylinder barrel and connected to the first path; and a third path formed between the outer circumferential surface of the sub bearing and the inner circumferential surface of the housing and connected to the second path. At this time, at least one of the first path and the third path may be configured by being axially arranged through portions having different dimensions of the radial width of the first bearing or the second bearing.

[0053] The oil drainage path may include: a first passage formed between the upper end portion of the outer circumferential surface of the main bearing and the inner circumferential surface of the housing; a second passage formed at a position axially lower than the upper end portion, formed between the outer circumferential surface of the main bearing and the inner circumferential surface of the housing, and wider in the radial direction than the first passage; and a third passage formed axially through the cylinder barrel.

[0054] The compressor of the present invention as described above has the following effects.

[0055] According to the present invention, an oil drainage path continuous in the axial direction may be formed in the main bearing, the sub-bearing, and the cylinder barrel constituting the compression part. Such an oil drainage path is formed along the edge of the compression part, enabling the oil inside the compressor to be smoothly recovered. Through the oil drainage path, not only can the oil recovery rate be improved, but also the lubrication performance and operation reliability can be enhanced by smoothly lubricating the components inside the compressor with oil.

[0056] Moreover, in the present invention, since the oil drainage path is formed along the edge of the compression part which is the outside of the compression chamber, a relatively wide compression chamber can be ensured inside the compression part. Therefore, while ensuring a relatively wide compression chamber, the oil drainage path can be formed relatively wide.

[0057] In addition, in the present invention, the oil drainage path may have a structure recessed radially from the side surface of the compression part. Thus, even when the outer diameters of the components constituting the compression part are similar to each other, the oil drainage path will not be narrowed due to interference between the components.

[0058] Furthermore, in the present invention, even if the outer diameters of the components constituting the compression part are similar to each other, resulting in the holes (second oil drainage part) constituting the oil drainage path being blocked by other components axially, the radially recessed part (first oil drainage part) can connect the oil drainage path axially. Thus, there is no need to complicate the shape of other components, such as the main bearing, to prevent the blocking of the holes for recovering oil, and the structure of the compression part can be simply achieved.

[0059] In addition, in the present invention, the first oil drainage part, which is a part of the oil drainage path, may be formed by being recessed radially from the compression part, and the second oil drainage part, which is another part, may be formed by penetrating the compression part axially. The first oil drainage part can provide a relatively wide oil recovery passage through the recessed structure, and the component having the second oil drainage part can maintain a circular edge, thereby providing a continuous close contact surface between the outer peripheral surface of the compression part and the inner peripheral surface of the housing. Thus, the compression part can be stably installed inside the housing.

[0060] In particular, the top surface of a component maintaining a circular shape, such as the main bearing, may also be circular. Thus, a relatively wide discharge muffler mounting surface can be formed on the top surface of the main bearing. Thus, there is no need to complicate the shape of the discharge muffler to mount it on the top surface of the main bearing, and the structure of the compression part can be simplified.

[0061] In addition, since the oil drainage path is formed at the edge of the compression part, the oil can be more effectively recovered when flowing radially along the rotation force of the rotor, which can improve the lubrication performance and operation reliability of the compression part.

[0062] Moreover, even if the diameter of the main bearing (or auxiliary bearing) for shielding the compression space increases together with the increase of the compression space, the first oil drainage portion recessed from the edge of the main bearing (or auxiliary bearing) can provide a relatively wide passage for flowing toward the second oil drainage portion of the cylinder barrel. Thus, even if an environment-friendly refrigerant is used in the compressor, a decrease in compression performance or oil recovery rate can be prevented.

[0063] In addition, in the present invention, the radial width of the passage formed between the inner peripheral surface of the housing and the first oil drainage portion may be larger than the radial width of the passage formed by the second oil drainage portion. In this way, the bottleneck phenomenon of oil flow during the process of oil flowing from the first oil drainage portion via the second oil drainage portion can be eliminated, and relatively smooth oil recovery can be carried out.

[0064] Furthermore, in the present invention, the first oil drainage portion and the second oil drainage portion forming the oil drainage path may have continuous planes or curved surfaces with each other. Thus, oil can flow smoothly along the surfaces of the first oil drainage portion and the second oil drainage portion, and effective oil recovery can be achieved.

[0065] Moreover, in the present invention, in the component where the first oil drainage portion is formed, such as the main bearing, the ratio of the axial height of the first oil drainage portion to the overall axial height of the main bearing may be formed to be 0.2 to 0.35. Thus, while a part of the main bearing remains circular, the height of the oil film is maintained above the suitable height of the compression portion, so that the effect of being able to lubricate the compression portion smoothly can be obtained.

[0066] In addition, in the present invention, an oil drainage path may be formed between the fastening holes for fastening the compression portion. Thus, while avoiding interference between the fastening holes and the oil drainage path, the fastening holes can be arranged adjacent to the edge of the compression portion. Thereby, a relatively wide compression chamber can be ensured at the central portion of the compression portion, and the compression capacity can be improved.

[0067] Moreover, in the present invention, a flange portion may be formed at the upper end of the outer peripheral surface of the main bearing, and the first oil drainage portion may be formed below the flange portion. Thus, the top surface of the flange portion can maintain a circular shape, so that the area for installing a circular discharge muffler can be provided relatively widely. Therefore, it is not necessary to change the discharge muffler into a complex shape due to the first oil drainage portion, and the compatibility of the compressor can also be improved.

[0068] In addition, a relatively wide oil contact area can be formed by forming a stepped structure between the flange portion and the first oil drainage portion. Thus, the amount of oil floating inside the compressor can be reduced.

[0069] In addition, in the present invention, the first oil drainage portion and the second oil drainage portion may be connected to be radially offset from each other. Thus, an oil drainage path in which an axial path and a radial path are mixed with each other can be formed, the amount of oil floating inside the compressor can be reduced by ensuring a relatively wide oil contact area, and the oil recovery rate can be improved.

[0070] In addition, in the present invention, since the first oil drainage part can be formed along the outer peripheral surface of the compression part, it can have a larger volume compared with the case where it is formed in the central part of the compression part. Thus, a relatively wide oil storage space can be provided inside the compressor, and the amount of oil flowing out to the outside of the compressor can be reduced.

[0071] In addition, in the present invention, the first oil drainage part has a structure that is recessed in the radial direction from the outer peripheral surface of the compression part, so it has the advantages of simple shape and easy processing. In addition, through this simple structure, it has the effect of being able to reduce the manufacturing cost for processing the first oil drainage part and is conducive to mass production. BRIEF DESCRIPTION OF THE DRAWINGS

[0072] Figure 1 It is a cross-sectional view showing an embodiment of the compressor of the present invention.

[0073] Figure 2 It is a cross-sectional view showing the electric part and the compression part of an embodiment constituting the compressor of the present invention.

[0074] Figure 3 It is a perspective view showing the structure of the compression part of an embodiment of the present invention.

[0075] Figure 4 It is from Figure 3 A perspective view showing the structure of the compression part of an embodiment of the present invention from a different angle.

[0076] Figure 5 It is a perspective view showing the components of the compression part of an embodiment of the present invention disassembled and shown.

[0077] Figure 6 It is a perspective view showing the components of the compression part of an embodiment of the present invention disassembled and observed from a different angle from Figure 5 A perspective view.

[0078] Figure 7 It is a top view showing a perspective view of the internal structure of the compression part of an embodiment of the present invention.

[0079] Figure 8 It is a bottom view of the compression space showing the removal of the auxiliary bearing of the compression part of an embodiment of the present invention and shown.

[0080] Figure 9 It is an operating state diagram showing the process of compressing the refrigerant through an embodiment of the present invention in sequence.

[0081] Figure 10 It is Figure 7 A top view showing the enlarged A1 part of

[0082] Figure 11 The Figure 8 top view in which the A2 portion of

[0083] Figure 12 is an enlarged cross-sectional view showing the structure of the compression section constituting one embodiment of the present invention.

[0084] Figure 13 is the Figure 12 side view in which the A3 portion of

[0085] Figure 14 is a side view showing the structure of the compression section constituting one embodiment of the present invention.

[0086] Figure 15 is the Figure 14 side view in which the A4 portion of

[0087] Figure 16 is an enlarged cross-sectional view showing the first oil discharge section and the second oil discharge section constituting one embodiment of the present invention.

[0088] Figure 17 is from Figure 3 and Figure 4 a perspective view showing the structure of the compression section constituting one embodiment of the present invention from a different angle.

[0089] Figure 18 is a perspective view showing the structure of the compression section with the discharge muffler removed, which constitutes one embodiment of the present invention.

[0090] Figure 19 is a perspective view showing the state in which the main bearing and the discharge muffler constituting one embodiment of the present invention are combined with each other.

[0091] Figure 20 is a perspective view showing the state in which oil moves through the oil discharge path constituting one embodiment of the present invention.

[0092] Figure 21 is the Figure 20 perspective view in which the A5 portion of

[0093] Figure 22 is a curve showing the oil level height that changes according to the height of the first oil discharge section constituting one embodiment of the present invention.

[0094] Figure 23 is a perspective view showing the structure of the compression section constituting the second embodiment of the compressor of the present invention.

[0095] Figure 24 is a side view showing the structure of the compression section constituting the third embodiment of the compressor of the present invention.

[0096] Figure 25 It is a side view showing the structure of the compression section constituting the fourth embodiment of the compressor of the present invention.

[0097] Figure 26 It is a side view showing the structure of the compression section constituting the fifth embodiment of the compressor of the present invention.

[0098] Figure 27 It is a cross-sectional view showing the structure of the oil drainage path constituting the sixth embodiment of the compressor of the present invention.

[0099] Figure 28 It is a perspective view showing the structure of the compression section constituting the seventh embodiment of the compressor of the present invention.

[0100] Figure 29 It is a top view showing the structure of the main bearing constituting the eighth embodiment of the compressor of the present invention.

[0101] Figure 30 It is a side view showing the structure of the compression section constituting the ninth embodiment of the compressor of the present invention.

[0102] Explanation of reference numerals

[0103] 10: Housing 11: Main body housing

[0104] 12: Upper housing 13: Lower housing

[0105] 14: Discharge pipe 20: Electric part

[0106] 21: Stator 23: Rotor core

[0107] 25: Coil 30: Rotating shaft

[0108] 34: Oil flow path 40: Main bearing

[0109] 47: Main oil discharge part 48: Main flange part

[0110] 50: Sub-bearing 57: Sub-oil discharge part

[0111] 58: Sub-flange part 60: Cylinder barrel

[0112] 67: Second oil discharge part 70: Roller

[0113] 73A, 73B, 73C: Vane grooves 74A, 74B, 74C: Back pressure chambers

[0114] 75A, 75B, 75C: Vanes 81, 82: Discharge valves

[0115] C: Compression section OP: Oil drainage path

[0116] V1, V2, V3: Compression chambers Detailed Embodiments

[0117] Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that when assigning reference numerals to the constituent elements of each drawing, the same constituent elements are assigned the same reference numerals as much as possible, although they are marked on different drawings. In addition, during the description of the embodiments of the present invention, when it is determined that a detailed description of a related well-known structure or function hinders the understanding of the embodiments of the present invention, the detailed description thereof is omitted.

[0118] The compressor according to an embodiment of the present invention may include a housing 10, an electric unit 20, a rotating shaft 30, and a compression unit C. The main bearing 40, the sub-bearing 50, and the cylinder block 60 constituting the compression unit C may be stacked on one another. Hereinafter, a compressor in which the compression unit C is disposed below the electric unit 20 will be described as an example.

[0119] The housing 10 may form the appearance of the compressor. The housing 10 is a part that forms the appearance of the compressor and may be divided into a vertical type or a horizontal type according to the installation form of the compressor. The vertical housing 10 is a structure in which the electric unit 20 and the compression unit C are arranged axially on the upper and lower sides, and the horizontal housing 10 is a structure in which the electric unit 20 and the compression unit C are arranged on the left and right sides. The housing 10 of the present embodiment will be described by taking the vertical housing 10 as an example.

[0120] The housing 10 may be formed of a main housing 11 having an open top and bottom in a cylindrical shape. The upper part of the main housing 11 of the housing 10 that is open may be sealed with an upper housing 12. A discharge space DS for the compressed refrigerant to flow in may be formed below the upper housing 12. The part of the main housing 11 that is open downward may be sealed with a lower housing 13. The main housing 11 may also be regarded as an intermediate housing.

[0121] The electric unit 20 and the compression unit C may be fixed inside the main housing 11. An intake pipe IP may be provided in the main housing 11. The intake pipe IP forms an inlet for sucking the refrigerant. The intake pipe IP may be directly connected to the compression unit C. This structure will be described again later.

[0122] A discharge pipe 14 for discharging the refrigerant to the outside may be provided in the upper housing 12. The discharge pipe 14 may be connected to a pipe (not shown) for delivering the refrigerant to a condenser (not shown) in the refrigeration cycle.

[0123] In the upper housing 12, a cluster 15 for transmitting external power to the electric unit 20 may be disposed. The cluster 15 can be regarded as a kind of connector. If an external connector (not shown) is coupled to the cluster 15, external power can be transmitted to the electric unit 20 through a wire (not shown). As another example, the cluster 15 may also be disposed in the main body housing 11 instead of the upper housing 12. Reference numeral 17 denotes a support plate for supporting the compressor.

[0124] An electric unit 20 may be disposed inside the housing 10. The electric unit 20 is for generating a rotational force, and the electric unit 20 can rotate the rotating shaft 30. In the present embodiment, the electric unit 20 is disposed at a position higher than the compression unit C. On the contrary, the compression unit C may also be disposed above the electric unit 20. The electric unit 20 may generally be composed of a stator 21 and rotors 23, 25.

[0125] The rotors 23, 25 constituting the electric unit 20 may include a rotor core 23 and coils 25. The stator 21 may be formed in a cylindrical shape and fixed to the inner circumferential surface 11a of the main body housing 11 by shrink fitting. The coils 25 may be wound around the rotor core 23 and are electrically connected to an external power source by means of the cluster 15 penetrating and being coupled to the main body housing 11.

[0126] The rotating shaft 30 is rotatably supported by the main bearing 40 and the sub-bearing 50. The main bearing 40 and the sub-bearing 50 may be stacked on the upper and lower portions of the cylinder barrel 60, respectively. Through the main bearing 40, the sub-bearing 50 and the cylinder barrel 60 can be fixed inside the housing 10. The main bearing 40 and the sub-bearing 50 are distinguished for ease of explanation, so the main bearing 40 and the sub-bearing 50 may also be referred to as the first bearing and the second bearing, respectively. The structures of the main bearing 40 and the sub-bearing 50 will be described in detail again later. For reference, hereinafter, the axial direction refers to the length direction of the rotating shaft 30 (the up and down direction based on Figure 1 ).

[0127] An oil flow path 34 may be formed along the axial direction of the rotating shaft 30 at the center of the rotating shaft 30. Oil may be stored in an oil storage space RS provided at the inner bottom side of the housing 10, and the stored oil may be transferred upward through the oil flow path 34 provided in the rotating shaft 30. The transferred oil can be supplied to each component and perform a lubricating function.

[0128] As Figure 1As shown, oil through-holes 35a and 35b can be formed in the middle of the oil flow path 34, and the oil through-holes 35a and 35b are formed along the radial direction of the rotation shaft 30. In this embodiment, the oil through-holes 35a and 35b include a first oil through-hole 35a and a second oil through-hole 35b. The first oil through-hole 35a is connected to the electric part 20, and the second oil through-hole 35b is connected to the main bearing 40 and the sub-bearing 50. The second oil through-hole 35b is composed of two second oil through-holes 35b with different heights, and is respectively connected to the main bearing 40 and the sub-bearing 50.

[0129] An oil suction device 37 can be provided in the middle or lower end of the oil flow path 34. The oil suction device 37 can use a gear pump, a viscous pump, a centrifugal pump, etc. This embodiment illustrates an example of using a centrifugal pump. When the rotation shaft 30 rotates, the oil filled in the oil storage space RS of the housing 10 can be sucked by the oil suction device 37, and the sucked oil can be supplied to the sub-bearing 50 and the main bearing 40 through the second oil through-hole 35b on the way of rising along the oil flow path 34, so that the rotation of the rotation shaft 30 can be made smooth. The oil that continues to rise can also be supplied in the direction of the electric part 20 through the first oil through-hole 35a.

[0130] Next, the compression part C will be described. As Figure 2 shown, the compression part C can include a cylinder 60 arranged at the center, a main bearing 40 and a sub-bearing 50 respectively arranged at the upper and lower parts of the cylinder 60, and a roller 70 arranged at the center of the cylinder 60. The cylinder 60 can be combined with the main bearing 40 and the sub-bearing 50, and a compression space V is formed at the opposite parts.

[0131] The roller 70 is rotatably arranged in the compression space V, and vanes 75A, 75B, and 75C can be slidably inserted into the roller 70 and divide the compression space V into a plurality of compression chambers V1, V2, and V3. The roller 70 is surrounded by the cylinder 60, the main bearing 40, and the sub-bearing 50, so as not to be exposed to the outside of the compression part C. The detailed structure of the roller 70 will be described again later.

[0132] At least one of the main bearing 40, the sub-bearing 50, and the cylinder 60 can be fixedly arranged on the main body housing 11. In this embodiment, the cylinder 60 is fixed to the inner peripheral surface 11a of the main body housing 11. For example, the cylinder 60 can be inserted into the main body housing 11 and welded.

[0133] As Figure 2As shown, in this embodiment, the outer diameter CW of the cylinder barrel 60 and the inner diameter of the main body housing 11 are greater than the outer diameters BW of the main bearing 40 and the sub-bearing 50. Therefore, although the outer peripheral surface 63 of the cylinder barrel 60 contacts the inner peripheral surface 11a of the main body housing 11, the outer peripheral surface 43 of the main bearing 40 and the outer peripheral surface 53 of the sub-bearing 50 are spaced apart from the inner peripheral surface 11a of the main body housing 11. In this way, the portions where the outer peripheral surface 43 of the main bearing 40 and the outer peripheral surface 53 of the sub-bearing 50 are spaced apart from the inner peripheral surface 11a of the main body housing 11 can form part of the oil discharge path OP described later. Refer to Figure 13 wherein the reference numeral RD represents the difference between the outer diameter of the cylinder barrel 60 and the outer diameters of the main bearing 40 and the sub-bearing 50.

[0134] Refer to Figure 2 and Figure 3 In the compression part C, an oil discharge path OP is formed. The oil discharge path OP is a path for the movement of oil, more precisely, a path for recycling the oil after performing the lubrication function back to the oil storage space RS. The oil discharge path OP can be formed along the edge of the compression part C. Here, the edge refers to the peripheral part of the compression part C close to the inner peripheral surface 11a of the main body housing 11. Thus, the oil can move along the edge of the compression part C through the oil discharge path OP. In Figure 2 the direction of recycling the oil by using the continuous passage formed by the oil discharge path OP is indicated by an arrow.

[0135] The oil discharge path OP can pass through the main bearing 40, the sub-bearing 50, and the cylinder barrel 60 that constitute the compression part C. The oil discharge path OP is formed respectively in the main bearing 40, the sub-bearing 50, and the cylinder barrel 60, and an oil movement path can be formed by connecting the respectively formed flow paths. The specific structure thereof will be described again later.

[0136] First, refer to Figure 5 and Figure 6 for a detailed description of the main bearing 40 that constitutes the compression part C. The bottom surface 41B of the main bearing 40 can be arranged to face the top surface 61A of the cylinder barrel 60. The bottom surface 41B of the main bearing 40 can constitute the top surface of the compression spaces V1, V2, V3 by covering the upper parts of the compression spaces V1, V2, V3 penetrating through the cylinder barrel 60. Main back pressure grooves 44, 46 for providing back pressure to the rear ends of the vanes 75A, 75B, 75C can be recessed and formed on the bottom surface 41B of the main bearing 40 facing the cylinder barrel 60. Sub back pressure grooves 54, 56 for providing back pressure to the rear ends of the vanes 75A, 75B, 75C can be recessed and formed on the top surface 51A of the sub-bearing 50 facing the cylinder barrel 60.

[0137] In this embodiment, the main bearing 40 (i) supports the rotating shaft 30 so as to be rotatable, (ii) covers the upper part of the compression space V penetrating the cylinder 60, (iii) discharges the refrigerant compressed in the compression space V, and (iv) forms main back-pressure grooves 44 and 46 for providing back pressure to the rear ends of the vanes 75A, 75B, and 75C.

[0138] For the purpose of distinguishing from the sub-back-pressure grooves 54 and 56 of the sub-bearing 50 described later, the main back-pressure grooves 44 and 46 are referred to as the main back-pressure grooves 44 and 46. Differently, the main back-pressure grooves 44 and 46 and the sub-back-pressure grooves 54 and 56 may also be both referred to as back-pressure grooves. In addition, the first main back-pressure groove 44 and the second main back-pressure groove 46 may be respectively referred to as the first groove 44 and the second groove 46. As an alternative to the main back-pressure grooves 44 and 46, the first sub-back-pressure groove 54 and the second sub-back-pressure groove 56 may be respectively referred to as the first groove 46 and the second groove 56. This structure will be described again later.

[0139] As a reference, first refer to Figure 5 To explain the discharge valves 81 and 82, the discharge valves 81 and 82 may be provided on the top surface 41A of the main bearing 40. The discharge valves 81 and 82 may function to open and close the discharge ports 42 formed in the main bearing 40. A plurality of the discharge valves 81 and 82 may be provided. In this embodiment, the discharge valves 81 and 82 include a first discharge valve 81 and a second discharge valve 82. The first discharge valve 81 opens and closes the first discharge port 42A described later, and the second discharge valve 82 opens and closes the second discharge port 42B. The first discharge valve 81 and the second discharge valve 82 may be arranged at intervals in the circumferential direction of the main bearing 40.

[0140] The first discharge valve 81 may be composed of a first locator 81A (refer to Figure 12 ), a first valve plate 81C (refer to Figure 12 ), and a first valve fastening hole (not shown) for inserting a fastening solid. Although not shown, the second discharge valve 82 may also be composed of a second locator, a second valve plate, and a second valve fastening hole for inserting a fastening solid in the same manner as the first discharge valve 81. As another example, when the discharge ports 42A and 42B are formed on the side surface of the main bearing 40, the discharge valves 81 and 82 may also be formed on the side surface of the main bearing 40. Since this valve structure is a common structure, detailed description thereof is omitted.

[0141] If the main bearing 40 is disassembled, the compression space V can be exposed. Refer to Figure 8, the compression space V can be divided into a plurality of compression chambers V1, V2, V3 by a plurality of the vanes 75A, 75B, 75C. If the plurality of the vanes 75A, 75B, 75C rotate, compression of the refrigerant can be formed in the compression chambers V1, V2, V3. This process will be described again later.

[0142] Referring to Figure 7 , the discharge ports 42A, 42B can be formed to penetrate the main bearing 40 in the axial direction. Here, the axial direction refers to the length direction of the rotating shaft 30, that is, Figure 1 the up and down direction. In this embodiment, a plurality of the discharge ports 42A, 42B can be provided. The discharge ports 42A, 42B include a first discharge port 42A and a second discharge port 42B. The first discharge port 42A can be constituted again by a plurality of first discharge ports 42A, and the plurality of first discharge ports 42A can be arranged in a circumferential direction around the rotating shaft 30 disposed at the center of the main bearing 40. The second discharge port 42B can also be constituted by a plurality of second discharge ports 42B, and the plurality of second discharge ports 42B can be arranged in a circumferential direction around the rotating shaft 30 disposed at the center of the main bearing 40. As another example, the discharge ports 42A, 42B can also be constituted only by the first discharge port 42A. For reference, Figure 1 in

[0143] Referring again to Figure 5 , a main bushing portion 42' can be provided at the center of the main bearing 40. The main bushing portion 42' can be provided in a cylindrical shape at the center portion of the main bearing 40 and surround the rotating shaft 30. A first shaft support hole AH1 is formed at the center of the main bushing portion 42'. The main bushing portion 42' can surround and fix the rotating shaft 30 together with a sub-bushing portion 52' described later at different heights so as to be rotatable.

[0144] Referring to Figure 6 , main backpressure grooves 44, 46 are formed in the main bearing 40. The main backpressure grooves 44, 46 increase the pressure of the backpressure chambers formed at one ends of the vane grooves 73A, 73B, 73C and provide backpressure to the vanes 75A, 75B, 75C in a direction protruding from the vane grooves 73A, 73B, 73C. The main backpressure grooves 44, 46 can be constituted by a plurality of main backpressure grooves 44, 46 separated in the circumferential direction of the main bearing 40. The plurality of main backpressure grooves 44, 46 can have different internal pressures from each other.

[0145] Although the main back-pressure grooves 44 and 46 are given different names in order to distinguish them from the sub-back-pressure grooves 54 and 56 described later, in the case where the sub-back-pressure grooves 54 and 56 are omitted, the main back-pressure grooves 44 and 46 can also be referred to as back-pressure grooves 44 and 46. As another example, the main back-pressure grooves 44 and 46 and the sub-back-pressure grooves 54 and 56 can be collectively referred to as back-pressure grooves 44, 46, 54, and 56.

[0146] Referring Figure 7 , the first main back-pressure groove 44 and the second main back-pressure groove 46 can be formed within the outer diameter range of the roller 70. Here, the outer diameter range of the roller 70 refers to the range formed by the outer peripheral surface of the roller 70 that forms the edge of the roller 70. Thus, the first main back-pressure groove 44 and the second main back-pressure groove 46 can be separated from the compression chambers V1, V2, and V3. However, if there is no additional sealing member between the bottom surface 41B of the main bearing 40 (refer to Figure 6 ) and the top surface of the roller 70, the first main back-pressure groove 44 and the second main back-pressure groove 46 may be slightly connected due to the gap between the two side surfaces. Refrigerant and oil can flow through this slight passage.

[0147] In the present embodiment, the main back-pressure grooves 44 and 46 are composed of a first main back-pressure groove 44 and a second main back-pressure groove 46. The first main back-pressure groove 44 and the second main back-pressure groove 46 can each have an arc shape that surrounds the rotation axis 30 with the rotation axis 30 as the center. The first main back-pressure groove 44 and the second main back-pressure groove 46 can overlap with a part of the blade grooves 73A, 73B, and 73C and the back-pressure chamber during the rotation of the roller 70 to provide back-pressure to the blades 75A, 75B, and 75C. The inner peripheral surfaces of the first main back-pressure groove 44 and the second main back-pressure groove 46 can each be formed in a circular shape, and the outer peripheral surfaces can be formed in an elliptical shape respectively considering the overlapping relationship with the blade grooves 73A, 73B, and 73C described later.

[0148] In the present embodiment, the first main back-pressure groove 44 can have a higher pressure than the second main back-pressure groove 46. For example, a discharge pressure is formed inside the first main back-pressure groove 44, or an intermediate pressure between the suction pressure and the discharge pressure close to the discharge pressure is formed. The oil transmitted to the main bearing 40 through the second oil through-hole 35b can flow into the first main back-pressure groove 44. The first main back-pressure groove 44 can be formed within the range of the compression chambers V1, V2, and V3 that form the discharge pressure in the compression space V. Thus, the first main back-pressure groove 44 maintains the discharge pressure.

[0149] The second main back-pressure groove 46 may have a pressure lower than that of the first main back-pressure groove 44. For example, an intermediate pressure between the suction pressure and the discharge pressure is formed inside the second main back-pressure groove 46. Refrigerant or oil may flow into the second main back-pressure groove 46 through a fine passage between the bottom surface of the main bearing 40 and the top surface of the roller 70. That is, the first main back-pressure groove 44 and the second main back-pressure groove 46 may be finely connected through a fine gap. In addition, the second main back-pressure groove 46 may be formed within the range of the compression chambers V1, V2, and V3 that form the intermediate pressure in the compression space V. Thus, the second main back-pressure groove 46 maintains the intermediate pressure.

[0150] A first oil drain portion 47 may be formed on the side surface of the main bearing 40. Here, the side surface of the main bearing 40 refers to the outer peripheral surface 43 of the main bearing 40. The first oil drain portion 47 may be formed by being recessed from the outer peripheral surface 43 of the main bearing 40. The first oil drain portion 47 widens the gap between the inner peripheral surface 11a of the main body housing 11 and the outer peripheral surface 43 of the main bearing 40, thereby ensuring a passage for recycling the oil back to the oil storage space RS. The first oil drain portion 47 is referred to as the main oil drain portion 47 to distinguish it from the first oil drain portion 57 formed on the sub-bearing 50. The detailed structure of the main oil drain portion 47 will be described again later.

[0151] Next, the sub-bearing 50 will be described. The sub-bearing 50 may be fixed to the inside of the main body housing 11 by means of the cylinder 60. The sub-bearing 50 may have a substantially circular plate shape similar to the main bearing 40. In this embodiment, the sub-bearing 50 (i) supports the rotating shaft 30 so that it can rotate, (ii) covers the lower part of the compression space V penetrating through the cylinder 60, and (iii) forms sub-back-pressure grooves 54 and 56 for providing back-pressure to the rear ends of the vanes 75A, 75B, and 75C.

[0152] The top surface of the sub-bearing 50 may be configured to face the bottom surface of the cylinder 60. The top surface of the sub-bearing 50 may constitute the bottom surface of the compression space V by covering the lower part of the compression space V penetrating through the cylinder 60. Sub-back-pressure grooves 54 and 56 for providing back-pressure to the rear ends of the vanes 75A, 75B, and 75C may be recessed in the top surface of the sub-bearing 50.

[0153] As Figure 6As shown, a sub-bushing portion 52' may be provided at the center of the sub-bearing 50. The sub-bushing portion 52' may be provided in a cylindrical shape at the central portion of the sub-bearing 50 and surround the rotating shaft 30. A second shaft support hole AH2 is formed at the center of the sub-bushing portion 52'. The sub-bushing portion 52' may, together with the main bushing portion 42', surround and fix the rotating shaft 30 at different heights so that it can rotate.

[0154] Referring to Figure 5 , sub-back pressure grooves 54, 56 are formed in the sub-bearing 50. The sub-back pressure grooves 54, 56 can increase the pressure of the back pressure chambers formed at one ends of the blade grooves 73A, 73B, 73C and provide back pressure to the blades 75A, 75B, 75C in the direction protruding from the blade grooves 73A, 73B, 73C. That is, the sub-back pressure grooves 54, 56 can provide back pressure to the blades 75A, 75B, 75C together with the main back pressure grooves 44, 46.

[0155] The sub-back pressure grooves 54, 56 may be composed of a plurality of sub-back pressure grooves 54, 56 separated in the circumferential direction of the sub-bearing 50, similarly to the main back pressure grooves 44, 46. The plurality of sub-back pressure grooves 54, 56 may have different internal pressures. Since the structure of the sub-back pressure grooves 54, 56 is symmetric with the structure of the aforementioned main back pressure grooves 44, 46, the detailed description of the structure of the sub-back pressure grooves 54, 56 is omitted.

[0156] In this embodiment, the first sub-back pressure groove 54 in the sub-back pressure grooves 54, 56 may have a higher pressure than the second sub-back pressure groove 56. For example, a discharge pressure is formed inside the first sub-back pressure groove 54, or an intermediate pressure between the suction pressure close to the discharge pressure and the discharge pressure is formed. The oil transmitted to the main bearing 40 through the second oil through-hole 35b may flow into the first sub-back pressure groove 54. The first sub-back pressure groove 54 may be formed within the range of the compression chambers V1, V2, V3 that form the discharge pressure in the compression space V. Thus, the first sub-back pressure groove 54 maintains the discharge pressure.

[0157] The second sub-back pressure groove 56 may have a pressure lower than that of the first sub-back pressure groove 54. For example, an intermediate pressure between the suction pressure and the discharge pressure is formed inside the second sub-back pressure groove 56. Oil may flow into the second sub-back pressure groove 56 through the fine passage between the second sub-bearing convex portion and the bottom surface of the roller 70. The second sub-back pressure groove 56 may be formed within the range of the compression chambers V1, V2, V3 that form the intermediate pressure in the compression space V. Thus, the second sub-back pressure groove 56 maintains the intermediate pressure.

[0158] The pressure of the first auxiliary back-pressure groove 54 can be transmitted to the second auxiliary back-pressure groove 56. Fluids such as refrigerant or oil can leak from the gap formed between the top surface of the auxiliary bearing 50 and the bottom surface of the roller 70. Therefore, the pressure of the second auxiliary back-pressure groove 56 can rise.

[0159] As another example, with the roller 70 as the center, the first auxiliary back-pressure groove 54 and the second auxiliary back-pressure groove 56 can be formed asymmetrically with respect to the first main back-pressure groove 44 and the second main back-pressure groove 46, respectively. For example, the first auxiliary back-pressure groove 54 and the second auxiliary back-pressure groove 56 can be formed to be longer in the circumferential direction than the first main back-pressure groove 44 and the second main back-pressure groove 46, respectively, or have a higher depression height in the vertical direction. Additionally, although not shown, the back-pressure grooves 44, 46, 54, 56 can also be formed only on either the main bearing 40 or the auxiliary bearing 50.

[0160] In the present embodiment, although the description is centered on the embodiment in which the discharge ports 42A, 42B are formed in the main bearing 40, as another example, the discharge ports 42A, 42B can be formed in the auxiliary bearing 50 instead of the main bearing 40, or can be formed in both the main bearing 40 and the auxiliary bearing 50, respectively. As still another example, the discharge ports 42A, 42B can also be formed through the side surface of the cylinder 60.

[0161] A first oil drain portion 57 can be formed on the side surface of the auxiliary bearing 50. Here, the side surface of the auxiliary bearing 50 refers to the outer peripheral surface 53 of the auxiliary bearing 50. The first oil drain portion 57 can be formed by being recessed from the outer peripheral surface 53 of the auxiliary bearing 50. The first oil drain portion 57 widens the interval between the inner peripheral surface 11a of the main body housing 11 and the outer peripheral surface 53 of the auxiliary bearing 50, thereby ensuring a passage for the oil to be recovered into the oil storage space RS again. Hereinafter, the first oil drain portion 57 will be referred to as the auxiliary oil drain portion 57 to distinguish it from the main oil drain portion 47 formed in the main bearing 40. The detailed structure of the auxiliary oil drain portion 57 will be described again later.

[0162] Next, the cylinder 60 will be described. The cylinder 60 can also be in close contact with the bottom surface of the main bearing 40 and, together with the auxiliary bearing 50, be fastened to the main bearing 40 by a fastening member B such as a bolt. At this time, since the cylinder 60 is fixed to the inner peripheral surface 11a of the main body housing 11 by means such as welding, the main bearing 40 and the auxiliary bearing 50 can be fixed to the housing 10 together by the cylinder 60.

[0163] A compression space V can be formed in the center of the cylinder 60 (refer to Figure 5)。The annular empty space formed in the central part of the cylinder 60 can form the compression space V. The upper and lower parts of the empty space can be shielded by the main bearing 40 and the sub-bearing 50 respectively, thereby forming the compression space V. The roller 70 can be rotatably arranged in the compression space V.

[0164] An intake port 62 can be formed in the cylinder 60. The intake port 62 can be formed to penetrate the cylinder 60 in the radial direction. The intake port 62 can serve as a supply path for the refrigerant to flow in. The intake port 62 can be connected to the aforementioned suction pipe IP (refer to Figure 1 ). As another example, the intake port 62 can also be formed to penetrate the main bearing 40 or the sub-bearing 50.

[0165] Refer to Figure 7 , the intake port 62 can be formed at a position circumferentially spaced apart from the contact point P. The contact point P refers to the position where the outer peripheral surface of the roller 70 and the inner peripheral surface 61c of the compression space V are in contact with each other. The aforementioned discharge ports 42A, 42B can be formed in the main bearing 40 on the side opposite to the intake port 62 in the circumferential direction with the contact point P as a reference.

[0166] Refer to Figure 8 , the inner peripheral surfaces 61c of the compression spaces V1, V2, V3, which are the empty spaces formed in the central part of the cylinder 60, can be elliptical in shape. The inner peripheral surface 61c of the cylinder 60 in this embodiment can be formed in an asymmetric elliptical shape by combining a plurality of ellipses, for example, four ellipses with different aspect ratios, to have two origins. As a reference, the inner peripheral surfaces 61c of the compression spaces V1, V2, V3 can also be regarded as the inner peripheral surface 61c of the cylinder 60.

[0167] The roller 70 is arranged in the compression space V. The roller 70 of this embodiment is rotatably provided in the compression space V of the cylinder 60, and a plurality of vanes 75A, 75B, 75C can be inserted into the roller 70 at intervals in the circumferential direction. Thus, in the compression space V, compression chambers V1, V2, V3 corresponding to the number of the plurality of vanes 75A, 75B, 75C can be divided. In this embodiment, an example in which the plurality of vanes 75A, 75B, 75C are composed of three and the compression space V is divided into three compression chambers V1, V2, V3 will be mainly described.

[0168] The roller 70 may be integrally provided with the rotating shaft 30 or may be separately manufactured and then assembled with the rotating shaft 30. In this embodiment, an example in which the roller 70 is assembled with the rotating shaft 30 later is taken as a reference for description. However, in the case where the roller 70 is integrally provided with the rotating shaft 30, the rotating shaft 30 and the roller 70 may also be formed similarly to this embodiment. However, as in this embodiment, in the case where the roller 70 is assembled with the rotating shaft 30 later, the roller 70 may be formed of a material different from that of the rotating shaft 30, for example, a lighter material than the rotating shaft 30. In this case, it is possible to facilitate the processing of the roller 70 and improve the compressor efficiency by reducing the weight of the rotating body including the roller 70.

[0169] Referring to Figure 5 and Figure 6 , in this embodiment, the rotating shaft 30 is coupled to the center of the roller 70, and the roller 70 rotates together with the rotating shaft 30. The roller 70 may divide the compression space V into a plurality of compression chambers V1, V2, and V3 as it rotates together with the rotating shaft 30, and sequentially compress and discharge the refrigerant flowing into each of the compression chambers V1, V2, and V3.

[0170] The rotation center of the roller 70 and the center of the rotating shaft 30, that is, the axis center are concentric. Thus, the roller 70 can rotate concentrically with the rotating shaft 30. The inner circumferential surface 61c of the cylinder 60 is formed as an asymmetric ellipse rather than a circle. The outer circumferential surface of the roller 70 may contact the inner circumferential surface 61c of the cylinder 60 at a single contact point P, and a compression space V is formed between the outer circumferential surface of the roller 70 and the inner circumferential surface 61c of the cylinder 60.

[0171] A plurality of vane grooves 73A, 73B, and 73C are formed in the roller 70. One ends of the vane grooves 73A, 73B, and 73C open toward the compression chambers V1, V2, and V3 to form openings, while the other ends are in a blocked state. A back pressure chamber may be formed at the blocked other ends of the vane grooves 73A, 73B, and 73C.

[0172] The vanes 75A, 75B, and 75C may be slidably inserted into the plurality of vane grooves 73A, 73B, and 73C, respectively. Here, the sliding direction in which the vanes 75A, 75B, and 75C are slidably coupled is a direction orthogonal to the axial direction and is a direction inclined with respect to the radial direction of the roller 70. The plurality of vane grooves 73A, 73B, and 73C may be spaced apart in the circumferential direction of the roller 70.

[0173] A plurality of the blade grooves 73A, 73B, 73C may include a first blade groove 73A, a second blade groove 73B, and a third blade groove 73C along the rotation direction of the roller 70 which is the compression proceeding direction. The first blade groove 73A, the second blade groove 73B, and the third blade groove 73C may each be spaced apart by the same interval or different intervals in the circumferential direction and formed in the same shape as each other.

[0174] At the innermost other ends of the blade grooves 73A, 73B, 73C, back pressure chambers (not assigned reference numerals) may be respectively formed. The back pressure chambers may be spaces for accommodating refrigerant or oil of discharge pressure or intermediate pressure on the rear side of the blades 75A, 75B, 75C, that is, on the rear end face sides of the blades 75A, 75B, 75C. By the pressure of the refrigerant or oil filled in the back pressure chambers, a plurality of the blades 75A, 75B, 75C may be pressurized against the inner peripheral surface 61c of the compression space V. Hereinafter, based on the movement direction of the blades 75A, 75B, 75C, the direction toward the inner peripheral surface 61c of the compression space V will be defined as the front, and the opposite side will be defined as the rear, and the description will be made.

[0175] The back pressure chambers may be formed such that the upper and lower portions are respectively shielded by the main bearing 40 and the sub-bearing 50. The back pressure chambers may be independently communicated with the respective back pressure grooves 44, 46, 54, 56, or may be communicated with each other through the back pressure grooves 44, 46, 54, 56.

[0176] Refer to Figure 5 , a plurality of the blades 75A, 75B, 75C of the present embodiment may be respectively slidably inserted into the blade grooves 73A, 73B, 73C. A plurality of the blades 75A, 75B, 75C may be respectively formed in substantially the same shape as the blade grooves 73A, 73B, 73C. In this way, the blades 75A, 75B, 75C may be stably introduced and withdrawn without shaking inside the blade grooves 73A, 73B, 73C.

[0177] A plurality of the blades 75A, 75B, 75C may be defined as a first blade 75A, a second blade 75B, and a third blade 75C along the rotation direction of the roller 70. The first blade 75A may be inserted into the first blade groove 73A, the second blade 75B may be inserted into the second blade groove 73B, and the third blade 75C may be inserted into the third blade groove 73C.

[0178] In the compressor of the present embodiment, if power is applied to the electric unit 20 through the cluster 15, the rotors 23, 25 and the rotating shaft 30 coupled to the rotors 23, 25 rotate. Accordingly, the rollers 70 coupled to the rotating shaft 30 or integrally formed with the rotating shaft 30 rotate together with the rotating shaft 30.

[0179] Due to the centrifugal force generated by the rotation of the rollers 70 and the back pressure of the back pressure chamber that supports the rear of the blades 75A, 75B, 75C, the plurality of blades 75A, 75B, 75C protrude from the blade grooves 73A, 73B, 73C respectively and contact the inner circumferential surface 61c of the compression space V. Accordingly, the compression space V is divided into a plurality of compression chambers V1, V2, V3 by the plurality of blades 75A, 75B, 75C, and when the divided compression chambers V1, V2, V3 move as the roller 70 rotates, the volumes of the compression chambers V1, V2, V3 can change. The refrigerant inhaled into each of the compression chambers V1, V2, V3 is repeatedly compressed as it moves with the roller 70 and the blades 75A, 75B, 75C, and is discharged into the internal space S of the housing 10. Therefore, the compression chambers V1, V2, V3 can include an inhalation chamber and a discharge chamber.

[0180] At this time, since the interval between the inner circumferential surface 61c of the compression space V and the outer circumferential surface of the roller 70 rapidly narrows as it approaches the contact point P (refer to Figure 7 ), the compressed refrigerant can be discharged through the first discharge port 42A and the second discharge port 42B that constitute the discharge port 42. Since the first discharge port 42A and the second discharge port 42B are arranged in the circumferential direction of the main bearing 40, the refrigerant can be discharged in sequence.

[0181] On the other hand, the discharge muffler 90 that constitutes the compression unit C will be described. The discharge muffler 90 can be arranged above the main bearing 40. The discharge muffler 90 can accommodate the discharge port 42 and the discharge valves 81, 82 between the top surface 41A of the main bearing 40.

[0182] When the discharge port 42 and the discharge muffler 90 are provided in the main bearing 40, the refrigerant compressed in the compression chambers V1, V2, V3 is discharged into the discharge space 91' (refer to Figure 1 ) of the discharge muffler 90 through the discharge port 42, and the discharged refrigerant is discharged into the internal space S of the housing 10 through a partition portion (not shown) between the inner circumferential surface of the discharge muffler 90 and the outer circumferential surface of the main bushing portion 42' of the main bearing 40. At this time, the pulsating pressure of the discharged refrigerant decreases in the discharge space 91'.

[0183] Reference Figure 5 and Figure 6 ,the discharge muffler 90 may include a muffler plate 91 in the shape of a circular plate and a muffler cover 92 provided on the upper portion of the muffler plate 91. The discharge space 91' may be formed inside the muffler cover 92.

[0184] A plurality of muffler fastening holes 93 may be formed in the muffler plate 91. The muffler fastening holes 93 penetrate along the axial direction. The muffler fastening holes 93 may be formed at positions corresponding to the main fastening hole 49, the cylinder fastening hole 69, and the sub-fastening hole 59. Thus, the fastening member B can sequentially pass through the muffler fastening holes 93, the main fastening hole 49, the cylinder fastening hole 69, and the sub-fastening hole 59, and fasten the discharge muffler 90, the main bearing 40, the cylinder 60, and the sub-bearing 50 to each other.

[0185] A muffler recess 95 avoiding the muffler fastening holes 93 may be formed in the muffler cover 92. The muffler recess 95 is recessed radially inward toward the center of the discharge muffler 90. The muffler recess 95 may provide an empty space so that a tool can enter the muffler fastening holes 93. For this purpose, the muffler recess 95 may have a structure extending along the axial direction.

[0186] Reference Figure 3 ,the edge of the muffler plate 91 may correspond to the top surface of the main bearing 40. In this embodiment, although the main oil discharge portion 47 is formed in the main bearing 40, since the top surface of the main bearing 40 has a sufficiently large area, the muffler plate 91 can be placed on the top surface of the main bearing 40. That is, in this embodiment, a part of the top surface of the main bearing 40 does not recess radially inward to form the main oil discharge portion 47, and the top surface of the main bearing 40 maintains a perfect circular shape, so the muffler plate 91 can also be formed in a perfect circular shape. Thus, there is no need to complexly form the shape of the discharge muffler 90 in order to mount the discharge muffler 90 on the top surface of the main bearing 40.

[0187] Figure 9 of (a) to Figure 9 of (d) are cross-sectional views showing the process of sucking, compressing, and discharging the refrigerant in the cylinder 60 constituting this embodiment. In Figure 9 of (a) to Figure 9 of (d), the sub-back pressure grooves 54, 56 of the sub-bearing 50 are shown in a projected state, and the main bearing 40 not shown is the same as the sub-bearing 50. In the drawings, the refrigerant is represented by different materials.

[0188] AsFigure 9 As shown in (a) of Figure 9 , the refrigerant can flow in through the suction port 62. The refrigerant that flows in can be stored between two blades 75A and 75B that are different from each other. In

[0189] this state, if the roller 70 rotates, then as shown in (b) of Figure 9 , before the second blade 75B reaches the suction completion time point, the volume of the first compression chamber V1 continuously increases through the suction port 62, and the refrigerant can continuously flow into the first compression chamber V1 from the suction port 62.

[0190] The rear of the first blade 75A is exposed to the second sub-back pressure groove 56 among the sub-back pressure grooves 54 and 56, so that the first blade 75A is applied with a back pressure of intermediate pressure. In addition, the rear of the third blade 75C is exposed to the first sub-back pressure groove 54 among the sub-back pressure grooves 54 and 56, so that the third blade 75C is applied with a back pressure of discharge pressure or a pressure close to the discharge pressure (hereinafter, referred to as "discharge pressure"). Thus, the first blade 75A can closely adhere to the inner peripheral surface 61c of the cylinder 60 with intermediate pressure, and the third blade 75C can closely adhere to the inner peripheral surface 61c of the cylinder 60 with discharge pressure.

[0191] If the second blade 75B passes through the suction completion time point (or compression start time point) and performs a compression stroke, the first compression chamber V1 becomes a sealed state and moves together with the roller 70 toward the discharge port 42. During this process, the volume of the first compression chamber V1 continuously decreases, and the refrigerant in the first compression chamber V1 can be gradually compressed.

[0192] At this time, if the refrigerant pressure in the first compression chamber V1 rises, the first blade 75A may be pushed toward the rear of the first blade groove 73A. In this way, the first compression chamber V1 may communicate with the preceding third compression chamber V3, resulting in refrigerant leakage. In particular, at the initial stage of driving the compressor, before the back pressure in the second sub-back pressure groove 56 (or the second main back pressure groove 46) is sufficiently high, the first blade 75A is easily pushed backward, resulting in such leakage, and jitter may occur during this process. In this embodiment, in order to prevent this phenomenon, the pressure transmission path is realized, and the detailed structure of the pressure transmission path will be described again later.

[0193] On the other hand, referring to (b) of Figure 9 and Figure 9In (c), if the first vane 75A disengages from the second sub-back pressure groove 56 and enters the first sub-back pressure groove 54, the first vane 75A can change from the back pressure of the intermediate pressure to the back pressure to which the discharge pressure is applied. Thus, the first vane 75A can be prevented from being pushed backward by increasing the back pressure applied to the first vane 75A.

[0194] As Figure 9 shown in (c), if the first vane 75A passes through the first discharge port 42A ( Figure 9 not shown in the figure), and the second vane 75B reaches the first discharge port 42A, the first compression chamber V1 communicates with the first discharge port 42A, and the first discharge port 42A is opened by the pressure of the first compression chamber V1. Therefore, a part of the refrigerant in the first compression chamber V1 is discharged into the internal space S of the housing 10 through the first discharge port 42A, and the pressure of the first compression chamber V1 drops to a specified pressure. As another example, in the absence of the first discharge port 42A, the first compression chamber V1 does not discharge the refrigerant, and the refrigerant can be concentrated in the second discharge port 42B which is the main discharge port 42.

[0195] At this time, the volume of the first compression chamber V1 further decreases, so that the refrigerant in the first compression chamber V1 is further compressed. Since the first vane groove 73A accommodating the first vane 75A is in a state of being completely communicated with the first back pressure chamber 74A and the first sub-back pressure groove 54, the first vane 75A is applied with a back pressure almost close to the discharge pressure. Thus, the first vane 75A is prevented from being pushed backward, that is, in the direction away from the inner peripheral surface 61c of the cylinder 60, so that the refrigerant does not leak between the compression chambers V1, V2, and V3.

[0196] As Figure 9 shown in (d), if the first vane 75A passes through the contact point P, the above-described process can be repeated and the refrigerant can be continuously compressed. Although Figure 9 only the process of compressing the refrigerant in the first compression chamber V1 is shown to assist understanding, the second compression chamber V2 and the third compression chamber V3 can also continuously compress the refrigerant following the first compression chamber V1. Therefore, the compressor of the present embodiment can continuously compress and discharge the refrigerant by using a plurality of compression chambers V1, V2, and V3.

[0197] As described above, during the process of compressing the refrigerant, oil is supplied to the compression part C, so that the movement and rotation between components can proceed smoothly. In addition, as Figure 10 shown, the oil can be recycled to the oil storage space RS through the oil discharge path OP. Hereinafter, the oil discharge path OP will be described in detail.

[0198] The oil drainage path OP can provide an axial path to the compression part C. The oil drainage path OP is a passage extending axially along the edge of the compression part C. Refer to Figure 2 , the upper end of the oil drainage path OP opens towards the internal space S of the housing 10, and the lower end of the oil drainage path OP opens towards the oil storage space RS. Thus, the oil flowing in through the upper end of the oil drainage path OP can be discharged from the lower end of the oil drainage path OP and recovered into the oil storage space RS. Here, recovery means that the oil existing in the internal space S of the housing 10 moves due to gravity and accumulates again in the oil storage space RS.

[0199] The oil drainage path OP may include first oil drainage parts 47, 57 and a second oil drainage part 67. The first oil drainage parts 47, 57 and the second oil drainage part 67 may form different axial heights in the compression part C. The first oil drainage parts 47, 57 and the second oil drainage part 67 are axially connected to each other. The first oil drainage parts 47, 57 may be provided on either the main bearing 40 (or the sub-bearing 50) or the cylinder 60, and the second oil drainage part 67 may be provided on the remaining one. In this embodiment, the first oil drainage parts 47, 57 are provided on the main bearing 40 and the sub-bearing 50, and the second oil drainage part 67 is provided on the cylinder 60.

[0200] As described above, the outer diameter CW of the cylinder 60 (refer to Figure 2 ) is larger than the outer diameters of the main bearing 40 and the sub-bearing 50 BW (refer to Figure 2 ). Therefore, the outer peripheral surface 43 of the main bearing 40 with a relatively smaller diameter among the main bearing 40 and the cylinder 60 may be provided with the first oil drainage parts 47, 57. The outer peripheral surface 63 of the cylinder 60 with a relatively larger diameter among the main bearing 40 and the cylinder 60 may be provided with the second oil drainage part 67. Moreover, the first oil drainage parts 47, 57 and the second oil drainage part 67 are axially connected to each other, thereby forming an oil drainage flow path OP.

[0201] As described above, the first oil drainage parts 47, 57 may include a main oil drainage part 47 formed on the main bearing 40 and a sub-oil drainage part 57 formed on the sub-bearing 50. Since the main oil drainage part 47 and the sub-oil drainage part 57 have symmetrical structures with each other, the description will be made with the main oil drainage part 47 as the center.

[0202] The main oil drain portion 47 may be recessed radially inward from the outer peripheral surface 43 of the main bearing 40. Here, the radial direction refers to the direction connecting the central portion of the main bearing 40 and the outer peripheral surface 43 of the main bearing 40. The central portion of the main bearing 40 may also be regarded as the center of the rotating shaft 30. If the main oil drain portion 47 is recessed from the outer peripheral surface 43 of the main bearing 40, the radius of the portion of the main bearing 40 where the main oil drain portion 47 is formed may be smaller than the radii of other portions.

[0203] As Figure 5 and Figure 6 shown, the main oil drain portion 47 may be recessed from the outer peripheral surface 43 of the main bearing 40 and formed along the circumferential direction on the outer peripheral surface 43 of the main bearing 40. The main oil drain portion 47 may be formed at positions corresponding axially to the second oil drain portion 67 and the sub oil drain portion 57 arranged below, respectively.

[0204] A rim portion 48 may be provided on the upper part of the main oil drain portion 47. The rim portion 48 is provided on the outer peripheral surface 43 of the main bearing 40. The rim portion 48 is in a ring shape along the edge of the main bearing 40. As the main oil drain portion 47 is recessed from the outer peripheral surface 43 of the main bearing 40, the rim portion 48 may be regarded as a portion protruding relatively radially outward from the outer peripheral surface 43 of the main bearing 40. Hereinafter, the rim portion 48 will be referred to as the main rim portion 48 to distinguish it from the sub rim portion 58 formed on the sub bearing 50.

[0205] As Figure 7 shown, when projected onto a plane, the main rim portion 48 may block a part or all of the second oil drain portion 67. Here, blocking means that the main rim portion 48 overlaps the second oil drain portion 67 axially, so that when observing the compression portion C from top to bottom, a part or all of the second oil drain portion 67 cannot be seen. Refer to Figure 7 and Figure 10 , the main rim portion 48 blocks a part of the second oil drain portion 67, and only the remaining part of the second oil drain portion 67 is exposed.

[0206] Refer to the enlarged view of A1 as Figure 7 and Figure 10, the main edge portion 48 shields the second oil drainage portion 67, so that only a part of the second oil drainage portion 67 is exposed. The radial width of the exposed second oil drainage portion 67 is marked as D1. Since the second oil drainage portion 67 has a greater width in the radial direction than the outer peripheral surface of the main edge portion 48, a part of the second oil drainage portion 67 does not overlap with the main edge portion 48. This non-overlapping part between the main edge portion 48 and the second oil drainage portion 67 becomes a part where the oil in the passage can fall. As will be described later, the main oil drainage portion 47 has a planar or curved surface shape that is continuous with the second oil drainage portion 67 and the sub-oil drainage portion 57. Therefore Figure 7 The portion indicated by the dashed line in

[0207] Figure 8 and Figure 11 illustrates the state of removing the sub-bearing 50 and observing the compression portion C from below. As shown, since it is observed from below the cylinder 60, the second oil drainage portion 67 is completely exposed. However, the main edge portion 48 that overlaps the upper part of the second oil drainage portion 67 shields the second oil drainage portion 67 on the opposite side.

[0208] As described above, in the present embodiment, a part of the region of the second oil drainage portion 67 overlaps with the main bearing 40 in the axial direction, but the oil can flow smoothly due to the first oil drainage portions 47 and 57. That is, the first oil drainage portions 47 and 57 are formed along the radial direction orthogonal to the axial direction, so that a relatively wide oil recovery passage can be provided.

[0209] If the difference between the outer diameter of the cylinder 60 and the outer diameter of the main bearing 40 is large, there may be no interference between the main edge portion 48 and the second oil drainage portion 67. Refer to Figure 2 , in the present embodiment, the ratio (BW / CW) of the size BW of the outer diameter of the main bearing 40 to the size CW of the outer diameter of the cylinder 60 (which is also the inner diameter of the housing 10) is greater than 0.8. In addition, the difference (CW - BW) between the size of the outer diameter of the cylinder 60 (which is also the inner diameter of the housing 10) and the size of the outer diameter of the main bearing 40 is less than 10 mm. In this way, the second oil drainage portion 67 is shielded by the main edge portion 48 in the axial direction, and the necessity of forming the oil drainage path OP through the structures of the first oil drainage portions 47 and 57 and the second oil drainage portion 67 becomes higher.

[0210] Next, refer to Figure 12, the main oil discharge portion 47, the second oil discharge portion 67, and the sub oil discharge portion 57 are arranged axially along the edge portion of the compression portion C. The main oil discharge portion 47, the second oil discharge portion 67, and the sub oil discharge portion 57 may be formed along the circumferential direction of the compression portion C and arranged at corresponding positions to form a continuous path.

[0211] Refer to Figure 12 the enlarged Figure 13 A3 portion of Figure 13 . The inner peripheral surface 11a of the main body housing 11 is indicated by a dotted line. The first oil discharge portions 47, 57 are recessed radially (to the right in the drawing) from the inner peripheral surface 11a of the main body housing 11. That is, the main oil discharge portion 47 is recessed in a direction away from the inner peripheral surface 11a of the main body housing 11. Thus, a relatively wide axial passage (refer to Figure 13 P2) can be ensured between the main oil discharge portion 47 and the inner peripheral surface 11a of the main body housing 11.

[0212] Moreover, the second passage P2 formed by the first oil discharge portions 47, 57 is axially connected to the first passage ( Figure 13 P1) formed above the main oil discharge portion 47. Therefore, the first passage P1 formed between the main edge portion 48 and the inner peripheral surface 11a of the main body housing 11 at the uppermost part of the compression portion C is connected to the third passage P3 formed by the second oil discharge portion 67 via the second passage P2. As a result, while maintaining the entire upper area formed by the top surface 41A of the main bearing 40 and the radius of the main edge portion 48, a relatively recessed-shaped main oil discharge portion 47 can be realized.

[0213] In the present embodiment, the top surface of the main edge portion 48 is formed in a circular shape. The top surface of the main edge portion 48 constitutes the edge in the top surface of the main bearing 40, and the main edge portion 48 is circular in the top surface of the main bearing 40. The discharge muffler 90 may be disposed on the top surface of the main edge portion 48. If the main edge portion 48 is a perfect circle, it can correspond to the edge of the muffler plate 91. Thus, even without changing the shape of the discharge muffler 90, the installation area of the discharge muffler 90 can be formed relatively wide due to the top surface of the main edge portion 48.

[0214] The main oil discharge portion 47 may extend from a position axially downwardly spaced from the upper end of the outer peripheral surface 43 of the main bearing 40 to the lower end of the outer peripheral surface 43 of the main bearing 40. The main edge portion 48 may be provided from the upper end of the outer peripheral surface 43 of the main bearing 40 to a position axially downwardly spaced, and the main oil discharge portion 47 may be formed from the axially lower end of the main edge portion 48 to the axially lower end of the main bearing 40. That is, it can be regarded that the lower end of the main oil discharge portion 47 is open to the second oil discharge portion 67.

[0215] Reference Figure 13 and Figure 14 wherein the main oil drainage part 47 includes a main outer peripheral surface 47a constituting the outer peripheral surface 43 of the main bearing 40, a main upper surface 47b constituting the top surface of the main oil drainage part 47, and main side surfaces 47c1, 47c2 constituting the side surfaces of the main oil drainage part 47. The main upper surface 47b may be connected to the axially upper end of the main outer peripheral surface 47a. The main side surfaces 47c1, 47c2 may be connected to the circumferentially both ends of the main outer peripheral surface 47a. Thus, the main oil drainage part 47 may have a structure in which the upper end part and both side end parts are respectively surrounded by the main upper surface 47b and the main side surfaces 47c1, 47c2. In addition, the axially lower end of the main oil drainage part 47 may be connected to the second oil drainage part 67.

[0216] At this time, as will be described later, the surfaces of the first oil drainage parts 47, 57 may form a continuous flat surface or curved surface with the surface of the second oil drainage part 67. More precisely, the main outer peripheral surface 47a may form a continuous flat surface or curved surface with the first discharge inner surface 67a of the second oil drainage part 67. The main side surfaces 47c1, 47c2 may form a continuous flat surface or curved surface with the connection inner surfaces 67c1, 67c2 of the second oil drainage part 67. Thus, oil may flow smoothly along the surfaces of the first oil drainage parts 47, 57 and the surface of the second oil drainage part 67, and oil recovery may be effectively formed.

[0217] In addition, the first discharge inner surface 67a may form a continuous flat surface or curved surface with the sub-outer peripheral surface 57a of the sub-oil drainage part 57. The connection inner surfaces 67c1, 67c2 of the second oil drainage part 67 may form a continuous flat surface or curved surface with the sub-side surfaces 57c1, 57c2 of the sub-oil drainage part 57. As a result, the main outer peripheral surface 47a, the first discharge inner surface 67a, and the sub-outer peripheral surface 57a may form a continuous flat surface or curved surface along the axial direction. The main side surfaces 47c1, 47c2, the connection inner surfaces 67c1, 67c2, and the sub-side surfaces 57c1, 57c2 may also form a continuous flat surface or curved surface along the axial direction. This structure will be described again later.

[0218] The main oil drainage part 47 may be formed along the circumferential direction of the main bearing 40. In the present embodiment, a plurality of the main oil drainage parts 47 are arranged at intervals from each other along the circumferential direction of the main bearing 40. In this way, oil may be recovered at a plurality of positions of the main bearing 40, that is, positions having various phase differences.

[0219] At this time, the first oil drainage parts 47, 57 may be formed between the main fastening holes 49. Reference Figure 7 , Figure 7In the state where the fastening member B is fastened, the main fastening hole 49 is thus blocked. Between the imaginary extension lines T1 and T2 that respectively connect the centers of two adjacent fastening members B among the plurality of fastening members B and the center of the rotating shaft 30, the main oil discharge portion 47 may be formed. Further, between the imaginary extension lines T1 and T2 that respectively connect the centers of two adjacent fastening members B among the plurality of fastening members B and the center of the rotating shaft 30, the sub oil discharge portion 57 and the second oil discharge portion 67 may also be formed.

[0220] In this way, the oil discharge path OP does not interfere with the main fastening hole 49 for fastening the fastening member B, the cylinder fastening hole 69, and the sub fastening hole 59. As described above, if the oil discharge path OP does not interfere with the fastening holes 49, 59, and 69 with each other, the fastening holes 49, 59, and 69 can be arranged at positions close to the edge of the compression portion C. Since the fastening holes 49, 59, and 69 need to avoid interference with the compression space V, the closer the fastening holes 49, 59, and 69 are arranged to the edge side, the wider the compression space V can be ensured. Therefore, this embodiment can not only ensure a wide compression space V but also improve the compression capacity of the compressor.

[0221] Refer to Figure 7 , the centers of the plurality of main fastening holes 49 may be formed between the compression space V and the main oil discharge portion 47. Although not shown, the centers of the plurality of cylinder fastening holes 69 may be formed between the compression space V and the second oil discharge portion 67. Further, although not shown, the centers of the plurality of sub fastening holes 59 may be formed between the compression space V and the sub oil discharge portion 57. In this embodiment, since the main fastening hole 49, the cylinder fastening hole 69, and the sub fastening hole 59 are arranged close to the edge of the compression portion C, the compression space V can be formed relatively wider accordingly.

[0222] On the other hand, a flange portion 48 that protrudes more toward the inner peripheral surface 11a of the housing 10 than the first oil discharge portions 47 and 57 may be formed on the upper portion of the first oil discharge portion 47. In this embodiment, the axial height of the first oil discharge portion 47 may be lower than or equal to the axial height of the flange portion 48. In this way, it is possible to prevent a decrease in the overall strength of the main bearing 40 caused by the recessed main oil discharge portion 47.

[0223] The first oil discharge portions 47 and 57 may have the same cross-sectional shape in the axial direction. Refer to Figure 5 and Figure 6, the main oil drain portion 47 may have the same shape in the axial direction. More precisely, the main oil drain portion 47 may be substantially in an elliptical shape extending in the circumferential direction. If so, and the main oil drain portion 47 has the same cross-sectional shape in the axial direction, a constant passage without obstacles (steps) can be formed along the oil recovery path, thereby enabling smooth oil recovery. In addition, if the main oil drain portion 47 has the same cross-sectional shape in the axial direction, the workability for machining the main oil drain portion 47 can also be improved.

[0224] Next, the second oil drain portion 67 will be described. The second oil drain portion 67 may be formed to axially penetrate the other one of the main bearing and the cylinder block having a relatively larger diameter. In this embodiment, since the outer diameter CW of the cylinder block 60 is larger than the outer diameter BW of the main bearing 40 and the sub-bearing 50, the second oil drain portion 67 may be formed to axially penetrate the cylinder block 60.

[0225] As described above, in this embodiment, the second oil drain portion 67 may axially overlap with the main edge portion 48, so that a part thereof is blocked. However, since the main oil drain portion 47 is recessed radially inward of the main bearing 40, the portion where the main oil drain portion 47 and the second oil drain portion 67 are connected may be formed wide enough.

[0226] Refer to Figure 14 , since the second oil drain portion 67 penetrates the cylinder block 60, the second oil drain portion 67 does not expose to the side or the front of the compression portion C. However, the main oil drain portion 47 and the sub-oil drain portion 57 are respectively disposed at the upper and lower portions of the second oil drain portion 67, so that they can expose to the upper and lower portions of the compression portion C.

[0227] Refer to Figure 15 , the second oil drain portion 67 is shown by a dashed line. The upper end portion of the second oil drain portion 67 may be connected to the main oil drain portion 47. The lower end portion of the second oil drain portion 67 may be connected to the sub-oil drain portion 57. Thus, the oil drain path OP continuous with the main oil drain portion 47, the second oil drain portion 67, and the sub-oil drain portion 57 can be formed.

[0228] When observing from the front direction (radial direction) with Figure 15 as a reference, the first oil drain portions 47, 57 and the second oil drain portion 67 may be substantially in a quadrilateral shape. This is because the first oil drain portions 47, 57 and the second oil drain portion 67 have the same width in the circumferential direction of the compression portion C. In this way, obstacles or steps that impede the flow of oil can be eliminated on both sides of the oil drain path OP.

[0229] Refer to Figure 13 and Figure 15The structure of the second oil drainage part 67 will be described. The second oil drainage part 67 is formed by axially penetrating the cylinder barrel 60 along the edge of the cylinder barrel 60. The upper and lower parts of the second oil drainage part 67 are open based on the axial direction. More precisely, the upper part of the second oil drainage part 67 is open to the main oil drainage part 47, and the lower part of the second oil drainage part 67 is open to the sub-oil drainage part 57. In other words, the upper part of the second oil drainage part 67 is open towards the upper part of the internal space S, and the lower part of the second oil drainage part 67 is open towards the oil storage space RS.

[0230] Referring to Figure 13 , in the second oil drainage part 67, a first discharge inner surface 67a that forms the inner surface of the second oil drainage part 67 is included. A second discharge inner surface 67b spaced apart from the first discharge inner surface 67a is formed in the second oil drainage part 67. The second discharge inner surface 67b is formed at a position relatively closer to the inner peripheral surface 11a of the main body housing 11 than the first discharge inner surface 67a. Therefore, the first discharge inner surface 67a and the second discharge inner surface 67b can face each other based on the radial direction of the cylinder barrel 60. A third passage P3 can be formed between the first discharge inner surface 67a and the second discharge inner surface 67b.

[0231] Referring to Figure 11 and Figure 15 , connection inner surfaces 67c1 and 67c2 can be respectively formed at both ends of the second oil drainage part 67. A pair of the connection inner surfaces 67c1 and 67c2 can connect the first discharge inner surface 67a and the second discharge inner surface 67b. In this embodiment, a pair of the connection inner surfaces 67c1 and 67c2 are curved surfaces. Thus, no sharp edges will be formed between the connection inner surfaces 67c1 and 67c2 and the first discharge inner surface 67a and the second discharge inner surface 67b, and a curved surface can be formed through which oil can flow relatively smoothly.

[0232] The first discharge inner surface 67a, the second discharge inner surface 67b, and a pair of connection inner surfaces 67c1 and 67c2 are connected to each other. Thus, the first discharge inner surface 67a, the second discharge inner surface 67b, and a pair of connection inner surfaces 67c1 and 67c2 can form a structure that surrounds the part except for the upper and lower parts of the second oil drainage part 67.

[0233] As described above, the first discharge inner surface 67a can form a continuous flat surface or curved surface with the first oil drainage parts 47 and 57. Referring to Figure 13, the main outer peripheral surface 47a of the main oil discharge portion 47 disposed at the upper part can form a continuous plane or curved surface with the first discharge inner surface 67a disposed at the lower part. In addition, the sub-outer peripheral surface 57a disposed at the lower part of the first discharge inner surface 67a can also form a continuous plane or curved surface with the first discharge inner surface 67a.

[0234] Refer to Figure 8 , the second oil discharge portion 67 can be formed between the cylinder barrel fastening holes 69. Between two adjacent fastening bodies B in the fastening body B fastened to a plurality of the cylinder barrel fastening holes 69, the second oil discharge portion 67 can be formed. In this way, the oil discharge path OP does not interfere with the main fastening hole 49, the cylinder barrel fastening hole 69, and the sub-fastening hole 59 for fastening the fastening body B. Since this structure is the same as the aforementioned main oil discharge portion 47, detailed description thereof is omitted.

[0235] Refer to the Figure 13 partially enlarged Figure 16 , the radial width of the passage formed between the inner peripheral surface 11a of the housing 10 and the first oil discharge portions 47 and 57 can be larger than the radial width of the second oil discharge portion 67. More precisely, the radial distance W1a between the inner peripheral surface 11a of the main body housing 11 and the main outer peripheral surface 47a of the main oil discharge portion 47 is larger than the radial width W2 of the second oil discharge portion 67. Thereby, it is ensured that the main oil discharge portion 47 forms a wide second passage P2 (refer to Figure 13 ), so that even if a large amount of oil passes through the second passage P2, it is possible to prevent a bottleneck phenomenon from occurring in the second passage P2.

[0236] Refer to the Figure 11 as a top view, the radial distance between the main edge portion 48 and the inner peripheral surface 11a of the main body housing 11 is represented by L1. The radial distance between the surfaces of the first oil discharge portions 47 and 57 and the inner peripheral surface 11a of the main body housing 11 is represented by L2. The radial distance between the second discharge inner surface 67b and the inner peripheral surface 11a of the main body housing 11 is represented by L3. For reference, the surface of the first oil discharge portions 47 and 57 refers to the main outer peripheral surface 47a, and the L2 is the same as Figure 16 the W1a of

[0237] At this time, the dimensional relationship among L1, L2, and L3 may be L3 < L1 < L2. In this way, (i) the entire lower end portion of the first passage P1 formed between the main edge portion 48 and the inner peripheral surface 11a of the main body housing 11 can be completely included in the upper end portion of the second passage P2 formed between the main outer peripheral surface 47a and the inner peripheral surface 11a of the main body housing 11, and (ii) at least a part of the upper end portion of the third passage P3 formed by the second oil discharge portion 67 can overlap and connect with the lower end portion of the second passage P2. Therefore, the oil discharge path OP can form a continuous passage.

[0238] On the other hand, in Figure 11 the radial distance between the first discharge inner surface 67a and the inner peripheral surface 11a of the housing 10 is represented by L4, and the radial distance L4 between the first discharge inner surface 67a and the inner peripheral surface 11a of the housing 10 is the same as the radial distance L2 between the main outer peripheral surface 47a and the inner peripheral surface 11a of the main body housing 11. Therefore, the magnitude relationship among L1, L2, L3, and L4 may be L3 < L1 < L2 = L4. Thus, the entire upper end portion of the third passage P3 can be completely included in the lower end portion of the second passage P2, and a relatively wide connection space can be formed between the second passage P2 and the third passage P3.

[0239] Referring to Figure 17 the sub-oil discharge portion 57 is illustrated. The sub-oil discharge portion 57 may be recessed from the outer peripheral surface 53 of the sub-bearing 50 toward the radial inner side of the sub-bearing 50. In this embodiment, the sub-oil discharge portion 57 has a structure symmetric to the main oil discharge portion 47. Therefore, the sub-oil discharge portion 57 will be described with reference to the structure of the main oil discharge portion 47 for the parts different from the main oil discharge portion 47.

[0240] The sub-oil discharge portion 57 is connected to the second oil discharge portion 67. Therefore, the main oil discharge portion 47 and the sub-oil discharge portion 57 can form the oil discharge path OP via the second oil discharge portion 67. Although Figure 17 only the open state of the sub-oil discharge portion 57 is shown, the second oil discharge portion 67 is continuously formed toward the upper side of the sub-oil discharge portion 57.

[0241] The sub-oil discharge portion 57 may extend from a position axially upwardly spaced from the lower end of the outer peripheral surface 53 of the sub-bearing 50 to the upper end of the outer peripheral surface 53 of the sub-bearing 50. The sub-edge portion 58 is provided from the lower end of the outer peripheral surface 53 of the sub-bearing 50 to a position axially upwardly spaced, and the sub-oil discharge portion 57 may be formed from the upper end in the axial direction of the sub-edge portion 58 to the upper end in the axial direction of the sub-bearing 50. That is, it can be regarded that the upper end of the sub-oil discharge portion 57 is open toward the second oil discharge portion 67.

[0242] Reference Figure 13 A fourth passage P4 formed by the auxiliary bearing 50 may be formed between the auxiliary oil drain portion 57 and the inner peripheral surface 11a of the main body housing 11. The fourth passage P4 is axially connected to a fifth passage P5 formed at the lower portion of the auxiliary oil drain portion 57. Accordingly, the second oil drain portion 67 may be connected to the fifth passage P5 forming an outlet of the oil drain path OP via the fourth passage P4 formed between the auxiliary oil drain portion 57 and the inner peripheral surface 11a of the main body housing 11. As a result, while maintaining the entire area formed by the bottom surface of the auxiliary bearing 50 and the radius of the auxiliary flange portion 58, the auxiliary oil drain portion 57 having a relatively recessed shape can be realized.

[0243] Reference Figure 13 and Figure 15 The auxiliary oil drain portion 57 includes an auxiliary outer peripheral surface 57a constituting the outer peripheral surface 53 of the auxiliary bearing 50, an auxiliary lower surface 57b constituting the bottom surface of the auxiliary oil drain portion 57, and auxiliary side surfaces 57c1, 57c2 constituting the side surfaces of the auxiliary oil drain portion 57. The auxiliary lower surface 57b may be connected to the axially lower end portion of the auxiliary outer peripheral surface 57a. The auxiliary side surfaces 57c1, 57c2 may be connected to the circumferentially both end portions of the auxiliary outer peripheral surface 57a. Accordingly, the auxiliary oil drain portion 57 may have a structure in which the lower end portion and both side end portions are respectively surrounded by the auxiliary lower surface 57b and the auxiliary side surfaces 57c1, 57c2. Also, the axially upper end portion of the auxiliary oil drain portion 57 may be connected to the lower end portion of the second oil drain portion 67.

[0244] Reference Figure 17 The auxiliary oil drain portion 57 may be formed between the auxiliary fastening holes 59. The auxiliary oil drain portion 57 may be formed between two adjacent auxiliary fastening holes 59 among the plurality of auxiliary fastening holes 59. In this way, the oil drain path OP does not interfere with the main fastening hole 49, the cylinder fastening hole 69, and the auxiliary fastening hole 59 for fastening the fastening body B. This structure is the same as the foregoing main oil drain portion 47 and the second oil drain portion 67, and thus a detailed description thereof is omitted.

[0245] Reference Figure 18 Plural oil drain paths OP are illustrated. Figure 18 A first oil drain path OP1 and a second oil drain path OP2 among the plural oil drain paths OP are illustrated in Figure 18 . The first oil drain path OP1 and the second oil drain path OP2 may be separated from each other and form independent paths. A separating table 43A may be provided between the plural main oil drain portions 47 of the main bearing 40 to separate the main oil drain portions 47 from each other. Similarly, separating portions connected to the separating table 43A may be respectively formed on the outer peripheral surface 63 of the cylinder 60 and the outer peripheral surface 53 of the auxiliary bearing 50.

[0246] A plurality of such oil drainage paths OP1 and OP2 can be arranged along the circumferential direction of the compression part C. More precisely, a plurality of the oil drainage paths OP1 and OP2 can be respectively arranged between a plurality of the fastening bodies B. In this way, oil can be recovered at a plurality of positions of the compression part C.

[0247] Refer to Figure 20 and Figure 21 , and the path of recovering oil through the oil drainage path OP formed in the compression part C is indicated by an arrow. As shown in the figure, the oil flowing along the top surface of the main bearing 40 constituting the compression part C, or Figure 20 the surface of the discharge muffler 90 omitted in and the inner peripheral surface 11a of the main body housing 11 can flow into the space between the inner peripheral surface 11a of the main body housing 11 and the outer peripheral surface 43 of the main bearing 40. And the oil can flow into the oil drainage path OP through the main oil drainage part 47 recessed from the outer peripheral surface 43 of the main bearing 40. Therefore, the main oil drainage part 47 can also be regarded as the entrance of the path for recovering oil.

[0248] Refer to Figure 21 , and the oil can flow along the surface of the main edge part 48 provided on the upper part of the main oil drainage part 47. In addition, the oil gathered in the space formed by the outer peripheral surface 43 of the main bearing 40, the top surface of the cylinder barrel 60, and the inner peripheral surface 11a of the main body housing 11 can also flow into the main oil drainage part 47 during the movement along the circumferential direction of the cylinder barrel 60.

[0249] The oil flowing into the main oil drainage part 47 in this way can move downward along the oil drainage path OP. Figure 20 The reference numeral PL in represents the surface where the main oil drainage part 47 is in close contact with the second oil drainage part 67. If the main oil drainage part 47 and the second oil drainage part 67 are in close contact with each other, a continuous oil drainage path OP is formed. As described above, since the first oil drainage parts 47 and 57 and the second oil drainage part 67 can form a continuous plane or curved surface, the oil can flow smoothly without stagnating due to a stepped structure.

[0250] On the other hand, the oil drainage path OP can include a first path formed between the outer peripheral surface 43 of the main bearing 40 and the inner peripheral surface 11a of the housing 10. The first path can be connected to a second path formed axially through the cylinder barrel 60. A third path can be formed between the outer peripheral surface 53 of the sub-bearing 50 and the inner peripheral surface 11a of the housing 10. The third path can be connected to the second path and open to the oil storage space RS. At this time, the first path and the second path can be axially connected, and the second path and the third path can also be axially connected.

[0251] At this time, at least one of the first path and the third path may be formed by axially connecting portions having different radial widths of the radial width of the compression portion C. Refer to Figure 13 , in this embodiment, the radial width of the first passage P1 in the first path is smaller than the radial width of the second passage P2. In addition, the radial width of the fifth passage P5 included in the third path is smaller than the radial width of the fourth passage P4.

[0252] Refer to again Figure 16 , the overall axial height of the main edge portion 48 and the main oil drain portion 47 is represented by BH, and the axial height of the main oil drain portion 47 is represented by OH. Here, it can also be regarded that the overall axial height BH of the main edge portion 48 and the main oil drain portion 47 is the axial height BH of the main bearing 40. The main oil drain portion 47 only occupies a part of the height range OH in the overall axial height range BH.

[0253] At this time, the relative ratio (OH / BH) of the axial height OH of the main oil drain portion 47 to the overall axial height BH of the main edge portion 48 and the main oil drain portion 47 may be 0.2 to 0.35. If the relative ratio (OH / BH) is less than 0.2, the axial height occupied by the main oil drain portion 47 is low, resulting in a low height of the second passage P2 as a passage between the first passage P1 and the third passage P3, and it is difficult to form a smooth oil flow. On the contrary, if the relative ratio (OH / BH) is greater than 0.35, the oil recovery rate will not increase further and remains unchanged.

[0254] Figure 22 The oil level height changing according to the relative ratio (OH / BH) is shown by a curve. Here, the oil level height refers to the height formed by the oil inside the housing 10. The oil level height is formed at least to the height A where the roller 70 is located to enable smooth lubrication. If the oil recovery is not smooth, the oil floats inside the compressor and cannot perform the lubrication function, so the oil level height also becomes low. Figure 22 A represents the minimum oil level height for the smooth operation of the compressor.

[0255] As Figure 22 shown, if the relative ratio (OH / BH) is less than 0.2, the oil level height is lower than the minimum oil level height A, resulting in problems with the lubrication function. On the contrary, if the relative ratio (OH / BH) is greater than 0.35, the oil level height will not increase further and remains unchanged. Therefore, considering the durability of the main bearing 40, it is preferable to keep the relative ratio (OH / BH) below 0.35 rather than further increasing the axial height OH of the main oil drain portion 47.

[0256] Figure 23 The structure of the compression part constituting the second embodiment of the compressor of the present invention is illustrated. Parts identical to those of the foregoing embodiment are given the same reference numerals and description thereof is omitted. As shown in the figure, the main oil discharge part 147 may extend continuously from the upper end of the outer peripheral surface of the main bearing 40 to the lower end of the outer peripheral surface of the main bearing 40. That is, differently from the foregoing embodiment, the main edge part 48 at the upper part in the axial direction of the main oil discharge part 147 is omitted. However, such a structure can only be applied to a position where the main fastening hole 49 is not provided at the upper end part of the main oil discharge part 147. As Figure 23 shown, it may also be that, in the main oil discharge part 47 provided in the main bearing 40, a part does not extend to the upper end of the outer peripheral surface of the main bearing 40, while another part extends to the upper end of the outer peripheral surface of the main bearing 40.

[0257] Figure 24 The structure of the compression part constituting the third embodiment of the compressor of the present invention is shown in a side view. Parts identical to those of the foregoing embodiment are given the same reference numerals and description thereof is omitted. As shown in the figure, in the present embodiment, the diameters of the main bearing 40 and the sub-bearing 50 are larger than the diameter of the cylinder 60. Therefore, the main bearing 40 or the sub-bearing 50 can be fixed to the inner peripheral surface 11a of the main body housing 11.

[0258] At this time, a first oil discharge part 267 recessed radially inward from the outer peripheral surface 63 of the cylinder 60 may be formed in the cylinder 60. Second oil discharge parts 247 and 257 penetrating in the axial direction of the compression part C may be formed in the main bearing 40 and the sub-bearing 50, respectively. In the present embodiment, the first oil discharge part 267 may be axially connected to all or a part of the second oil discharge parts 247 and 257. Therefore, the first oil discharge part 267 and the second oil discharge parts 247 and 257 may form an oil discharge path OP continuous with each other. In the present embodiment, the discharge muffler 90 may have a shape that does not block the entrance of the oil discharge path OP that is the upper end part of the main oil discharge part 247 among the second oil discharge parts 247 and 257.

[0259] Figure 25 The structure of the compression part constituting the fourth embodiment of the compressor of the present invention is shown in a side view. Parts identical to those of the foregoing embodiment are given the same reference numerals and description thereof is omitted. As shown in the figure, the first oil discharge part of the sub-bearing 50 may be omitted. In the present embodiment, the diameter of the sub-bearing 50 is smaller than the diameter of the main bearing 40. Therefore, the sub-bearing 50 does not block the exit of the oil discharge path OP that is the lower end part of the second oil discharge part 67 at the lower part of the second oil discharge part 67, and thus an additional sub oil discharge part can be omitted in the sub-bearing 50.

[0260] Figure 26The structure of the compression part of the fifth embodiment of the compressor of the present invention is shown in a side view. As shown in the figure, the auxiliary oil discharge portion 457 formed on the auxiliary bearing 50 in the first oil discharge portion 47, 57 can be continuous from the upper end of the outer peripheral surface 53 of the auxiliary bearing 50 to the lower end of the outer peripheral surface 53 of the auxiliary bearing 50. That is, unlike the aforementioned embodiment, the auxiliary edge portion of the axial lower portion of the auxiliary oil discharge portion 457 is omitted. However, this structure can only be applied to a position where the main fastening hole is not configured at the lower end of the auxiliary oil discharge portion 457. Figure 26 As shown, it is also possible that, in the auxiliary oil drain portion 457 provided in the auxiliary bearing 50 , a portion does not extend to the lower end of the outer circumferential surface 53 of the auxiliary bearing 50 , while another portion extends to the lower end of the outer circumferential surface 53 of the auxiliary bearing 50 .

[0261] Figure 27 A cross-sectional view illustrates the structure of an oil discharge path OP, which constitutes a sixth embodiment of a compressor according to the present invention. Identical components to those in the previous embodiments are designated by the same reference numerals, and their descriptions are omitted. As shown, the main bearing 40 includes a main oil discharge portion 547, one of the first oil discharge portions 547 and 557. A main edge portion 48 protrudes axially from the upper portion of the main oil discharge portion 547.

[0262] In this case, the main edge 48 can shield the upper end of the second oil-draining portion 567 formed axially below. In this embodiment, the main edge 48 axially overlaps the entire upper end of the second oil-draining portion 567. More specifically, if N1 is an imaginary line extending axially along the inner circumferential surface 11a of the main housing 11, N2 is an imaginary line extending axially along the outer circumferential surface of the main edge 48, and N3 is an imaginary line extending axially along the inner circumferential surface of the second oil-draining portion 567 that is relatively close to the inner circumferential surface 11a of the main housing 11, then N2 is between N1 and N3. Even in this case, N2 is separated from N1, thereby ensuring an entrance to the oil-draining path OP through which oil can flow.

[0263] Figure 28 The structure of the compression section of the seventh embodiment of the compressor of the present invention is shown in a three-dimensional diagram. Parts identical to those in the previous embodiments are given the same reference numerals, and descriptions thereof are omitted. As shown in the figure, the main oil drain portion 647 and the auxiliary oil drain portion 657 that constitute the first oil drain portions 647 and 657 can have different sizes. More specifically, the main oil drain portion 647 and the auxiliary oil drain portion 657 have different widths relative to the circumferential direction. In this embodiment, the circumferential width of the main oil drain portion 647 is smaller than that of the auxiliary oil drain portion 657. As another example, the circumferential width of the main oil drain portion 647 can also be larger than that of the auxiliary oil drain portion 657.

[0264] Figure 29 The structure of the main bearing 40 constituting the eighth embodiment of the compressor of the present invention is shown in a top view. The same parts as those in the foregoing embodiments are given the same reference numerals and the description thereof is omitted. As shown in the figure, in this embodiment, a second oil discharge portion 847 may be formed in the main bearing 40. At this time, a plurality of second oil discharge portions 847 may be arranged in the circumferential direction. Moreover, the circumferential widths of the plurality of second oil discharge portions 847 may be different from each other.

[0265] Figure 30 The structure of the compression part constituting the ninth embodiment of the compressor of the present invention is shown in a side view. The same parts as those in the foregoing embodiments are given the same reference numerals and the description thereof is omitted. As shown in the figure, the discharge muffler 190 may also be arranged on the bottom surface of the sub-bearing 50 instead of the top surface of the main bearing 40. In this embodiment, the bottom surface of the sub-bearing 50 has a perfect circular shape, so that a sufficient area for accommodating the discharge muffler 190 can be provided. Although not shown, as another example, the discharge muffler 190 may also be omitted.

[0266] The above description is only for exemplarily explaining the technical idea of the present invention. Those skilled in the art can make various modifications, changes and substitutions without departing from the essential features of the present invention. Therefore, the embodiments and drawings disclosed in the present invention are not used to limit the technical idea of the present invention, but to explain. The scope of the technical idea of the present invention is not limited to the above embodiments. The protection scope of the present invention should be interpreted by the appended claims, and all technical ideas within the same scope as it should be included in the protection scope of the present invention.

Claims

1. A compressor, wherein, Comprising: A housing; An electric part disposed inside the housing to rotate a rotating shaft; A compression part disposed inside the housing, including a cylinder, a main bearing, and a sub-bearing that together form a compression space; A first oil-draining part recessed radially inward from the outer peripheral surface of either the main bearing or the cylinder with a relatively smaller diameter; and A second oil-draining part formed by axially penetrating the other of the main bearing and the cylinder with a relatively larger diameter; The first oil-draining part and the second oil-draining part are connected to each other in the axial direction to form an oil-draining path.

2. The compressor according to claim 1, wherein The first oil-draining part is formed in the main bearing; The first oil-draining part forms a passage between the outer peripheral surface of the main bearing and the inner peripheral surface of the housing.

3. The compressor according to claim 1, wherein The first oil-draining part extends from a position axially downwardly spaced from the upper end of the outer peripheral surface of the main bearing to the lower end of the outer peripheral surface of the main bearing.

4. The compressor according to claim 1, wherein The radial width of the passage formed between the inner peripheral surface of the housing and the first oil-draining part is greater than the radial width of the second oil-draining part.

5. The compressor according to claim 1, wherein The surface of the first oil-draining part and the surface of the second oil-draining part form a continuous plane or curved surface.

6. The compressor according to claim 1, wherein The second oil-draining part includes: A first discharge inner surface forming the inner surface of the second oil-draining part; A second discharge inner surface spaced apart from and facing the first discharge inner surface, formed at a position closer to the inner peripheral surface of the housing than the first discharge inner surface; and A connecting inner surface connecting the first discharge inner surface and the second discharge inner surface; The first discharge inner surface and the first oil-draining part form a continuous plane or curved surface.

7. The compressor according to claim 6, wherein A rim part that protrudes radially more toward the inner peripheral surface of the housing than the first oil-draining part is formed on the upper part of the first oil-draining part; When the radial distance between the rim part and the inner peripheral surface of the housing is set as L1, the radial distance between the surface of the first oil-draining part and the inner peripheral surface of the housing is set as L2, the radial distance between the second discharge inner surface and the inner peripheral surface of the housing is set as L3, and the radial distance between the first discharge inner surface and the inner peripheral surface of the housing is set as L, the relationship among L3, L1, L2, and L4 is L3 < L1 < L2 = L4.

8. The compressor according to claim 6, wherein A rim part that protrudes radially more toward the inner peripheral surface of the housing than the first oil-draining part is formed on the upper part of the first oil-draining part; When the radial distance between the rim part and the inner peripheral surface of the housing is set as L1, the radial distance between the surface of the first oil-draining part and the inner peripheral surface of the housing is set as L2, and the radial distance between the second discharge inner surface and the inner peripheral surface of the housing is set as L3, the relationship among L3, L1, and L2 is L3 < L1 < L2.

9. The compressor according to claim 1, wherein An edge portion that protrudes more radially toward the inner peripheral surface of the housing than the first oil drainage portion is formed above the first oil drainage portion; The relative ratio of the axial height (OH) of the first oil drainage portion to the overall axial height (BH) of the edge portion and the first oil drainage portion is 0.2 to 0.

35.

10. The compressor according to claim 1, wherein, An edge portion that protrudes more radially toward the inner peripheral surface of the housing than the first oil drainage portion is formed above the first oil drainage portion; The edge portion is axially spaced apart upward from the upper end of the second oil drainage portion; The first oil drainage portion is formed between the edge portion and the second oil drainage portion.

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