KR20230163192A - Scroll compressor - Google Patents

Abstract

A scroll compressor is disclosed. In the scroll compressor, the outer peripheral surface of the rotating shaft coupling portion of the orbiting scroll and/or the inner peripheral surface of the orbiting space portion of the main frame radially facing the outer peripheral surface of the rotating shaft coupling portion may be formed to be inclined with respect to the axial direction of the rotating shaft of the driving motor. Through this, the oil stored in the pivot space can easily rise along the outer peripheral surface of the rotating shaft coupling portion and/or the inner peripheral surface of the pivot space and can easily reach the axial bearing surface. Therefore, the efficiency of the compressor can be increased by reducing friction on the axial bearing surface.

Description

Scroll compressor{SCROLL COMPRESSOR}

The present invention relates to scroll compressors, and particularly to variable radius scroll compressors.

Compared to other types of compressors, scroll compressors have the advantage of being able to achieve a relatively high compression ratio because they are continuously compressed through interlocking scroll shapes, and the suction, compression, and discharge strokes of the refrigerant are smoothly connected to obtain stable torque. For this reason, scroll compressors are widely used for refrigerant compression in air conditioning equipment, etc.

Scroll compressors can be classified into an upper compression type or a lower compression type depending on the location of the compression section and the drive motor that forms the driving or transmission section. The upper compression type is a type in which the compression part is located above the drive motor, and the bottom compression type is a type in which the compression part is located below the drive motor. This is a classification based on the case where the casing is installed vertically or vertically. If the casing is installed horizontally, the left side can be divided into the upper side and the right side can be divided into the lower side.

Additionally, scroll compressors can be divided into high-pressure and low-pressure types depending on the way the refrigerant is sucked. The high-pressure type is a method in which the refrigerant suction pipe communicates directly with the suction chamber and the inhaled refrigerant is sucked into the compression chamber (suction chamber) without passing through the inner space of the casing. The low-pressure type is a method in which the refrigerant suction pipe communicates with the inner space of the casing and the inhaled refrigerant is suctioned into the compression chamber (suction chamber). This method involves passing through the internal space of the casing and then being sucked into the compression chamber (suction chamber).

Patent Document 1 (US Patent Publication US 2015/0345493 A1) shows a scroll compressor that is a top compression type and a low pressure type.

Meanwhile, scroll compressors can be divided into fixed radius type and variable radius type depending on the turning method of the orbiting scroll. The fixed radius type is a type in which the orbiting scroll always rotates along the same trajectory regardless of changes in compression conditions, and the variable radius type is a type in which the orbiting scroll rotates when liquid refrigerant, oil, or foreign substances enter the compression chamber and the pressure in the compression chamber rises abnormally. This is a method that prevents damage to the swing wrap and non-swivel wrap while retreating in the radial direction. Patent Document 2 (Japanese Patent Publication 2009-235991 A) shows a scroll compressor of the upper compression type, low pressure type, and variable radius type.

The top-compression, low-pressure, variable-radius scroll compressor (hereinafter abbreviated as variable-radius scroll compressor or scroll compressor) disclosed in Patent Document 2 compresses oil stored on the opposite side of the compression section through an oil passage penetrating between both ends of the rotating shaft. It is pumped and supplied to the compression section.

In these conventional scroll compressors, the lower end of the rotation shaft of the drive motor rotates while submerged in oil stored in the oil storage space of the casing. Then, the oil in the oil storage space is pumped by the oil pickup, and this oil is sucked along the oil passage of the rotating shaft and scattered to the outside of the oil passage. Some of this oil is supplied to the bearing surfaces between neighboring members through the internal space of the main frame to lubricate them.

However, in a typical scroll compressor including the conventional variable radius scroll compressor as described above, when the amount of oil pumped to the main frame is insufficient and the oil is not smoothly supplied to the bearing surfaces between neighboring members, the neighboring members Friction loss and/or wear increases on the bearing surfaces between the bearings. This causes the efficiency of the compressor to decrease. This can occur particularly frequently when starting the compressor.

US Published Patent US 2015/0345493 A1 (Publication Date: 2015.12.03.)

Japanese Patent Publication No. 2009-235991 A (Publication Date: 2009.10.15.)

The purpose of the present invention is to provide a scroll compressor that can suppress friction loss and/or wear due to oil shortage in the pivot space of the main frame.

Furthermore, the purpose of the present invention is to provide a scroll compressor in which oil flowing into the orbital space can be easily supplied to the axial bearing surface.

Furthermore, the purpose of the present invention is to provide a scroll compressor that can continuously supply a large amount of oil to the axial bearing surface.

In order to achieve the purpose of the present invention, a scroll compressor including a non-orbiting scroll, an orbiting scroll, and a main frame may be provided. The orbiting scroll can perform a pivoting movement relative to the non-orbiting scroll by extending from one side of the pivoting plate portion the rotating shaft coupling portion to which the rotating shaft of the drive motor is coupled. The main frame may be provided with a scroll support portion so that the orbiting mirror plate portion of the orbiting scroll is supported in the axial direction of the rotation axis of the drive motor, and the scroll support portion may be formed with a recessed orbiting space portion so that the rotation axis coupling portion of the orbiting scroll can be pivotably inserted. At least one of the outer peripheral surface of the rotating shaft coupling portion of the orbiting scroll and the inner peripheral surface of the orbiting space portion of the main frame facing it in the radial direction may be formed to be inclined with respect to the axial direction of the rotating shaft. Through this, the oil in the pivot space can easily rise along the outer peripheral surface of the rotating shaft coupling portion and/or the inner peripheral surface of the pivot space and can easily reach the axial bearing surface. Therefore, the efficiency of the compressor can be increased by reducing friction on the axial bearing surface.

For example, the rotating shaft coupling portion may be formed to be inclined so that the outer diameter increases in the direction toward the rotating mirror plate portion. Through this, when the rotary shaft coupling unit rotates, the oil stored in the pivot space can easily rise along the outer peripheral surface of the rotary shaft coupling unit while rotating along the rotary shaft coupling unit, allowing it to move more easily toward the scroll support unit.

Additionally, the orbiting space portion may be formed to be inclined so that its inner diameter increases in the direction toward the scroll support portion to correspond to the outer peripheral surface of the rotating shaft coupling portion. Through this, the oil rotating in the space between the inner peripheral surface of the rotating space portion and the outer peripheral surface of the rotating shaft coupling portion can rotate without obstructing the flow and can be uniformly supplied to the axial bearing surface.

As another example, an oil movement groove may be formed on at least one of the inner peripheral surface of the pivot space and the outer peripheral surface of the rotating shaft coupling portion. Through this, the oil in the orbiting space can easily rise along the oil movement groove under the influence of the rotational force caused by the rotation of the orbiting scroll, and can move more quickly to the axial bearing surface.

Specifically, the oil transfer groove formed on the inner peripheral surface of the pivot space portion and the outer peripheral surface of the rotating shaft coupling portion may be formed to be inclined at a predetermined angle based on the axial direction of the rotating shaft. Through this, the oil in the oil transfer groove can rise more quickly along the oil transfer groove under the influence of the rotational force caused by the rotation of the orbiting scroll.

More specifically, the oil movement groove may be inclined in the rotation direction of the rotation shaft as it moves from the main frame toward the orbiting scroll. Through this, the oil in the rotating space rotates in the same direction as the rotation direction of the rotating shaft, so if the oil moving groove is formed to be inclined in the turning direction of the oil, the oil can easily rise along the oil moving groove while rotating.

As another example, a plurality of oil moving grooves may be formed on the inner peripheral surface of the pivot space at predetermined intervals along the circumferential direction, and the spacing between the plurality of oil moving grooves may be the same or different from each other. Through this, a large amount of oil stored in the orbiting space can be moved to the axial bearing surface through the plurality of oil movement grooves formed in the orbiting space.

Additionally, a plurality of oil moving grooves may be formed on the outer peripheral surface of the rotating shaft coupling portion at predetermined intervals along the circumferential direction, and the spacing between the plurality of oil moving grooves may be the same or different from each other. Through this, a large amount of oil stored in the swing space can be moved to the axial bearing surface through the plurality of oil movement grooves.

As another example, the oil movement groove may be formed to have a predetermined length on the inner peripheral surface of the pivot space, and the cross-sectional area of the oil movement groove may be constant or different along the length of the oil movement groove. Through this, even if the oil stored in the orbiting space is insufficient and only the bottom of the orbiting space is filled with oil, the oil can move toward the scroll support portion along the oil movement groove that is continuously connected from one end of the orbiting space to the other end.

Additionally, the oil transfer groove may be formed to have a predetermined length on the outer peripheral surface of the rotating shaft coupling portion, and the cross-sectional area of the oil transfer groove may be constant or different along the length of the oil transfer groove. Through this, even if the oil stored in the pivot space is insufficient and only the bottom of the pivot space is filled with oil, the oil is greatly scattered under the influence of the rotation of the rotary shaft coupling portion, and at the same time, the oil is continuously connected from one end of the rotary shaft coupling portion to the other end. It can move toward the pivot plate along the moving groove.

As another example, one or more oil guide grooves may be formed in the scroll support portion facing the pivot plate portion. Through this, the oil rising along the inner circumferential surface of the orbiting space can easily move to the oil guide groove that is lower in height than the upper surface of the scroll support portion, and the oil in the oil guide groove is influenced by the rotation of the pivoting plate portion and moves to the upper surface of the scroll support portion. You can move. Therefore, the efficiency of the compressor can be increased by reducing friction on the upper surface of the scroll support part.

Additionally, the oil guide groove may communicate with an oil movement groove formed on the inner peripheral surface of the pivot space and/or the outer peripheral surface of the rotating shaft coupling portion. Through this, the oil rising along the oil movement groove of the pivot space can move directly to the communicating oil guide groove, and the oil can be supplied to the axial bearing surface more quickly.

In order to achieve another object of the present invention, a scroll compressor including a non-orbiting scroll, an orbiting scroll, and a main frame may be provided. The orbiting scroll can perform a pivoting movement relative to the non-orbiting scroll by extending from one side of the pivoting plate portion the rotating shaft coupling portion to which the rotating shaft of the drive motor is coupled. The main frame may be provided with a scroll support portion so that the orbiting mirror plate portion of the orbiting scroll is supported in the axial direction of the rotation axis of the drive motor, and the scroll support portion may be formed with a recessed orbiting space portion so that the rotation axis coupling portion of the orbiting scroll can be pivotably inserted. Additionally, an oil movement groove may be formed on at least one of the inner circumferential surface of the orbiting space portion of the main frame and the outer peripheral surface of the rotating shaft coupling portion of the orbiting scroll. Through this, the inner peripheral surface of the orbiting space portion is formed to be identical in the axial direction of the rotating shaft, thereby securing the axial bearing surface and stabilizing the behavior of the orbiting scroll. In addition, since the outer peripheral surface of the rotating shaft coupling portion is formed to be the same in the axial direction of the rotating shaft, the weight of the orbiting scroll can be reduced compared to the above-described embodiment, and thus the efficiency of the motor can be improved.

In the scroll compressor according to the present invention, at least one of the outer peripheral surface of the rotating shaft coupling portion of the orbiting scroll and the inner peripheral surface of the orbiting space portion of the main frame facing it in the radial direction may be formed to be inclined with respect to the axial direction of the rotating shaft. Through this, the oil stored in the pivot space can easily rise along the outer peripheral surface of the rotating shaft coupling portion and/or the inner peripheral surface of the pivot space and can easily reach the axial bearing surface. Therefore, the efficiency of the compressor can be increased by reducing friction on the axial bearing surface.

In the scroll compressor according to the present invention, an oil movement groove may be formed on one or more of the inner peripheral surface of the orbiting space portion and the outer peripheral surface of the rotating shaft coupling portion. Through this, the oil in the swing space can move more quickly to the axial bearing surface.

In the scroll compressor according to the present invention, a plurality of oil moving grooves may be formed on the inner peripheral surface of the pivot space and the outer peripheral surface of the rotating shaft coupling portion at predetermined intervals along the circumferential direction. Through this, a large amount of oil stored in the swing space can be moved to the axial bearing surface through the plurality of oil movement grooves.

In the scroll compressor according to the present invention, the oil movement groove may be formed to have a predetermined length on the inner peripheral surface of the orbiting space portion and the outer peripheral surface of the rotating shaft coupling portion. Through this, even if the oil stored in the pivot space is insufficient and only the bottom of the pivot space is filled with oil, the oil flows to the axial bearing surface along the oil transfer groove that is continuously connected from one end to the other end of the pivot space and the rotary shaft joint. You can move.

In the scroll compressor according to the present invention, one or more oil guide grooves may be formed in the scroll support portion facing the pivot plate portion. Through this, the oil rising along the inner circumferential surface of the orbiting space can easily move to the oil guide groove that is lower in height than the upper surface of the scroll support portion, and the oil in the oil guide groove is influenced by the rotation of the pivoting plate portion and moves to the upper surface of the scroll support portion. You can move. Therefore, the efficiency of the compressor can be increased by reducing friction on the upper surface of the scroll support part.

1 is a longitudinal cross-sectional view showing the inside of a scroll compressor according to this embodiment.
Figure 2 is a cross-sectional view showing the oil movement process in the turning space of Figure 1.
Figure 3 is a cross-sectional view showing the main frame and orbiting scroll of Figure 2.
Figure 4 is an embodiment in which an oil moving groove is formed in the pivot space and the rotating shaft coupling part of Figure 3.
Figure 5 shows another embodiment in which oil movement grooves are formed in the pivot space and the rotating shaft coupling portion.
Figure 6 is an embodiment in which an oil guide groove is formed in the scroll support part of Figure 4.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings.

Scroll compressors can be divided into high-pressure scroll compressors and low-pressure scroll compressors depending on the path through which the refrigerant is sucked. Hereinafter, a low-pressure scroll compressor will be described as an example, in which the internal space of the casing is divided into a low-pressure section and a high-pressure section by a high-low pressure separator, and the refrigerant suction pipe communicates with the low-pressure section.

In addition, scroll compressors can be divided into a non-orbiting back pressure method that pressurizes the non-orbiting scroll toward the orbiting scroll and a orbiting back pressure method that pressurizes the orbiting scroll toward the non-orbiting scroll according to the back pressure method. Hereinafter, the description will focus on the scroll compressor according to the non-swivel back pressure method. However, the same can be applied to the rotating back pressure method.

In addition, scroll compressors can be divided into a vertical scroll compressor whose rotation axis is arranged perpendicular to the ground and a horizontal scroll compressor whose rotation axis is arranged parallel to the ground. For example, in a vertical scroll compressor, the upper side may be defined as facing away from the ground, and the lower side may be defined as facing toward the ground. Hereinafter, a vertical scroll compressor will be described as an example. However, the same can be applied to horizontal scroll compressors.

In addition, scroll compressors can be divided into top compression type and bottom compression type depending on the relative position of the compression part with respect to the transmission unit. Hereinafter, the description will focus on the top compression type scroll compressor, which is vertical and has a compression unit located above the transmission unit.

In addition, scroll-type compressors can be divided into fixed-radius type and variable-radius type depending on the turning method of the orbiting scroll. Below, the description will focus on the variable radius scroll compressor.

1 is a longitudinal cross-sectional view showing the inside of a scroll compressor according to this embodiment.

Referring to FIG. 1, the scroll compressor according to this embodiment is provided with a drive motor 120 forming a transmission unit in the lower half of the casing 110, and a main frame 130 forming a compression unit on the upper side of the drive motor 120. , a non-orbiting scroll 140, an orbiting scroll 150, and a back pressure chamber assembly 160 are provided. The transmission part is coupled to one end of the rotation shaft 125, and the compression part is coupled to the other end of the rotation shaft 125. Accordingly, the compression unit is connected to the transmission unit by the rotation shaft 125 and operates by the rotational force of the transmission unit.

The casing 110 includes a cylindrical shell 111, an upper cap 112, and a lower cap 113.

The cylindrical shell 111 has a cylindrical shape with openings at both upper and lower ends, and the above-described drive motor 120 and main frame 130 are inserted and fixed to the inner peripheral surface. A terminal bracket (not shown) is coupled to the upper half of the cylindrical shell 111. A terminal (not shown) for transmitting external power to the drive motor 120 is coupled through the terminal bracket. A refrigerant suction pipe 117, which will be described later, penetrates and is coupled to the upper half of the cylindrical shell 111, for example, the upper side of the drive motor 120.

The upper cap 112 is coupled to cover the open top of the cylindrical shell 111. The lower cap 113 is coupled to cover the opened lower end of the cylindrical shell 111. The rim of the high and low pressure separator plate 115, which will be described later, is inserted between the cylindrical shell 111 and the upper cap 112 and welded together with the cylindrical shell 111 and the upper cap 112. The rim of a support bracket 116, which will be described later, is inserted between the cylindrical shell 111 and the lower cap 113 and welded together with the cylindrical shell 111 and the lower cap 113. Accordingly, the internal space of the casing 110 can be sealed.

The edge of the high and low pressure separator plate 115 is welded to the casing 110 as described above. The central portion of the high-low pressure separator plate 115 is bent to protrude toward the upper side of the upper cap 112 and is disposed on the upper side of the back pressure chamber assembly 160, which will be described later. A refrigerant suction pipe 117 is connected to the lower side of the high-low pressure separator 115, and a refrigerant discharge pipe 118 is connected to the upper side of the high-low pressure separator plate 115. Accordingly, a low-pressure part 110a forming a suction space may be formed on the lower side of the high-low pressure separator 115, and a high-pressure part 110b forming a discharge space may be formed on the upper side.

Additionally, a through hole 115a is formed in the center of the high and low pressure separator plate 115. A sealing plate 1151, from which a floating plate 165, which will be described later, is removable, is inserted and coupled to the through hole 115a. The low-pressure section 110a and the high-pressure section 110b may be blocked by attaching or detaching the floating plate 165 and the sealing plate 1151, or may communicate through the high-low pressure communication hole 1151a of the sealing plate 1151.

In addition, the lower cap 113 forms an oil storage space 110c together with the lower half of the cylindrical shell 111 forming the low pressure portion 110a. In other words, the oil storage space 110c is formed in the lower half of the low pressure part 110a, and the oil storage space 110c forms a part of the low pressure part 110a. An oil pickup 126, which will be described later, is immersed in the oil storage space 110c, and when the compressor is operating, the oil stored in the oil storage space 110c is pumped by the oil pickup 126 to the oil passage 1254 of the rotating shaft 125. It is supplied to the sliding part through.

Next, the driving motor will be described.

Referring to FIG. 1, the drive motor 120 according to this embodiment is installed in the lower half of the low-pressure part 110a and includes a stator 121 and a rotor 122. The stator 121 is fixed to the inner wall of the cylindrical shell 111 by hot pressing, and the rotor 122 is rotatably provided inside the stator 121.

The stator 121 includes a stator core 1211 and a stator coil 1212.

The stator core 1211 is formed in a cylindrical shape and is fixed to the inner peripheral surface of the cylindrical shell 111 by hot pressing. The stator coil 1212 is wound around the stator core 1211 and can be electrically connected to an external power source through a terminal (not shown) that is penetratingly coupled to the casing 110.

The rotor 122 includes a rotor core 1221 and a permanent magnet 1222.

The rotor core 1221 is formed in a cylindrical shape and is rotatably inserted into the stator core 1211 at intervals equal to a predetermined gap. The permanent magnets 1222 are embedded inside the rotor core 1222 at preset intervals along the circumferential direction.

Additionally, the rotating shaft 125 is press-fitted and coupled to the center of the rotor core 1221. An eccentric pin portion 1252 is provided at the top of the rotation shaft 125, so that the orbiting scroll 150, which will be described later, is eccentrically coupled. Accordingly, the rotational force of the drive motor 120 can be transmitted to the orbiting scroll 150 through the rotation shaft 125.

Meanwhile, the lower end of the rotation shaft 125 is coupled to the rotor 122 and the upper end is coupled to the orbiting scroll 150, which will be described later. Accordingly, the rotational force of the drive motor 120 is transmitted to the orbiting scroll 150 through the rotation shaft 125.

An oil passage 1254 is formed penetrating inside the rotating shaft 125. For example, the oil flow path 1254 passes between the bottom and top of the rotation shaft 125, and is formed to be inclined at a preset angle so as to move away from the axis center from the bottom to the top. Accordingly, centrifugal force is generated in the oil passage 1254, allowing oil to be smoothly supplied to the top of the rotating shaft 125.

An oil pickup 126 is provided at the bottom of the rotating shaft 125 to absorb oil stored in the oil storage space 110c of the casing 110. The oil pickup 126 can be applied to various applications such as centrifugal pumps, viscous pumps, and gear pumps. This embodiment shows an example in which a centrifugal pump is applied. Manufacturing costs can be reduced when centrifugal pumps are applied.

Next, the mainframe is explained.

Referring to FIG. 1, the main frame 130 according to this embodiment is installed on the upper side of the drive motor 120, and is fixed to the inner wall of the cylindrical shell 111 by hot pressing or welding.

The main frame 130 according to this embodiment includes a main flange portion 131, a main bearing portion 132, a pivoting space portion 133, a scroll support portion 134, an Oldham ring support portion 135, and a frame fixing portion 136. ) includes.

The main flange portion 131 is formed in an annular shape and is accommodated in the low pressure portion 110a of the casing 110. The outer diameter of the main flange portion 131 is smaller than the inner diameter of the cylindrical shell 111, so that the outer peripheral surface of the main flange portion 131 is spaced apart from the inner peripheral surface of the cylindrical shell 111. However, a frame fixing part 136, which will be described later, protrudes in the radial direction from the outer peripheral surface of the main flange part 131. The outer peripheral surface of the frame fixing part 136 is fixed in close contact with the inner peripheral surface of the casing 110. Accordingly, the frame 130 is fixedly coupled to the casing 110.

The main bearing portion 132 protrudes downward from the central lower surface of the main flange portion 131 toward the drive motor 120. The main bearing portion 132 has a cylindrical bearing hole 132a penetrating in the axial direction. A rotating shaft 125 is inserted into the inner peripheral surface of the bearing hole 132a and supported in the radial direction.

The pivoting space portion 133 is depressed from the center of the main flange portion 131 toward the main bearing portion 132 to a preset depth and outer diameter. The orbiting space 133 is formed to be larger than the outer diameter of the rotation shaft coupling portion 153 provided in the orbiting scroll 150, which will be described later. Accordingly, the rotation shaft coupling portion 153 can be rotatably accommodated within the pivot space portion 133.

The scroll support portion 134 is formed in an annular shape along the periphery of the pivot space portion 133 on the upper surface of the main flange portion 131. Accordingly, the scroll support portion 134 supports the lower surface of the turning disk portion 151, which will be described later, in the axial direction.

The Oldham ring support portion 135 is formed in an annular shape along the outer peripheral surface of the scroll support portion 134 on the upper surface of the main flange portion 131. Accordingly, the Oldham ring 170 is inserted into the Oldham ring support portion 135 and is rotatably received.

The frame fixing portion 136 extends radially from the outside of the Oldham ring support portion 135. The frame fixing portion 136 extends in an annular shape or with a plurality of protrusions spaced apart from each other by a predetermined distance along the circumferential direction. This embodiment shows an example in which the frame fixing portion 136 is formed of a plurality of protrusions along the circumferential direction.

Next, non-orbiting scrolling will be explained.

Referring to FIG. 1, the non-orbiting scroll 140 according to this embodiment is disposed on the upper part 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 or movably coupled to the main frame 130. This embodiment shows an example in which the non-orbiting scroll 140 is movably coupled to the main frame 130 in the axial direction.

The non-orbiting scroll 140 according to this embodiment includes a non-orbiting head plate portion 141, a non-orbiting wrap 142, a non-orbiting side wall portion 143, and a guide protrusion 144.

The non-swivel plate portion 141 is formed in a disk shape and is disposed laterally in the low pressure portion 110a of the casing 110. A discharge port 1411, a bypass hole 1412, and a scroll side pressure hole 1413 are each penetrated in the central portion of the non-swivel mirror plate portion 141 in the axial direction.

The discharge port 1411 is formed at a position where the discharge pressure chambers (not marked) of both compression chambers V formed inside and outside the non-circulating wrap 142 communicate with each other. The bypass hole 1412 is formed to communicate with both compression chambers (V). The scroll side back pressure hole (hereinafter referred to as the first back pressure hole) 1413 is spaced apart from the discharge port 1411 and the bypass hole 1412.

The non-swivel wrap 142 extends from the lower surface of the non-swivel head plate 141 facing the orbital scroll 150 to a preset height in the axial direction, and extends from the non-swivel side wall portion 143 around the discharge port 1411. It extends to be wound several times in a spiral direction. The non-swivel wrap 142 is formed to correspond to the swing wrap 152, which will be described later, and can form a pair of compression chambers (V) between the swing wraps 152 and the swing wrap 152.

The non-swivel side wall portion 143 extends in the axial direction from the lower edge of the non-swivel hard plate portion 141 to surround the non-swivel wrap 142 and is formed in an annular shape. An intake port 1431 penetrating in the radial direction is formed on one side of the outer peripheral surface of the non-circulating side wall portion 143.

The guide protrusion 144 may extend in the radial direction from the lower outer peripheral surface of the non-circulating side wall portion 143. The guide protrusion 144 may be formed in a single annular shape, or may be formed in plural pieces at predetermined intervals along the circumferential direction. This embodiment will be described focusing on an example in which a plurality of guide protrusions 144 are formed at preset intervals along the circumferential direction.

Next, orbital scrolling will be explained.

Referring to FIG. 1, the orbiting scroll 150 according to this embodiment is coupled to the rotation shaft 125 and disposed on the upper surface of the main frame 130. For example, the orbiting scroll 150 is provided between the main frame 130 and the non-orbiting scroll 140. An Oldham ring 170, an anti-rotation mechanism, is provided between the main frame 130. Accordingly, the rotating movement of the orbiting scroll 150 is restricted and the orbiting scroll 150 performs a rotating movement with respect to the non-orbiting scroll 140.

Specifically, the orbiting scroll 150 includes a pivoting plate portion 151, a pivoting wrap 152, and a rotating shaft engaging portion 153.

The pivot plate portion 151 is formed in a substantially disk shape. The rotating mirror plate portion 151 is supported in the axial direction by the scroll support portion 134 of the main frame 130. Accordingly, the pivot plate portion 151 and the scroll support portion 134 facing it form an axial bearing surface (not denoted).

The orbital wrap 152 forms a compression chamber (V) together with the non-swivel wrap 142. The orbiting wrap 152 is formed in a spiral shape by protruding at a preset height from the upper surface of the orbiting mirror plate portion 151 facing the non-orbiting scroll 140. The orbiting wrap 152 is formed to correspond to the non-orbiting wrap 142 of the non-orbiting scroll 140, which will be described later, so as to engage with the non-orbiting wrap 142 and perform a rotating movement.

The rotation shaft coupling portion 153 protrudes toward the main frame 130 from the lower surface of the pivot plate portion 151. The rotating shaft coupling portion 153 has an inner peripheral surface formed in a cylindrical shape so that a slew bearing (not shown) made of a bush bearing can be press-fitted.

The sliding bush 155 is rotatably inserted into the inside of the slewing bearing, and the eccentric pin portion 1252 of the rotation shaft 125 described above is inserted into the inside of the sliding bush 155 so as to slide in the transverse direction. Accordingly, the rotational force of the drive motor 120 is transmitted to the rotation shaft coupling portion 153 through the eccentric pin portion 1252 and the sliding bush 155 of the rotation shaft 125, and the rotational force transmitted to the rotation shaft coupling portion 153 is all It is limited by the dam ring 170 to rotate the orbiting scroll 150.

At this time, the eccentric pin portion 1252 and the sliding bush 155 slide in the radial direction due to the centrifugal force generated by the orbiting scroll 150 and the pressure difference in the compression chamber (V), so that the turning radius of the orbiting scroll 150 is variable. It can be. Through this, when overcompression occurs in the compression chamber (V), leakage between the compression chambers (V) is allowed and overcompression is resolved, thereby preventing wrap damage in advance.

Next, the back pressure chamber assembly will be described.

Referring to FIG. 1, the back pressure chamber assembly 160 according to this embodiment is provided above the non-orbiting scroll 140. Accordingly, the back pressure of the back pressure chamber 160a (more precisely, the force that the back pressure exerts on the back pressure chamber) acts on the non-orbiting scroll 140. In other words, the non-orbiting scroll 140 is pressed in the direction toward the orbiting scroll 150 by back pressure to seal the compression chamber (V).

Specifically, the back pressure chamber assembly 160 includes a back pressure plate 161 and a floating plate 165. The back pressure plate 161 is coupled to the upper surface of the non-swivel plate portion 141. The floating plate 165 may be slidably coupled to the back pressure plate 161 to form a back pressure chamber 160a together with the back pressure plate 161.

The back pressure plate 161 includes a fixing plate portion 1611, a first annular wall portion 1612, and a second annular wall portion 1613.

The fixing plate portion 1611 is formed in the shape of an annular plate with an empty center. The plate side back pressure hole (hereinafter referred to as the second back pressure hole) 1611a penetrates in the axial direction. The second back pressure hole 1611a communicates with the compression chamber V through the first back pressure hole 1413. Accordingly, the second back pressure hole 1611a, together with the first back pressure hole 1413, communicates between the compression chamber V and the back pressure chamber 160a.

The first annular wall portion 1612 and the second annular wall portion 1613 surround the inner peripheral surface and the outer peripheral surface of the fixed plate portion 1611 on the upper surface of the fixed plate portion 1611. Accordingly, the outer peripheral surface of the first annular wall portion 1612, the inner peripheral surface of the second annular wall portion 1613, the upper surface of the fixing plate portion 1611, and the lower surface of the floating plate 165 form an annular back pressure chamber 160a. do.

An intermediate discharge port 1612a communicating with the discharge port 1411 of the non-orbiting scroll 140 is formed in the first annular wall portion 1612. Inside the middle discharge port 1612a, a valve guide groove 1612b is formed into which a check valve (hereinafter referred to as discharge valve) 145 is slidably inserted. A backflow prevention hole (1612c) is formed in the center of the valve guide groove (1612b). Accordingly, the discharge valve 145 selectively opens and closes between the discharge port 1411 and the intermediate discharge port 1612a to block the discharged refrigerant from flowing back into the compression chamber.

The floating plate 165 is formed in a ring shape. It may be made of a material lighter than the back pressure plate 161. Accordingly, the floating plate 165 moves in the axial direction with respect to the back pressure plate 161 according to the pressure of the back pressure chamber 160a and is attached to and detached from the lower side of the high and low pressure separator plate 115. For example, when the floating plate 165 comes into contact with the high-low pressure separator plate 115, it serves to seal the discharged refrigerant so that it is discharged to the high-pressure section 110b without leaking into the low-pressure section 110a.

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

That is, when power is applied to the stator coil 121a of the stator 121, the rotor 122 rotates together with the rotation shaft 125. Then, the orbiting scroll 150 coupled to the rotation axis 125 makes a orbital movement with respect to the non-orbiting scroll 140, and between the orbiting wrap 152 and the non-orbiting wrap 142, two pairs of compressions are formed. A thread (V) is formed.

The compression chamber (V) gradually decreases in volume as it moves from the outside to the inside according to the turning movement of the turning scroll (150). At this time, the refrigerant is sucked into the low pressure part 110a of the casing 110 through the refrigerant suction pipe 117, and a part of this refrigerant is sucked directly into each suction pressure chamber (not marked) forming both compression chambers V. The remainder moves toward the drive motor 120, cools the drive motor 120, and is then sucked into the suction pressure chamber (not marked).

Next, the refrigerant sucked into the suction pressure chamber (not marked) is compressed while moving toward the intermediate pressure chamber and the discharge pressure chamber (not marked) along the movement path of the compression chamber (V). The refrigerant moving to the discharge pressure chamber (not marked) is discharged to the high pressure section (110b) through the discharge port 1411 and the intermediate discharge port 1612a while pushing the discharge valve 145, and this refrigerant fills the high pressure section (110b) and then discharges the refrigerant. A series of processes are repeated to discharge through the condenser of the refrigeration cycle through the pipe 118.

At this time, a portion of the refrigerant that is compressed while passing through the intermediate pressure chamber (uncoded) passes through the bypass hole 1412 before reaching the discharge port 1411 and enters the high pressure section in the intermediate pressure chamber (uncoded) forming each compression chamber (V). By bypassing in advance toward (110b), the refrigerant can be prevented from being overcompressed beyond the set pressure in the compression chamber.

In addition, another part of the refrigerant compressed while passing through the intermediate pressure chamber (not marked) also flows into the back pressure chamber 160a through the first back pressure hole 1413 before reaching the discharge port 1411, thereby forming the back pressure chamber 160a. This creates an intermediate pressure. Then, the floating plate 165 rises toward the high-low pressure separator 115 and comes into close contact with the sealing plate 1151 provided on the high-low pressure separator 115, and the back pressure plate 161 is connected to the back pressure chamber 160a. It is pressed down in the direction toward the non-orbiting scroll 140 by the pressure, and the non-orbiting scroll 140 is pressed toward the orbiting scroll 150.

At this time, as the floating plate 165 rises and comes into close contact with the sealing plate 1151, the high pressure part 110b of the casing 110 is separated from the low pressure part 110a and flows from each compression chamber V to the high pressure part 110b. It is possible to prevent the discharged refrigerant from flowing back into the low pressure part 110a. On the other hand, as the back pressure plate 161 descends toward the non-orbiting scroll 140, the non-orbiting scroll 140 comes in close contact with the orbiting scroll 150 and the compressed refrigerant is compressed on the low-pressure side in the high-pressure side compression chamber forming the intermediate pressure chamber. It is possible to block leakage.

Meanwhile, the lower end of the rotation shaft 125 rotates while submerged in the oil stored in the oil storage space 110c of the casing 110. Then, the oil in the oil storage space 110c is pumped by the oil pickup 126, and this oil is absorbed along the oil passage 1254 of the rotating shaft 125 and scatters inside the rotating shaft coupling portion 153. Some of this oil flows down along the inner peripheral surface of the rotating shaft coupling portion 153 and is supplied to the bearing surfaces between neighboring members through the orbital space portion 133 to lubricate them.

For example, the oil that scatters from the rotating shaft coupling portion 153 and fills the orbiting space 133 moves to the scroll support portion 134 surrounding the orbiting space 133 and connects the scroll support portion 134 to the axial direction. The axial bearing surface formed between the opposing pivot plates 151 is lubricated. In other words, the oil filled in the orbiting space 133 flows from the orbiting space 133 toward the scroll support 134 due to the difference between the internal pressure in the orbiting space 133 and the external pressure in the scroll support 134. It moves.

However, in this embodiment, the inner peripheral surface of the orbiting space 133 of the main frame 130 and/or the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 slopes outward toward the top, thereby forming the orbiting space. A high centrifugal force is generated between the inner peripheral surface of the portion 133 and the outer peripheral surface of the rotating shaft coupling portion 153, and this centrifugal force allows the oil in the orbital space portion 133 to move more quickly toward the scroll support portion 134.

Hereinafter, the description will focus on an example in which the inner peripheral surface of the orbiting space 133 of the main frame 130 and the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 are inclined. However, it is not necessary for both the inner peripheral surface of the orbiting space 133 of the main frame 130 and the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 to be inclined. For example, only the inner peripheral surface of the orbiting space 133 of the main frame 130 may be inclined, or only the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 may be inclined.

FIG. 2 is a cross-sectional view showing the oil movement process in the orbiting space of FIG. 1, and FIG. 3 is a cross-sectional view showing the main frame and orbiting scroll of FIG. 2.

Referring to FIGS. 1 to 3, the inner peripheral surface of the pivot space 133 of the main frame 130 is formed in a circular cross-sectional shape when projected in the axial direction of the rotation axis 125, and the shape of the rotation axis 125 along the axial direction is It may be formed to be inclined with respect to the axial direction.

Specifically, the inner peripheral surface of the pivot space 133 may be formed to be inclined by a preset inclination angle (β) with respect to the axial direction of the rotation axis 125. In other words, the inner peripheral surface of the orbiting space 133 may be inclined so that the cross-sectional diameter (this is referred to as the inner diameter) of the inner peripheral surface of the orbiting space 133 increases in the direction toward the scroll support unit 134. Here, the cross-sectional diameter refers to the diameter in the radial direction of the inner peripheral surface of the orbital space portion 133.

When the rotating shaft coupling portion 153 of the orbiting scroll 150 rotates in the orbiting space 133 of the main frame 130, the oil stored in the orbiting space 133 is affected by the rotational movement of the rotating shaft engaging portion 153. It receives and rotates in the orbiting space unit 133. At this time, a high centrifugal force is generated in the oil on the bottom of the orbiting space 133, and the oil scatters from the orbiting space 133. Since the inner peripheral surface of the orbital space 133 is inclined with respect to the axial direction of the rotation shaft 125, the flying oil can easily move toward the scroll support portion 134 without obstruction. Therefore, even if the oil level in the orbital space 133 is low due to insufficient oil supplied to the orbital space 133, oil can be quickly supplied to the axial bearing surface.

The inner peripheral surface of the pivoting space 133 may be formed so that the inclination angle β between both axial ends (defined below) of the pivoting space 133 is the same (see FIG. 3). Accordingly, not only can processing be facilitated by simplifying the structure of the inner peripheral surface of the pivot space portion 133, but flow resistance to oil can be minimized and centrifugal force can be further increased.

Although not shown in the drawings, the inner peripheral surface of the pivot space 133 may have different inclination angles (β) between both ends in the axial direction.

Specifically, the pivot space 133 has both ends in the axial direction of the rotation shaft 125, and the both ends represent one end and the other end opposite to the one end. Here, one end of the orbiting space 133 is an end of the orbiting space 133 located in a direction opposite to the direction toward the scroll support 134, and the other end of the orbiting space 133 is located at the scroll support 134. It is the end of the pivot space 133 located in the facing direction. The other end of the orbiting space 133 is an end connected to (abuts with) the scroll support 134.

An inclination angle A of the inner peripheral surface of the orbiting space 133 from one end of the orbiting space 133 to a point spaced a predetermined distance in the direction toward the scroll support 134, and The inclination angle B of the inner peripheral surface of the pivot space 133 up to the end may be different. Even when B is made larger than A and the oil is filled below the point spaced a predetermined distance apart, the swirling oil can be quickly supplied to the axial bearing surface without obstruction along with high centrifugal force.

In addition, according to this embodiment, the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 is formed in a circular cross-sectional shape when projected in the axial direction of the rotation shaft 125, and the axis of the rotation shaft 125 is formed along the axial direction. It may be formed to be inclined with respect to the direction.

Specifically, the outer peripheral surface of the rotation shaft coupling portion 153 may be formed to be inclined by a preset inclination angle (α) with respect to the axial direction of the rotation shaft 125. In other words, the outer peripheral surface of the rotating shaft coupling portion 153 may be formed to be inclined so that the cross-sectional diameter (this is referred to as the outer diameter) of the outer peripheral surface of the rotating shaft coupling portion 153 increases in the direction toward the pivot plate portion 151. Here, the cross-sectional diameter refers to the diameter in the radial direction of the outer peripheral surface of the rotating shaft coupling portion 153. Through this, when the rotary shaft coupling portion 153 rotates, the oil stored in the rotating space portion 133 can easily rise along the outer peripheral surface of the rotating shaft coupling portion 153 while rotating along the rotating shaft coupling portion 153, thereby allowing the scroll It can be moved more easily toward the support portion 134.

The outer peripheral surface of the rotation shaft coupling portion 153 may be formed such that the inclination angle α between both axial ends of the rotation shaft coupling portion 153 (defined below) is the same (see FIG. 3). Accordingly, not only can the structure of the outer peripheral surface of the rotary shaft coupling portion 153 be simplified to facilitate processing, but also the flow resistance to oil can be minimized and the centrifugal force can be further increased.

Although not shown in the drawing, the outer peripheral surface of the rotating shaft coupling portion 153 may have different inclination angles (α) between both ends in the axial direction.

Specifically, the rotation shaft coupling portion 153 has both ends in the axial direction of the rotation shaft 125, and the both ends include one end and the other end opposite to the one end. Here, one end of the rotation shaft coupling portion 153 is an end of the rotation shaft coupling portion 153 located in the opposite direction to the direction toward the pivoting disk portion 151, and the other end of the rotating shaft coupling portion 153 is the pivoting disk portion 151. ) is the end of the rotation shaft coupling portion 153 located in the direction facing. The other end of the rotating shaft coupling portion 153 is an end connected to (abutting) the pivot plate portion 151.

An inclination angle C of the outer circumferential surface of the rotary shaft coupling portion 153 from one end of the rotary shaft coupling portion 153 to a point spaced a predetermined distance in the direction toward the pivot plate portion 151, and from the point spaced a predetermined distance away from the rotary shaft coupling portion 153. The inclination angle (D) of the outer peripheral surface of the rotation shaft coupling portion 153 up to the other end may be different. By making D larger than C, the oil that swirls and/or scatters and rises along the inner peripheral surface of the rotating space portion 133 is guided by the more inclined outer peripheral surface (outer peripheral surface with an inclination angle of D) of the rotating shaft coupling portion 153, making it more It can quickly move toward the scroll support unit 134.

In addition, as described above, when the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 is formed to be inclined with respect to the axial direction of the rotation shaft 125, the orbiting space portion 133 is formed on the outer peripheral surface of the rotation shaft coupling portion 153. It may be formed to be inclined so that its inner diameter increases in the direction toward the scroll support portion 134 to correspond to the. Through this, the radial distance (this is referred to as space) between the inner peripheral surface of the rotating space portion 133 and the outer peripheral surface of the rotating shaft coupling portion 153 is maintained constant, so that the oil rotating in the space can flow without obstruction. It can rotate so it can be supplied evenly to the axial bearing surface.

Alternatively, unlike the present embodiment, the orbiting space 133 does not correspond to the outer peripheral surface of the rotating shaft engaging portion 153, but is oriented toward the scroll support portion 134 so as to be inclined more than the inclination of the outer peripheral surface of the rotating shaft engaging portion 153. It can be formed to be inclined to increase its inner diameter (not shown). Therefore, even if the oil level in the orbital space 133 is lower due to insufficient oil supplied to the orbital space 133 at the beginning of operation of the compressor, oil can be easily supplied to the axial bearing surface.

Additionally, according to this embodiment, the rotation shaft coupling portion 153 may be formed to be inclined so that its outer diameter increases in the direction toward the pivot plate portion 151 to correspond to the inner peripheral surface of the pivot space portion 133. Through this, the space between the outer peripheral surface of the rotating shaft coupling portion 153 and the inner peripheral surface of the rotating space portion 133 is maintained constant, so that the oil rotating in the space can rotate without disturbing the flow and is uniformly distributed on the axial bearing surface. can be supplied.

Alternatively, unlike the present embodiment, the rotation shaft coupling portion 153 does not correspond to the inner peripheral surface of the pivoting space portion 133 but is directed toward the pivoting plate portion 151 so as to be less inclined than the inclination of the inner peripheral surface of the pivoting space portion 133. It may be formed to be inclined so that its outer diameter increases in that direction (not shown). Therefore, even if the oil level in the orbital space 133 is lower due to insufficient oil supplied to the orbital space 133 at the beginning of operation of the compressor, oil can be easily supplied to the axial bearing surface.

According to this embodiment, the movement of oil will be described focusing on the example where the inner peripheral surface of the orbiting space portion 133 of the main frame 130 and the outer peripheral surface of the rotating shaft coupling portion 153 of the orbiting scroll 150 are inclined as follows. same.

Referring to FIGS. 1 to 3, some of the oil flows down along the inner peripheral surface of the rotating shaft coupling portion 153 and is stored in the orbiting space portion 133. The stored oil rotates under the influence of the rotational movement of the rotating shaft coupling portion 153, and easily rises along the inclined space between the inclined inner peripheral surface of the rotating space portion 133 and the inclined outer peripheral surface of the rotating shaft coupling portion 153. and can quickly move toward the scroll support unit 134. Therefore, even if the oil level is low due to insufficient oil supplied to the orbital space 133, oil can be easily supplied to the axial bearing surface.

In addition, an oil transfer groove may be formed on the inner peripheral surface of the orbiting space 133 of the above-described main frame 130 and/or the outer peripheral surface of the rotation shaft engaging portion 153 of the orbiting scroll 150. The oil movement groove is a recess through which oil in the pivot space 133 can move.

Through the oil movement groove, the oil in the orbiting space portion 133 can easily move to the oil movement groove, and can easily rise along the oil movement groove due to the influence of the rotational force caused by the rotation of the orbiting scroll 150. You can move more quickly with the directional bearing surface.

Hereinafter, the description will focus on an example in which oil movement grooves are formed on both the inner peripheral surface of the pivot space portion 133 and the outer peripheral surface of the rotating shaft coupling portion 153. However, there is no need for the oil movement groove to be formed on both the inner peripheral surface of the pivot space 133 and the outer peripheral surface of the rotating shaft coupling portion 153. For example, the oil movement groove may be formed only on the inner peripheral surface of the pivot space 133, or the oil movement groove may be formed only on the outer peripheral surface of the rotating shaft coupling portion 153.

Figure 4 is an example in which an oil moving groove is formed in the pivot space and the rotating shaft coupling part of Figure 3.

Referring to FIG. 4, the oil movement groove 133a according to the present embodiment is formed on the inner peripheral surface of the pivot space 133 in the axial direction of the rotation shaft 125 or in the axial direction (based on the axial direction). It may be formed by tilting at a predetermined angle. Because of this, the oil in the oil transfer groove (133a) can easily rise along the oil transfer groove (133a) under the influence of the rotational force caused by the rotation of the orbiting scroll (150).

Specifically, the oil movement groove 133a may be formed to be inclined in the rotation direction of the rotation shaft 125 as it moves from the main frame 130 toward the orbiting scroll 150. The oil in the orbiting space 133 rotates in the same direction as the rotation direction of the orbiting scroll 150, and when the oil movement groove (133a) is formed to be inclined in the direction in which the oil rotates, the oil rotates and the oil movement groove (133a) rotates. You can easily ascend along 133a).

Additionally, according to this embodiment, the oil movement groove 133a may be formed in a spiral shape on the inner peripheral surface of the pivot space 133. For this reason, the oil on the bottom of the orbiting space 133 can be moved toward the scroll support portion 134 along the oil movement groove 133a by the centrifugal force of the orbiting oil.

Additionally, a plurality of oil movement grooves 133a may be formed on the inner peripheral surface of the pivot space 133 at predetermined intervals along the circumferential direction. For this reason, a large amount of oil stored in the orbiting space 133 can be moved to the axial bearing surface through the plurality of oil movement grooves 133a formed in the orbiting space 133.

The spacing between the plurality of oil movement grooves 133a may be the same or different from each other.

Since the spacing between the plurality of oil movement grooves 133a is formed to be the same, the oil moving to the other end of the pivot space 133 (the part in contact with the scroll support 134) through the oil movement groove 133a is The quantity may be the same along the circumferential direction. Accordingly, the oil supplied to the scroll support part 134 may be uniform along the circumferential direction of the scroll support part 134.

In addition, as an example where the spacing between the plurality of oil moving grooves 133a is different from each other, the spacing between the plurality of oil moving grooves 133a gradually widens from one end to the other end of the pivot space 133. There is (not shown). In this case, even though a smaller number of oil transfer grooves 133a are used, oil can be uniformly supplied to the other end of the pivot space 133.

Additionally, the oil movement groove 133a may be formed on the inner peripheral surface of the pivot space 133 to have a predetermined length.

Specifically, according to this embodiment, the oil transfer groove 133a may be formed to connect one end and the other end of the pivot space 133 (see FIG. 4). For this reason, even if the oil stored in the orbiting space 133 is insufficient and only the bottom of the orbiting space 133 is filled with oil, the oil flows into the oil transfer groove connected seamlessly from one end to the other end of the orbiting space 133. It can move toward the scroll support unit 134 along (133a).

Alternatively, unlike the above-described embodiment, the oil transfer groove 133a may be partially formed without connecting one end and the other end of the pivot space 133 (not shown). For example, the oil movement groove 133a may be formed starting from a position spaced apart from one end of the orbiting space 133 by a predetermined distance in the direction toward the scroll support portion 134 to the other end of the orbiting space 133. You can. As a result, the processing time required to form (process) the oil transfer groove 133a on the inner peripheral surface of the pivot space 133 can be saved and the convenience of processing can be improved.

Additionally, the cross-sectional area of the oil transfer groove 133a may be constant or different along the length of the oil transfer groove 133a. Here, the cross-sectional area of the oil movement groove (133a) refers to the area of the cross-section of the oil movement groove (133a) in a direction perpendicular to the longitudinal direction of the oil movement groove (133a).

Specifically, the cross-sectional area of the oil movement groove 133a, the width and/or depth of the oil movement groove 133a may be constant or different along the length of the oil movement groove 133a.

When the cross-sectional area of the oil transfer groove (133a) is formed uniformly along the length of the oil transfer groove (133a), not only is it convenient to process the oil transfer groove (133a), but also the speed of the oil passing through the oil transfer groove (133a) and Since the amount can be maintained constant, the amount of oil moving to the other end of the pivot space 133 through the oil transfer groove 133a can be maintained the same along the circumferential direction.

In addition, for example, the cross-sectional area of the oil movement groove (133a) is different along the length of the oil movement groove (133a) (specifically, the width and/or depth of the oil movement groove (133a) is determined by the length of the oil movement groove (133a). As another example), there are cases where the cross-sectional area of the oil transfer groove 133a on the other end side of the orbiting space 133 is smaller than the cross-sectional area of the oil transfer groove 133a on the one end side of the orbiting space 133. In this case, the speed of the oil passing through the oil moving groove (133a) on the other end side of the pivoting space 133 is faster than the speed of the oil passing through the oil moving groove (133a) on one end side, so the oil flowing through the oil moving groove (133a) on the other end side is faster. Oil passing through the moving groove 133a can reach the scroll support 134 more quickly.

In addition, the oil movement groove 153a according to this embodiment is formed on the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 in the axial direction of the rotation shaft 125 or in the axial direction (based on the axial direction). ) can be formed to be inclined at a predetermined angle.

Specifically, the oil movement groove 153a may be formed to be inclined in the rotation direction of the rotation shaft 125 as it moves from the main frame 130 toward the orbiting scroll 150. The oil in the oil transfer groove (153a) has centrifugal force as the orbiting scroll (150) rotates. As the oil moves toward the orbital space 133 in the radial direction within the oil movement groove 153a under the influence of centrifugal force, it may collide with the inner peripheral surface of the orbital space 133 and scatter significantly. Additionally, the oil in the oil transfer groove 153a can easily rise (move) toward the pivot plate portion 151 by being pushed by the inner surface of the oil transfer groove 153a.

Additionally, according to this embodiment, the oil moving groove 153a may be formed in a spiral shape on the outer peripheral surface of the rotating shaft coupling portion 153. Because of this, the oil on the bottom of the orbiting space 133 can be moved toward the scroll support portion 134 along the oil movement groove 153a.

Additionally, a plurality of oil moving grooves 153a may be formed on the outer peripheral surface of the rotating shaft coupling portion 153 at predetermined intervals along the circumferential direction. For this reason, a large amount of oil stored in the orbiting space 133 can be moved to the axial bearing surface through the plurality of oil movement grooves 153a.

The spacing between the plurality of oil movement grooves 153a may be the same or different from each other.

Since the spacing between the plurality of oil movement grooves 153a is formed to be the same, the oil moving to the other end of the rotation shaft coupling portion 153 (the portion in contact with the pivot plate portion 151) through the oil movement groove 153a is The amount may be the same along the circumferential direction. Therefore, the oil supplied to the axial bearing surface may be uniform along the circumferential direction of the pivot plate portion 151.

In addition, as an example where the spacing between the plurality of oil moving grooves 153a is different from each other, the spacing between the plurality of oil moving grooves 153a gradually widens from one end to the other end of the rotating shaft coupling portion 153. There is (not shown). In this case, even though a smaller number of oil transfer grooves 153a are used, oil can be uniformly supplied to the other end of the rotary shaft coupling portion 153.

Additionally, the oil movement groove 153a may be formed to have a predetermined length on the outer peripheral surface of the rotating shaft coupling portion 153.

Specifically, according to this embodiment, the oil transfer groove 153a may be formed to connect one end and the other end of the rotation shaft coupling portion 153 (see FIG. 4). For this reason, even if the oil stored in the pivot space 133 is insufficient and only the bottom of the pivot space 133 is filled with oil, the oil scatters greatly under the influence of the rotation of the rotary shaft coupling portion 153 and at the same time, the oil is not connected to the rotary shaft coupling portion 153. It can move toward the pivot plate portion 151 along the oil movement groove 153a that is seamlessly connected from one end of the portion 153 to the other end.

Alternatively, unlike the above-described embodiment, the oil transfer groove 153a may be partially formed without connecting one end and the other end of the rotation shaft coupling portion 153 (not shown). For example, the oil movement groove 153a is formed from a position spaced apart from one end of the rotary shaft coupling portion 153 at a predetermined distance in the direction toward the pivot plate portion 151 and extends to the other end of the rotary shaft coupling portion 153. It can be. As a result, the processing time required to form (process) the oil transfer groove 153a on the outer peripheral surface of the rotary shaft coupling portion 153 can be saved, and the convenience of processing can be improved.

Additionally, the cross-sectional area of the oil transfer groove 153a may be constant or different along the length of the oil transfer groove 153a.

Specifically, the cross-sectional area of the oil movement groove 153a, the width and/or depth of the oil movement groove 153a may be constant or different along the length of the oil movement groove 153a.

When the cross-sectional area of the oil transfer groove (153a) is formed consistently along the length of the oil transfer groove (153a), not only is it convenient to process the oil transfer groove (153a), but also the speed of oil passing through the oil transfer groove (153a) and Since the amount can be maintained constant, the amount of oil moving to the other end of the rotary shaft coupling portion 153 through the oil movement groove 153a can be maintained the same along the circumferential direction.

In addition, for example, the cross-sectional area of the oil movement groove (153a) is different along the length of the oil movement groove (153a) (specifically, the width and/or depth of the oil movement groove (153a) is determined by the length of the oil movement groove (153a). As another example), there are cases where the cross-sectional area of the oil movement groove 153a on the other end side of the rotation shaft coupling portion 153 is smaller than the cross-sectional area of the oil movement groove 153a on one end side of the rotation shaft coupling portion 153. In this case, the speed of the oil passing through the oil movement groove (153a) on the other end side of the rotating shaft coupling portion 153 is faster than the speed of the oil passing through the oil movement groove (153a) on one end side, so the oil on the other end side Oil passing through the moving groove (153a) can reach the axial bearing surface more quickly.

Alternatively, as shown in FIG. 5, the inner peripheral surface of the orbiting space 133 of the main frame 130 and/or the outer peripheral surface of the rotation shaft coupling portion 153 of the orbiting scroll 150 are formed to be inclined with respect to the axial direction of the rotation shaft 125. The oil movement grooves 133a and 153a may be formed without Figure 5 is another embodiment in which oil movement grooves are formed in the pivot space and the rotating shaft coupling portion.

Since the contents of the oil movement grooves 133a and 153a in the embodiment shown in FIG. 5 are the same as the contents of the oil movement grooves 133a and 153a in the embodiment shown in FIG. 4 described above, the contents of FIG. 5 The description of the oil movement grooves 133a and 153a in the embodiment shown in will be replaced with the description of the oil movement grooves 133a and 153a in the embodiment shown in FIG. 4 described above.

In the embodiment shown in FIG. 5, the inner peripheral surface of the pivot space 133 is formed to be identical in the axial direction of the rotating shaft 125, thereby securing the axial bearing surface, and thus the surface pressure on the axial bearing surface is The increase can be suppressed, and it can be advantageous in suppressing deformation of the pivot plate portion 151. Additionally, the behavior of the orbiting scroll 150 can be stabilized. In addition, the outer peripheral surface of the rotating shaft coupling portion 153 is formed to be the same in the axial direction of the rotating shaft 125, so that the weight of the orbiting scroll 150 can be reduced by reducing the thickness of the rotating shaft coupling portion 153 compared to the above-described embodiment. can be achieved, and thus the efficiency of the motor can be improved.

Additionally, as shown in FIG. 6, an oil guide groove 134a may be formed in the scroll support portion 134 of the main frame 130 facing the orbiting mirror plate portion 151 of the orbiting scroll 150. Figure 6 is an embodiment in which an oil guide groove is formed in the scroll support part of Figure 4. One or more oil guide grooves 134a may be formed on the upper surface of the scroll support portion 134.

The oil guide groove 134a is a groove through which oil that has moved (rising) along the inner peripheral surface of the pivot space 133 can move.

The oil rising along the inner peripheral surface of the orbiting space 133 can quickly move to the oil guide groove 134a, which is lower in height than the upper surface of the scroll support 134, and the oil in the oil guide groove 134a is directed to the pivot plate portion. It may move to the upper surface of the scroll support unit 134 under the influence of the rotation of (151). Accordingly, the efficiency of the compressor can be increased by reducing friction on the upper surface of the scroll support part 134, that is, the axial bearing surface.

In addition, due to the oil guide groove 134a, the contact area between the lower surface of the pivot plate portion 151 and the upper surface of the scroll support portion 134 is reduced (the area of the axial bearing surface is reduced), thereby reducing the axial bearing. Friction on the surface is reduced.

Additionally, the oil guide groove 134a may be in communication with the oil movement groove 133a. The oil that moves (rises) along the oil movement groove (133a) of the orbital space portion (133) can move directly to the communicating oil guide groove (134a), so the oil moves more quickly to the upper surface (axial direction) of the scroll support portion (134). bearing surface).

110: Casing 110a: Low pressure part (suction space)
110b: High pressure part (discharge space) 110c: Oil storage space
111: cylindrical shell 112: upper cap
113: lower cap 115: high and low pressure separator plate
115a: Through hole 1151: Sealing plate
1151a: High and low pressure communication hole 116: Support bracket
117: Refrigerant suction pipe 118: Refrigerant discharge pipe
119: Subframe 1191: Sub-bearing part
120: Drive motor 121: Stator
1211: stator core 1212: stator coil
122: rotor 1221: rotor core
1222: permanent magnet 125: rotation axis
1251: Main shaft 1252: Eccentric pin 1254: Oil passage 126: Oil pickup
130: main frame 131: main flange branch
132: main bearing part 132a: bearing hole
133: Swivel space 133a: Oil movement groove of pivot space
134: Scroll support 134a: Oil guide groove
135: Oldham ring support part 136: Frame fixing part
140: Non-orbiting scroll 141: Non-orbiting hard plate part
1411: discharge port 1412: bypass hole
1413: First back pressure hole 142: Non-swivel wrap
143: Non-turning side wall 144: Guide protrusion
145: discharge valve 150: orbiting scroll
151: Swivel hard plate 152: Swivel wrap
153: Rotating shaft coupling portion 153a: Oil movement groove of rotating shaft coupling portion
155: sliding bush 160: back pressure chamber assembly
160a: Back pressure chamber 161: Back pressure plate
1611: fixing plate part 1611a: second pressure hole
1612: First annular wall portion 1612a: Middle discharge port
1612b: Valve guide groove 1612c: Backflow prevention hole
1613: Second annular wall 165: Floating plate
170: Oldham Ring V: Compression chamber
α: Inclination angle of the outer peripheral surface of the rotating shaft coupling part
β: Inclination angle of the inner peripheral surface of the pivot space

Claims (13)

Non-orbiting scroll;
A rotating shaft coupling portion to which the rotating shaft is coupled extends from one side of the rotating mirror plate portion and makes a rotating movement with respect to the non-orbiting scroll; and
A scroll support part is provided so that the turning mirror plate part is supported in the axial direction of the rotating shaft, and the scroll supporting part includes a main frame in which a turning space part is recessed so that the rotating shaft coupling part is rotatably inserted,
A scroll compressor in which at least one of the outer peripheral surface of the rotating shaft coupling portion and the inner peripheral surface of the orbiting space portion facing it in the radial direction is inclined with respect to the axial direction of the rotating shaft.
According to claim 1,
A scroll compressor wherein the rotating shaft coupling portion is formed to be inclined so that its outer diameter increases in a direction toward the rotating mirror plate portion.
According to claim 2,
The orbiting space portion is inclined so that its inner diameter increases in a direction toward the scroll support portion to correspond to the outer peripheral surface of the rotating shaft coupling portion.
According to claim 1,
A scroll compressor wherein an oil movement groove is formed on at least one of the inner peripheral surface of the orbiting space portion and the outer peripheral surface of the rotating shaft coupling portion.
According to claim 4,
The oil moving groove is formed to be inclined at a predetermined angle based on the axial direction of the rotation shaft.
According to claim 5,
The oil movement groove is inclined in the rotation direction of the rotation shaft as it moves from the main frame toward the orbiting scroll.
According to claim 4,
A plurality of oil moving grooves are formed on the inner peripheral surface of the pivot space at predetermined intervals along the circumferential direction,
A scroll compressor wherein the spacing between the plurality of oil moving grooves is the same or different from each other.
According to claim 4,
A plurality of oil moving grooves are formed on the outer peripheral surface of the rotating shaft coupling portion at predetermined intervals along the circumferential direction,
A scroll compressor wherein the spacing between the plurality of oil moving grooves is the same or different from each other.
According to claim 4,
The oil movement groove is formed to have a predetermined length on the inner peripheral surface of the pivot space,
A scroll compressor wherein the cross-sectional area of the oil movement groove is constant or different along the length of the oil movement groove.
According to claim 4,
The oil movement groove is formed to have a predetermined length on the outer peripheral surface of the rotating shaft coupling portion,
A scroll compressor wherein the cross-sectional area of the oil movement groove is constant or different along the length of the oil movement groove.
The method according to any one of claims 4 to 10,
A scroll compressor in which one or more oil guide grooves are formed in the scroll support portion facing the pivot plate portion.
According to claim 11,
A scroll compressor wherein the oil guide groove is in communication with the oil movement groove.
Non-orbiting scroll;
A rotating shaft coupling portion to which the rotating shaft is coupled extends from one side of the rotating mirror plate portion and makes a rotating movement with respect to the non-orbiting scroll; and
A scroll support part is provided so that the turning mirror plate part is supported in the axial direction of the rotating shaft, and the scroll supporting part includes a main frame in which a turning space part is recessed so that the rotating shaft coupling part is rotatably inserted,
A scroll compressor wherein an oil movement groove is formed on at least one of the inner peripheral surface of the orbiting space portion and the outer peripheral surface of the rotating shaft coupling portion.

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