KR20200131206A - Compressor - Google Patents

Abstract

The present invention relates to a compressor and, more specifically, to a compressor capable of effectively separating lubricating oil and a compressed refrigerant in a compressor. According to one embodiment of the present invention, the compressor includes: a case; a driving motor including a stator mounted inside the case and a rotor provided to be rotatable in a radial direction of the stator; a centrifugal separation space defined by the case and one stream (downstream side) of the driving motor in the case, and performing the centrifugal separation of lubricating oil and a compressed refrigerant; a discharge pipe penetrating the case, and provided such that an end forming a refrigerant inlet is extended into the centrifugal separation space; a rotary shaft combined with the rotor to be rotated; a compression part provided on the other stream (upstream side) of the driving motor, and compressing the refrigerant through the rotation of the rotary shaft; and a terminal provided on a side of the case, which is also a side of the centrifugal separation space, to be connected with a coil of the stator.

Description

Compressor {COMPRESSOR}

The present invention relates to a compressor, and more particularly, to a compressor capable of effectively separating lubricating oil and a compressed refrigerant inside the compressor.

In general, compressors are applied to refrigerant compression refrigeration cycles (hereinafter, abbreviated as refrigeration cycles) such as refrigerators and air conditioners.

The compressor may be classified into a reciprocating compressor and a rotary compressor according to a method of compressing the refrigerant, and the rotary compressor may include a scroll compressor.

The scroll compressor may be classified into an upper compression type or a lower compression type according to the position of the driving motor and the compression unit. The upper compression type is a method in which the compression unit is located above the driving motor, and the lower compression type is a method in which the compression unit is located below the driving motor.

That is, the compressor may be named differently according to the relative position of the driving motor and the compression unit. The compressor may be mounted horizontally rather than vertically. Therefore, the compressor can be named by more generalization according to the relative position of the driving motor and the compression unit. Depending on the flow direction of the refrigerant in the compressor and the position of the driving motor, the compressor in which the refrigerant is compressed at the upstream side of the driving motor and the refrigerant is discharged from the downstream side of the driving motor is called an upstream compressor. I can. In addition, a compressor in which the refrigerant is compressed and the refrigerant is discharged at an upsteam of the driving motor may be referred to as a downstream compressor.

In the case of an upper compression compressor (downstream compressor), there is a high possibility that the refrigerant is compressed and discharged from the compression unit located above the driving motor, and then the lubricating oil is discharged together with the refrigerant. That is, the lubricating oil is mixed with the discharged refrigerant. The lubricating oil mixed with the refrigerant lowers the cooling efficiency and causes a lack of lubricating oil inside the compressor. Therefore, in the case of an upper compression compressor, it is common to periodically need to recover lubricating oil or to install a separate oil recovery device or oil separation device.

In the case of the lower compression type compressor (upstream compressor), the compressed refrigerant passes through the drive motor and is discharged to the outside of the compressor through the discharge space.

In the discharge space, a rotational flow may be generated by a rotor and a rotational shaft of a driving motor. That is, the discharge space may be referred to as a centrifugal separation space. A rotational flow is generated around the center of the discharge space, that is, the center of the centrifugal separation space, and centrifugal separation of the refrigerant and lubricating oil may occur by this rotational flow.

The density of the lubricating oil is significantly greater than that of the refrigerant. Accordingly, by centrifugal separation, the lubricating oil is driven in a direction opposite to the discharge space, and the refrigerant is driven toward the center of the discharge space, so that it can be discharged to the outside of the compressor.

Therefore, it can be said that the lower compression type compressor has a significantly smaller oil discharge amount compared to the upper compression type compressor. However, the amount of oil discharged from the lower compression type compressor cannot be neglected, and therefore a separate oil recovery device or an oil separation device is generally installed. Therefore, there is a need to find a way to significantly reduce the amount of oil discharged so that a separate oil recovery device or oil separation device can be omitted in the lower compression compressor.

An object of the present embodiment is to provide a compressor that can significantly reduce the amount of oil discharged.

An object of the present embodiment is to provide a compressor capable of effectively using a refrigerant discharge space as a centrifugal separation space. In particular, it is intended to provide a compressor capable of using substantially the entire space, not part of the exposed space of the refrigerant, as a centrifugal space.

Through the present embodiment, it is intended to provide a compressor capable of significantly reducing the amount of oil discharge through only a very small change in the conventional compressor configuration.

Through this embodiment, it is intended to provide a compressor capable of remarkably reducing the amount of oil discharged by effectively removing elements that hinder the flow due to centrifugation in the centrifugation space.

Through this embodiment, by reducing the flow resistance according to the shape of the upper shell to provide a compressor that can significantly reduce the amount of oil discharge.

Through this embodiment, it is intended to provide a compressor capable of significantly reducing the amount of oil discharge by providing a terminal provided in the upper shell in a cylindrical shell that is a side surface of the case.

Through this embodiment, by simultaneously performing the expansion of the centrifugation space and the removal of the resistance element of the centrifugal flow, it is intended to provide a compressor capable of satisfying less than 0.01 weight percent, which is significantly lower than 0.1 weight percent of the required oil discharge amount.

In order to implement the above object, according to an embodiment of the present invention, a case; A drive motor including a stator mounted inside the case and a rotor rotatably provided inside the stator in a radial direction; A centrifugal separation space defined by a downstream side of the driving motor and the case inside the case, in which centrifugal separation of compressed refrigerant and lubricating oil is performed; A discharge pipe passing through the case and having an end forming a refrigerant inlet hole extending into the centrifugal separation space; A rotating shaft coupled to the rotor and rotating; A compression unit provided on an upsteam side of the drive motor and compressing a refrigerant by rotation of the rotation shaft; In addition, a compressor may be provided that is a side of the centrifugal separation space and includes a terminal provided on the side of the case and connected to the coil of the stator.

The case includes an upper shell and a cylindrical shell through which the discharge pipe passes, and the centrifugal separation space may be defined by an inner lower portion of the upper shell, an inner upper portion of the cylindrical shell, and an upper portion of the driving motor.

The terminal is preferably provided on the upper side of the cylindrical shell.

The terminal may include a body provided with a plurality of tabs to which a plurality of lead wires are connected.

The plurality of tabs may be spaced apart from each other and may be provided side by side on the same line.

The main body of the terminal is preferably mounted on the cylindrical shell so that the plurality of tabs are positioned in parallel with the longitudinal direction of the compressor.

The lead wire may extend radially outward from an upper portion of the stator to be connected to the terminal. Accordingly, the length of the lead wire is shorter and the height at which the lead wire is connected to the terminal is lower than when the terminal is provided in the upper shell.

The upper shell is formed with a flat surface, and may be bent at an end in a radial direction to be connected to the cylindrical shell.

The upper shell is formed in a curved surface inclined downward in a radial direction and may be connected to the cylindrical shell at an end in the radial direction.

The curved surface is formed to have a multi-stage radius of curvature, and the radius of curvature may decrease toward the outer side in the radial direction.

A value obtained by dividing the sum of values obtained by multiplying each radius of curvature and the length of each arc on the curved surface by the diameter of the centrifugation space is preferably at least 0.1 times the diameter of the centrifugation space. This value can be defined as the mean radius of curvature factor.

The upper shell has two continuous surfaces having a height difference in the radial direction, and the height of the continuous surface in the radial direction inside may be greater than the height of the continuous surface in the radial direction outside.

The two continuous surfaces may be planar.

The two continuous surfaces may be curved surfaces that are convex upward.

The curvature centers of the two continuous surfaces may be located inside the compressor, and the curvature centers of the stepped surfaces connecting the two continuous surfaces may be located outside the compressor.

In the case of having two or more continuous surfaces, the sum of the values obtained by multiplying the radius of curvature of each upper shell and the length of each arc divided by the diameter of the centrifugation space is preferably at least 0.1 times the diameter of the centrifugation space. Do.

It may further include a rotating member provided to provide a centrifugal force to the refrigerant and oil by expanding the rotational force of the rotor to the centrifugal space.

The rotating member may include a rotor blade positioned in the centrifugal separation space and provided to be spaced apart from the center of the rotor by a predetermined distance.

It is preferable that the rotation member includes a flange portion coupled to the rotor or rotation shaft, and is provided to rotate integrally with the rotor or rotation shaft.

It is preferable that the upper position of the rotor blade is equal to or higher than the upper position of the terminal.

In order to implement the above object, according to an embodiment of the present invention, a case; A drive motor including a stator mounted inside the case and a rotor rotatably provided inside the stator in a radial direction; A centrifugal separation space defined by a downstream side of the driving motor and the case inside the case, in which centrifugal separation of compressed refrigerant and lubricating oil is performed; A discharge pipe passing through the case and having an end forming a refrigerant inlet hole extending into the centrifugal separation space; A rotating shaft coupled to the rotor and rotating; A compression unit provided on an upsteam side of the drive motor and compressing a refrigerant by rotation of the rotation shaft; And a compressor including a rotating member provided to provide centrifugal force to the refrigerant and oil by expanding the rotational force of the rotor into the centrifugal space, and integrally rotated with the rotor on one side of the rotor. Can be provided.

The rotating member may include a rotor blade positioned in the centrifugal separation space and provided to be spaced apart from the center of the rotor by a predetermined distance. The rotor blade may be provided to have a predetermined radius at the center of the rotor.

The maximum outer diameter of the rotor may be equal to or smaller than the outer diameter of the rotor. In addition, the maximum outer diameter of the rotor blade may be equal to or greater than the outer diameter of the rotor.

The rotor blade may be a single rotor blade having a circular horizontal cross section or a single rotor blade having a polygonal horizontal cross section.

It is preferable that the minimum inner diameter of the rotor blade is larger than the outer diameter of the discharge pipe so as to surround the discharge pipe.

The rotor blade is provided to have a predetermined height in the rotor, and may define an inner space of the rotating member within the centrifugal separation space.

The rotor blade may have a uniform height or a height differently formed along a circumferential direction, but may be formed to be symmetrical in the circumferential direction.

It is preferable that an end of the discharge pipe is provided to further extend into the inner space of the rotating member.

The extra linear distance (T) through which the compressed refrigerant can flow into the refrigerant inlet hole of the discharge pipe within the inner space of the rotating member is less than 0.1 times the linear distance (d) between the upper end of the circumferential wall and the inner surface of the case. It is desirable to have a large one.

It is preferable that the height of the rotor blade is formed to be greater than or equal to the height of the end coil wound on the stator.

It is preferable that the rotating member includes a flange portion coupled to the rotor, and the rotor blade is formed to protrude from the flange portion to have a height.

The flange portion may prevent refrigerant and oil flowing into the centrifugal separation space from directly flowing into the inner space of the rotating member through the gap. That is, it is preferable that the refrigerant is bypassed to the outside in the radial direction of the rotor blade of the rotating member to flow into the inner space of the rotating member.

When the distance between the lowermost end of the rotor and the uppermost end of the rotor is narrow, the maximum outer diameter of the rotor is preferably equal to or smaller than the outer diameter of the rotor. In this case, the refrigerant and oil flowing into the centrifugal space through the gap are not affected by the flange portion and are driven outward in the radial direction under the influence of the rotor blade.

However, when the distance between the lowermost end of the rotor and the uppermost end of the rotor is large, the maximum outer diameter of the rotor is preferably equal to or greater than the outer diameter of the rotor. In this case, the refrigerant and oil flowing into the centrifugal space through the gap are driven outward in the radial direction under the influence of the flange portion and the rotor blade. Since the separation distance between the flange portion and the gap is sufficient, the time to receive the centrifugal force can be increased.

It is preferable that the flange portion and the rotor blade are integrally formed.

In order to prevent the lubricating oil from flowing into the refrigerant inlet hole of the discharge pipe near the outer surface of the discharge pipe, a guide may be included in the vicinity of the end of the discharge pipe surrounding the discharge pipe.

It is preferable that the guide has a skirt shape extending in a radial direction from an outer surface of the discharge pipe.

It is preferable that the position of the uppermost portion of the guide is formed equal to or higher than the position of the uppermost portion of the rotor blade.

The guide may have a circular plate shape through which the discharge pipe passes through a central portion.

It is preferable that the maximum outer diameter of the guide is smaller than the minimum inner diameter of the rotor blade.

It is preferable that the guide is provided inside the inner space of the rotating member defined by the rotor blade, and the end of the discharge pipe is provided to further extend into the inner space of the rotating member.

The extra linear distance (T) through which the compressed refrigerant can be introduced into the refrigerant inlet hole of the discharge pipe within the inner space of the rotating member is greater than 0.1 times the linear distance (h1) between the end of the rotor blade and the inner surface of the case. desirable.

The rotating member may include a plate-shaped flange portion; And a coupling portion provided to fix the flange portion to the rotor or rotation shaft so that the center of the flange portion coincides with the center of the rotor or rotation shaft, and to separate the flange portion from the rotor toward the centrifugal separation space. have.

The compressor may include a terminal provided on the side of the case as well as a side of the centrifugal space, and connected to the coil of the stator. Through this, it is possible to further enhance the centrifugation effect by preventing abnormal flow in the centrifugation space.

Through this embodiment, it is possible to provide a compressor that can significantly reduce the amount of oil discharged.

Through this embodiment, it is possible to provide a compressor that can effectively use a refrigerant discharge space as a centrifugal separation space. In particular, it is possible to provide a compressor capable of using substantially the entire space, not part of the exposed space of the refrigerant, as a centrifugal space.

Through this embodiment, it is possible to provide a compressor capable of remarkably reducing the amount of oil discharge through only a very small change in the conventional compressor configuration.

Through the present embodiment, it is possible to provide a compressor capable of remarkably reducing the amount of oil discharged by effectively removing elements that hinder the flow due to centrifugation in the centrifugation space.

Through this embodiment, it is possible to provide a compressor capable of remarkably reducing the amount of oil discharge by reducing the flow resistance according to the shape of the upper shell.

Through this embodiment, it is possible to provide a compressor capable of remarkably reducing the amount of oil discharge by providing a terminal provided in the upper shell in a cylindrical shell that is a side surface of the case.

Through this embodiment, it is possible to provide a compressor capable of satisfying less than 0.01 weight percent, which is significantly lower than 0.1 weight percent of the required oil discharge, by simultaneously performing expansion of the centrifugation space and removal of the resistance element of the centrifugal flow. .

1 is a cross-sectional view of a compressor applicable to the present invention, especially a lower (upstream side) compression type scroll compressor,
2 is a simplified cross-sectional view of a compressor according to an embodiment of the present invention,
Figure 3 shows the flow of oil and refrigerant in the centrifugal space inside the compressor shown in Figure 2,
4 is a simplified cross-sectional view of a compressor according to another embodiment of the present invention,
5 is a simplified cross-sectional view of a compressor according to another embodiment of the present invention,
6 is a simplified cross-sectional view of a compressor according to another embodiment of the present invention,
7 is a table comparing OCR performance in the embodiments shown in FIGS. 2, 4, 5, and 6;
2 to 7 are diagrams for embodiments of a first embodiment for OCR reduction,
8 is a simplified cross-sectional view of a conventional compressor,
9 is a simplified cross-sectional view of a compressor according to an embodiment of the present invention,
10 is a simplified cross-sectional view of a compressor according to another embodiment of the present invention,
11 is a simplified cross-sectional view of a compressor according to another embodiment of the present invention,
12 is a table comparing OCR performance in the embodiments shown in FIGS. 8 to 11,
13 is an OCR change table according to the average radius of curvature factor of the upper shell and the position of the terminal,
8 to 13 are diagrams of embodiments of a second form for OCR reduction.

A preferred embodiment according to the present invention will be described in detail with reference to the accompanying drawings. In the drawings, the same reference numerals are used to indicate the same or similar elements.

First, a compressor that can be applied to an embodiment of the present invention will be described in detail with reference to FIG. 1.

1 is a cross-sectional view of a scroll compressor applicable to an embodiment of the present invention. Since the compression unit is located under the driving motor, it can be referred to as a lower compression type compressor or an upstream compressor.

For convenience of description, upper/lower positions may be named based on a vertically positioned compressor. The upstream/downstream positions may be named based on the flow of the refrigerant and the position of the driving motor 120. In the same compressor, upper would mean downstream and lower would mean upsteam.

The compressor according to the present invention may include a case 110, a drive motor 120, a compression unit 100, and a rotation shaft 126.

The case 110 may be formed to have an inner space. For example, a storage space in which oil is stored may be provided under the case 110. The storage space may mean a fourth space V4 to be described later. That is, the fourth space V4 to be described later may be formed as the storage space.

In addition, a refrigerant discharge pipe 116 for discharging the compressed refrigerant may be provided at the upper portion.

Specifically, the inner space of the case 110 is a first space V1 disposed above the drive motor 110, and a second space V2 disposed between the drive motor 120 and the compression unit 100. ), a third space V3 partitioned by a discharge cover 170 to be described later, and a fourth space V4 disposed under the compression unit 100.

The case 110 may be formed in a cylindrical shape. For example, the case 110 may include a cylindrical shell 111 whose top and bottom are open.

An upper shell 112 may be installed on the upper portion of the cylindrical shell 111, and a lower shell 114 may be installed under the cylindrical shell 111. The upper and lower shells 112 and 114 may be coupled to the cylindrical shell 111 by welding, for example, to form an inner space.

A refrigerant discharge pipe 116 may be installed in the upper shell 112. The refrigerant compressed by the compression unit 100 may be discharged to the outside through the refrigerant discharge pipe 116. For example, the refrigerant compressed in the compression unit 100 passes through the third space (V3), the second space (V2), and the first space (V1) sequentially, and then through the refrigerant discharge pipe (116). Can be discharged to the outside.

1 does not show an oil separation device or an oil recovery device connected to a compressor in a general configuration. This means that in the compressor according to the present embodiment, oil can be sufficiently effectively separated so that a separate oil separation device is not required.

The lower shell 114 may partition the fourth space V4, which is a storage space capable of storing oil. The fourth space V4 may function as an oil chamber supplying oil to the compression unit 100 so that the compressor can operate smoothly.

In addition, a refrigerant suction pipe 118 which is a passage through which refrigerant to be compressed is introduced may be installed on the side of the cylindrical shell 111. The refrigerant suction pipe 118 may be installed to pass through to the compression chamber S1 along the side of the fixed scroll 150 to be described later.

The driving motor 120 may be installed inside the case 110. For example, the drive motor 120 may be disposed inside the case 110 and above the compression unit 100.

The driving motor 120 may include a stator 122 and a rotor 124. The stator 122 may be cylindrical, for example, and may be fixed to the case 110. A coil 122a may be wound around the stator 122. In addition, a refrigerant passage groove 112a may be formed between the outer circumferential surface of the rotor 124 and the inner circumferential surface of the stator 122 so that the refrigerant or oil discharged from the compression unit 100 passes. That is, the refrigerant passage groove 112a may be partitioned by an inner peripheral surface of the stator 122 and an outer peripheral surface of the rotor 124.

The rotor 124 is disposed inside the stator 122 in the radial direction and may generate rotational power. That is, the rotor 124 may rotate with the rotation shaft 126 by pressing the rotation shaft 126 at the center thereof. The rotational power generated by the rotor 124 may be transmitted to the compression unit 100 through the rotation shaft 126.

The compression unit 100 may be coupled to the driving motor 120 to compress the refrigerant. The compression unit 100 may be formed so that the rotation shaft 126 connected to the driving motor 120 passes.

The compression unit 100 may include a shaft receiving portion protruding upward and downward, and the rotation shaft 126 may penetrate at least a portion of the shaft receiving portion. For example, the bearing unit may include a first bearing section protruding upward from the compression unit 100 and a second bearing section protruding downward, and a detailed description thereof will be described later.

The compression unit 110 may include a main frame 130, a fixed scroll 150, and an orbiting scroll 140.

Specifically, the compression unit 100 may further include an Oldham's ring 135. The Oldham ring 135 may be installed between the orbiting scroll 140 and the main frame 130. In addition, the Oldham ring 135 enables orbiting movement of the orbiting scroll 140 on the fixed scroll 150 while preventing the orbiting scroll 140 from rotating.

The main frame 130 may be provided under the driving motor 120 and may form an upper portion of the compression unit 100.

The main frame 130 has a frame plate portion (hereinafter referred to as a'first plate portion') 132 having an approximately circular shape, and the number of frame axes provided at the center of the first plate portion 132 and through which the rotation shaft 126 passes. A portion (hereinafter referred to as a'first shaft receiving portion') 132a, and a frame side wall portion protruding downward from the outer peripheral portion of the first plate portion 132 (hereinafter referred to as'first side wall portion') 131 May be provided.

The first side wall portion 131 may have an outer peripheral portion in contact with the inner peripheral surface of the cylindrical shell 111, and a lower portion thereof may contact an upper portion of the fixed scroll side wall portion 155 to be described later.

The first side wall part 131 may be provided with a frame discharge hole 131a passing through the inside of the first side wall part 131 in the axial direction to form a refrigerant passage. The frame discharge hole 131a may have an inlet communicating with the outlet of the fixed scroll discharge hole 155a to be described later, and the outlet may communicate with the second space V2. The frame discharge hole 131a and the fixed scroll discharge hole 155a communicated with each other may be represented by second discharge holes 131a and 155a.

A plurality of frame discharge holes 131a may be provided along the circumference of the main frame 130. Further, a plurality of fixed scroll discharge holes 155a may also be provided along the circumference of the fixed scroll 150 so as to correspond to the frame discharge holes 131a.

The first shaft receiving part 132a may be formed to protrude from the top surface of the first hard plate part 132 toward the driving motor 120. In addition, a first bearing part may be formed in the first shaft receiving part 132a so that the main bearing part 126c of the rotating shaft 126 to be described later is supported through.

That is, in the center of the main frame 130, the first bearing portion 132a of the rotation shaft 126 constituting the first bearing portion is rotatably inserted and supported therethrough may be formed through the axial direction. .

An oil pocket 132b for collecting oil discharged between the first shaft receiving part 132a and the rotating shaft 126 may be formed on the upper surface of the first hard plate part 132.

The oil pocket 132b may be concavely formed on the upper surface of the first hard plate portion 132 and may be formed in an annular shape along the circumference of the first bearing portion 132a. In addition, a back pressure chamber (S2) may be formed at the bottom of the main frame 130 to form a space together with the fixed scroll 150 and the orbiting scroll 140 to support the orbiting scroll 140 by the pressure of the space. have.

For reference, the back pressure chamber S2 may include an intermediate pressure region (i.e., an intermediate pressure chamber), and the oil supply passage 126a provided in the rotation shaft 126 is a high pressure region having a higher pressure than the back pressure chamber S2. Can include.

A back pressure seal 180 may be provided between the main frame 130 and the orbiting scroll 140 to distinguish the high pressure region and the medium pressure region, and the back pressure seal 180 is, for example, a sealing member. Can play a role.

In addition, the main frame 130 may be combined with the fixed scroll 150 to form a space in which the orbiting scroll 140 can be installed to be orbitable.

The fixed scroll 150 may be provided under the main frame 130. That is, the fixed scroll 150 constituting the first scroll may be coupled to the bottom of the main frame 130.

The fixed scroll 150 includes a fixed scroll plate portion (hereinafter referred to as a'second plate portion') 154 having a substantially circular shape, and a fixed scroll side wall portion protruding upward from the outer peripheral portion of the second plate portion 154 (hereinafter ,'Second side wall part') 155, the second hard plate part 154 protrudes from the upper surface and meshes with the orbiting wrap 141 of the orbiting scroll 140 to be described later to form a compression chamber (S1) A wrap 151 and a fixed scroll shaft receiving portion (hereinafter referred to as a'second shaft receiving portion') 152 formed in the center of the rear surface of the second plate portion 154 and through which the rotating shaft 126 passes may be provided. .

The compression unit 100 is spaced radially outward of the compression unit 100 from the first discharge hole 153 and the first discharge hole 153 for discharging the compressed refrigerant to the discharge cover 170 and compresses The second discharge holes 131a and 155a may be provided to guide the refrigerant toward the refrigerant discharge pipe 116.

Specifically, a first discharge hole 153 for guiding the compressed refrigerant from the compression chamber S1 to the inner space of the discharge cover 170 may be formed in the second hard plate part 154. In addition, the position of the first discharge hole 153 may be arbitrarily set in consideration of the required discharge pressure.

As the first discharge hole 153 is formed toward the lower shell 114, on the bottom of the fixed scroll 150, a discharge cover for guiding the refrigerant discharged from the compression unit to the fixed scroll discharge hole 155a to be described later ( 170) can be combined.

The discharge cover 170 may be hermetically coupled to the lower end of the compression unit 100. The discharge cover 170 may be formed to guide the refrigerant compressed by the compression unit 100 toward the refrigerant discharge pipe 116.

For example, the discharge cover 170 may be hermetically coupled to the bottom of the fixed scroll 150 so as to separate the refrigerant discharge passage and the fourth space V4.

In addition, in the discharge cover 170, the oil feeder 171 is coupled to the sub-bearing part 126g of the rotation shaft 126 constituting the second bearing part and is at least partially immersed in the oil accommodated in the fourth space V4 of the case 110. A through hole 176 may be formed to penetrate through.

Meanwhile, the second side wall part 155 may be provided with a fixed scroll discharge hole 155a that penetrates the inside of the second side wall part 155 in the axial direction and forms a refrigerant passage together with the frame discharge hole 131a. .

The fixed scroll discharge hole 155a is formed to correspond to the frame discharge hole 131a, and the inlet communicates with the inner space of the discharge cover 170, and the outlet may communicate with the inlet of the frame discharge hole 131a.

The fixed scroll discharge hole (155a) and the frame discharge hole (131a) is a third space (V3) so that the refrigerant discharged from the compression chamber (S1) to the inner space of the discharge cover (170) is guided to the second space (V2). ) And the second space V2 can be communicated.

In addition, a refrigerant suction pipe 118 may be installed in the second side wall portion 155 to communicate with the suction side of the compression chamber S1. In addition, the refrigerant suction pipe 118 may be installed to be spaced apart from the fixed scroll discharge hole 155a.

The second bearing portion 152 may be formed to protrude from the lower surface of the second hard plate portion 154 toward the fourth space V4. In addition, a second bearing part may be provided in the second shaft receiving part 152 so that the sub-bearing part 126g of the rotating shaft 126 is inserted and supported.

In addition, the second shaft receiving part 152 may be bent toward the center of the axis so that the lower end of the second shaft receiving part 152 supports the lower end of the sub-bearing part 126g of the rotating shaft 126 to form a thrust bearing surface.

The orbiting scroll 140 may be disposed between the main frame 130 and the fixed scroll 150, and may form a second scroll.

Specifically, the orbiting scroll 140 may be coupled to the rotation shaft 126 to form a pair of compression chambers S1 between the fixed scroll 150 and the fixed scroll 150 while performing orbiting motion.

The orbiting scroll 140 protrudes from the lower surface of the orbiting scroll hard plate part (hereinafter referred to as'the third hard plate part') 145 and the third hard plate part 145 having an approximately circular shape to engage with the fixed wrap 151. It may include a rotating shaft coupling portion 142 provided in the center of the orbiting wrap 141 and the third hard plate portion 145 and rotatably coupled to the eccentric portion 126f of the rotating shaft 126.

The outer periphery of the third hard plate part 145 is located at the upper end of the second side wall part 155, and the lower end of the orbiting wrap 141 is in close contact with the upper surface of the second hard plate part 154, so that the fixed scroll 150 Can be supported.

For reference, a pocket groove 185 for guiding the oil discharged through the oil holes 128a, 128b, 128d, and 128e to be described later to the intermediate pressure chamber may be formed on the upper surface of the orbiting scroll 140.

Specifically, the pocket groove 185 may be formed to be concave on the upper surface of the third hard plate part 145. That is, the pocket groove 185 may be formed on the upper surface of the third hard plate part 145 between the back pressure seal 180 and the rotation shaft 126.

In addition, as shown in the drawing, one or more pocket grooves 185 may be formed on both sides of the rotation shaft 126. The pocket groove 185 may be formed in an annular shape about the rotation shaft 126 on the upper surface of the third plate portion 145 between the back pressure seal 180 and the rotation shaft 126.

The outer circumferential portion of the rotation shaft coupling portion 142 is connected to the orbiting wrap 141 and serves to form a compression chamber S1 together with the fixed wrap 151 during the compression process.

The fixing wrap 151 and the revolving wrap 141 may be formed in an involute shape. The involute shape may mean a curve corresponding to a trajectory drawn by an end of a thread when unwinding a thread wound around a basic circle having an arbitrary radius.

In addition, the eccentric portion 126f of the rotation shaft 126 may be inserted into the rotation shaft coupling portion 142. The eccentric portion 126f inserted into the rotation shaft coupling portion 142 may overlap the orbiting wrap 141 or the fixed wrap 151 in the radial direction of the compressor.

Here, the radial direction may mean a direction orthogonal to the axial direction (ie, the vertical direction) (ie, the left and right direction).

As described above, when the eccentric part 126f of the rotation shaft 126 penetrates the third hard plate part 145 and overlaps in the radial direction with the orbiting wrap 141, the repulsive force and the compressive force of the refrigerant are applied to the third hard plate part 145 ) Can be applied to the same plane and partially cancel each other.

In addition, the rotation shaft 126 is coupled to the driving motor 120 and may include an oil supply passage 126a for guiding the oil contained in the fourth space V4, which is a storage space of the case 110, upward.

Specifically, the upper portion of the rotation shaft 126 is pressed into the center of the rotor 124 and coupled, and the lower portion thereof is coupled to the compression unit 100 and supported in a radial direction.

The rotation shaft 126 may transmit the rotational force of the driving motor 120 to the orbiting scroll 140 of the compression unit 100. Through this, the orbiting scroll 140 eccentrically coupled to the rotation shaft 126 may perform a orbiting motion with respect to the fixed scroll 150.

A main bearing part 126c may be formed below the rotation shaft 126 to be inserted into the first shaft receiving part 132a of the main frame 130 and supported in the radial direction. In addition, a sub-bearing part 126g may be formed under the main bearing part 126c to be inserted into the second bearing part 152 of the fixed scroll 150 and supported in a radial direction. In addition, an eccentric portion 126f may be formed between the main bearing portion 126c and the sub bearing portion 126g to be inserted into and coupled to the rotation shaft coupling portion 142 of the orbiting scroll 140.

The main bearing part 126c and the sub bearing part 126g are formed on a coaxial line to have the same axial center, and the eccentric part 126f is radially directed to the main bearing part 126c or the sub-bearing part 126g. It can be formed eccentrically.

The eccentric portion 126f may have an outer diameter smaller than the outer diameter of the main bearing portion 126c and larger than the outer diameter of the sub-bearing portion 126g. In this case, it may be advantageous in coupling the rotation shaft 126 through the respective shaft receiving portions 132a and 152 and the rotation shaft coupling portion 142.

In addition, an oil supply channel 126a for supplying the oil in the fourth space V4, which is a storage space, to the outer circumferential surface of each bearing unit 126c and 126g and the eccentric part 126f is formed inside the rotary shaft 126. Can be. In addition, oil holes 128a, 128b, 128d, and 128e are formed in the bearings and eccentric portions 126c, 126g, and 126f of the rotating shaft 126 in the radial direction of the rotating shaft 126 from the oil supply passage 126a. Can be.

Specifically, the oil hole may include a first oil hole 128a, a second oil hole 128b, a third oil hole 128d, and a fourth oil hole 128e.

First, the first oil hole 128a may be formed to penetrate the outer peripheral surface of the main bearing part 126c. The first oil hole 128a may be formed to penetrate from the oil supply flow path 126a to the outer peripheral surface of the main bearing part 126c.

In addition, the first oil hole 128a may be formed to penetrate the upper part of the outer peripheral surface of the main bearing part 126c, for example, but is not limited thereto. When the first oil hole 128a includes a plurality of holes, each hole may be formed only in the upper or lower part of the outer circumferential surface of the main bearing part 126c, or at the upper and lower part of the outer circumferential surface of the main bearing part 126c. Each may be formed.

The second oil hole 128b may be formed between the main bearing portion 126c and the eccentric portion 126f. Unlike that shown in the drawing, the second oil hole 128b may include a plurality of holes.

The third oil hole 128d may be formed to penetrate the outer peripheral surface of the eccentric portion 126f. Specifically, the third oil hole 128d may be formed to penetrate from the oil supply passage 126a to the outer peripheral surface of the eccentric portion 126f.

The fourth oil hole 128e may be formed between the eccentric portion 126f and the sub-bearing portion 126g.

The oil guided upward through the oil supply passage 126a may be discharged through the first oil hole 128a to be supplied to the outer peripheral surface of the main bearing part 126c as a whole.

In addition, the oil guided upward through the oil supply passage 126a is discharged through the second oil hole 128b and supplied to the upper surface of the orbiting scroll 140, and is discharged through the third oil hole 128d. It may be entirely supplied to the outer peripheral surface of the eccentric portion (126f).

In addition, the oil guided upward through the oil supply flow path 126a is discharged through the fourth oil hole 128e, and the outer circumferential surface of the sub-bearing part 126g or between the orbiting scroll 140 and the fixed scroll 150 Can be supplied.

An oil feeder 171 for pumping the oil filled in the fourth space V4 may be coupled to a lower end of the rotation shaft 126, that is, a lower end of the sub-bearing part 126g. The oil feeder 171 may be formed to supply oil accommodated in the fourth space V4 toward the aforementioned oil holes 128a, 128b, 128d, and 128e.

The oil feeder 171 includes an oil supply pipe 173 inserted into and coupled to the oil supply passage 126a of the rotation shaft 126, and an oil suction member 174 inserted into the oil supply pipe 173 to absorb oil. Can be done.

The oil supply pipe 173 may be installed to pass through the through hole 176 of the discharge cover 170 and be immersed in the fourth space V4, and the oil suction member 174 may function like a propeller.

The oil suction member 174 may have a spiral groove 174a extending along the longitudinal direction of the oil suction member 174. The spiral groove 174a may be formed around the oil suction member 174, and may extend toward the aforementioned oil holes 128a, 128b, 128d, and 128e.

When the oil feeder 171 is rotated together with the rotation shaft 126, the oil accommodated in the fourth space V4 may be guided to the oil holes 128a, 128b, 128d, and 128e along the spiral groove 174a.

A balance weight 127 for suppressing noise and vibration may be coupled to the rotor 124 or the rotation shaft 126. The balance weight 127 may be provided in the second space V2 between the driving motor 120 and the compression unit 100.

Next, an operation process of the scroll compressor according to an embodiment of the present invention will be described as follows.

When power is applied to the driving motor 120 to generate rotational force, the rotational shaft 126 coupled to the rotor 124 of the driving motor 120 rotates. Then, a compression chamber S1 is formed between the orbiting wrap 141 and the fixed wrap 151 while the orbiting scroll 140 eccentrically coupled to the rotating shaft 126 performs a orbiting motion with respect to the fixed scroll 150. The compression chamber S1 may be formed in several stages in succession while gradually decreasing in volume toward the center.

Then, the refrigerant supplied from the outside of the case 110 through the refrigerant suction pipe 118 may be directly introduced into the compression chamber S1. This refrigerant is compressed while moving in the direction of the discharge chamber of the compression chamber S1 by the orbiting motion of the orbiting scroll 140, and then from the discharge chamber to the third space V3 through the discharge port 153 of the fixed scroll 150. Can be ejected.

Thereafter, the compressed refrigerant discharged into the third space V3 is discharged into the inner space of the case 110 through the fixed scroll discharge hole 155a and the frame discharge hole 131a, and then the refrigerant discharge pipe 116 Through a series of processes that are discharged to the outside of the case 110 is repeated.

While the compressor is operating, the oil contained in the fourth space (V4) is guided upward through the rotary shaft 126 and smoothly on the bearing portion, that is, the bearing surface through a plurality of oil holes (128a, 128b, 128d, 128e). By being supplied in such a way, wear of the bearing part can be prevented.

In addition, oil discharged through the plurality of oil holes 128a, 128b, 128d, and 128e may form an oil film between the fixed scroll 150 and the orbiting scroll 140 to maintain an airtight state in the compression unit.

Due to such oil, oil may be mixed in the refrigerant compressed by the compression unit 100 and discharged to the first discharge hole 153. Hereinafter, for convenience of explanation, a refrigerant mixed with oil may be referred to as an oil mixed refrigerant.

The oil-mixed refrigerant is guided to the first space V1 through the second discharge holes 131a and 155a, the second space V2, and the refrigerant passage groove 112a. In addition, the refrigerant among oil-mixed refrigerants guided to the first space V1 may be discharged to the outside of the compressor through the refrigerant discharge pipe 116, and the oil may be discharged into the fourth space V4 through the oil return passage 112b. Can be recovered.

For example, the oil return passage 112b may be disposed at the outermost side in the radial direction within the case 110. Specifically, the oil return passage 112b is a flow path between the outer circumferential surface of the stator 122 and the inner circumferential surface of the cylindrical shell 111, the flow path between the outer circumferential surface of the main frame 130 and the inner circumferential surface of the cylindrical shell 111, and a fixed scroll It may include a flow path between the outer peripheral surface of 150 and the inner peripheral surface of the cylindrical shell 111.

Meanwhile, since the discharge cover 170 is coupled to the lower end of the compression unit 100, a fine gap may exist between the lower end of the compression unit 100 and the upper end of the discharge cover 170. These minute gaps may cause refrigerant leakage.

That is, when the refrigerant is discharged into the third space V3 through the first discharge hole 153 of the compression unit 100 and guided to the second discharge holes 131a and 155a, a part of the refrigerant is discharged into the compression unit 100 ) And the discharge cover 170 may leak through a gap that may exist.

In addition, such a leakage of the refrigerant has a problem that may lower the compression efficiency of the compressor. This problem is with the sealing members 210 and 220 and the compression unit 100 provided between the compression unit 100 and the discharge cover 170 (that is, the coupling unit between the compression unit 100 and the discharge cover 170). It can be solved through the coupling structure of the discharge cover 170.

This embodiment may provide a compressor further including a rotating member 200 in the compressor illustrated in FIG. 1. That is, a compressor in which the rotating member 200 is installed so that centrifugal separation occurs more effectively in the first space V1 may be provided. Accordingly, the first space V1 may be referred to as a centrifugal separation space in which refrigerant and oil are centrifuged by the rotating member 200.

An example of a compressor equipped with a rotating member 200 will be described in detail with reference to FIG. 2.

A centrifugal separation space V1 is formed in the upper or downstream side of the compressor. Specifically, a centrifugal separation space defined by the inside of the case 110 on the upper or downstream side and one side of the driving motor is formed. The refrigerant and lubricating oil compressed in the compression unit flow into the centrifugal separation space.

A discharge pipe 116 having a refrigerant inlet hole 116b formed at the end 116a passes through the case 110, particularly the upper shell 112, and extends into the centrifugal separation space. The refrigerant compressed through the refrigerant inlet hole 116b is discharged to the outside of the compressor.

The stator 122 of the driving motor 120 is fixed to the inner wall of the case 110, in particular, the cylindrical shell 111, and the rotor 124 is rotatably provided inside the stator 122 in the radial direction. A rotation shaft 126 is provided at the center of the rotor 124. The rotor 124 and the rotation shaft 126 rotate integrally.

Since the upper surface of the rotor 124 and the rotation shaft 126 defines the centrifugation space V1, the lower surface of the centrifugal separation space or the center of the lower region prevents the rotation of the rotor 124 and the rotation shaft 126. The centrifugal force is generated. However, this centrifugal force is difficult to extend to the entire centrifugation space. That is, it is difficult to expand the centrifugal force to the upper shell 112.

For this reason, in order to increase the generation of centrifugal force in the centrifugal separation space while expanding the centrifugal force to the entire area of the centrifugation space, the rotating member 200 may be provided.

The rotation member 200 is provided to be fixed to the upper side (downstream side) of the rotor 124 and/or the rotation shaft 126, and may be provided to rotate integrally with the rotor 124 and the rotation shaft 126. The rotation member 200 may be formed to extend upward (downstream) from the rotor 124 and/or the rotation shaft 126. That is, the rotating member 200 may be provided to extend the rotational force of the rotor to the centrifugal separation space to provide centrifugal force to the refrigerant and oil.

The rotating member 200 may include a rotor blade 210 positioned in the centrifugal separation space and provided to have a predetermined radius and spaced apart from the center of the rotor 124.

The rotor blade 210 is formed to have a predetermined height. Accordingly, as the rotor blade 21 rotates, the inner space V12 of the rotating member is defined by the radius of the rotor blade 210 and the height of the rotor blade 210. That is, the centrifugal separation space V1 may be divided into an outer space V11 of the rotating member and an inner space V12 of the rotating member.

It is preferable that the rotor blade 210 is provided to have a predetermined height in the rotor. The refrigerant and oil are introduced into the centrifugal separation space V1 through the gap between the rotor 124 and the stator 122, that is, the refrigerant passage groove 112a. Therefore, after the refrigerant and oil are smoothly discharged into the centrifugal separation space, it is to be affected by the centrifugal force by the rotor blade.

The rotor blade 210 may have a uniform height. Of course, the height of the rotor blade may be formed differently along the circumferential direction. For example, it may be formed in a wavy shape or a step shape along the circumferential direction. The rotor blade 210 may be formed in the form of a single circumferential wall. In this case, the rotating member 200 has a cup shape.

In order to form and easily fix the rotating member 200 in a simple shape, the rotating member 200 may include a flange portion 220. The flange portion 220 may be fixed to the rotor 124 or the rotation shaft 126. The flange portion 220 may be fixed through stud, bolt or screw coupling.

The rotor blade may be formed to protrude from the flange portion to have a height. That is, the rotor blade protrudes upward from the periphery of the flange portion so that the rotating member 200 may have a cup shape. It is preferable that the flange portion 220 has a flat plate shape. Therefore, the rotating member 200 may be referred to as a rotating cup.

The rotating member 200 can be easily manufactured by being integrally formed with the flange portion 220 and the rotor blade 210.

Meanwhile, the coil 112a shown in FIG. 1 has an end coil 122b further protruding upward from the upper surface of the stator 112. Therefore, it is preferable that the centrifugal force through the rotating member 200 extends further to the top than the end coil 122b. To this end, it is preferable that the height of the rotor 210 is formed to be greater than or equal to the height of the upper end of the coil wound on the stator, that is, the upper end coil 122b. Accordingly, the flow generated by the rotating member 200 may be further expanded radially outward beyond the upper end coil 122b.

It is preferable that the end (116a) of the discharge pipe (116) is provided to further extend into the inner space (V12) of the rotating member (200). Because, the rotating member 200 divides the centrifugal separation space (V1) into an inner space (V12) and an outer space (V11) of the rotating member, and the oil with high density is driven outward in the radial direction, and the refrigerant with low density is in the radial direction. Because it is driven inward. This is because the discharge pipe 116 communicates a relatively high pressure internal space of the compressor and a relatively low pressure external space of the compressor. Therefore, it is preferable that the position of the end (116a) of the discharge pipe (116) extends further downward from the center of the centrifugation space. Through this, it is possible to overcome centrifugal force and effectively prevent high-density oil from flowing into the discharge pipe. That is, it is possible to significantly prevent oil from flowing through the refrigerant inlet hole 116b of the discharge pipe 116.

When the height of the centrifugal separation space is H, H can be said to be the sum of h2, the height of the rotor, and h1, the distance between the top and upper shells of the rotor. In addition, the inner diameter of the discharge pipe may be referred to as d1, the outer diameter of the discharge pipe may be referred to as d2, and the diameter of the centrifugation space may be referred to as D1.

Since the size of the discharge pipe will be determined according to the amount of refrigerant discharged or the capacity or standard of the compressor, d1 and d2 will be fixed values, and H and D1 will also be fixed values. Of course, these values can be changed, but the change is not desirable because it requires a change in the overall structure and size of the pre-designed compressor.

Therefore, it would be desirable to appropriately determine the diameter D2 of the rotating member 200, the height h2 of the rotating member 200, and the separation distance T between the rotating member 200 and the discharging tube end 116a, excluding other values. .

As described above, since the discharge tube end 116a is preferably located in the inner space of the rotating member 200, T must be smaller than h2. As h2 increases, the volume of the inner space V12 of the rotating member 200 increases. However, in this case, there may be a problem in that the refrigerant located in the outer space V11 of the rotating member 200 cannot be smoothly discharged. This is because h1 decreases as h2 increases, so that the area for the refrigerant to flow from the outer space V11 of the rotating member to the inner space V12 decreases.

Therefore, it is preferable to make h1 equal to d2, which is the outer diameter of the discharge pipe, or to increase or decrease substantially about 10% from d2. And it is preferable that h2 is greater than h1. Through this, the centrifugal force by the rotating member can be further extended to the centrifugal separation space, while the refrigerant can be smoothly introduced from the outer space of the rotating member to the inner space.

On the other hand, the smaller T is, the smaller the area in which the refrigerant flows through the refrigerant inlet hole 116b of the discharge pipe. Therefore, the flow resistance becomes large. Therefore, T can be determined to be greater than 0.25 times d2. As T becomes larger, the refrigerant inlet hole 116b of the discharge pipe becomes closer to the outer space of the rotating member. Therefore, the possibility of oil flowing into the discharge pipe increases. In consideration of this, T may be determined equal to or smaller than d1.

Meanwhile, the rotating member means an additional load of the driving motor. Therefore, it is preferable that the thickness of the rotating member 200 is thin. However, it is preferable that the thickness of the rotating member 200, particularly the rotor 210, has a stiffness that is not susceptible to deformation.

3 shows the flow of refrigerant and oil when the rotating member shown in FIG. 2 is applied.

As shown, it can be seen that the refrigerant indicated in light color is discharged through the discharge tube through the discharge tube, and the oil indicated in dark color flows in the centrifuge space and is driven to the bottom of the centrifuge space.

However, as can be seen in this flow analysis, the oil directed toward the discharge pipe can be seen near the outer wall 116c of the end 116c of the discharge pipe 116. Oil can flow around the end of the discharge pipe with an angle of approximately 80 degrees (about 10 degrees with respect to the outer wall of the discharge pipe). There is a possibility that a trace amount of oil is discharged to the discharge pipe by this oil flow.

In order to solve the problem of the possibility of oil discharge, as shown in FIG. 4, in an embodiment of the present invention, a guide 230 may be further provided.

The lubricating oil may be prevented from flowing downward through the guide 230 along the outer wall 116c of the discharge pipe 116 and flowing into the refrigerant inlet hole 116b.

The guide 230 may be provided to surround the discharge pipe 116 near the end 116a of the discharge pipe. The guide 230 may be formed in a skirt shape extending in a radial direction from an outer wall of the discharge pipe.

The guide 230 may have a plate shape through which the discharge pipe 116 penetrates at a center portion, and may have a circular plate shape.

It is preferable that the maximum outer diameter (D3) of the guide is smaller than the minimum inner diameter of the rotor blade. Accordingly, an annular space is formed between the radially inner side of the minimum inner diameter of the rotor blade and the radially outer side of the maximum outer diameter of the guide. That is, the refrigerant and oil may flow into the inner space V12 of the rotating member through the annular space. However, as described above, since the oil having high density is driven outward in the radial direction, only the refrigerant may substantially flow into the inner space V12 through the annular space. In addition, the flow of oil toward the outer wall of the discharge pipe 116 is blocked by the guide 230 and flows outward in the radial direction. The flow of oil outside the radial direction is influenced by the rotational force of the rotating member 200 and scatters upward and then is driven to the outside in the radial direction.

The position of the upper surface of the guide 230 may be the same as the position of the upper end of the rotor blade 210. Of course, the position of the upper surface of the guide 230 may be above or below the position of the upper end of the rotor blade 210. However, as shown in FIG. 3, since the flow of oil toward the discharge pipe 116 is generated from above the upper end of the rotating member, the position of the upper surface of the guide 230 is equal to the upper position of the rotor blade 210 It would be desirable to be the same or located on top.

Meanwhile, the guide 230 may be formed to have an umbrella shape. That is, it may be formed to be inclined downward from the center in the radial direction toward the outside. In this case, the center of the guide 230 may be located more rightly above the discharge pipe. However, the position of the radial end may be the same as the radial end position shown in FIG. 4 or may be located slightly above, and it is preferable that the maximum radius is the same.

The difference in the area formed by the outer diameter of the guide from the area formed by the inner diameter of the rotating member may be referred to as an area through which the refrigerant flows into the rotating member. Therefore, it is preferable that the size of the area is larger than the area of the refrigerant inlet hole of the discharge pipe.

5 shows another embodiment of the guide. The guide 240 in this embodiment may be said to be located above the guide in the above-described embodiment and have a larger maximum radius. That is, it can be said that a guide having an outer diameter larger than the maximum outer diameter of the rotating member 200 is provided.

In this case, the flow of oil toward the outer wall of the discharge pipe 116 is blocked beforehand, so that the oil is effectively blocked from flowing into the inner space of the rotating member. Therefore, it can be sufficiently expected that the oil discharge amount is reduced compared to the embodiment shown in FIG. 3.

6 shows another embodiment of the guide. The guide 250 in this embodiment may include a horizontal portion 251 and a vertical portion 252. The horizontal portion may be the same as the guide 240 described above, and the vertical portion 252 may extend downward from the radial end of the horizontal portion 251.

The vertical part 252 blocks the flow of oil toward the outer wall of the discharge pipe 116 in advance and effectively blocks the oil from flowing into the inner space of the rotating member. In addition, the oil scattered in the radial direction from the horizontal portion 251 is blocked by the vertical portion 252 and thus it is not easy to flow into the inner space of the rotating member. Therefore, it can be sufficiently expected that the oil discharge amount is reduced compared to the embodiment shown in FIG. 3.

7 shows a table comparing the effects of the oil discharge amount. The basic concept shown in FIG. 2, case 1 shown in FIG. 4, case 2 shown in FIG. 5, and case 3 shown in FIG. 6 show the oil content rate (OCR). The oil discharge amount may be expressed as a ratio of the weight percent of oil to the total weight percent of the refrigerant and oil discharged from the discharge pipe 116.

As shown in FIG. 7, it can be seen that if the rotating member 200 is simply applied as in Case 1, a 0.02 OCR result can be obtained under the same driving condition (for example, 120 Hz) of the compressor. This is a very effective oil separation result, and can be said to be a result of oil separation at a level that does not require an oil separator or oil recovery device in practice.

It can be seen that when the rotating member 200 and the guide 230 are applied as in Case 2, a 0.01 OCR result can be obtained under more severe compressor driving conditions (for example, 161 Hz). This can be said to be a very remarkable oil separation result. In other words, it can be said that the result of oil separation does not require an oil separator or an oil recovery device.

In cases 3 and 4, it can be seen that the oil separation result is superior to the basic concept. That is, in any case, it can be seen that the oil separation result is improved by providing the rotating member 200 and the guides 230, 240, 250.

However, as can be seen in Case 3 and Case 4, it can be seen that the flow path from the outside to the inside of the rotating member 200 through the guides 240 and 250 is bent or the area of the flow path is narrowed, which is not an optimal solution. have.

This is because the pressure sucked from the discharge pipe 116 is the same in the difference between the internal pressure and the external pressure of the compressor, but when the flow resistance to the discharge pipe 116 occurs, the refrigerant flows and a certain portion of the oil flows together. It can be seen as something.

Therefore, it is preferable that the area of the refrigerant flow path into the internal space of the rotating member 200, that is, the number of bends of the flow path formed between the rotor blade 210 of the rotating member 210 and the guides 230, 240, 250 is smaller. can do.

The basic concept and case 1 can be said to flow into the internal space of the rotating member 200 by 0 to 1 bend, case 2 1 to 2 times, and case 3 2 to 3 flow bends.

As the area of the flow path decreases, the refrigerant is not smoothly discharged, which may lead to an increase in the amount of oil discharged. Accordingly, it is preferable that the cross-sectional area of the flow path between the rotating member and the guide is larger than the area by the inner diameter of the discharge pipe.

In the above, embodiments having an effect of reducing the amount of oil discharged through the rotating member 200 in the centrifugal separation space have been described. That is, embodiments in which the amount of oil discharge can be reduced by increasing the centrifugal force by adding the rotating member 200 in the centrifugal separation space has been described.

The present inventors have found that the oil discharge amount can be reduced by not only reducing the oil discharge amount by increasing the centrifugal force or expanding the area where the centrifugal force is applied, but also removing the obstruction factor of the centrifugal force. In other words, it was found that the obstruction factor of the centrifugal force was considered in the centrifugal separation space inside the compressor, and the amount of oil discharge can be reduced by effectively solving this.

Hereinafter, embodiments in which the centrifugal force impeding element is effectively improved will be described in detail. The same components are described with the same reference numerals, and redundant descriptions may be omitted.

8 is a top cross-sectional view of a conventional rotary compressor. In the related art, for convenience of manufacture or conventionally, a step 113c was formed on the upper shell 113, and a terminal 300 for power connection was formed on the uppermost portion of the upper shell 113. That is, a terminal was provided on the center upper surface 113a of the upper shell 113. The terminal 300 includes a main body 310 and tabs 311, 312, and 313. Each single-phase tap may be a plus tap, a minus tap, and a ground tap. In the case of three phase, each tap may be a one-phase tap, a two-phase tap, and a three-phase tap.

The tab is connected to the lead wires 314, 315, 316 inside the compressor. That is, the lead wire may extend downward from the tab to be connected to the coil 122a of the stator.

As described above, it has been described that the amount of oil discharge can be reduced by using the upper space or the downstream space inside the compressor as a centrifugal separation space in a compressor of a lower compression or an upstream compression type.

The present inventors have paid attention to the influence of the shape of the upper shell 113 and the position of the terminal 300 as a factor that interferes with centrifugation in the centrifugation space. The upper shell can also be referred to as a top cap.

Oil having a high density by centrifugal force must flow smoothly in a radially outward direction. And this smooth flow must be carried out throughout the centrifugation space. In addition, on the contrary, the refrigerant existing outside the radial direction must flow smoothly in the radial direction inward.

However, in the upper part of the centrifugation space, it was found that flow resistance is generated by the shape of the upper shell 113 and the tab terminal, which may interfere with centrifugation. In addition, it was found that interference of centrifugation may occur in the lead wires 314, 315, and 316 extending downward from the tab terminal 300 and radially outward.

The shape of the upper shell 113 and the position of the tab terminal 300 are not a problem in the conventional compressor of the upper or downstream compression type. This is because the centrifugation space was not formed, so oil separation using the centrifugation space was not applied.

In addition, since the upper shell 113 is formed with an upper central surface 113a, a step 113c and a lower peripheral surface 113b, the discharge pipe and the terminal can be easily installed, so the shape of the upper shell and the installation position of the terminal can be changed. There was no need.

On the other hand, in the case of a rotary or scroll compressor that can apply an upper space or a downstream space as a centrifugal separation space as in the embodiment of the present invention, more effective oil separation can be performed through the removal of such a centrifugal separation obstacle. .

First, an embodiment in which the position of the tab terminal is changed will be described with reference to FIG. 9.

In this embodiment, while applying the conventional step-type upper shell as it is, the position of the terminal 300 is formed on the side of the compressor rather than the top. For example, it may be said that the terminal 300 is formed on the upper portion of the cylindrical shell 111.

In this case, the height difference between the terminal 300 and the stator 122 may be significantly reduced. Further, the lead wires 314, 315, and 316 may extend radially outward from the stator 122 in the radial direction rather than in the radial direction. That is, the length of the lead wire in the centrifugation space may be reduced, and the position of the lead wire may be located at a position lower than the upper and lower centers or the upper and lower centers of the centrifuge space.

Here, the positional relationship of the tabs 311, 312, 313 of the terminal 300 is important. That is, the tabs may have the same or different heights. That is, the main body 310 of the tab terminal may be positioned horizontally or vertically.

Since a certain gap must be formed between the tabs, a certain gap is also formed between the lead wires. Therefore, assuming that flow occurs in the radial direction, when the tab terminal body 310 is positioned horizontally, the flow resistance area is generated even more. That is, a flow resistance area may be formed in all three lead wires. On the other hand, when the tab terminal body 310 is vertically positioned, the flow resistance area is significantly reduced. That is, since the three lead wires overlap in the radial direction, it can be said that a flow resistance area is formed in one lead wire.

Accordingly, flow due to centrifugation may be effectively generated by the position of the terminal 300 shown in FIG. 9, the installation posture of the terminal body 310, and the extension direction of the lead wire. That is, the area of the centrifugal separation can be significantly reduced. Therefore, it can be expected that the oil separation effect by centrifugation will be enhanced.

In the embodiment shown in Fig. 10, in the embodiment shown in Fig. 9, the shape of the upper shell 113 is flat. That is, the upper shell is formed in a flat shape rather than a step-shaped upper shell.

Therefore, since the elements that interfere with centrifugation due to the shape of the upper shell can be remarkably reduced, the oil separation effect can be expected to be enhanced. In particular, the centrifugal separation space can be increased, and a remarkable oil separation effect can be expected due to a decrease in flow resistance due to the continuous surface.

In the embodiment shown in FIG. 11, in the embodiment shown in FIG. 9, the shape of the upper shell 113 is formed in a curved surface. That is, the upper shell 113 is formed to be convex toward the upper or the downstream side. The inner surface of the compressor of the upper shell 113 forms a curved surface, and the curved surface may be formed to be inclined downward toward a radial direction.

Accordingly, smooth flow may occur radially outward along the inner surface of the upper shell 113. That is, the flow resistance can be significantly reduced.

Meanwhile, in order to further reduce the flow resistance along the inner surface of the upper shell 113, the inner surface of the upper shell 113 may have a curvature in multiple stages. That is, it may be formed such that the radius of curvature decreases from the inner side to the outer side in the radial direction.

FIG. 12 compares OCR values in the compressor shown in FIG. 8, in particular the rotary compressor, the compressor shown in FIG. 9, in particular the rotary compressor, the compressor shown in FIG. 10, and the scroll compressor in particular, and the compressor shown in FIG. It's a table. This is a table comparing OCR values under the same operating conditions.

The OCR value in the lower compression type rotary compressor shown in FIG. 8 is relatively large. In particular, it can be said that a separate oil separator or the like is required due to the shape of the upper shell having a multi-section and the position of the terminal.

It can be seen that the OCR value in the lower compression type rotary compressor shown in FIG. 9 decreases to 0.13 due to the position of the terminal. However, it can still be said to be higher than the 0.1 weight percent required.

It can be seen that the OCR value in the lower compression type scroll compressor shown in FIGS. 10 and 11 has a significantly lower 0.02 weight percent than the 0.1 weight percent required due to the position of the terminal and the shape of the upper shell.

It can be seen that the OCR performance in the lower compression type scroll compressor is significantly superior to the lower compression type rotary compressor. In addition, it can be seen that very excellent OCR performance can be exhibited by changing the shape of the upper shell and the terminal.

Meanwhile, the shape of the upper shell can be variously changed. Therefore, it is necessary to examine the generalization and process of the upper shell shape and the change in OCR accordingly.

The upper shell 113 shown in FIG. 9 has two continuous surfaces having a height difference and a stepped surface between the two continuous surfaces. The two continuous surfaces may be planar or curved. In this case, the center of the radius of curvature may be inside the compressor. Of course, the center of the radius of curvature of the stepped surface may be outside the compressor. Therefore, the radius of curvature has a plurality of them along the radial direction.

The upper shell 113 shown in FIG. 10 may be formed substantially in one plane. Thus, the radius of curvature is substantially infinite.

The upper shell 113 shown in FIG. 11 may have one curved surface. However, the radius of curvature may vary along the radial direction.

13 shows the relationship between the curvature of the upper shell 113 and the amount of oil discharged.

When the terminal 300 is provided on the upper shell 113 as in the related art and the heights of the plurality of tabs are the same, it can be seen that the oil discharge amount decreases as the average curvature radius factor of the upper shell increases. The average radius of curvature factor can be said to be a value obtained by dividing the upper shell into a plurality of sections along the radial direction, adding all values obtained by multiplying the radius of curvature and the length of the arc in each section and dividing by the diameter of the centrifugation space. More than one radius of curvature may be provided, and in some cases, may be provided in multiple stages. Therefore, it can be said that this average curvature radius factor is determined.

Here, it can be seen that the oil discharge amount decreases as the average curvature radius factor increases, but it can be reduced only up to 0.05 OCR.

Assuming that the required OCR is 0.1, it can be seen that it is difficult to satisfy the required value for reducing the amount of oil discharge by having a terminal in the upper shell and changing the shape of the upper cell.

On the other hand, by providing the terminal 300 on the side of the cylindrical shell 111, it can be seen that the required OCR can be easily satisfied. It can be seen that when the average radius of curvature factor is more than 0.1 times the diameter of the centrifuge space, the required OCR, 0.1% by weight, can be satisfied.

It can be seen that gradually increasing the mean radius of curvature factor can satisfy up to approximately 0.02 weight percent.

Therefore, it is possible to very effectively improve OCR performance by forming an upper shell in a form that is easy to manufacture and having a terminal in the cylindrical shell. In particular, it is possible to obtain OCR values lower than the required 0.1 weight percent. The lower the OCR value, the better. Therefore, it is possible to implement this without requiring a separate oil separator or the like without a large configuration change of the compressor itself.

In the above, an OCR improvement example (first form) using a rotating member and a guide and an OCR improvement example (second form) according to the shape of the upper shell and the position of the terminal have been described.

Here, each shape does not contradict each other. That is, one form can be implemented in combination with another form. That is, it can be easily predicted that OCR improvement can be further enhanced.

As an example, the case 1 shown in FIG. 7 is an optimal embodiment and an embodiment having an upper shell of a side terminal plane shape shown in FIG. 12 may be implemented in combination. In this case, an OCR lower than 0.01 can be expected. In particular, the OCR improvement effect will be very remarkable in a scroll compressor other than a rotary compressor.

It is very encouraging that the compressor itself can significantly improve OCR at low cost and at only an additional cost. In particular, implementing OCR with less than 0.01 weight percent, which is significantly lower than the required 0.1 weight percent, is a surprising achievement. This means that many problems such as cost of a separate oil separator, installation cost, maintenance cost, heat exchange efficiency decrease, compressor damage due to wear of bearings, etc. can be easily solved.

100: compression unit 110: case
112, 113: upper shell 111: cylindrical shell
120: drive motor 126: rotation shaft
130: main frame 140: orbiting scroll
150: fixed scroll 200: rotating member
210: rotor 220: rotary member flange portion
300: terminal

Claims (19)

A case including a discharge pipe forming a refrigerant inlet hole;
A drive motor including a stator mounted inside the case and a rotor rotatably provided inside the stator in a radial direction;
A centrifugal separation space defined by a downstream side of the driving motor and the case inside the case, in which centrifugal separation of compressed refrigerant and lubricating oil is performed;
A rotating shaft coupled to the rotor and rotating;
A compression unit that is coupled to the rotation shaft on the other side of the driving motor and compresses the refrigerant by the rotation of the rotation shaft;
A rotating member surrounding at least a portion of the discharge pipe and coupled to the rotation shaft or the rotor to provide centrifugal force to the centrifugal separation space; And
Includes; a terminal coupled to the case and connected to the coil of the stator,
The case is
An upper shell through which the discharge pipe passes and facing the stator or the rotor, and a cylindrical shell coupled to an outer circumferential surface of the upper shell to receive the stator and the compression unit and to form the centrifugal separation space together with the upper shell and,
The rotating member includes a flange portion coupled to the rotation shaft or the rotor and provided larger than a diameter of the rotor, and a rotor blade extending from an outer circumferential surface of the flange portion toward the upper shell and facing the cylindrical shell,
The terminal is coupled to the cylindrical shell in a region facing the side of the rotor so that interference with the rotor blade is prevented,
The compressor, characterized in that the distance between the outer peripheral surface of the upper shell and the stator is provided longer than the length of the rotor and the terminal. The method of claim 1,
The terminal is
A plurality of lead wires connected to the coil of the stator; And
And a main body provided with a plurality of tabs to which the lead wires are connected. The method of claim 2,
The plurality of taps are spaced apart from each other, characterized in that the compressor is provided in parallel on the same line. The method of claim 3,
The plurality of taps are arranged in the cylindrical shell along the axial direction of the rotary shaft. The method of claim 4,
The main body of the terminal is provided in the cylindrical shell so that the plurality of tabs are arranged in parallel with the axial direction of the rotation shaft. The method of claim 4,
The lead wire is a compressor, characterized in that extending from the upper portion of the stator to the outer side in the radial direction of the rotation shaft is connected to the tab. The method of claim 6,
The plurality of lead wires are provided so as to overlap each other in a radial direction of the rotation shaft to reduce the flow resistance of the oil. The method of claim 1,
The upper shell is formed with a flat surface, the compressor characterized in that the bent at the radial end to be connected to the cylindrical shell. The method of claim 1,
The upper shell is formed in a curved surface inclined downward radially outward, the compressor, characterized in that connected to the cylindrical shell at a radial end. The method of claim 9,
The curved surface is formed to have a multi-stage radius of curvature, and the radius of curvature decreases toward an outer side in a radial direction. The method of claim 10,
The sum of the values obtained by multiplying each radius of curvature and the length of each arc in the curved surface is defined as one surface of the stator, the rotor, and the rotation shaft facing the upper shell, the inner surface of the upper shell, and the inner surface of the cylindrical shell. Compressor, characterized in that the value divided by the diameter of the centrifugation space is at least 0.1 times the diameter of the centrifugation space. The method of claim 1,
The upper shell has two continuous surfaces having a height difference in a radial direction, and the height of the continuous surface in the radial direction is greater than the height of the continuous surface in the radial direction. The method of claim 12,
The compressor, characterized in that the two continuous surfaces are flat. The method of claim 12,
The compressor, characterized in that the two continuous surfaces are curved surfaces convex upward. The method of claim 14,
And the center of curvature of the two continuous surfaces is located inside the compressor, and the center of curvature of the stepped surface connecting the two continuous surfaces is located outside the compressor. The method of claim 14,
The sum of the values obtained by multiplying the radius of curvature of each of the two continuous surfaces by the length of each arc is calculated as one surface of the stator, the rotor, and the rotation shaft facing the upper shell, the inner surface of the upper shell, and the inner surface of the cylindrical shell. A value divided by the diameter of the centrifugation space defined as is a compressor, characterized in that at least 0.1 times the diameter of the centrifugation space. The method according to any one of claims 1 to 16,
The rotor blade is a compressor, characterized in that provided to be spaced a predetermined distance from the center of the rotor. The method of claim 17,
The compressor, characterized in that the flange portion is provided to rotate integrally with the rotor or rotating shaft. The method of claim 18,
Compressor, characterized in that the upper position of the rotor blade is equal to or higher than the upper position of the terminal.

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