KR102271447B1 - Compressor - Google Patents

Abstract

The present invention relates to a compressor, and more particularly, to a compressor capable of effectively separating a lubricating oil and a compressed refrigerant inside the compressor.
According to an embodiment of the present invention, the case; a driving 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 and 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 to rotate; a compression unit provided on an upsteam side of the driving motor and compressing the refrigerant by the rotation of the rotating shaft; And a compressor including a rotating member provided to extend the rotational force of the rotor into the centrifugal separation space to provide centrifugal force to the refrigerant and oil, and to rotate integrally with the rotor on one side of the rotor can be provided.

Description

Compressor {COMPRESSOR}

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

In general, a compressor is applied to a refrigerant compression type refrigeration cycle (hereinafter, abbreviated as refrigeration cycle) such as a refrigerator or an air conditioner.

The compressor may be classified into a reciprocating compressor and a rotary compressor according to a method of compressing a 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 positions of the driving motor and the compression unit. The upper compression type is a method in which the compression unit is located above the drive motor, and the lower compression type is a method in which the compression unit is located below the drive motor.

That is, the compressor may be differently named according to the relative positions of the driving motor and the compression unit. The compressor may be capable of horizontal rather than vertical mounting. Accordingly, the name of the compressor may be more generalized according to the relative positions of the driving motor and the compression unit. According to the flow direction of the refrigerant and the position of the driving motor in the compressor, the compressor in which the refrigerant is compressed on 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. can In addition, a compressor in which the refrigerant is compressed and the refrigerant is discharged at an upstream side of the driving motor may be referred to as a downstream compressor.

In the case of the upper compression type compressor (downstream compressor), there is a high possibility that the refrigerant is compressed and discharged from the compression unit located above the drive motor, and then the lubricating oil is discharged together with the refrigerant. That is, the lubricating oil is mixed with the discharged refrigerant. Lubricating oil mixed with the refrigerant lowers the cooling efficiency and causes a shortage of lubricating oil inside the compressor. Accordingly, in the case of the upper compression type compressor, it is common to periodically need to recover the lubricating oil or to be equipped with a separate oil recovery device or oil separation device.

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

A rotational flow may be generated in the discharge space by the rotor and the rotation shaft of the 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 the lubricating oil may be generated by this rotational flow.

The density of the lubricating oil is significantly greater than that of the refrigerant. Therefore, the lubricating oil may be driven in the opposite direction to the discharge space by centrifugation and the refrigerant may be discharged to the outside of the compressor by being driven toward the center of the discharge space.

Accordingly, it can be said that the oil discharge amount of the lower compression type compressor is significantly smaller than that of the upper compression type compressor. However, the amount of oil discharged from the lower compression compressor is not negligible, and therefore, a separate oil recovery device or oil separator is generally installed. Therefore, it is necessary to find a way to significantly reduce the oil discharge amount to the extent that a separate oil recovery device or oil separation device can be omitted from the lower compression compressor.

An object of the present embodiment is to provide a compressor capable of remarkably reducing an oil discharge amount.

An object of this embodiment is to provide a compressor capable of effectively using a refrigerant discharge space as a centrifugal separation space. In particular, it is an object of the present invention to provide a compressor capable of using substantially the entire space as a centrifugal separation space instead of a part of the refrigerant exposure space.

Through this embodiment, an object of the present invention is to provide a compressor capable of remarkably reducing the oil discharge amount through only a very small change in the configuration of the existing compressor.

An object of the present embodiment is to provide a compressor capable of remarkably reducing the oil discharge amount by effectively removing elements that prevent flow due to centrifugation in the centrifugal separation space.

An object of the present embodiment is to provide a compressor capable of remarkably reducing the oil discharge amount by reducing the flow resistance according to the shape of the upper shell.

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

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

In order to implement the above object, according to an embodiment of the present invention, a case; a driving 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 and 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 to rotate; a compression unit provided on an upsteam side of the driving motor and compressing the refrigerant by the rotation of the rotating shaft; And a compressor including a rotating member provided to extend the rotational force of the rotor into the centrifugal separation space to provide centrifugal force to the refrigerant and oil, and to rotate integrally with the rotor on one side of the rotor (downstream side) may be provided.

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

The maximum outer diameter of the rotor blade may be the same as or smaller than the outer diameter of the rotor. In addition, the maximum outer diameter of the rotor blade may be the same as 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.

The minimum inner diameter of the rotor blade is preferably larger than the outer diameter of the discharge tube to surround the discharge tube.

The rotor blade may be provided to have a predetermined height in the rotor to define an internal space of the rotating member in the centrifugal separation space.

The rotor blade may be formed to have a constant height or to be symmetrically formed in a circumferential direction with a different height along the circumferential direction.

The distal end of the discharge pipe is preferably provided to further extend into the inner space of the rotating member.

The free linear distance (T) through which the compressed refrigerant can be introduced into the refrigerant inlet hole of the discharge pipe in the inner space of the rotating member is 0.1 times greater than the linear distance (d) between the upper end of the circumferential wall and the inner surface of the case A large one is preferable.

The height of the rotor blade is preferably formed to have or be greater than the height of the end coil wound on the stator.

Preferably, 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 the refrigerant and oil flowing into the centrifugal separation space through the gap from directly flowing into the inner space of the rotating member. That is, it is preferable that the refrigerant bypasses the radial direction of the rotor blade of the rotating member and flows 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 separation space through the gap are not affected by the flange but are driven radially outward under the influence of the rotor.

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 separation space through the gap are driven outward in the radial direction under the influence of the flange part and the rotor blade. Since the separation distance between the flange portion and the gap is sufficient, the time for receiving the centrifugal force may be increased.

Preferably, the flange portion and the rotor blade are integrally formed.

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

The guide preferably has a skirt shape extending in a radial direction from the outer surface of the discharge pipe.

The uppermost position of the guide is preferably the same as or higher than the uppermost position of the rotor blade.

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

Preferably, the maximum outer diameter of the guide is smaller than the minimum inner diameter of the rotor blade.

Preferably, the guide is provided inside the inner space of the rotary member defined by the rotary blade, and the distal end of the discharge pipe is provided to further extend into the inner space of the rotary member.

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

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

The compressor may include a terminal provided on a side surface of the centrifugal separation space and a side surface of the case, 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 capable of remarkably reducing the oil discharge amount.

Through this embodiment, it is possible to provide a compressor capable of effectively using the 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 a part of the refrigerant exposure space, as the centrifugal separation space.

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

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

Through the present embodiment, it is possible to provide a compressor capable of significantly reducing the oil discharge amount 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 oil discharge amount by providing a terminal provided in the upper shell to the cylindrical shell, which 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, significantly lower than 0.1 weight percent of the required oil discharge amount, by simultaneously expanding the centrifugal space and removing the resistance element of the centrifugal flow. .

1 is a cross-sectional view of a compressor applicable to the present invention, particularly a lower (upstream) 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 separation 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 of embodiments of the first form 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 the 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 components.

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 illustrates a cross-section of a scroll compressor that can be applied to an embodiment of the present invention. Since the compression unit is located below 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. An upstream/downstream position 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 driving motor 120 , a compression unit 100 , and a rotation shaft 126 .

The case 110 may be formed to have an internal space. For example, an oil storage space in which oil is stored may be provided at a lower portion of the case 110 . The oil storage space may mean a fourth space V4 to be described later. That is, a fourth space V4 to be described later may be formed as the oil 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 includes a first space V1 disposed above the driving motor 110 and a second space V2 disposed between the driving 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 below 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 having an open top and bottom.

An upper shell 112 may be installed on an upper portion of the cylindrical shell 111 , and a lower shell 114 may be installed on a lower portion of 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 sequentially passes through the third space V3, the second space V2, and the first space V1, and then passes through the refrigerant discharge pipe 116. It can be discharged to the outside.

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

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

In addition, a refrigerant suction pipe 118 that is a passage through which the 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 penetrate to the compression chamber S1 along the side surface of the fixed scroll 150 , which will be described later.

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

The driving motor 120 may include a stator 122 and a rotor 124 . The stator 122 may be, for example, cylindrical, and may be fixed to the case 110 . A coil 122a may be wound around the stator 122 . In addition, between the outer peripheral surface of the rotor 124 and the inner peripheral surface of the stator 122, a refrigerant passage groove 112a may be formed 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 circumferential surface of the stator 122 and an outer circumferential surface of the rotor 124 .

The rotor 124 is disposed inside the radial direction of the stator 122, and may generate rotational power. That is, the rotor 124 may rotate with the rotation shaft 126 by press-fitting the rotation shaft 126 in 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 part 100 may be formed so that the rotation shaft 126 connected to the driving motor 120 passes therethrough.

The compression unit 100 may include a bearing portion protruding upward and downward, and the rotating shaft 126 may pass through at least a portion of the bearing portion. For example, the bearing unit may include a first bearing unit protruding upwardly from the compression unit 100 and a second bearing unit projecting downwardly, and a detailed description thereof will be provided 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 the orbiting scroll 140 to rotate while preventing the orbiting scroll 140 from rotating on the fixed scroll 150 .

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

The main frame 130 has a frame end plate part (hereinafter, referred to as a 'first end plate part') 132 having a substantially circular shape, and the number of frame shafts provided at the center of the first end plate part 132 and through which the rotation shaft 126 passes. part (hereinafter, referred to as a 'first bearing part') 132a, and a frame sidewall part (hereinafter, referred to as a 'first sidewall part') protruding downward from the outer periphery of the first end plate 132 (hereinafter referred to as a 'first sidewall part') 131 ) may be provided.

The first sidewall portion 131 may have an outer peripheral portion in contact with an inner peripheral surface of the cylindrical shell 111 , and a lower end portion in contact with an upper portion of a fixed scroll sidewall portion 155 , which will be described later.

The first sidewall part 131 may be provided with a frame discharge hole 131a penetrating the inside of the first sidewall part 131 in the axial direction to form a refrigerant passage. The frame discharge hole 131a may have an entrance that communicates with an exit of a fixed scroll discharge hole 155a, which will be described later, and an exit that communicates with the second space V2. The frame discharge hole 131a and the fixed scroll discharge hole 155a communicating with each other may be referred to as second discharge holes 131a and 155a.

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

The first bearing part 132a may be formed to protrude from the upper surface of the first head plate part 132 toward the driving motor 120 . In addition, a first bearing part may be formed in the first bearing part 132a so that the main bearing part 126c of the rotation shaft 126 to be described later is supported therethrough.

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

An oil pocket 132b for collecting oil discharged between the first bearing part 132a and the rotation shaft 126 may be formed on an upper surface of the first end plate part 132 .

The oil pocket 132b may be concavely formed on the upper surface of the first end plate 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 on the bottom surface of the main frame 130 to support the orbiting scroll 140 by the pressure of the space by forming a space together with the fixed scroll 150 and the orbiting scroll 140 . have.

For reference, the back pressure chamber S2 may include an intermediate pressure region (ie, an intermediate pressure chamber), and the oil supply passage 126a provided in the rotation shaft 126 has a high pressure region having a higher pressure than that of the back pressure chamber S2 . may include

A back pressure seal 180 may be provided between the main frame 130 and the orbiting scroll 140 to separate the high pressure region and the intermediate 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 so as to be pivotable.

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 surface of the main frame 130 .

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

The compression unit 100 is spaced apart from the first discharge hole 153 for discharging the compressed refrigerant to the discharge cover 170 and the first discharge hole 153 in the radial direction outward of the compression unit 100 and compressed. The above-described second discharge holes 131a and 155a for guiding the cooled refrigerant toward the refrigerant discharge pipe 116 may be provided.

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 end plate 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 lower surface of the fixed scroll 150, a discharge cover for guiding the refrigerant discharged from the compression unit to the fixed scroll discharge hole 155a, which will be described later. 170) may be combined.

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

For example, the discharge cover 170 may be sealingly coupled to the bottom surface of the fixed scroll 150 to separate the refrigerant discharge passage from the fourth space V4.

In addition, the discharge cover 170 has an oil feeder 171 that is coupled to the sub-bearing part 126g of the rotary shaft 126 constituting the second bearing part and is at least partially submerged in the oil accommodated in the fourth space V4 of the case 110 . ) may be formed with a through hole 176 to pass through.

On the other hand, the second sidewall part 155 may be provided with a fixed scroll discharge hole 155a that passes through the inside of the second sidewall part 155 in the axial direction and forms a refrigerant passage together with the frame discharge hole 131a. .

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

The fixed scroll discharge hole 155a and the frame discharge hole 131a are formed in the 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 may be communicated.

In addition, the 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 . Also, the refrigerant suction pipe 118 may be installed to be spaced apart from the fixed scroll discharge hole 155a.

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

In addition, the lower end of the second bearing unit 152 may be bent toward the center of the axis so that the lower end supports the lower end of the sub bearing unit 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 two pairs of compression chambers S1 between the fixed scroll 150 and the fixed scroll 150 while rotating.

The orbiting scroll 140 has an orbiting scroll end plate part (hereinafter, referred to as a 'third end plate part') 145 having a substantially circular shape, protruding from the lower surface of the third head plate part 145 and engaging the fixing wrap 151 . It is provided at the center of the orbital wrap 141 and the third end plate 145 and may include a rotation shaft coupling portion 142 rotatably coupled to the eccentric portion 126f of the rotation shaft 126 .

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

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

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

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

The outer periphery of the rotating shaft coupling part 142 is connected to the orbital wrap 141 and serves to form the compression chamber S1 together with the fixed wrap 151 in the compression process.

The fixed wrap 151 and the orbit wrap 141 may be formed in an involute shape. The involute shape may mean a curve corresponding to a trajectory drawn by the end of the thread when the thread wound around the base circle having an arbitrary radius is unwound.

Also, 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 orbital wrap 141 or the fixed wrap 151 in the radial direction of the compressor.

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

As described above, when the eccentric portion 126f of the rotation shaft 126 passes through the third head plate portion 145 and overlaps with the orbital wrap 141 in the radial direction, the repulsive force and compressive force of the refrigerant are applied to the third head plate portion 145 . ) as a reference, they may be partially offset from each other while being applied to the same plane.

In addition, the rotating 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 that is the oil storage space of the case 110 upward.

Specifically, the upper portion of the rotation shaft 126 may be press-fitted to the center of the rotor 124 and coupled, and the lower portion thereof may be coupled to the compression unit 100 to be radially supported.

The rotating 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 pivot with respect to the fixed scroll 150 .

A main bearing portion 126c may be formed at a lower portion of the rotation shaft 126 to be inserted into the first bearing portion 132a of the main frame 130 to be radially supported. Also, a sub bearing part 126g may be formed at a lower portion of the main bearing part 126c to be inserted into the second bearing part 152 of the fixed scroll 150 to be radially supported. 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 portion 126c and the sub-bearing portion 126g are formed on a coaxial line to have the same axial center, and the eccentric portion 126f is radial with respect to the main bearing portion 126c or the sub-bearing portion 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 for the rotation shaft 126 to pass through each of the bearing parts 132a and 152 and the rotation shaft coupling part 142 to couple.

And inside the rotation shaft 126, an oil supply flow path 126a for supplying the oil of the fourth space V4, which is a storage space, to the outer peripheral surfaces of the bearing parts 126c and 126g and the outer peripheral surfaces of the eccentric parts 126f is formed. can be In addition, oil holes 128a, 128b, 128d, and 128e that penetrate radially outward of the rotary shaft 126 in the oil supply passage 126a are formed in the bearing portions and the eccentric portions 126c, 126g, and 126f of the rotary shaft 126. 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 passage 126a to the outer circumferential surface of the main bearing part 126c.

Also, the first oil hole 128a may be formed to pass through, for example, an upper portion of an outer circumferential surface of the main bearing part 126c, but is not limited thereto. When the first oil hole 128a includes a plurality of holes, each hole may be formed only on the upper or lower part of the outer peripheral surface of the main bearing part 126c, and may be formed on the upper and lower parts of the outer peripheral surface of the main bearing part 126c. Each may be formed.

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

The third oil hole 128d may be formed to pass through the outer circumferential 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 circumferential 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 entirely supplied to the outer circumferential surface of the main bearing part 126c.

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

In addition, the oil guided upward through the oil supply passage 126a is discharged through the fourth oil hole 128e and is disposed between the outer peripheral surface of the sub bearing part 126g or the orbiting scroll 140 and the fixed scroll 150 . can be supplied.

An oil feeder 171 for pumping 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 the 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 that is inserted into and coupled to the oil supply passage 126a of the rotary shaft 126, and an oil suction member 174 that is inserted into the oil supply pipe 173 to suck oil. can be done

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

Oil suction member 174 may be provided with a spiral groove (174a) extending along the longitudinal direction of the oil suction member (174). The spiral groove 174a may be formed on the periphery of the oil suction member 174, and may extend toward the oil holes 128a, 128b, 128d, and 128e described above.

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 rotating 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 rotation 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 rotation shaft 126 performs a pivoting motion with respect to the fixed scroll 150 . The compression chamber S1 may be continuously formed in several stages while gradually decreasing in volume in the central direction.

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 is discharged through the refrigerant discharge pipe 116 . Through a series of processes 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 rotating shaft 126 and smoothly on the bearing portion, that is, the bearing surface through the plurality of oil holes 128a, 128b, 128d, and 128e. Abrasion of the bearing part can be prevented by supplying it properly.

In addition, the 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 the oil, the refrigerant compressed by the compression unit 100 and discharged to the first discharge hole 153 may contain oil. Hereinafter, for convenience of description, 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 via the second discharge holes 131a and 155a, the second space V2, and the refrigerant passage groove 112a. And, among the oil mixed refrigerant guided to the first space V1, the refrigerant may be discharged to the outside of the compressor through the refrigerant discharge pipe 116, and the oil may be discharged to the fourth space V4 through the oil return passage 112b. can be recovered as

For example, the oil return passage 112b may be disposed radially outward in the case 110 . Specifically, the oil return flow path 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 circumferential surface of 150 and the inner circumferential surface of the cylindrical shell 111 .

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

That is, when the refrigerant is discharged to 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 portion of the refrigerant is transferred to the compression unit 100 ) and the discharge cover 170 may leak into a gap that may exist.

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

The present embodiment may provide a compressor further including a rotating member 200 in the compressor shown in FIG. 1 . That is, the compressor in which the rotating member 200 is installed for centrifugal separation to occur more effectively in the first space V1 may be provided. Accordingly, the first space V1 may be a centrifugal separation space in which the refrigerant and oil are centrifuged by the rotating member 200 .

An example of the compressor provided with the 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 upper or downstream side of the case 110 and one side of the driving motor is formed. The refrigerant and lubricating oil compressed in the compression unit are introduced 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 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 , particularly 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 rotating shaft 126 rotate integrally.

Since the upper end surfaces of the rotor 124 and the rotating shaft 126 define the centrifugal separation space V1, the lower surface of the centrifugal separation space or the central portion of the lower region prevents the rotation of the rotor 124 and the rotating shaft 126 from each other. centrifugal force is generated. However, this centrifugal force is difficult to extend to the entire centrifugation space. That is, it is difficult to extend the centrifugal force to the upper shell 112 .

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

The rotating member 200 may be provided to be fixed to the upper side (downstream side) of the rotor 124 and/or the rotating shaft 126 , and may be provided to rotate integrally with the rotor 124 and the rotating shaft 126 . The rotating member 200 may be formed to extend upwardly (downstream) from the rotor 124 and/or the rotating 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 rotation member 200 may include a rotor blade 210 positioned in the centrifugal separation space and spaced apart from the center of the rotor 124 with a predetermined radius.

The rotor blade 210 is formed to have a predetermined height. Accordingly, as the rotor blade 21 rotates, the inner space V12 of the rotation 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 external space V11 of the rotating member and an internal space V12 of the rotating member.

The rotor blade 210 is preferably 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 blades.

The rotor blade 210 may have a constant 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 the rotating member 200 in a simple shape and to easily fix it, the rotating member 200 may include a flange part 220 . The flange part 220 may be fixed to the rotor 124 or the rotation shaft 126 . The flange 220 may be fixed through studs, bolts, or screw coupling.

The rotor blade may be formed to protrude from the flange portion to have a height. That is, the rotor blades protrude upward from the circumference of the flange portion so that the rotation member 200 may have a cup shape. The flange portion 220 is preferably in the form of a flat plate. Accordingly, the rotating member 200 may be referred to as a rotating cup.

The rotary member 200 can be easily manufactured by integrally forming the flange 220 and the rotary blade 210 .

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

The distal end 116a of the discharge pipe 116 is preferably 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 the inner space (V12) and the outer space (V11) of the rotating member, the high-density oil is driven radially outward and the low-density refrigerant is radially Because it's going inward. And the discharge pipe 116 is because the relatively high pressure compressor inner space and the relatively low pressure compressor outer space to communicate. Therefore, the position of the end 116a of the discharge pipe 116 is preferably such that it further extends downward from the center of the centrifugation space. Through this, it is possible to overcome the centrifugal force and effectively prevent the 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 .

If the height of the centrifugation space is H, H is the sum of h2, which is the height of the rotor, and h1, which is the distance between the upper end of the rotor and the upper shell. In addition, the inner diameter of the discharge pipe may be referred to as d1, the outer diameter of the discharge tube as d2, and the diameter of the centrifugal separation 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 specification 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 this change is not preferable because it requires a change in the overall structure and size of the pre-designed compressor.

Therefore, it will be preferable 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 discharge pipe end 116a except for other values. .

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

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

Meanwhile, as T decreases, the area through which the refrigerant flows through the refrigerant inlet hole 116b of the discharge pipe becomes smaller. Therefore, the flow resistance increases. Therefore, T can be determined to be greater than 0.25 times d2. As T increases, the refrigerant inlet hole 116b of the discharge pipe becomes closer to the outer space of the rotating member. Therefore, the possibility that oil flows into the discharge pipe increases. Taking this into consideration, T may be determined to be equal to or smaller than d1.

On the other hand, the rotating member means an additional load of the driving motor. Therefore, the thickness of the rotating member 200 is preferably thin. However, the thickness of the rotary member 200, particularly the rotor blade 210, will preferably have a thickness having a degree of rigidity that is not vulnerable to deformation.

FIG. 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 pipe through the discharge pipe, and the oil indicated in dark color flows in the centrifugation space and rushes to the bottom of the centrifugal separation space.

However, as can be seen from this flow analysis, oil toward the discharge pipe can be seen near the outer wall 116c of the discharge pipe 116 end 116c. Oil can flow to the vicinity of the end of the discharge pipe with an angle of about 80 degrees (about an angle of about 10 degrees with respect to the outer wall of the discharge pipe). There is a possibility that a small amount of oil may be discharged into the discharge pipe by such oil flow.

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

It is possible to prevent the lubricating oil from flowing downward through the guide 230 along the outer wall 116c of the discharge pipe 116 and from 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 the shape of a skirt extending in a radial direction from the outer wall of the discharge pipe.

The guide 230 may have a plate shape through which the discharge pipe 116 passes at a central 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 be introduced into the inner space V12 of the rotating member through the annular space. However, as described above, since the high-density oil is driven outward in the radial direction, substantially only the refrigerant may be introduced into the inner space V12 through the annular space. And, the flow of oil toward the outer wall of the discharge pipe 116 is blocked by the guide 230 to flow outward in the radial direction. The flow of the oil outside in the radial direction is influenced by the rotational force of the rotating member 200 to scatter upward and then is driven radially outward.

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 higher or lower than 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 an upper side than the upper end of the rotating member, the position of the upper surface of the guide 230 is the upper end position of the rotating blade 210 and It would be desirable to be located on the same or above.

Meanwhile, the guide 230 may be formed to have an umbrella shape. That is, it may be formed to be inclined downward from the radial center toward the outside. In this case, the center of the guide 230 may be located on the upper side with respect to the discharge pipe. However, the position of the radial end may be the same as or slightly above the radial end position shown in FIG. 4, preferably the maximum radius is the same.

The difference between the area formed by the outer diameter of the guide and the area formed by the inner diameter of the rotating member may be an area in which the refrigerant flows into the rotating member. Therefore, the size of the area is preferably 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 is located above the guide in the above-described embodiment and has a larger maximum radius. That is, it can be said that the guide having an outer diameter greater 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 in advance, effectively blocking the flow of oil into the inner space of the rotating member. Accordingly, it can be sufficiently expected that the oil discharge amount is reduced than in 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 portion 252 blocks the flow of oil toward the outer wall of the discharge pipe 116 in advance, effectively blocking the inflow of oil into the inner space of the rotating member. In addition, oil scattered in the radial direction from the horizontal portion 251 is blocked by the vertical portion 252, so it is not easy to flow into the inner space of the rotating member. Accordingly, it can be sufficiently expected that the oil discharge amount is reduced than in 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 an oil discharge amount (OCR, Oil Content Rate). The oil discharge amount may be expressed as a ratio of the weight percent of the oil to the total weight percent of the refrigerant and the 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, 0.02 OCR result can be obtained under the same driving condition of the compressor (for example, 120 Hz). This is a very effective oil separation result, and it can be said that it is a level of oil separation that does not require an oil separator or an oil recovery machine.

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

In the case of cases 3 and 4, it can be seen that the oil separation result is better than 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 , and 250 .

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

This is due to the fact that 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 flow resistance occurs up to the discharge pipe 116, the refrigerant flows and some oil flows together. it can be seen that

Therefore, the area of the flow path of the refrigerant into the inner space of the rotating member 200, that is, the number of bending of the flow path formed between the rotor blade 210 of the rotating member 210 and the guides 230, 240, 250 is preferably as small as possible. can do.

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

As the area of the flow path becomes narrower, the discharge of the refrigerant does not occur smoothly, which may cause an increase in the discharge amount of oil. Therefore, it is preferable that the cross-sectional area of the flow path between the rotating member and the guide be larger than the area by the inner diameter of the discharge pipe.

In the above, embodiments having the effect of reducing the oil discharge amount through the rotating member 200 in the centrifugal separation space have been described. That is, by adding the rotating member 200 in the centrifugal separation space, the centrifugal force is enhanced to reduce the oil discharge amount has been described.

The present inventors have found that the oil discharge amount can be reduced by increasing the centrifugal force or expanding the area affected by the centrifugal force, as well as reducing the oil discharge amount by removing the elements that interfere with the centrifugal force. In other words, it was found that the oil discharge amount could be reduced by considering the factors that interfere with the centrifugal force in the centrifugal separation space inside the compressor and effectively solving them.

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

8 shows an upper cross-section of a conventional rotary compressor. Conventionally, a step 113c is formed on the upper shell 113 for convenience or customary in manufacturing, and a terminal 300 for power connection is formed on the uppermost portion of the upper shell 113 . That is, a terminal is provided on the center upper surface 113a of the upper shell 113 . The terminal 300 includes a body 310 and tabs 311 , 312 , and 313 . Each tap being single-phase can be a plus tap, a minus tap and a ground tap. In the case of three phases, 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 , and 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 oil discharge amount can be reduced by using the upper space or the downstream space inside the compressor as the centrifugal separation space in the lower compression or upstream compression type compressor.

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

Due to centrifugal force, oil with high density should flow smoothly in the radial outward direction. And this smooth flow should be performed throughout the centrifugation space. In addition, on the contrary, the refrigerant existing outside the radial direction should flow smoothly in the radial direction.

However, it was found that flow resistance was generated in the upper part of the centrifugation space due to the shape of the upper shell 113 and the tap terminal, thereby preventing centrifugation. In addition, it was found that the centrifugation may be disturbed even in the lead wires 314 , 315 , and 316 extending downward and radially outward from the tap terminal 300 .

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

In addition, since the upper shell 113 is formed with the upper central surface 113a, the step 113c, and the lower peripheral surface 113b, it is easy to install the discharge pipe and the terminal, so that 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 in which the upper space or the downstream space can be applied as a centrifugal separation space as in the embodiment of the present invention, more effective oil separation can be performed by removing such a centrifugation impeding element. .

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

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

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

Here, the positional relationship of the tabs 311 , 312 , and 313 of the terminal 300 is important. That is, the tabs may have the same height or different heights. That is, the main body 310 of the tap 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 the flow occurs in the radial direction, when the tap terminal body 310 is horizontally positioned, the flow resistance area is larger. That is, a flow resistance area may be formed in all three lead wires. On the other hand, when the tap 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.

Therefore, the flow by centrifugation can 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 interference area of centrifugation can be significantly reduced. Therefore, it can be expected that the oil separation effect by centrifugation will be enhanced.

The embodiment shown in FIG. 10 is different from the embodiment shown in FIG. 9 in that the shape of the upper shell 113 is flattened. That is, the upper shell is formed in a flat shape rather than in a step shape.

Accordingly, since the element that interferes with centrifugation due to the shape of the upper shell can be significantly reduced, the oil separation effect can be expected to be enhanced. In particular, the centrifugation space can be increased and a significant oil separation effect can be expected due to the reduction of flow resistance due to the continuous surface.

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

Accordingly, smooth flow may be generated 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 multi-stage curvature. That is, the radius of curvature may decrease from the inner side to the outer side in the radial direction.

12 is a comparison of OCR values in the compressor shown in FIG. 8, particularly the rotary compressor, the compressor shown in FIG. 9, particularly the rotary compressor, the compressor shown in FIG. 10, particularly the scroll compressor, and the compressor shown in FIG. 11, in particular the scroll compressor; It is a table. All are tables comparing OCR values under the same operating conditions.

The OCR value in the lower compression type rotary compressor shown in FIG. 8 is relatively very large. In particular, it can be said that a separate oil separator 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 of the lower compression type rotary compressor shown in FIG. 9 is reduced to 0.13 due to the position of the terminal. However, it can still be said to be higher than the required 0.1 weight percent.

It can be seen that the OCR value in the lower compression type scroll compressor shown in FIGS. 10 and 11 has 0.02 weight percent, which is significantly lower 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 of the lower compression type scroll compressor is significantly better than that of 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 may be variously changed. Therefore, it is necessary to examine the generalization and process of the shape of the upper shell and the change of 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 consecutive surfaces may be flat or curved. And 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 step surface may be outside the compressor. Accordingly, the radius of curvature has a plurality along the radial direction.

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

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 oil discharge amount.

When the terminal 300 is provided on the upper shell 113 as in the prior 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 radius of curvature factor of the upper shell increases. The average radius of curvature factor is a value obtained by dividing the upper shell into a plurality of sections along the radial direction, adding all the values obtained by multiplying the radius of curvature in each section by the length of the arc, and dividing by the diameter of the centrifugation space. One or more radii of curvature may be provided, and in some cases, may be provided in multiple stages. Therefore, it can be said that such an average radius of curvature factor is determined.

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

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

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

It can be seen that by gradually increasing the average radius of curvature factor, up to about 0.02 weight percent can be satisfied.

Therefore, it is possible to very effectively enhance OCR performance by forming the upper shell of a shape that is easy to manufacture and having terminals 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 and without a large configuration change of the compressor itself.

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

Here, the respective forms do not contradict each other. That is, any one form may be implemented in combination with another form. That is, it can be easily predicted that the OCR improvement can be further enhanced.

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

It is very encouraging that the compressor itself can significantly improve OCR at an additional cost at a low cost. In particular, it can be called a surprising achievement to implement OCR with less than 0.01 weight percent, which is significantly lower than the required 0.1 weight percent. This means that very many problems such as cost of a separate oil separator, installation cost, management cost, heat exchange efficiency decrease, and 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 blade 220: rotation member flange portion
300 : terminal

Claims (17)

a case including a discharge pipe for discharging refrigerant on one side and a space for storing oil on the other side;
a driving motor coupled to the inner circumferential surface of the case and including a stator for generating a rotating magnetic field and a rotor accommodated in the stator to rotate by the rotating magnetic field;
a rotating shaft coupled to the rotor to rotate;
a compression unit located farther from the discharge pipe than the rotor, coupled to the rotation shaft and provided to be lubricated with the oil, and compressing the refrigerant;
a rotating member coupled to the rotating shaft to separate the oil from the refrigerant guided to the discharge pipe; and
A balance weight coupled to the rotor and positioned between the rotating member and the rotor, the balance weight reducing noise and vibration of the compression unit and the rotating shaft;
The rotating member is
a flange portion coupled to the rotation shaft, provided in a flat shape and positioned closer to one side of the case than the balance weight;
a coupling part for fixing the flange part to the rotation shaft; and
a rotary blade extending from the periphery of the flange portion toward the discharge pipe; and
The discharge pipe faces the flange portion and includes a refrigerant inlet hole through which the refrigerant flows;
the case is
an upper shell including one surface through which the discharge pipe passes and facing the stator and an outer peripheral surface extending from the one surface toward the stator; and
and a cylindrical shell coupled to one end of the outer circumferential surface and accommodating the stator and the compression part;
The rotation shaft protrudes more toward the coolant inlet hole than the rotor, and the rotor blade has an end closer to the one surface than the coolant inlet hole, and the coolant inlet hole is closer to the one surface than the one end of the outer peripheral surface. is located,
A length (h2) extending from the flange portion of the rotor blade is greater than a distance (h1) from the one surface of the upper shell to the end of the rotor blade. According to claim 1,
The rotor blade
Compressor, characterized in that the diameter is provided larger than the diameter of the rotor, the outer peripheral surface is located closer to the cylindrical shell than the outer peripheral surface of the balance weight. 3. The method of claim 2,
The distance (T) between the flange part and the refrigerant inlet hole is greater than 0.1 times the distance (h1) between the one surface of the upper shell and the end of the rotor blade. 3. The method of claim 2,
The rotor blade is provided in a cylindrical shape and is provided in parallel with the cylindrical shell. delete 5. The method of claim 4,
A distance (h1) from the one surface of the upper shell to the end of the rotor blade is the same as or greater than the outer diameter of the discharge pipe. According to claim 1,
The compressor, characterized in that the flange portion and the rotor blades are integrally formed. According to claim 1,
and a guide provided to surround the discharge pipe to prevent the oil from flowing into the refrigerant inlet hole. 9. The method of claim 8,
The guide is a compressor, characterized in that provided in the shape of a skirt extending in the radial direction of the discharge pipe. 9. The method of claim 8,
The guide is positioned so that the distance from the end of the rotor blade and the flange portion is the same. 9. The method of claim 8,
The guide is provided in the shape of a circular plate through which the center is penetrated, and the compressor is inserted into and coupled to the discharge pipe. 12. The method of claim 11,
Compressor, characterized in that the outer diameter of the guide is provided to be smaller than the inner diameter of the rotor. 13. The method of claim 12,
The compressor, characterized in that the cross-sectional area of the space formed between the inner peripheral surface of the rotor and the outer peripheral surface of the guide into which the refrigerant is introduced is larger than the cross-sectional area of the refrigerant inlet hole. According to claim 1,
It is provided on the cylindrical shell and further includes a terminal connected to the stator,
The terminal is a compressor, characterized in that coupled to the cylindrical shell so as to face the outer peripheral surface of the rotor. 15. The method of claim 14,
The compressor, characterized in that the one surface of the upper shell is provided in a flat shape. 15. The method of claim 14,
The compressor, characterized in that the one surface of the upper shell is provided with a curved surface to prevent the formation of a step. According to claim 1,
the compression unit
an orbiting scroll coupled to the rotating shaft and provided to perform an orbital motion when the rotating shaft rotates;
a fixed scroll provided in engagement with the orbiting scroll to receive the refrigerant and compress and discharge the refrigerant; and
and a main frame seated on the fixed scroll to accommodate the orbiting scroll and through which the rotating shaft passes;
and a discharge cover coupled to the fixed scroll and guiding the refrigerant discharged from the fixed scroll to the discharge pipe.

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