SCROLL COMPRESSOR

A scroll compressor is disclosed. In the scroll compressor, a bearing shock absorbing portion that allows an axial deformation of a bearing plate is arranged in a thrust surface of a main frame, and a height of the bearing shock absorbing portion may be formed smaller than a height of a bearing support portion. Accordingly, as the bearing plate supports an orbiting scroll while being elastically deformed, the structure of the main frame can be simplified, and friction loss and/or abrasion between the main frame (or orbiting scroll) and the bearing plate can be effectively suppressed.

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Description
CROSS-REFERENCE TO RELATED APPLICATION

Pursuant to 35 U.S.C. § 119(a), this application claims the benefit of the earlier filing date and the right of priority to Korean Patent Application No. 10-2025-0022460, filed on February 20, 2025, the contents of which are incorporated by reference herein in their entirety.

BACKGROUND 1. Field

This disclosure relates to a scroll compressor.

2. Description of the Related Art

In a scroll compressor, an orbiting scroll and a non-orbiting scroll are engaged with each other, and a pair of two compression chambers is formed between the orbiting scroll and the non-orbiting scroll while the orbiting scroll performs an orbiting motion with respect to the non-orbiting scroll.

In the scroll compressor, as the orbiting scroll is supported in an axial direction with respect to a main frame to perform an orbiting motion, friction loss and/or abrasion is increased on a thrust surface between the orbiting scroll and the main frame. Therefore, minimizing a thrust area (or axial bearing area) between the orbiting scroll and the main frame may be advantageous in improving the performance and/or reliability of the compressor.

However, when the thrust surface between the orbiting scroll and the main frame is reduced, behavior of the orbiting scroll becomes unstable as an axial bearing force of the orbiting scroll is decreased. Therefore, leakage between compression chambers may occur.

Accordingly, conventionally, a method was proposed in which an elastic portion or a lubrication portion was located between the orbiting scroll and the main frame, thereby securing an axial bearing force of the orbiting scroll while minimizing an axial bearing area between the orbiting scroll and the main frame.

Patent Document 1 (US2022/0316478 A1) discloses an example in which a thrust surface of a main frame is formed in a so-called trepan structure so as to increase a shock absorbing effect on the thrust surface. However, as disclosed in Patent Document 1, it is not easy to perform processing for maximizing an elastic force on a structure having an elastic portion, and there is a limitation in reducing friction loss and/or abrasion as the elastic portion is made of a same material as the main frame.

Patent Document 2 (US4772188 B) discloses an example in which an oil groove is formed in a thrust surface of a main frame so as to increase a lubrication effect on the thrust surface. However, as disclosed in Patent Document 2, a structure having a lubrication portion hardly has a shock absorbing effect between an orbiting scroll and the main frame, and therefore, there is a limitation in reducing an axial load. In addition, an amount of oil supplied to the corresponding lubrication portion is not secured during initial start-up and/or a restriction operation of a compressor, and therefore, the above problem may become more serious.

SUMMARY

Therefore, the present disclosure provides a scroll compressor capable of suppressing friction loss and/or abrasion between an orbiting scroll and a main frame supporting the orbiting scroll in an axial direction.

The present disclosure also provides a scroll compressor capable of easily processing an orbiting scroll and a main frame supporting the orbiting scroll in an axial direction and suppressing friction loss and/or abrasion between the orbiting scroll and the main frame.

The present disclosure also provides a scroll compressor capable of improving a shock absorbing effect between an orbiting scroll and a main frame supporting the orbiting scroll in an axial direction, thereby suppressing friction loss and/or abrasion between the orbiting scroll and the main frame.

The present disclosure also provides a scroll compressor capable of improving a shock absorbing effect between an orbiting scroll and a main frame supporting the orbiting scroll in an axial direction and increasing an oil supply amount, thereby friction loss and/or abrasion between the orbiting scroll and the main frame.

In order to achieve these and other advantages and in accordance with the purpose of this specification, as embodied and broadly described herein, there is provided a scroll compressor including a casing, an orbiting scroll, a non-orbiting scroll, a main frame, and a bearing plate. The orbiting scroll may be coupled to a rotary shaft inside the casing to perform an orbiting motion. The non-orbiting scroll may form a compression chamber together with the orbiting scroll. The main frame may be fixed to the casing in an internal space of the casing and may support the orbiting scroll in an axial direction. The bearing plate may be located between a thrust surface of the main frame and a thrust surface of the orbiting scroll, which faces the thrust surface of the main frame. The thrust surface of the main frame may include a bearing support portion supporting the bearing plate in the axial direction, and a bearing shock absorbing portion extending to an inner circumferential side thereof from the bearing support portion to allow an axial deformation of the bearing plate. A height of the bearing shock absorbing portion may be formed smaller than a height of the bearing support portion. Accordingly, as the bearing plate supports the orbiting scroll while being elastically deformed, the structure of the main frame can be simplified, and friction loss and/or abrasion between the main frame (or orbiting scroll) and the bearing plate can be effectively suppressed.

In an example, the bearing shock absorbing portion may include at least one inclined surface. The inclined surface may be formed to be inclined downwardly from an outer circumferential side of the bearing shock absorbing portion, which is in contact with the bearing support portion, to the inner circumferential side of the bearing shock absorbing portion. Accordingly, an interval between the thrust surface of the main frame and the bearing plate facing the thrust surface of the main frame increases as approaching an inner circumferential side of the bearing shock absorbing portion, so that a shock absorbing space capable of absorbing a deformation of the bearing plate can be effectively secured.

For example, the bearing shock absorbing portion may include a plurality of inclined surfaces having different inclination angles, which are formed continuously along a radial direction. The plurality of inclined surfaces may be formed such that the inclination angles increase as becoming distant from the bearing support portion. Accordingly, the bearing plate is gradually deformed, thereby improving the reliability of the bearing plate.

In another example, the bearing shock absorbing portion may include ate least one stepped surface. Accordingly, the bearing shock absorbing portion can be easily processed, and a shock absorbing space capable of absorbing a deformation of the bearing plate can be effectively secured.

For example, the bearing shock absorbing portion may include a plurality of stepped surfaces formed continuously along the radial direction. The plurality of stepped surfaces may be formed to have a same axial height and/or a same radial width.

Alternatively, the bearing shock absorbing portion may include a plurality of stepped surfaces formed continuously along the radial direction. The plurality of stepped surfaces may be formed such that an axial height and/or a radial width of an inner circumferential side stepped surface is larger than an axial height and/or a radial width of an outer circumferential side stepped surface.

In still another example, a radial width of the bearing shock absorbing portion is equally formed along a circumferential direction. Accordingly, as the bearing area of the bearing support portion is equally formed along the circumferential direction, the bearing plate can be stably supported.

For example, the radial width of the bearing shock absorbing portion may be formed to become 15% to 17% of a radial width of the bearing plate.

In still another example, the main frame may include a bearing accommodation portion extending in the axial direction from the bearing support portion to support an outer circumferential surface of the bearing plate in a radial direction. An inner diameter of the bearing accommodation portion may be formed larger than or equal to an outer diameter of the bearing plate. Accordingly, the bearing plate is slidingly supported inside the bearing accommodation portion, so that friction loss and/or abrasion between the bearing plate and the bearing support portion can be effectively suppressed.

For example, the bearing accommodation portion may be formed in an annular shape or may include a plurality of projections spaced apart from each other along the circumferential direction.

Alternatively, the bearing accommodation portion may include a plurality of projections spaced apart from each other along the circumferential direction, and at least one oil supply groove may be formed in the bearing support portion. At least some of the oil supply grooves may be formed between the plurality of bearing accommodation portions.

In still another example, an oil supply groove is formed in at least one of the main frame and the orbiting scroll, and wherein at least a portion of the oil supply groove is formed to overlap an axial surface of the bearing plate in the axial direction. Accordingly, an oil in the orbiting space portion is quickly introduce between the bearing plate and the main frame and/or the orbiting scroll, facing the bearing plate, to smoothly lubricate between the bearing plate and the bearing support portion.

For example, the oil supply groove may be formed in the bearing support portion of the main frame. One end of the oil supply groove may be formed to be connected to the bearing shock absorbing portion.

In addition, the oil supply groove may be formed in the thrust surface of the orbiting scroll. One end of the oil supply groove may extend inwardly of an inner circumferential surface of the bearing plate.

In still another example, the main frame may include an orbiting space portion, a scroll support portion, and an Oldham ring support portion. In the orbiting space portion, the rotary shaft may be coupled to the orbiting scroll to perform an orbiting motion. The scroll support portion may extend in the axial direction from the orbiting space portion to include the bearing support portion and the bearing shock absorbing portion. The Oldham ring support portion may surround an outer circumferential side of the scroll support portion. At least one of an inner circumferential surface of the scroll support portion, which is connected to the orbiting space portion, and an outer circumferential surface of the scroll support portion, which is connected to the Oldham ring support portion, may be formed in a smooth tubular shape. Accordingly, the scroll support portion can be easily processed, and friction loss and/or abrasion between the bearing plate and the main frame can be effectively suppressed by absorbing an axial load of the bearing plate.

In an example, each of the inner circumferential surface and the outer circumferential surface of the scroll support portion may be formed in a smooth tubular shape.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other aspects, features and other advantages of the present disclosure will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a sectional view showing an interior of a scroll compressor according to an embodiment;

FIG. 2 is an exploded perspective view showing a compression unit including a main frame in FIG. 1;

FIG. 3 is an assembled plan view showing a portion of the compression unit in the scroll compressor according to this embodiment;

FIG. 4 is a sectional view taken along line "IV-IV" of FIG. 3;

FIG. 5 is a sectional view showing another embodiment of the main frame

in FIG. 3;

FIG. 6 is a graph showing surface pressure improvement rate depending on radial width of a bearing shock absorbing portion according to this embodiment;

FIG. 7 is a sectional view showing another embodiment of the bearing shock absorbing portion;

FIG. 8 is a sectional view showing still another embodiment of the bearing shock absorbing portion in FIG. 7;

FIG. 9 is an exploded perspective view showing another embodiment of a bearing support portion;

FIG. 10 is a sectional view showing the bearing support portion in FIG. 9;

FIG. 11 is an exploded perspective view showing still another embodiment of the bearing support portion; and

FIG. 12 is a sectional view showing the bearing support portion in FIG. 11.

 DETAILED DESCRIPTION OF THE EMBODIMENTS

Hereinafter, a scroll compressor according to the present disclosure will be described in detail, based on embodiments illustrated in the accompanying drawings.

In general, a scroll compressor may be divided into a low pressure type and a high pressure type according to a path through with a refrigerant is sucked. The low pressure type is a type in which a refrigerant suction pipe communicates with an internal space of a casing such that a low temperature refrigerant passes through the internal space of the casing and then is guided to a compression chamber, and the high pressure type is a type in which the refrigerant suction pipe is connected directly to the compression chamber such that the refrigerant does not pass through the internal space of the casing but is guided directly to the compression chamber.

In addition, the scroll compressor may be divided into an upper compression type and a lower compression type according to a relative position of a compression unit with respect to an electric unit. The upper compression type is a type in which the compression unit is located above a driving unit, and the lower compression type is a type in which the compression unit is located below the driving unit. In this embodiment, an upper compression type scroll compressor is described as an example. However, this embodiment may be equally or similarly applied even to a lower compression type scroll compressor.

In addition, the scroll compressor may be divided into an open type and a closed type according to whether or not a driving unit (electric unit) and a compression unit are installed together in an internal space of a casing. The open type is a type in which the electric unit constituting the driving unit is arranged to be separated from the compression unit, and the closed type is a type in which the electric unit is arranged together with the compression unit in the internal space of the casing. In this embodiment, a closed type scroll compressor is described as an example. However, this embodiment may be equally or similarly applied even to an open type scroll compressor.

In addition, the scroll compressor may be divided into a vertical type and a horizontal type according to a relationship between a ground and a rotary shaft. The vertical type is a type in which the rotary shaft is located vertically to the ground, and the horizontal type is a type in which the rotary shaft is located parallel or inclined to the ground. For example, in a vertical type scroll compressor, an upper side may be defined as a side opposite to the ground, and a lower side may be defined as a side toward the ground. In this embodiment, the vertical type scroll compressor is described as an example. However, this embodiment may be equally or similarly applied even to a horizontal type scroll compressor. Therefore, hereinafter, an axial direction may be understood as an axial direction of the rotary shaft, and a radial direction may be understood as a radial direction of the rotary shaft. In addition, the axial direction may be understood as an up-down (or vertical) direction, the radial direction may be understood as a left/right (or horizontal) side surface, an inner circumferential surface may be understood as an upper surface, and an axial radial direction may be understood as a side surface.

In addition, the scroll compressor may be divided into a fixed back pressure type and an orbiting back pressure type according to a direction in which a scroll is pressurized. The fixed back pressure type is a type in which a non-orbiting scroll is pressurized toward an orbiting scroll, and the orbiting back pressure type is a type in which the orbiting scroll is pressurized toward the non-orbiting scroll. In this embodiment, a scroll compression according to the fixed back pressure type is mainly described. However, this embodiment may be equally or similarly even to the orbiting back pressure type.

Besides, the scroll compressor may be divided into various types according to references, but this embodiment may be equally or similarly applied to a scroll compressor to which a bearing plate is applied so as to support the axial direction of an orbiting scroll.

FIG. 1 is a sectional view showing an interior of a scroll compressor according to an embodiment. FIG. 2 is an exploded perspective view showing a compression unit including a main frame in FIG. 1.

Referring to FIG. 1, in the scroll compressor according to this embodiment, a driving motor 120 may be installed in a lower half portion of a casing 120, and a main frame 130, a non-orbiting scroll 140, an orbiting scroll 150, and a back pressure chamber assembly 160 may be sequentially installed above the driving motor 120. The driving motor 120 constitutes an electric unit, and the main frame 130, the non-orbiting scroll 140, the orbiting scroll 150, and the back pressure chamber assembly 160 constitute a compression unit. The electric unit may be coupled to one end of a rotary shaft 125, and the compression unit may be coupled to the other end of the rotary shaft 125. Therefore, the compression unit is connected to the electric unit by the rotary shaft 125 to be operated by a rotational force of the electric unit.

Referring to FIG. 1, the casing 110 may include a cylindrical shell 111, an upper cap 112, and a lower cap 113.

The cylindrical shell 111 may be formed in a cylindrical shape having both open upper and lower ends, and the driving motor 120 and the main frame 130 may be inserted into an inner circumferential surface of the cylindrical shell 111 to be fixed to the cylindrical shell 111. A terminal bracket (not shown) may be coupled to an upper half portion of the cylindrical shell 111, and a terminal (not shown) for transferring external power to the driving motor 120 may path through and be coupled to the terminal bracket.

The upper cap 112 may be coupled to the cylindrical shell 111 to cover the open upper end of the cylindrical shell 111, and the lower cap 113 may be coupled to the cylindrical shell 111 to cover the open lower end of the cylindrical shell 111. An edge of a high and low pressure separation plate 115 to be described later may be inserted between the cylindrical shell 111 and the upper cap 112 to be welded and coupled to both the cylindrical shell 111 and the upper cap 112, and an edge of a support bracket 116 may be inserted between the cylindrical shell 111 and the lower cap 113 to be welded and coupled to both the cylindrical shell 111 and the lower cap 113. Therefore, an internal space of the casing 110 may be sealed.

In this case, with respect to the high and low pressure separation plate 115, a refrigerant suction pipe 117 may pass through the cylindrical shell 111 to be coupled to the cylindrical shell 111, and a refrigerant discharge pipe 118 may pass through the upper cap 112 to be coupled to the upper cap 112. Therefore, a low pressure portion 110a forming a suction space may be formed on a lower side of the high and low pressure separation plate 115, and a high pressure portion 110b forming a discharge space may be formed on an upper side of the high and low pressure separation plate 115.

The lower cap 113 along with a lower half portion of the cylindrical shell 111, which forms the low pressure portion 110a, may form an oil storage space 110c. In other words, the oil storage space 110c is formed in a lower half portion of the low pressure portion 110a, and may form a portion of the low pressure portion 110a.

Referring to FIG. 1, the driving motor 120 according to this embodiment may be installed in the lower half portion of the low pressure portion 110a, and may include a stator 121 and a rotor 122. The stator 121 may be fixed to an inner wall surface of the cylindrical shell 111 through warm shrink fitting, and the rotor 122 may be rotatably arranged inside the stator 121.

The stator 121 may include a stator core 1211 and a stator coil 1212.

The stator core 1211 may be formed in a cylindrical shape and may be fixed to the inner circumferential surface of the cylindrical shell 111 through warm shrink fitting. The stator coil 1212 may be wound around the stator core 1211, and may be electrically connected to an external power source through the terminal (not shown) which passes through and is coupled to the casing 110.

The rotor 122 may include a rotor core 1221 and a permanent magnet 1222.

The rotor core 1221 may be formed in a cylindrical shape to be rotatably inserted into the stator core 1211 at an interval by a predetermined void. The permanent magnet 1222 may be embedded inside the rotor core 1221 at a predetermined interval along a circumferential direction.

The rotary shaft 125 may be press-fitted into the center of the rotor core 1221, and an eccentric portion 125a may be arranged on an upper end of the rotary shaft 125 such that the orbiting scroll 150 to be described later is eccentrically coupled to the rotary shaft 125. Therefore, a rotational force of the driving motor 120 may be transferred to the orbiting scroll 150 through the rotary shaft 125.

An oil flow path 125b may be formed inside the rotary shaft 125 to pass through the rotary shaft 125 in the axial direction, and an oil pickup 126 for sucking up an oil stored in a lower portion of the casing 110 may be arranged on a lower end of the rotary shaft 125. Therefore, the oil stored in the lower portion of the casing 110 is sucked up along the oil flow path 125b of the rotary shaft 125 to flow into an orbiting space portion 133, and is scattered by a pressure difference and/or collision with a rotary shaft insertion portion 153 orbiting in the orbiting space portion 133 to be supplied to a bearing surface between adjacent members.

In this case, a positive displacement pump such as a trochoid gear may be applied to the oil pickup 126, but a centrifugal pump such as a propeller may be applied to the oil pickup 126. In the embodiment, an example is illustrated in which the latter, i.e., the centrifugal pump capable of inducing differential pressure oil supply is applied to the oil pickup 126.

Referring to FIGS. 1 and 2, the main frame 130 according to this embodiment may be fixed to the inner wall surface of the cylindrical shell 111 through warm shrink fitting or be welded and fixed to the inner wall surface of the cylindrical shell 111 above the driving motor 120 constituting the low pressure portion 110a.

Specifically, the main frame 130 according to this embodiment may include a main flange portion 131, a main bearing portion 132, the orbiting space portion 133, a scroll support portion 134, an Oldham ring support portion 135, and a frame fixing portion 136.

An outer circumferential surface of the main flange portion 131 may be spaced apart from the inner circumferential surface of the cylindrical shell 111, and the frame fixing portion 136 to be described later may protrude in the radial direction from the outer circumferential surface of the main flange portion 131 to be fixed to the inner circumferential surface of the cylindrical shell 111. Therefore, the main frame 130 may be fixedly coupled to the casing 110.

The main bearing portion 132 may protrude downwardly toward the driving motor 120 from a center-side lower surface of the main flange portion 131, and a cylindrical bearing hole 132a may pass through the main flange portion 131 in the axial direction at a central portion of the main flange portion 131. Therefore, the rotary shaft 125 may be inserted into an inner circumferential surface of the bearing hole 132a to be supported in a radial direction.

The orbiting space portion 133 may be formed to be recessed by a predetermined depth toward the main bearing portion 132 from a center-side upper surface of the main flange portion 131. An inner diameter of the orbiting space portion 133 may be formed larger than an outer diameter of the rotary shaft insertion portion 153 of the orbiting scroll 150 to be described later. Therefore, the rotary shaft insertion portion 153 may scatter the oil introduced into the orbiting space portion 133 while orbiting inside the orbiting space portion 133.

The scroll support portion 134 may be formed in an annular shape along the periphery of the orbiting space portion 133 on an upper surface of the main flange portion 131. In other words, a frame-side thrust surface 134a by which a scroll-side thrust surface 151a of the orbiting scroll 150 to be described later is slidingly supported in the axial direction may be formed on an upper surface of the scroll support portion 134. Accordingly, the orbiting scroll 150 to be described later can be stably supported by the frame-side thrust surface 134 of the scroll support portion 134.

In this case, the frame-side thrust surface 134a is formed in an annular shape, and may be formed at different heights along the radial direction. In other words, the frame-side thrust surface 134a may be formed such that a height of an outer circumferential side thereof and a height of an inner circumferential side thereof are different from each other. For example, the outer circumferential side of the frame-side thrust surface 134a may be formed higher than the inner circumferential side of the frame-side thrust surface 134a. Accordingly, a portion of a bearing plate 180 to be described later is spaced apart from the frame-side thrust surface 134a, so that the orbiting scroll 150 can be elastically supported as a shock absorbing effect occurs in the bearing plate 180. The frame-side thrust surface 134a along with the bearing plate 180 will be again described later.

The Oldham ring support portion 135 may be formed in an annular shape along an outer circumferential surface 134b of the scroll support portion 134 on the upper surface of the main flange portion 131. Therefore, an Oldham ring 170 may be inserted into the Oldham ring support portion 134 to be rotatably accommodated in the Oldham ring support portion 134.

First key grooves 1351 into which first keys 172 of the Oldham ring 170 to be described later are respectively inserted to be slidable in the radial direction may be formed on an upper surface of the Oldham ring support portion 135. For example, the first key grooves 1351 may be arranged with a phase difference of 180 degrees along the circumferential direction. Therefore, the two first key grooves 1351 may be arranged on the same line.

Each of the first key grooves 1351 may extend in the radial direction such that while an outer end thereof is open toward the low pressure portion 110a of the casing 110, an inner end thereof is formed in a semicircular shape closed with respect to the outer circumferential surface 134b of the scroll support portion 134. Therefore, the oil introduced into the first key groove 1351 lubricates between the first key groove 1351 and the first key 172 while flowing from the inner end to the outer end of the first key groove 1351.

The frame fixing portion 136 may formed to extend in the radial direction from the outside of the Oldham ring support portion 135. The frame fixing portion 136 may extend in an annular shape or may include a plurality of protrusion portions spaced apart from each other along the circumferential direction by a predetermined interval. In the embodiment, an example is illustrated in which the frame fixing portion 136 includes a plurality of protrusion portions along the circumferential direction.

Each guide bush 137 slidingly inserted in the axial direction into the non-orbiting scroll 140 to be described later may be fixedly coupled to the frame fixing portion 136. Therefore, while the non-orbiting scroll 140 to be described later is slidingly supported in the axial direction by the main frame 130, the non-orbiting scroll 140 may be restricted in the radial direction by the main frame 130.

Referring to FIG. 1, the non-orbiting scroll 140 according to this embodiment may be coupled to an upper side of the main frame 130 with the orbiting scroll 150 interposed therebetween. The non-orbiting scroll 140 may be fixedly coupled to the main frame 130 and may be coupled to the main frame 130 to be movable in the up-down direction. In this embodiment, an example is illustrated in which the non-orbiting scroll 140 is coupled to the main frame 130 to be movable in the axial direction.

The non-orbiting scroll 140 according to this embodiment may include a non-orbiting end plate portion 141, a non-orbiting wrap 142, a non-orbiting sidewall portion 143, and a guide protrusion portion 144.

The non-orbiting end plate portion 141 may be formed in a disk shape to be arranged in a horizontal direction in the low pressure portion 110a of the casing 110. A discharge port 141a, a bypass hole 141b, and a scroll-side back pressure hole 141c may be formed in a central portion of the non-orbiting end plate portion 141 to pass through the non-orbiting end plate portion 141 in the axial direction.

The non-orbiting wrap 142 may extend by a predetermined height in the axial direction from a lower surface of the non-orbiting end plate portion 141, and may extend to be spirally wound several times toward the non-orbiting sidewall portion from a peripheral portion of the discharge port 141a. Therefore, the non-orbiting wrap 142 may be formed corresponding to an orbiting wrap 152 to be described later to form a pair of two compression chambers V1 and V2 between the non-orbiting wrap 142 and the orbiting wrap 152.

The non-orbiting sidewall portion 143 may extend in the axial direction from an edge of the lower surface of the non-orbiting end plate portion 141 while surrounding the non-orbiting wrap 142 to be formed in an annular shape. A suction port passing through the non-orbiting sidewall portion 143 in the radial direction may be formed in one side of an outer circumferential surface of the non-orbiting sidewall portion 143. Accordingly, a refrigerant sucked through the refrigerant suction pipe 117 can be quickly sucked into the compression chambers through the suction portion.

The guide protrusion portion 144 may extend in the radial direction from a lower outer circumferential surface of the non-orbiting sidewall portion 143. One guide protrusion portion 144 may be formed in an annular shape, or a plurality of guide protrusion portions may be formed along the circumferential direction at a predetermined interval. In this embodiment, an example is illustrated in which the plurality of guide protrusion portions 144 are formed along the circumferential direction at the predetermined interval.

The plurality of guide protrusion portions 144 may be slidingly inserted into the above-described guide bush 137 in the axial direction. Therefore, while the non-orbiting scroll is slidingly supported in the axial direction by the main frame, the non-orbiting scroll may be restricted in the radial direction by the main frame.

Referring to FIGS. 1 and 2, the orbiting scroll 150 according to this embodiment may be coupled to the rotary shaft 125 to be arranged on an upper surface of the main frame 130. For example, the orbiting scroll 150 may be located between the main frame 130 and the non-orbiting scroll 140, and the Oldham ring 170 which is an anti-rotation member may be located between the orbiting scroll 150 and the main frame 130. Therefore, the orbiting scroll 150 performs an orbiting motion with respect to the non-orbiting scroll 140 while an orbiting motion thereof is restricted.

Specifically, the orbiting scroll 150 may include an orbiting end plate portion 151, the orbiting wrap 152, and the rotary shaft insertion portion 153.

The orbiting end plate portion 151 may be formed in a substantially disk shape. The orbiting end plate portion 151 may be supported in the axial direction by the scroll support portion 134 of the main frame 130. In other words, the scroll-side thrust surface 151a supported in the axial direction by the frame-side thrust surface 134a of the scroll support portion 134 may be formed on a lower surface of the orbiting end plate portion 151 facing the frame-side thrust surface 134a. Therefore, the orbiting end plate portion 151 is supported in the axial direction by the scroll support portion 134, to smoothly perform an orbiting motion.

Second key grooves 1511 into which second keys 173 of the Oldham ring 170 to be described later are slidingly inserted, respectively, may be formed in the lower surface, i.e., the scroll-side thrust surface 151a of the orbiting end plate portion 151. Like the above-described first key grooves 1351, the second key grooves 1511 may be arranged with a phase difference of 180 degrees along the circumferential direction, and the first and second key grooves 1351 and 1511 may be arranged with a phase difference of about 90 degrees along the circumferential direction. Accordingly, the orbiting scroll 150 is restricted to the main frame 130 by the Oldham ring 170, to perform an orbiting motion while a rotational motion is restricted.

The scroll-side thrust surface 151a may formed flat like the above-described frame-side thrust surface 134a. Accordingly, the orbiting end plate portion 151 can be stably supported by the scroll support portion 134 of the main frame 130 while suppressing an increase in surface pressure on the scroll-side thrust surface 151a. However, in some cases, an oil supply guide groove (not shown) may be formed in the scroll-side thrust surface 151a, to enable the oil in the orbiting space portion 133, which is sucked up through the oil flow path 125b of the rotary shaft 125, to be more quickly flow toward the Oldham ring support portion 135. The oil supply guide groove (not shown) may be formed at a position spaced apart from the second key groove 1511 at a predetermined interval in the circumferential direction.

The orbiting wrap 152 may protrude by a predetermined height from an upper surface of the orbiting end plate portion 151 to be formed in a spiral shape. The orbiting wrap 152 may be formed corresponding to the non-orbiting wrap 142 of the non-orbiting scroll 140 to perform an orbiting motion while being engaged with the non-orbiting wrap 142. The orbiting wrap 152 along with the non-orbiting wrap 142 may form a compression chamber V.

The rotary shaft insertion portion 153 may be formed to protrude by a predetermined length toward the main frame 130 from the lower surface of the orbiting end plate portion 151. The rotary shaft insertion portion 153 may be formed in a cylindrical shape, and the eccentric portion 125a of the rotary shaft 125 may be rotatably coupled to an inner circumferential surface of the rotary shaft insertion portion 153. Therefore, a rotational force of the driving motor 120 is transferred to the rotary shaft insertion portion 153 through the eccentric portion 125a of the rotary shaft 125, and the rotational force transferred to the rotary shaft insertion portion 153 is restricted by the Oldham ring 170 to rotates the orbiting scroll 150.

Referring to FIG. 1, the back pressure chamber assembly 160 according to this embodiment may be arranged above the non-orbiting scroll 140. Therefore, a back pressure force of a back pressure chamber 160a (exactly, a force with which the back pressure force acts on the back pressure chamber) acts on the non-orbiting scroll 140. In other words, the non-orbiting scroll 140 presses the orbiting scroll 150 in a direction facing the orbiting scroll 150 by means of the back pressure force, thereby sealing the compression chamber V.

The back pressure assembly 160 may include a back pressure plate 161 and a floating plate 165. The back pressure plate 161 may be coupled to an upper surface of the non-orbiting end plate portion 141, and the floating plate 165 may be slidingly coupled to the back pressure plate 161 such that the floating plate 165 and the back pressure plate 161 form the pack pressure chamber 160a.

Referring to FIGS. 1 and 2, the Oldham ring 170 according to this embodiment may be located between the main frame 130 and the orbiting scroll 150. As described above, the Oldham ring 170 may be slidingly coupled to each of the main frame 130 and the orbiting scroll 150 or may be slidingly coupled to each of the non-orbiting scroll 140 and the orbiting scroll 150. In this embodiment, an example is illustrated in which a bidirectional Oldham ring is applied such that the Oldham ring 170 is slidingly coupled to each of the main frame 130 and the orbiting scroll 150.

For example, the Oldham ring 170 according to this embodiment may include a ring body 171, the first keys 172, and the second keys 173. The ring body 171 along with the first keys 172 and/or the second keys 173 may be formed as a single body, or the first keys 172 and the second keys 173 may be post-assembled to the ring body 171. In this embodiment, an example is illustrated in which the ring body 171 along with the first keys 172 and the second keys 173 is formed as a single body. However, this embodiment may be equally applied even when the first keys 172 and/or the second keys 173 are post-assembly to the ring body 171.

In this case, the first keys 172 may be formed on one surface of the ring body 171, and the second keys 173 may be formed on the other surface of the ring body 171. Therefore, the first key 172 may be slidingly coupled to the first key groove 1351 of the main frame 130, and the second key 173 may be slidingly coupled to the second key groove 1511 of the orbiting scroll 150 to be described later.

Although not shown in the drawings, the Oldham ring 170 may be configured as a unidirectional Oldham ring. For example, the Oldham ring 170 may be located between the main frame 130 and the orbiting scroll 150, and the first keys 172 and the second keys 173 may be formed on one surface of the ring body 171. In this case, the first keys 172 may be slidingly coupled to the non-orbiting scroll 140, and the second keys 173 may be slidingly coupled to the non-orbiting scroll 150. Accordingly, the first key 172 is slidingly inserted into a first key groove (not shown) formed in the non-orbiting scroll 140 in the radial direction, and the second key 173 is slidingly inserted into the second key groove 1511 formed in the orbiting scroll 150 in the radial direction, thereby restricting a rotational motion

The scroll compressor according to this embodiment described above is operated as follows.

That is, when power is applied to the stator coil 1212 of the stator 121, the rotor 122 rotates together with the rotary shaft 125. Then, the orbiting scroll 150 coupled to the rotary shaft 125 performs an orbiting motion with respect to the non-orbiting scroll 140, and the compression chamber V including the pair of two compression chambers is formed between the orbiting wrap 152 and the non-orbiting wrap 142.

Next, the volume of the compression chamber V is gradually decreased while each of the compression chambers moves from the outside to the inside according to the orbiting motion of the orbiting scroll 150. At this instance, a refrigerant is sucked into the low pressure portion 110a of the casing 110 through the refrigerant suction pipe 117. While a portion of the refrigerant is sucked immediately into suction pressure chambers (no reference numeral) respectively forming a first compression chamber V1 and a second compression chamber V2, the other of the refrigerant flows toward the driving motor 120 to refrigerate the driving motor 120 and then is sucked into the suction pressure chambers.

Next, a series of processes is repeated in which the refrigerant sucked into the compression chamber V is compressed while flowing toward the discharge port 141a along a flow path of the compression chamber V, is discharged to the high pressure portion 110b through the discharge port 141a while pushing a discharge valve 145 in the final compression chamber, and then is discharged to a refrigeration cycle through the refrigerant discharge pipe 118.

In this instance, a portion of the refrigerant compressed in the compression chamber V is bypassed in advance to the high pressure portion 110b from each of the compression chambers V1 and V2 through the bypass hole 141b before reaching the discharge port 141a, to suppress the refrigerant from being over-compressed to a set pressure or higher in each of the compression chambers V1 and V2.

In addition, another portion of the refrigerant compressed in the compression chamber V flows into the back pressure chamber 160a through the back pressure hole 141c before reaching the discharge port 141a, thereby forming the back pressure chamber 160a to an intermediate pressure. Then, the back pressure plate 161 moves down by receiving a pressure in a direction facing the non-orbiting scroll 140 by means of the pressure of the back pressure chamber 160a and pressurizes the non-orbiting scroll 140 toward the orbiting scroll 150. Then, leakage between the compression chambers of the compression chamber V is suppressed while the non-orbiting scroll 140 and the orbiting scroll 150 are closely sealed therebetween, so that the refrigerant can be compressed while flowing along the flow path of the compression chamber V as described above.

Meanwhile, when the rotary shaft 125 rotates, the oil pickup 126 pumps an oil stored in the oil storage space 110c of the casing 110, and the pumped oil is sucked up through the oil flow path 125b of the rotary shaft 125 to be scattered in the orbiting space portion 133. A portion of the oil is introduced into a gap between the scroll support portion 134 and the orbiting scroll 150, i.e., a gap between the frame-side thrust surface 134a and the scroll-side thrust surface 151a to lubricate between the frame-side thrust surface 134a of the main frame 130 and the scroll-side thrust surface 151a of the orbiting scroll 150.

However, as the orbiting scroll 150 performs an orbiting motion in a state in which the orbiting scroll 150 is adhered closely to the main frame 130 as described above, the oil is not smoothly supplied between the orbiting scroll 150 and the main frame 130, and therefore, friction loss and/or abrasion between both the thrust surfaces 134a and 151a of the two members 130 and 150 may be increased. The may equally occur not only in the orbiting back pressure type but also in the fixed back pressure type. However, in the fixed back pressure type, as the back pressure chamber 160a is located above (at a rear side) of the non-orbiting scroll 140, the orbiting scroll 150 is pressurized toward the main frame 130, and therefore, the friction loss and/or abrasion between the orbiting scroll 150 and the main frame 130 may be further increased.

By considering this, conventionally, an example was presented in which an elastic portion such as a trepan was formed on the scroll support portion 134 of the main frame 130 supporting the orbiting scroll 150 or a lubrication portion such as an oil supply groove was formed in the thrust surface. However, this has a limitation in reducing the friction loss and/or abrasion between both the thrust surfaces 134a and 151a.

Therefore, in this embodiment, the bearing plate 180 is located between the main frame 130 and the orbiting scroll 150, and a bearing shock absorbing portion 1343 may be arranged in the frame-side thrust surface 134a in contact with the bearing plate 180 such that a portion of the bearing plate 18 is spaced apart from the frame-side thrust surface 134a. Accordingly, the bearing plate 180 elastically absorbs an axial load between the main frame 130 and the orbiting scroll 150, thereby suppressing friction loss and/or abrasion between the main frame 130 and/or the orbiting scroll 150 and the bearing plate 180 facing the main frame 130 and/or the orbiting scroll 150.

FIG. 3 is an assembled plan view showing a portion of the compression unit in the scroll compressor according to this embodiment. FIG. 4 is a sectional view taken along line "IV-IV" of FIG. 3. FIG. 5 is a sectional view showing another embodiment of the main frame in FIG. 3.

Referring back to FIG. 2, the orbiting space portion 133 may be formed to be recessed at the center of the upper surface of the main frame 130, the scroll support portion 134 may be formed to protrude in an annular shape along the circumference of the orbiting space portion 133, and the Oldham ring support portion 135 may be formed recessed to surround the scroll support portion 134 at the outside of the scroll support portion 134. Therefore, the scroll support portion 134 may be formed in an annular projection shape protruding in the axial direction between the orbiting space portion 133 and the Oldham ring support portion 135.

In this case, at least one of an inner circumferential surface of the scroll support portion 134, which is connected to the orbiting space portion 133, and an outer circumferential surface of the scroll support portion 134, which is connected to the Oldham ring support portion 135, may be formed in a smooth tubular shape. For example, each of the inner circumferential surface and the outer circumferential surface of the scroll support portion 134 may be formed in a smooth tubular shape, and the bearing shock absorbing portion 1343 to be described later may be formed in the frame-side thrust surface 134a to elastically support the bearing plate 180. Thus, although a separate elastic portion such as a trepan structure is not formed in the scroll support portion 134, an axial load of the orbiting scroll 150 can be elastically absorbed. Accordingly, the scroll support portion 134 can be easily processed, and friction loss and/or abrasion between the orbiting scroll 150 and the main frame 130 (exactly, between the orbiting scroll and the bearing plate and/or between the main frame and the bearing plate) can be effectively suppressed. The bearing shock absorbing portion 1343 along with a bearing support portion 1341 and a bearing accommodation portion 1342 will be again described later.

Referring to FIGS. 2 to 4, the scroll support portion 134 of the main frame 130 according to this embodiment may include the frame-side thrust surface 134a facing the scroll-side thrust surface 151a of the orbiting scroll 150, and the frame-side thrust surface 134a may be formed to have a plurality of heights. Accordingly, as the bearing plate 180 located between the frame-side thrust surface 134a and the scroll-side thrust surface 151a elastically varies, a shock absorbing effect of an axial load between the main frame 130 and the orbiting scroll 150 can be improved.

For example, the bearing plate 180 may be inserted between the frame-side thrust surface 134a forming an end surface of the scroll support portion 134 and the scroll-side thrust surface 151a of the orbiting scroll 150, which faces the frame-side thrust surface 134a in the axial direction. The bearing plate 180 may be made of a metal material having a hardness higher than those of the main frame 130 and the orbiting scroll 150. Accordingly, the reliability of the bearing plate 180 can be improved, and friction loss and/or abrasion between the bearing plate 180 and the main frame 130 and/or the orbiting scroll 150, facing the bearing plate 180 can be effectively suppressed.

In this case, the bearing plate 180 may be formed in an annular shape, and each of one surface of the bearing plate 180, which faces the frame-side thrust surface 134a, and the other surface of the bearing plate 180, which faces the scroll-side thrust surface 151a, may be formed flat along the circumferential direction. Accordingly, a bearing area between the bearing plate 180 and both the thrust surfaces 134a and 151a facing the bearing plate 180 is secured as wide as possible, so that an increase in surface pressure due to a decrease in the bearing area can be minimized.

Although not shown in the drawings, the bearing plate 180 may be formed in an annular shape, and at least a portion of the bearing plate 180 may be formed to be bent along the circumferential direction. Accordingly, the self-elasticity in the bearing plate 180 more elastically supports to the orbiting scroll 15, and an oil supply path between the bearing plate 180 and both the thrust surfaces 134a and 151a is secured, thereby improving a lubricating effect.

Referring to FIGS. 3 and 4, the end surface, i.e., the frame-side thrust surface 134a of the scroll support portion 134 according to this embodiment may include the bearing support portion 1341, the bearing accommodation portion 1342, and the bearing shock absorbing portion 1343. The bearing support portion 1341 is a portion that supports the bearing plate 180 to be described later in the axial direction, the bearing accommodation portion 1342 is a portion that accommodates the bearing plate 180 and supports the bearing plate 180 in the radial direction, and the bearing shock absorbing portion 1343 is a portion that forms a deformation space such that the bearing plate 180 can be elastically deformed in the axial direction. Accordingly, with respect to a state in which the compressor is stopped, at least portions of the bearing support portion 1341 and the bearing accommodation portion 1342 may be in sliding contact with the bearing plate 180, and the bearing shock absorbing portion 1343 may be spaced apart from the bearing plate 180.

Referring to FIGS. 3 and 4, the bearing support portion 1341 may be formed in a substantially annular shape at the outer circumferential side of the frame-side thrust surface 134a. For example, the bearing support portion 1341 may be formed flat, and a radial width D1 of the bearing support portion 1341 may be equally formed along the circumferential direction. Accordingly, as the bearing area of the bearing support portion 1341 is equally formed along the circumferential direction, the bearing plate 180 can be stably supported.

Referring to FIGS. 3 and 4, the bearing accommodation portion 1342 may be formed to protrude by a predetermined height toward the orbiting scroll 150 from an outer circumferential surface of the frame-side thrust surface 134a, i.e., an outer circumferential side edge of the bearing support portion 1341. For example, the bearing accommodation portion 1342 may be formed to be stepped with respect to the bearing support portion 1341. Accordingly, as the bearing plate 180 placed on the bearing support portion 1341 is restricted in the radial direction by the bearing accommodation portion 1342, the reliability of the bearing plate 180 can be ensured.

In this case, the bearing accommodation portion 1342 may be formed in an annular shape, or may include a plurality of projections spaced apart from each other along the circumferential direction in some cases. In the former, the bearing accommodation portion 1342 can be easily processed, and the bearing plate 180 can be stably supported in the radial direction. In the latter, friction loss between the bearing accommodation portion 1342 and the bearing plate 180 can be reduced, and the oil of the orbiting space portion 133 can smoothly flow to the Oldham ring support portion 135 as an oil flow path is formed in the circumferential direction in the bearing accommodation portion 1342. This enables the oil to more smoothly flow by appropriately locating the position of an oil supply groove 1341a to be described later when the oil supply groove 1341a is formed in the bearing support portion 1341. In this embodiment, an example is illustrated in which the bearing accommodation portion 1342 is formed in the annular shape.

In addition, an axial height H1 of the bearing accommodation portion 1342 may be formed smaller than or equal to a thickness T1 of the bearing plate 180. For example, the axial height H1 of the bearing accommodation portion 1342 may be formed slightly smaller than the thickness T1 of the bearing plate 180. Accordingly, friction loss and/or abrasion between the orbiting scroll 150 and the bearing accommodation portion 1342 can be suppressed during an orbiting motion of the orbiting scroll 150.

In addition, a radial width D2 of the bearing accommodation portion 1342 may be formed smaller than or equal to the radial width D1 of the bearing support portion 1341. For example, the radial width D2 of the bearing accommodation portion 1342 may be formed smaller than the radial width D1 of the bearing support portion 1341. Accordingly, the friction loss and/or abrasion between the orbiting scroll 150 and the bearing accommodation portion 1342 can be suppressed during the orbiting motion of the orbiting scroll 150.

Referring to FIGS. 2 to 4, the bearing shock absorbing portion 1343 may be formed at the opposite side of the bearing accommodation portion 1342 with respect to the bearing support portion 1341, i.e., an inner circumferential side of the bearing support portion 1341. For example, the bearing shock absorbing portion 1343 may extend in the radial direction toward the inner circumferential surface of the scroll support portion 134 from an inner circumferential end of the bearing support portion 1341. Therefore, the bearing shock absorbing portion 1343 may be formed continuously from the bearing support portion 1341.

Specifically, the bearing shock absorbing portion 1343 may be formed in an annular shape, and a radial width D3 of the bearing shock absorbing portion 1343 may be equally formed along the circumferential direction. Therefore, an elastic force (or shock absorbing force) of the bearing plate 180 may be equally or almost equally formed along the circumferential direction.

The bearing shock absorbing portion 1343 according to this embodiment may be formed to be inclined. In other words, an outer circumferential side height (or outer circumferential side depth) H31 of the bearing shock absorbing portion 1343 and an inner circumferential side height (or inner circumferential side depth) H32 of the bearing shock absorbing portion 1343 may be formed different from each other. For example, the inner circumferential side height H32 of the bearing shock absorbing portion 1343 distant from the bearing support portion 1341 may be formed larger than the outer circumferential side height H31 of the bearing shock absorbing portion 1343 adjacent to the bearing support portion 1341. Therefore, as the gap between the bearing shock absorbing portion 1343 and the bearing plate 180 increases as approaching an inner circumferential side from an outer circumferential side of the bearing shock absorbing portion 1343, a height in the bearing shock absorbing portion forming the inner circumferential side of the frame-side thrust surface 134a may be formed smaller than a height in the bearing support portion 1341 forming the outer circumferential side of the frame-side thrust surface 134a. Accordingly, as a bearing deformation space (or bearing shock absorbing space) is formed in the inner circumferential side of the frame-side thrust surface 134a by a height (or depth) H3 of the bearing shock absorbing portion 1343, an inner circumferential side of the bearing plate 180 can be elastically deformed.

The bearing shock absorbing portion 1343 may include at least one inclined surface 1343a. In other words, the bearing shock absorbing portion 1343 may include one inclined surface (e.g., an inclination angle) 1343a as shown in FIG. 4 or may include a plurality of inclined surfaces (e.g., inclination angles) 1343a1 and 1343a2 formed continuously as shown in FIG. 5. In the case of the former, as the bearing shock absorbing portion 1343 includes a single inclined surface, the bearing shock absorbing portion 1343 can be easily processed. In the case of the latter, as the plurality of inclined surfaces 1343a1 and 1343a2 are formed, the height (or depth) H3 of the bearing shock absorbing portion 1343 can be properly adjusted. For example, when the bearing shock absorbing portion 1343 includes a first inclined surface 1343a1 and a first inclined surface 1343a2, a first inclination angle α1 of the first inclined surface 1343a1 continued from the bearing support portion 134 may be formed smaller than a second inclination angle α2 of the first inclined surface 1343a2 continued from the first inclined surface 1343a1. Accordingly, in the case of the latter, the height H3 of the bearing shock absorbing portion 1343 in contact with the bearing plate 180 gradually decreases, so that a physical bearing force of the bearing shock absorbing portion 1343 to the bearing plate 180 can be secured. In this embodiment, an example is illustrated in which the bearing shock absorbing portion 1343 includes one inclined surface 1343a.

Referring to FIG. 4, the bearing shock absorbing portion 1343 may be formed to have one inclination angle α with respect to the bearing support portion 1341. For example, the bearing shock absorbing portion 1343 may be formed to have the inclination angle α which is within about 45 degrees, i.e., greater than 0 degree and smaller than or equal to 45 degrees with respect to the bearing support portion 1341. Accordingly, as the bearing shock absorbing portion 1343 is formed lower than the bearing support portion 1341 with respect to a lower surface of the orbiting space portion 133 as described above, the bearing deformation space (shock absorbing space) can be formed in which the inner circumferential side of the bearing plate 180 can be elastically deformed on the frame-side thrust surface 134a.

In this case, the radial width D3 of the bearing shock absorbing portion 1343 may be formed smaller than the radial width D1 of the bearing support portion 1341 or may be formed larger than the radial width D1 of the bearing support portion 1341. In the case of the former, as the area of the baring support portion 1341 physically supporting the bearing plate 180 increases, the reliability of the bearing plate 180 can be improved. On the other hand, in the case of the latter, as the radial width D3 of the bearing shock absorbing portion 1343 increases, the elastic force (shock absorbing force) of the bearing plate 180 is increased to that extent, so that the shock absorbing effect of an axial load can be improved. In this embodiment, the radial width D3 is appropriately added/subtracted by considering the thickness T1 of the bearing plate 180, and may be formed to become about 15% to 70% of a radial width D4 of the bearing plate 180.

FIG. 6 is a graph showing surface pressure improvement rate depending on radial width of the bearing shock absorbing portion according to this embodiment. Referring to this, a surface pressure improvement depending on the radial width D3 of the bearing shock absorbing portion 1343 varies according to the thickness T1 of the bearing plate 180, but it can be seen that the surface pressure improvement rate is relatively greatly improved when the radial width D3 of the bearing shock absorbing portion 1343 is within about 15% to 70% of the radial width D4 of the bearing plate 180.

For example, when the thickness T1 of the bearing plate 180 is 2 mm, it can be seen that the surface pressure improvement rate is greatly improved while a shock absorbing period rate obtained by dividing the radial width D3 of the bearing shock absorbing portion 1343 by the radial width D4 of the bearing plate 180 comes close to about 15%, and on the other hand, the surface pressure improvement rate is greatly decreased when the shock absorbing period rate passes through about 70%. Therefore, the shock absorbing period rate obtained by dividing the radial width D3 of the bearing shock absorbing portion 1343 by the radial width D4 of the bearing plate 180 may be formed to be about 15% to 70%.

Meanwhile, a case where another embodiment of the scroll support portion exists is as follows.

That is, the bearing shock absorbing portion is formed to be inclined in the above-described embodiment, but may be formed to be stepped in some cases.

FIG. 7 is a sectional view showing another embodiment of the bearing shock absorbing portion. FIG. 8 is a sectional view showing still another embodiment of the bearing shock absorbing portion in FIG. 7.

Referring back to FIGS. 1 and 2, a basic configuration and an operation effect according thereto in a scroll compressor according to an embodiment may be identical or almost identical to those of the above-described embodiment. For example, the scroll compressor according to this embodiment may be configured as a scroll compressor of a low pressure type and an upper compression type, in which the annular shaped bearing plate 180 is inserted between the main frame 130 and the orbiting scroll 150 as described above.

In this case, the orbiting scroll 150 may be supported in the axial direction by the upper surface of the main frame 130, and the annular shaped bearing plate 180 may be located between the frame-side thrust surface 134a of the main frame 130 and the scroll-side thrust surface 151a of the orbiting scroll 150, which faces the frame-side thrust surface 134a of the main frame 130. A bearing shock absorbing portion 1343 may be formed lower than the bearing support portion 1341 in the upper surface of the main frame 130, i.e., the frame-side thrust surface 134a. Therefore, a bearing shock absorbing space that allows an elastic deformation of the bearing plate 180 may be formed in the frame-side thrust surface 134a such that an axial load transferred to the bearing plate 180 is absorbed. Accordingly, friction loss and/or abrasion occurring between the main frame 130 and the bearing plate 180 and between the orbiting scroll 150 and the bearing plate 180 can be effectively suppressed.

However, in this embodiment, the bearing shock absorbing portion 1343 may be formed to be stepped toward the inner circumferential surface of the scroll support portion 134 from the bearing support portion 1341. In other words, the bearing shock absorbing portion 1343 may include at least one stepped surface 1343b. For example, the bearing shock absorbing portion 1343 may include one stepped surface 1343b as shown in FIG. 7 or may include a plurality of stepped surfaces 1343b1 and 1343b2 formed continuously as shown in FIG. 8. In the case of the former, the bearing shock absorbing portion 1343 can be easily processed, and a shock absorbing space capable of absorbing a deformation of the bearing plate 180 can be appropriately secured. In the case of the latter, as the bearing shock absorbing portion 1343 includes the plurality of stepped surfaces 1343b1 and 1343b2, a height (or depth) H3 of the bearing shock absorbing portion 1343 can be properly adjusted. For example, when the bearing shock absorbing portion 1343 includes a first stepped surface 1343b1 and a second stepped surface 1343b2, an axial height H33 and/or a radial width D31 of the first stepped surface 1343b1 continued from the bearing support portion 1341 may be formed smaller than an axial height H34 and/or a radial width D32 of the second stepped surface 1343b2 continued from the first stepped surface 1343b1. Accordingly, in the case of the latter, a height H3 of the bearing shock absorbing portion facing the bearing plate 180 gradually decreases, so that the physical bearing force of the bearing shock absorbing portion 1343 to the bearing plate 180 can be improved. In this embodiment, an example is illustrated in which the bearing shock absorbing portion 1343 includes one stepped surface.

In this case, a radial width D3 of the bearing shock absorbing portion 1343 may be formed smaller or larger than the radial width D1 of the bearing support portion 1341. Accordingly, when the radial width D3 of the bearing shock absorbing portion 1343 is formed smaller than the radial width D1 of the bearing support portion 1341, the area of the bearing support portion 1341 physically supporting the bearing plate 180 increases, thereby improving the reliability of the bearing plate 180. On the other hand, in the case of the latter, as the radial width D3 of the bearing shock absorbing portion 1343 increases, the elastic force (shock absorbing force) of the bearing plate 180 can be improved to that extent. Like the above-described embodiment, in this embodiment, the radial width D3 is appropriately added/subtracted by considering the thickness of the bearing plate 180, and may be formed to become about 15 % to 70% of the radial width D4 of the bearing plate 180.

Meanwhile, a case where still another embodiment of the scroll support portion exists is as follows.

That is, the bearing support portion is formed flat in the above-described embodiments, but an oil supply groove may be formed in the bearing support portion in some cases.

FIG. 9 is an exploded perspective view showing another embodiment of the bearing support portion. FIG. 10 is a sectional view showing the bearing support portion in FIG. 9.

Referring back to FIGS. 1 and 2, a basic configuration and an operation effect according thereto in a scroll compressor according to an embodiment may be identical or almost identical to those of the above-described embodiment. For example, the scroll compressor according to this embodiment may be configured as a scroll compressor of a low pressure type and an upper compression type, in which the annular shaped bearing plate 180 is inserted between the main frame 130 and the orbiting scroll 150 as described above.

In this case, the orbiting scroll 150 may be supported in the axial direction by the upper surface of the main frame 130, and the annular shaped bearing plate 180 may be located between the frame-side thrust surface 134a of the main frame 130 and the scroll-side thrust surface 151a of the orbiting scroll 150, which faces the frame-side thrust surface 134a of the main frame 130. The bearing shock absorbing portion 1343 may be formed lower than the bearing support portion 1341 in the upper surface of the main frame 130, i.e., the frame-side thrust surface 134a. Therefore, a bearing shock absorbing space that allows an elastic deformation of the bearing plate 180 may be formed in the frame-side thrust surface 134a such that an axial load transferred to the bearing plate 180 is absorbed. Accordingly, friction loss and/or abrasion occurring between the main frame 130 and the bearing plate 180 and between the orbiting scroll 150 and the bearing plate 180 can be effectively suppressed.

However, referring to FIGS. 9 and 10, in this embodiment, at least one oil supply groove 1341a may be formed in the bearing support portion 1341 constituting the frame-side thrust surface 134a. For example, the oil supply groove 1341a may be formed long in the radial direction, and a plurality of oil supply grooves 1341a may be formed at a predetermined interval along the circumferential direction. Accordingly, the oil is introduced between the bearing support portion 1341 and a lower surface of the bearing plate 180 facing the bearing support portion 1341 in the axial direction, to effectively lubricate between the main frame (exactly, the bearing support portion) 130 and the bearing plate 180.

In this case, the plurality of oil supply grooves 1341a may be formed to be open toward the orbiting space portion 133. In other words, an inner end of each of the plurality of oil supply grooves 1341a may be formed to overlap the bearing shock absorbing portion 1343. Accordingly, the oil in the orbiting space portion 133 is quickly introduced into the oil supply grooves 1341, to more effectively lubricate between the main frame 130 and the bearing plate 180.

Also, in this case, as the above-described bearing accommodation portion 1342 is formed in an annular shape at an outer circumferential side of the bearing support portion 1341, an outer end of each oil supply groove 1341a is blocked by the bearing accommodation portion 1342. Therefore, a portion of the oil introduced into the oil supply groove 1341 may be stored in the oil supply groove 1341a. Accordingly, friction loss and/or abrasion between the main frame 130 and the bearing plate 180 during initial start-up and/or a short operation can be effectively suppressed.

Although not shown in the drawings, the oil supply groove 1341a may be formed in the scroll-side thrust surface 151a of the orbiting scroll 150. In this case, an inner end of the oil supply groove 1341a may extend further inwardly of an inner circumferential surface of the bearing plate 180. Accordingly, the oil in the orbiting space portion 133 is quickly introduced into the oil supply groove 1341a, to more effectively lubricate between the orbiting scroll 150 and the bearing plate 180.

Meanwhile, a case where still another embodiment of the scroll support portion exists is as follows.

That is, the bearing accommodation portion is formed in an annular shape in the above-described embodiments, but may include a plurality of projections in some cases.

FIG. 11 is an exploded perspective view showing still another embodiment of the bearing support portion. FIG. 12 is a sectional view showing the bearing support portion in FIG. 11.

Referring back to FIGS. 1 and 2, a basic configuration and an operation effect according thereto in a scroll compressor according to an embodiment may be identical or almost identical to those of the above-described embodiment. For example, the scroll compressor according to this embodiment may be configured as a scroll compressor of a low pressure type and an upper compression type, in which the annular shaped bearing plate 180 is inserted between the main frame 130 and the orbiting scroll 150 as described above.

In this case, the orbiting scroll 150 may be supported in the axial direction by the upper surface of the main frame 130, and the annular shaped bearing plate 180 may be located between the frame-side thrust surface 134a of the main frame 130 and the scroll-side thrust surface 151a of the orbiting scroll 150, which faces the frame-side thrust surface 134a of the main frame 130. The bearing shock absorbing portion 1343 may be formed lower than the bearing support portion 1341 in the upper surface of the main frame 130, i.e., the frame-side thrust surface 134a. Therefore, a bearing shock absorbing space that allows an elastic deformation of the bearing plate 180 may be formed in the frame-side thrust surface 134a such that an axial load transferred to the bearing plate 180 is absorbed. Accordingly, friction loss and/or abrasion occurring between the main frame 130 and the bearing plate 180 and between the orbiting scroll 150 and the bearing plate 180 can be effectively suppressed.

However, referring to FIGS. 11 and 12, a bearing accommodation portion 1342 protruding in the axial direction may be formed at the outer circumferential side of the bearing support portion 1341, and a plurality of bearing accommodation portions 1342 may be formed at a predetermined interval along the circumferential direction. For example, the plurality of bearing accommodation portions 1342 may be formed one by one to be spaced apart from each other along the circumferential direction. Thus, the contact area between an inner circumferential surface of the bearing accommodation portion 1342 and an outer circumferential surface of the bearing plate 180, which faces the inner circumferential surface of the bearing accommodation portion 1342, can be reduced. Accordingly, friction loss and/or abrasion between the bearing accommodation portion and the bearing plate 180 can be reduced.

In this case, a circumferential length of the bearing accommodation portion 1342 may be formed smaller than or equal to a half of a circumferential length of the bearing plate 180. Accordingly, the above-described friction loss and/or abrasion between the bearing accommodation portion 1342 and the bearing plate 180 can be more effectively reduced.

Also, in this case, the bearing support portion 1341 may be formed flat like the embodiment of FIG. 2, or oil supply grooves 1341a may be formed in the bearing support portion 1341 like the embodiment of FIG. 11. When the oil supply grooves 1341a are formed in the bearing support portion 1341 like the embodiment of FIG. 11, each of at least some of the oil supply grooves 1341a may be formed to be located in a circumferential gap 1342a between the bearing support portion 1341 and the bearing accommodation portion 1342. In other words, inner ends of at least some of the oil supply grooves 1341a may be formed to communicate with the orbiting space portion 133, and outer ends of at least some of the oil supply grooves 1341a may be formed to communicate with the Oldham ring support portion 135. Thus, a portion of the oil introduced to the frame-side thrust surface 134a of the scroll support portion 134 from the orbiting space portion 133 can quickly flow to the Oldham ring support portion 135 through the oil supply grooves 1341a. Accordingly, as the oil is quickly supplied between the upper surface of the Oldham ring support portion 135 and the Oldham ring 170 supported in the axial direction by the upper surface of the Oldham ring support portion 135, friction loss and/or abrasion between the main frame 130 and the Oldham ring 170 can be suppressed. At the same time, behavior of the Oldham ring 170 and/or the orbiting scroll 150 is stabilized, so that leakage between the compression chambers V1 and V2 can be suppressed.

Claims

1. A scroll compressor comprising:

a casing;
an orbiting scroll coupled to a rotary shaft inside the casing to perform an orbiting motion;
a non-orbiting scroll forming a compression chamber together with the orbiting scroll;
a main frame fixed to the casing in an internal space of the casing and supporting the orbiting scroll in an axial direction; and
a bearing plate located between a thrust surface of the main frame and a thrust surface of the orbiting scroll, which faces the thrust surface of the main frame,
wherein the thrust surface of the main frame comprises: a bearing support portion supporting the bearing plate in the axial direction; and a bearing shock absorbing portion extending to an inner circumferential side thereof from the bearing support portion to allow an axial deformation of the bearing plate, and wherein a height of the bearing shock absorbing portion is formed smaller than a height of the bearing support portion.

2. The scroll compressor of claim 1, wherein the bearing shock absorbing portion comprises at least one inclined surface, and wherein the inclined surface is formed to be inclined downwardly from an outer circumferential side of the bearing shock absorbing portion, which is in contact with the bearing support portion, to the inner circumferential side of the bearing shock absorbing portion.

3. The scroll compressor of claim 2, wherein the bearing shock absorbing portion comprises a plurality of inclined surfaces having different inclination angles, which are formed continuously along a radial direction, and wherein the plurality of inclined surfaces are formed such that the inclination angles increase as becoming distant from the bearing support portion.

4. The scroll compressor of claim 1, wherein the bearing shock absorbing portion comprises at least one stepped surface.

5. The scroll compressor of claim 4, wherein the bearing shock absorbing portion comprises a plurality of stepped surfaces formed continuously along the radial direction, and wherein the plurality of stepped surfaces are formed to have a same axial height and/or a same radial width.

6. The scroll compressor of claim 4, wherein the bearing shock absorbing portion comprises a plurality of stepped surfaces formed continuously along the radial direction, and wherein the plurality of stepped surfaces are formed such that an axial height and/or a radial width of an inner circumferential side stepped surface is larger than an axial height and/or a radial width of an outer circumferential side stepped surface.

7. The scroll compressor of claim 1, wherein a radial width of the bearing shock absorbing portion is equally formed along a circumferential direction.

8. The scroll compressor of claim 7, wherein the radial width of the bearing shock absorbing portion is formed to become 15% to 17% of a radial width of the bearing plate.

9. The scroll compressor of claim 1, wherein the main frame comprises a bearing accommodation portion extending in the axial direction from the bearing support portion to support an outer circumferential surface of the bearing plate in a radial direction, and wherein an inner diameter of the bearing accommodation portion is formed larger than or equal to an outer diameter of the bearing plate.

10. The scroll compressor of claim 9, wherein the bearing accommodation portion is formed in an annular shape or comprises a plurality of projections spaced apart from each other along the circumferential direction.

11. The scroll compressor of claim 9, wherein the bearing accommodation portion comprises a plurality of projections spaced apart from each other along the circumferential direction, and at least one oil supply groove is formed in the bearing support portion, and wherein at least some of the oil supply grooves are formed between the plurality of bearing accommodation portions.

12. The scroll compressor of claim 1, wherein an oil supply groove is formed in at least one of the main frame and the orbiting scroll, and wherein at least a portion of the oil supply groove is formed to overlap an axial surface of the bearing plate in the axial direction.

13. The scroll compressor of claim 12, wherein the oil supply groove is formed in the bearing support portion of the main frame, and wherein one end of the oil supply groove is formed to be connected to the bearing shock absorbing portion.

14. The scroll compressor of claim 12, wherein the oil supply groove is formed in the thrust surface of the orbiting scroll, and wherein one end of the oil supply groove extends inwardly of an inner circumferential surface of the bearing plate.

15. The scroll compressor of claims claim 1, wherein the main frame comprises:

an orbiting space portion in which the rotary shaft is coupled to the orbiting scroll to perform an orbiting motion;
a scroll support portion extending in the axial direction from the orbiting space portion to comprise the bearing support portion and the bearing shock absorbing portion; and
an Oldham ring support portion surrounding an outer circumferential side of the scroll support portion, and
wherein at least one of an inner circumferential surface of the scroll support portion, which is connected to the orbiting space portion, and an outer circumferential surface of the scroll support portion, which is connected to the Oldham ring support portion, is formed in a smooth tubular shape.

16. The scroll compressor of claim 15, wherein each of the inner circumferential surface and the outer circumferential surface of the scroll support portion is formed in a smooth tubular shape.

17. A scroll compressor comprising:

a casing;
an orbiting scroll coupled to a rotary shaft inside the casing to perform an orbiting motion;
a non-orbiting scroll forming a compression chamber together with the orbiting scroll;
a main frame fixed to the casing in an internal space of the casing and supporting the orbiting scroll in an axial direction; and
a bearing plate located between a thrust surface of the main frame and a thrust surface of the orbiting scroll, which faces the thrust surface of the main frame,
wherein the thrust surface of the main frame comprises: a bearing support portion supporting the bearing plate in the axial direction; and a bearing shock absorbing portion extending to an inner circumferential side thereof from the bearing support portion to allow an axial deformation of the bearing plate, wherein a height of the bearing shock absorbing portion is formed smaller than a height of the bearing support portion, wherein the bearing shock absorbing portion comprises at least one inclined surface or at least one stepped surface, wherein an oil supply groove is formed in at least one of the main frame and the orbiting scroll, and wherein at least a portion of the oil supply groove is formed to overlap an axial surface of the bearing plate in the axial direction.

18. The scroll compressor of claim 17, wherein the oil supply groove is formed in the bearing support portion of the main frame, and wherein one end of the oil supply groove is formed to be connected to the bearing shock absorbing portion.

19. The scroll compressor of claim 17, wherein the oil supply groove is formed in the thrust surface of the orbiting scroll, and wherein one end of the oil supply groove extends inwardly of an inner circumferential surface of the bearing plate.

20. The scroll compressor of claims claim 17, wherein the main frame comprises:

an orbiting space portion in which the rotary shaft is coupled to the orbiting scroll to perform an orbiting motion;
a scroll support portion extending in the axial direction from the orbiting space portion to comprise the bearing support portion and the bearing shock absorbing portion; and
an Oldham ring support portion surrounding an outer circumferential side of the scroll support portion, and
wherein at least one of an inner circumferential surface of the scroll support portion, which is connected to the orbiting space portion, and an outer circumferential surface of the scroll support portion, which is connected to the Oldham ring support portion, is formed in a smooth tubular shape.
Patent History
Publication number: 20260243255
Type: Application
Filed: Dec 30, 2025
Publication Date: Aug 20, 2026
Inventors: Changeol Jo (Seoul), Jeonghun Kim (Seoul), Sangwoo Joo (Seoul), Juhwan Yun (Seoul)
Application Number: 19/436,121
Classifications
International Classification: F04C 18/02 (20060101);