WO2018199488A1

WO2018199488A1 - Scroll compressor

Info

Publication number: WO2018199488A1
Application number: PCT/KR2018/003816
Authority: WO
Inventors: 최용규; 최중선; 김철환
Original assignee: 엘지전자 주식회사
Priority date: 2017-04-24
Filing date: 2018-03-30
Publication date: 2018-11-01
Also published as: CN110582643B; KR20180119054A; KR102318124B1; CN110582643A

Abstract

According to the present invention, a scroll compressor comprises: a first scroll including a first end plate part having a shaft receiving hole, through which a rotary shaft passes, formed in the center portion thereof, and having a discharge port formed around the shaft receiving hole, and a first wrap formed to protrude from one surface of the first end plate part; and a second scroll including a second end plate part having a rotary shaft coupling part formed in the center portion thereof such that the rotary shaft passing through the shaft receiving hole of the first scroll is eccentrically coupled thereto, and a second wrap formed to protrude from one surface of the second end plate part, and engaging with the first wrap so as to form a compression chamber with the same, wherein the first wrap is formed such that a limit range of a stiffness modulus, which is defined as a reciprocal obtained by dividing a wrap height by a wrap thickness and multiplying the value by a curvature radius of the first wrap, is 0.005 mm or more so as to restrain the wraps from deforming, thereby preventing friction loss and wear and enabling the breakage of the wraps to be prevented.

Description

Scroll compressor

The present invention relates to a scroll compressor, and more particularly to a compressor in which the compression unit is located on one side of the electric drive.

A scroll compressor is a compressor which engages a plurality of scrolls and makes a relative rotational movement and forms a compression chamber consisting of a suction chamber, an intermediate pressure chamber, and a discharge chamber between both scrolls. Such a scroll compressor has a relatively high compression ratio compared to other types of compressors, and smoothly sucks, compresses, and discharges the refrigerant, thereby obtaining stable torque. Therefore, scroll compressors are widely used for refrigerant compression in air conditioners and the like. Recently, high-efficiency scroll compressors with an operating speed of 180 Hz or higher due to eccentric loads have been introduced.

The scroll compressor may be classified into a low pressure type in which a suction pipe communicates with an inner space of a casing forming a low pressure part, and a high pressure type in which a suction pipe directly communicates with a compression chamber. Accordingly, the low pressure type is installed in the suction space in which the drive portion is the low pressure portion, while the high pressure type is installed in the discharge space in which the drive portion is the high pressure portion.

Such a scroll compressor may be classified into an upper compression type and a lower compression type according to the position of the driving unit and the compression unit. If the compression unit is located above the driving unit, the upper compression type is used.

In a scroll compressor, the rotating scroll is subjected to gas force in a direction away from the fixed scroll as the pressure in the compression chamber increases. Then, as the turning scroll is separated from the fixed scroll, leakage between the compression chambers is generated and the compression loss is increased.

In view of this, the scroll compressor adopts a tip seal method for inserting a sealing member into the front end faces of the fixed wrap and the swing wrap, or forms a back pressure chamber that forms an intermediate pressure or a discharge pressure on the back of the swing scroll or the fixed scroll. Back pressure is applied to press the turning scroll or the fixed scroll by the counter scroll with the pressure of.

In particular, in the back pressure method, a method is provided in which a back pressure chamber is formed inside or outside the sealing member by installing a sealing member between the back surface of the swing scroll (or the back surface of the fixed scroll) and the corresponding frame. In the back pressure method using such a sealing member, an annular groove is formed in one member forming a thrust surface, and an annular sealing member having a rectangular cross-sectional shape is inserted into the annular groove. Then, during operation of the compressor, the medium pressure refrigerant compressed in the compression chamber is introduced into the annular groove, and the back pressure chamber is formed by floating the sealing member by being in close contact with the opposite member by the pressure of the medium pressure.

However, in the conventional scroll compressor as described above, as the discharge port is formed in the center of the fixed scroll, the back pressure and gas force applied to the center of the fixed wrap and the swing wrap are greater than the back pressure and gas force applied to the edge portion. The central portion of the wrap or swing wrap may be deformed while bending towards the edges, resulting in deterioration of compressor efficiency while severe frictional loss or wear occurs between the scroll or the scroll facing the fixed wrap or swing wrap.

In the conventional scroll compressor as described above, in the case of a so-called shaft through scroll compressor in which the rotating shaft overlaps the compression chamber in the radial direction, as the rotating shaft penetrates through the center of the fixed scroll, the discharge end of the fixed wrap is connected to the rotating shaft. It is not possible to extend sufficiently to the center of the fixed scroll, which causes the rigidity of the discharge end of the fixed wrap is weakened, the fixed wrap may be severely bent or the discharge end of the fixed wrap may be broken at all. Furthermore, as disclosed in Korean Patent Registration No. 10-1059880, when the fixed wrap and the swiveling wrap are changed to an amorphous shape to increase the compression ratio of the compression chamber, the discharge end of the fixed wrap may be more severely deformed and damaged. In this case, even when a protrusion is formed at the discharging end of the fixed wrap to increase the support force of the wrap, the deformation of the wrap due to the increase in the compression ratio is not fully suppressed, and thus the reliability of the compressor may be reduced due to friction loss, wear, or break of the wrap.

In the conventional scroll compressor as described above, as described in Japanese Laid-Open Patent Publication No. 2000-257573, deformation and breaking of the wrap (especially the fixed wrap) are suppressed by changing the shape of the wrap. However, in the case of forming the root of the lap thickly, the same groove must be formed in the lap end of the facing scroll to complicate the manufacturing process of the lap, and the lap thickness becomes thinner from the middle of the lap to the end of the lap. The deformation or fracture problem of the was not solved.

In addition, in consideration of this, in the case where the overall thickness of the lap is formed to increase the size of the scroll to increase the size of the scroll by increasing the size of the compressor, or on the contrary, the size of the compression chamber could be reduced by reducing the size of the turning radius. This may be seen as a result of arbitrarily changing the shape of the wrap without considering the rigidity of the wrap.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor that can prevent friction loss or abrasion while being excessively in close contact with the hard plate portion of the scroll facing the discharge end of the wrap by optimizing the discharge end rigidity of the wrap.

Another object of the present invention is to provide a scroll compressor capable of optimizing the discharge end stiffness of the lap to suppress the break while the vicinity of the discharge end of the lap is excessively deformed.

Another object of the present invention is to optimize the discharge end rigidity of the fixed wrap even when the rotating shaft penetrates the fixed scroll in a radial direction with the compression chamber to prevent the discharge end of the fixed wrap from being excessively deformed or broken. In addition, through this it is to provide a scroll compressor that can increase the efficiency and reliability of the compressor.

In order to achieve the object of the present invention, there can be provided a scroll compressor that can prevent the wrap from being excessively deformed or broken by optimizing the discharge-side rigidity of the wrap formed on either of the two members that are mutually sliding. .

Here, the stiffness of the lap may define a range of stiffness coefficients defined based on the height and thickness of the lap and the radius of curvature.

In addition, the stiffness coefficient may be determined by the lap load + option value due to the slope of the lap x the gas force.

In addition, in order to achieve the object of the present invention, the first wrap having a discharge end in the center, and the suction end at the edge, each of which is formed by connecting a plurality of curves from the discharge end to the suction end; And a discharge end at the center and a suction end at the edge, and a plurality of curves are formed to be connected from the discharge end to the suction end, and the rotary shaft coupling part is coupled to the discharge end so that the rotating shaft overlaps with the first wrap. And a second lap formed in engagement with the first lap and pivoting with respect to the first lap to form a compression chamber moving toward the center with the first lap. A specific section of at least one lap of the laps obtains a first value by dividing the lap average height in the specific section by the lap average thickness, and multiplies the first value by the average radius of curvature of the lap to obtain a second value. A scroll compressor can be provided that is formed using a stiffness coefficient defined as the inverse of the second value.

In this case, the limiting range of the stiffness coefficient may be formed to be equal to or larger than the limiting limit defined by [(0.0001 to 0.0003) × lap load (N) + (7.0000 to 8.0000)].

The limit line limiting range may be defined as [0.0002 × lap load (N) +7.5202].

In addition, when the central end of the first lap is called the discharge end and the discharge end is 0 ° based on the rotation angle of the rotation shaft, the specific section is in a range of 0 to 45 ° based on the rotation angle of the rotation shaft. Can be.

In addition, an arc compression surface is formed on one side of the rotation shaft coupling portion, and a recess is formed in the section between the arc compression surface and the outer surface of the rotation shaft coupling portion to reduce the thickness of the second wrap, and discharge of the first wrap In a section near the end, a protrusion may be formed to engage the recess of the second wrap, and at least a portion of the section in which the protrusion is formed may be formed to satisfy the range of the stiffness coefficient.

In addition, in order to achieve the object of the present invention, the first hard plate portion is formed in the center of the bearing shaft through which the rotating shaft penetrates, the discharge port is formed in the periphery of the bearing hole, the first protrusion formed on one side surface of the first hard plate portion A first scroll comprising a wrap; And a second hard plate portion having a rotary shaft coupling portion formed therein so as to be eccentrically coupled to the rotary shaft penetrating through the bearing hole of the first scroll in a central portion thereof, and protruding from one side of the second hard plate portion and engaged with the first wrap to form a compression chamber. A second scroll comprising a second lap to form; wherein the first lap comprises: a lap stiffness divided by lap thickness, the value of which is defined as the inverse of the product of the first lap multiplied by the radius of curvature The scroll compressor may be provided so as to be formed to be 0.005 mm or more.

Herein, the stiffness coefficient limiting range is defined for a section between any two points along the advancing direction of the lap in the first lap, and the lap height, the lap thickness, and the lap curvature radius are the average lap height and average of the corresponding lap. Lap thickness, average lap curvature radius can be defined.

The stiffness coefficient limiting range is defined for any one point in the first lap, and the lap height, lap thickness, and lap curvature radius may be defined as a lap height, a lap thickness, and a lap curvature radius of the corresponding lap.

In addition, in the section from the end of the first lap to the point adjacent to the discharge port or at any point of the section, the limit range of the stiffness coefficient is [(0.0001 to 0.0003) × lap load (N) + ( 7.0000 to 8.0000)].

In addition, in order to achieve the object of the present invention, the casing in which the oil is stored in the inner space; A drive motor provided in the inner space of the casing; A rotating shaft coupled to the drive motor; A frame provided below the drive motor; A first scroll provided at a lower side of the frame and having a first wrap formed at one side thereof, a bearing hole through which the rotating shaft penetrates at a central portion thereof, and a discharge hole formed at a periphery of the bearing hole; And a second lap engaging with the first lap, the rotation axis being eccentrically coupled so as to radially overlap the second lap, between the first scroll and the first lap while pivoting with respect to the first scroll. A second scroll forming a compression chamber; It is provided between the frame and the second scroll and separates the interval between the frame and the second scroll into an inner interval on the central side and an outer interval on the edge side, oil sucked through the rotating shaft flows into the inner interval and back pressure And a sealing member configured to form a seal, wherein the first wrap is obtained by dividing the average wrap height by the average wrap thickness from the end of the side adjacent to the discharge port to the first point, and multiplying this value by the average wrap curvature radius. A scroll compressor can be provided which is formed such that the stiffness coefficient limit defined by multiplying the inverse by an arbitrary value of 1000 mm is 5 or more.

The central point of the first lap is referred to as an ejection end based on the rotation angle of the rotation shaft, and when the discharge end is referred to as 0 °, the first point is 0 to 60 ° based on the rotation angle of the rotation shaft. It may be any point within the range.

In addition, an arc compression surface is formed on one side of the rotation shaft coupling portion, and a recess is formed in the section between the arc compression surface and the outer surface of the rotation shaft coupling portion to reduce the thickness of the second wrap, and discharge of the first wrap A protruding portion may be formed in the section near the end to engage with the concave portion of the second wrap, and at least a part of the section in which the protruding portion is formed may be formed to satisfy a limit range of the stiffness coefficient.

The scroll compressor according to the present invention is formed by optimizing the stiffness of the portion adjacent to the discharge end of the fixed lap or the swivel lap, thereby minimizing the lap deformation of the discharge end of the central side receiving relatively high back pressure and gas force. It can prevent excessive close contact toward the opposite scroll, which can reduce the friction loss or wear between the scrolls, thereby increasing the compressor efficiency.

In addition, by optimizing the stiffness of the portion adjacent to the discharge end of the fixed wrap or the swivel wrap, it is possible to suppress the deformation of the discharge end of the center side of the fixed wrap or the swivel wrap in the radial direction outward, Through this, the compression chamber can be suppressed to increase the efficiency of the compressor and the breakage of the wrap can be suppressed to increase the reliability of the compressor.

In addition, even when the rotating shaft penetrates the center of the fixed scroll so that the discharge end of the fixed wrap is located away from the center of the fixed scroll, the stiffness of the wrap adjacent to the discharge end is optimized to reduce friction or wear between the fixed wrap and the scroll. By preventing deformation or breakage of the fixed wrap, the efficiency and reliability of the compressor can be improved.

1 is a longitudinal sectional view showing a lower compression scroll compressor according to the present invention;

2 is a cross-sectional view showing the compression unit in FIG.

3 is a front view showing a part of a rotating shaft to explain the sliding part in FIG.

Figure 4 is a longitudinal sectional view shown to explain the oil supply passage between the back pressure chamber and the compression chamber in Figure 1,

FIG. 5 is a schematic diagram illustrating the deformation amount of the deformation around the discharge end of the first wrap for each part in the scroll compressor according to FIG. 1;

6 is a schematic view showing the wrap shape at the front of the deformation amount in FIG. 5 from the front;

7 is a schematic view for explaining the standard for the discharge end of the wrap according to this embodiment,

8 is a graph analyzing the amount of deformation of the lap according to various standards and operating speeds for the first lap;

9 is a cross-sectional view showing a deformation amount of the discharge end of the wrap having a stiffness coefficient limitation range of the wrap according to the present embodiment.

Hereinafter, the scroll compressor according to the present invention will be described in detail with reference to the embodiment shown in the accompanying drawings. However, hereinafter, for convenience, the compression compressor will be described as a representative example of a scroll compressor having a rotary shaft overlapping with the swing wrap in the lower compression scroll compressor positioned below the electric drive. Scroll compressors of this type are known to be suitable for applications in refrigeration cycles at high temperature and high compression ratio conditions.

1 is a longitudinal sectional view showing a lower compression scroll compressor according to the present invention, Figure 2 is a cross-sectional view showing the compression portion in Figure 1, Figure 3 is a front view showing a part of the rotating shaft to explain the sliding portion in Figure 1, 4 is a longitudinal cross-sectional view shown to explain the oil supply passage between the back pressure chamber and the compression chamber in FIG.

Referring to FIG. 1, in the lower compression scroll compressor according to the present embodiment, an electric motor 20 that forms a driving motor and generates a rotational force is installed in the casing 10, and is provided below the electric motor 20. A compression unit 30 may be installed to leave a predetermined space (hereinafter, intermediate space) 10a and receive a rotational force of the transmission unit 20 to compress the refrigerant.

The casing 10 includes a cylindrical shell 11 forming an airtight container, an upper shell 12 covering an upper part of the cylindrical shell 11 together to form a sealed container, and a lower part of the cylindrical shell 11 covering an airtight container together. At the same time it can be made of a lower shell 13 to form a reservoir 10c.

The refrigerant suction pipe 15 penetrates through the side surface of the cylindrical shell 11 and directly communicates with the suction chamber of the compression unit 30, and communicates with the upper space 10b of the casing 10 at the upper portion of the upper shell 12. A refrigerant discharge tube 16 may be installed. The refrigerant discharge tube 16 corresponds to a passage through which the compressed refrigerant discharged from the compression unit 30 to the upper space 10b of the casing 10 is discharged to the outside, and the upper space 10b forms a kind of oil separation space. The refrigerant discharge pipe 16 may be inserted to the middle of the upper space 10b of the casing 10 so as to be formed. In some cases, an oil separator (not shown) for separating oil mixed in the refrigerant is connected to the refrigerant suction pipe 15 in the inner space or the upper space 10b of the casing 10 including the upper space 10b. Can be.

The transmission part 20 consists of the stator 21 and the rotor 22 rotating inside the stator 21. The stator 21 has a plurality of coil windings (unsigned) forming teeth and slots in the circumferential direction thereof, and coils 250 are wound around the stator 21. The second refrigerant path P _G2 is formed by joining the gap and the coil winding part. Accordingly, the refrigerant discharged into the intermediate space 10c between the transmission unit 20 and the compression unit 30 through the first refrigerant passage P _G1 to be described later is the second refrigerant passage formed in the transmission unit 20 ( It moves to the upper space 10b formed above the transmission part 20 via P _G2 ).

In addition, a plurality of D-cut surfaces 21a are formed on the outer circumferential surface of the stator 21 along the circumferential direction, and the decut surfaces 21a are formed to allow oil to pass between the inner circumferential surfaces of the cylindrical shell 11. 1 oil path (P _O1 ) may be formed. Thus, the oil separated from the refrigerant in the upper space 10b is moved to the lower space 10c through the first oil passage P _O1 and the second oil passage P _O2 to be described later.

The lower side of the stator 21 may be fixed to the inner circumferential surface of the casing 10, the frame 31 constituting the compression unit 30 at a predetermined interval. The frame 31 may be fixedly coupled to its outer circumferential surface by being shrunk or welded to the inner circumferential surface of the cylindrical shell 11.

An annular frame side wall portion (first side wall portion) 311 is formed at the edge of the frame 31, and a plurality of communication grooves 311 b are formed in the outer circumferential surface of the first side wall portion 311 along the circumferential direction. Can be. The communication groove 311b forms a second oil passage P _O2 together with the communication groove 322b of the first scroll 32 which will be described later.

In addition, a first bearing portion 312 for supporting the main bearing portion 51 of the rotating shaft 50 to be described later is formed at the center of the frame 31, and the main bearing portion of the rotating shaft 50 is formed at the first bearing portion. The first bearing hole 312a may be penetrated in the axial direction so that the 51 is rotatably inserted to be supported in the radial direction.

In addition, a fixed scroll (hereinafter referred to as a first scroll) 32 may be installed on a lower surface of the frame 31 with a pivoting scroll (hereinafter referred to as a second scroll) 33 eccentrically coupled to the rotation shaft 50. The first scroll 32 may be fixedly coupled to the frame 31, but may also be coupled to be movable in the axial direction.

Meanwhile, the first scroll 32 has a fixed hard plate portion (hereinafter referred to as a first hard plate portion) 321 having a substantially disc shape, and is coupled to the bottom edge of the frame 31 at the edge of the first hard plate portion 321. A scroll sidewall portion (hereinafter, referred to as a second sidewall portion) 322 may be formed.

One side of the second side wall portion 322 is formed through the inlet 324 through which the refrigerant suction pipe 15 communicates with the suction chamber, and the compressed refrigerant is discharged in communication with the discharge chamber in the central portion of the first hard plate portion 321. The discharge holes 325a and 325b may be formed. Although only one

discharge port

325a and 325b may be formed so as to communicate with both the first compression chamber V1 and the second compression chamber V2, which will be described later, each of the compression chambers V1 and V2 is independent. Plural dogs may be formed to communicate with each other.

In addition, a communication groove 322b described above is formed on an outer circumferential surface of the second side wall portion 322, and the communication groove 322b stores oil recovered together with the communication groove 311b of the first side wall portion 311 in a lower space. A second oil channel P _O2 for guiding to 10c is formed.

In addition, a discharge cover 34 for guiding the refrigerant discharged from the compression chamber V to the refrigerant passage, which will be described later, may be coupled to the lower side of the first scroll 32. The discharge cover 34 accommodates the

discharge holes

325a and 325b, and the refrigerant discharged from the compression chamber V through the

discharge holes

325a and 325b, and the upper space of the casing 10. 10b), more precisely, may be formed to accommodate an inlet of the first refrigerant passage P _G1 that guides into the space between the transmission part 20 and the compression part 30.

Here, the first refrigerant passage (P _G1 ) is the second side wall portion 322 of the fixed scroll (32) on the inside of the flow path separation unit 40, that is, the rotation shaft 50 inward with respect to the flow path separation unit 40. And may pass through the first sidewall portion 311 of the frame 31 in order. As a result, the second oil passage P _O2 described above is formed on the outside of the flow path separation unit 40 so as to communicate with the first oil passage P _O1 .

In addition, a fixing wrap (hereinafter referred to as a first wrap) 323 may be formed on an upper surface of the first hard plate part 321 to form a compression chamber V by engaging with a turning wrap (hereinafter referred to as a second wrap) 332 to be described later. have. The first wrap 323 will be described later together with the second wrap 332.

In addition, a second bearing portion 326 for supporting the sub bearing portion 52 of the rotating shaft 50, which will be described later, is formed at the center of the first hard plate portion 321, and the second bearing portion 326 is disposed in the axial direction. A second bearing hole 326a may be formed to penetrate and support the sub bearing portion 52 in the radial direction.

On the other hand, the second scroll 33 may be formed in the shape of a substantially circular disk portion (hereinafter, the second hard plate portion) 331 331. A second wrap 332 may be formed on a bottom surface of the second hard plate part 331 to form a compression chamber in engagement with the first wrap 322.

The second wrap 332 may be formed in an involute shape together with the first wrap 323, but may be formed in various other shapes. For example, as illustrated in FIG. 2, the second wrap 332 has a shape in which a plurality of arcs having different diameters and origins are connected to each other, and the outermost curve may be formed in an approximately elliptical shape having a long axis and a short axis. . This may be formed in the first wrap 323 as well.

A central shaft portion of the second hard plate portion 331 forms an inner end of the second wrap 332, and the rotation shaft coupling portion 333 to which the eccentric portion 53 of the rotation shaft 50, which will be described later, is rotatably inserted and coupled thereto is a shaft. It can be formed through in the direction.

The outer circumferential portion of the rotation shaft coupling portion 333 is connected to the second wrap 332 to serve to form the compression chamber V together with the first wrap 322 in the compression process.

In addition, the rotation shaft coupling portion 333 is formed at a height overlapping with the second wrap 332 on the same plane, and the height at which the eccentric portion 53 of the rotation shaft 50 overlaps with the second wrap 332 on the same plane. Can be placed in. As a result, the repulsive force and the compressive force of the refrigerant are offset to each other while being applied to the same plane with respect to the second hard plate part, thereby preventing the inclination of the second scroll 33 due to the action of the compressive force and the repulsive force.

In addition, the rotary shaft coupling portion 333 is formed with a recess 335 that is engaged with the protrusion 328 of the first wrap 323, which will be described later, on an outer circumferential portion facing the inner end of the first wrap 323. One side of the concave portion 335 is formed with an increasing portion 335a which increases in thickness from the inner circumference portion to the outer circumference portion of the rotary shaft coupling portion 333 along the forming direction of the compression chamber V. This makes the compression path of the first compression chamber V1 immediately before the discharge long, so that the compression ratio of the first compression chamber V1 can be increased close to the pressure ratio of the second compression chamber V2. The first compression chamber V1 is a compression chamber formed between the inner surface of the first wrap 323 and the outer surface of the second wrap 332, which will be described later separately from the second compression chamber V2.

The other side of the recess 335 is formed with an arc compression surface 335b having an arc shape. The diameter of the arc compression surface 335b is determined by the thickness of the inner end of the first wrap 323 (ie, the thickness of the discharge end) and the turning radius of the second wrap 332. Increasing the end thickness increases the diameter of the arc compression surface 335b. As a result, the thickness of the second wrap around the arc compression surface 335b may also be increased to ensure durability, and the compression path may be longer to increase the compression ratio of the second compression chamber V2.

In addition, a protruding portion 328 protruding toward the outer circumferential side of the rotating shaft engaging portion 333 is formed near the inner end (suction end or starting end) of the first wrap 323 corresponding to the rotating shaft engaging portion 333. A contact portion 328a may be formed at the 328 to protrude from the protrusion and to engage the recess 335. That is, the inner end of the first wrap 323 may be formed to have a larger thickness than other portions. As a result, the wrap strength of the inner end portion that receives the greatest compressive force among the first wraps 323 may be improved, and thus durability may be improved.

On the other hand, the compression chamber (V) is formed between the first hard plate portion 321 and the first wrap 323, and the second wrap 332 and the second hard plate portion 331, suction along the advancing direction of the wrap The chamber, the intermediate pressure chamber, and the discharge chamber may be formed continuously.

As shown in FIG. 2, the compression chamber V includes the first compression chamber V1 formed between the inner surface of the first wrap 323 and the outer surface of the second wrap 332 and the first wrap 323. The second compression chamber V2 may be formed between the outer surface and the inner surface of the second wrap 332.

That is, the first compression chamber V1 includes a compression chamber formed between two contact points P11 and P12 generated by contact between the inner surface of the first wrap 323 and the outer surface of the second wrap 332. The second compression chamber V2 includes a compression chamber formed between two contact points P21 and P22 formed by the contact between the outer surface of the first wrap 323 and the inner surface of the second wrap 332.

Here, the first compression chamber V1 immediately before the discharge has an angle having a larger value among the angles formed by the center of the eccentric portion, that is, the center O of the rotary shaft coupling portion and the two lines connecting the two contact points P11 and P12, respectively. When? Is?, At least immediately before the discharge start,? <360 ° and the distance l between the normal vectors at the two contact points P11 and P12 also has a value greater than zero.

As a result, the first compression chamber immediately before the discharge has a smaller volume as compared with the case where the fixed wrap and the swiveling wrap formed of the involute curve are used. Therefore, the size of the first wrap 323 and the second wrap 332 is not increased. Both the compression ratio of the first compression chamber V1 and the compression ratio of the second compression chamber V2 can be improved.

On the other hand, as described above, the second scroll 33 may be rotatably installed between the frame 31 and the fixed scroll (32). An old dam ring 35 is installed between the upper surface of the second scroll 33 and the lower surface of the frame 31 corresponding thereto to prevent rotation of the second scroll 33. Sealing member 36 to form a back pressure chamber (S1) may be installed.

In addition, an intermediate pressure space is formed on the outside of the sealing member 36 by the oil supply hole 321a provided in the second scroll 32. The intermediate pressure space communicates with the intermediate compression chamber (V) and may serve as a back pressure chamber as the medium pressure refrigerant is filled. Therefore, the back pressure chamber formed inside the center of the sealing member 36 can be called the 1st back pressure chamber S1, and the intermediate pressure space formed outside can be called the 2nd back pressure chamber S2. As a result, the back pressure chamber S1 is a space formed by the bottom surface of the frame 31 and the top surface of the second scroll 33 around the sealing member 36. The back pressure chamber S1 will be described later with a sealing member. Explain again with

On the other hand, the flow path separation unit 40 is installed in the intermediate space (10a) which is a transit space formed between the lower surface of the transmission unit 20 and the upper surface of the compression unit 30, the refrigerant discharged from the compression unit 30 It serves to prevent interference with the oil moving from the upper space (10b) of the oil separation space to the lower space (10c) of the compression section 30, the oil storage space.

To this end, the flow path separation unit 40 according to the present embodiment separates the first space 10a into a space (hereinafter, a refrigerant flow space) in which a refrigerant flows and a space (hereinafter, an oil flow space) in which oil flows. Includes a euro guide. The flow path guide may separate the first space 10a into a refrigerant flow space and an oil flow space by using only the flow path guide itself. However, in some cases, the flow path guide may serve as a flow path guide by combining a plurality of flow path guides.

The flow path separating unit according to the present embodiment includes a first flow path guide 410 provided on the frame 31 and extending upward, and a second flow path guide 420 provided on the stator 21 and extended downward. The first flow guide 410 and the second flow guide 420 overlap in the axial direction so that the intermediate space 10a can be separated into the refrigerant flow space and the oil flow space.

Here, the first flow path guide 410 is formed in an annular shape and fixedly coupled to the upper surface of the frame 31, the second flow path guide 420 is inserted into the stator 21 to extend from the insulator to insulate the winding coil Can be.

The first flow guide 410 may include a first annular wall portion 411 extending upwardly from the outside, a second annular wall portion 412 extending upwardly from the inside, and a first annular wall portion 411 and a second annular wall portion 412. It consists of an annular surface portion 413 extending radially so as to connect between. The first annular wall portion 411 is formed higher than the second annular wall portion 412, and the refrigerant hole may be formed in the annular surface portion 413 such that the refrigerant hole communicated from the compression part 30 to the intermediate space 10a. Can be.

In addition, the balance weight 26 is positioned inside the second annular wall portion 412, that is, in the rotation axis direction, and the balance weight 26 is coupled to the rotor 22 or the rotation shaft 50 to rotate. At this time, while the balance weight 26 rotates, the refrigerant can be stirred, but the second circular wall portion 412 prevents the refrigerant from moving toward the balance weight 26, thereby preventing the refrigerant from being stirred by the balance weight 26. It can be suppressed.

The second flow path guide 420 may include a first extension part 421 extending downward from the outside of the insulator and a second extension part 422 extending downward from the inside of the insulator. The first extension part 421 is formed to overlap the first annular wall part 411 in the axial direction, and serves to separate the refrigerant flow space and the oil flow space. Although the second extension part 422 may not be formed as necessary, the second extension part 422 may be formed at a sufficient interval in the radial direction so that the refrigerant may sufficiently flow even if the second extension part 422 does not overlap or overlaps with the second annular wall part 412 in the axial direction. It is preferable to be.

On the other hand, the rotating shaft 50 may be coupled to the upper portion of the rotor 22 is pressed in the center while the lower portion is coupled to the compression unit 30 can be radially supported. As a result, the rotation shaft 50 transmits the rotational force of the transmission unit 20 to the turning scroll 33 of the compression unit 30. Then, the second scroll 33, which is eccentrically coupled to the rotation shaft 50, rotates about the first scroll 32.

In the lower half of the rotating shaft 50, a main bearing portion (hereinafter referred to as a first bearing portion) 51 is formed to be inserted into the first bearing hole 312a of the frame 31 and supported radially, and the first bearing portion ( A sub bearing part (hereinafter referred to as a second bearing part) 52 may be formed below the 51 to be inserted into the second bearing hole 326a of the first scroll 32 to be radially supported. In addition, an eccentric portion 53 may be formed between the first bearing portion 51 and the second bearing portion 52 so as to be inserted into and coupled to the rotation shaft coupling portion 333.

The first bearing portion 51 and the second bearing portion 52 are formed coaxially to have the same axial center, and the eccentric portion 53 is formed on the first bearing portion 51 or the second bearing portion 52. It may be formed radially eccentric with respect to. The second bearing portion 52 may be eccentrically formed with respect to the first bearing portion 51.

The eccentric portion 53 must have an outer diameter smaller than the outer diameter of the first bearing portion 51 and larger than the outer diameter of the second bearing portion 52 so that the rotary shaft 50 can be formed with the respective bearing holes 312a and 326a. It may be advantageous to couple through the rotating shaft coupling portion 333. However, when the eccentric portion 53 is not formed integrally with the rotation shaft 50 and is formed using a separate bearing, the outer diameter of the second bearing portion 52 is not formed smaller than the outer diameter of the eccentric portion 53. Rotating shaft 50 can be inserted by inserting.

In addition, an oil supply passage 50a for supplying oil to each bearing part and the eccentric part may be formed along the axial direction in the rotation shaft 50. The oil supply passage 50a is approximately the bottom or middle height of the stator 21 at the lower end of the rotating shaft 50 or the first bearing part 31 as the compression unit 30 is positioned below the transmission unit 20. Grooves can be formed up to a position higher than the top of the. Of course, in some cases, the rotation shaft 50 may be formed to penetrate in the axial direction.

In addition, an oil feeder 60 for pumping oil filled in the lower space 10c may be coupled to the lower end of the rotation shaft 50, that is, the lower end of the second bearing part 52. The oil feeder 60 is composed of an oil supply pipe 61 inserted into and coupled to the oil supply flow path 50a of the rotation shaft 50 and a blocking member 62 that accommodates the oil supply pipe 61 to block intrusion of foreign substances. Can be. The oil supply pipe 61 may be positioned to penetrate the discharge cover 34 to be immersed in the oil of the lower space 10c.

On the other hand, as shown in Figure 3, each bearing

portion

51, 52 and the eccentric portion 53 of the rotating shaft 50 is connected to the oil supply passage (50a), the sliding portion for supplying oil to each sliding portion The flow path F1 is formed.

The sliding part oil supply passage F1 includes a plurality of oil supply holes 511, 521, and 531 passing through the oil supply passage 50a toward the outer circumferential surface of the rotation shaft 50, and each bearing

portion

51, 52. And a plurality of oil supply grooves 512 communicating with oil supply holes 511, 521, and 531 on the outer circumferential surface of the eccentric part 53 to lubricate each of the bearing

parts

51, 52 and the eccentric part 53 ( 522 and 532.

For example, the first bearing part 51 has a first oil supply hole 511 and a first oil supply groove 512, and the second bearing part 52 has a second oil supply hole 521 and a second oil supply groove ( 522 and the eccentric portion 53 are provided with a third oil supply hole 531 and a third oil supply groove 532, respectively. The first oil supply groove 512, the second oil supply groove 522, and the third oil supply groove 532 are each formed in a long groove shape in the axial direction or the inclined direction.

In addition, between the first bearing portion 51 and the eccentric portion 53, and between the eccentric portion 53 and the second bearing portion 52, an annular first connecting groove 541 and a second connecting groove, respectively. 542 are formed, respectively. The first connection groove 541 is connected to the lower end of the first oil supply groove 512, the second connection groove 542 is connected to the upper end of the second oil supply groove 522. As a result, a part of the oil lubricating the first bearing part 51 through the first oil supply groove 512 flows into the first connection groove 541, and the oil is collected into the first back pressure chamber S1. It is introduced to form a back pressure of the discharge pressure. In addition, the oil lubricating the second bearing portion 52 through the second oil supply groove 522 and the oil lubricating the eccentric portion 53 through the third oil supply groove 532 are connected to the second connection groove 542. Gather may be introduced into the compression unit 30 through the front end surface of the rotary shaft coupling portion 333 and the first hard plate portion 321.

In addition, a small amount of oil sucked in the upper direction of the first bearing part 51 flows out of the bearing surface at the upper end of the first bearing part 312 of the frame 31, and the frame 31 is along the first bearing part 312. After flowing down to the upper surface 31a of), the oil passage P _O1 (P _O1 ) (P _O1 ) formed continuously on the outer circumferential surface (or the groove communicating from the upper surface to the outer circumferential surface) of the frame 31 and the outer circumferential surface of the first scroll 32 _O2 ) is recovered to the lower space 10c.

In addition, the oil discharged from the compression chamber (V) together with the refrigerant into the upper space (10b) of the casing 10 is separated from the refrigerant in the upper space (10b) of the casing 10, the outer peripheral surface of the transmission portion 20 The first oil path P _O1 and the second oil channel P _O2 formed on the outer circumferential surface of the compression unit 30 are recovered to the lower space 10c. At this time, the flow path separation unit 40 is provided between the transmission unit 20 and the compression unit 30, the oil is separated from the refrigerant in the upper space (10b) is moved to the lower space (10c) compression unit 20 Oil is discharged through the different passages ((P _O1 ) (P _O2 )] [(P _G1 ) (P _G2 )] without interfering with the refrigerant discharged from the upper space 10b and moving to the upper space 10b. At 10c, the coolant can move to the upper space 10b.

On the other hand, the second scroll 33 is formed with a compression chamber supply passage (F2) for supplying the oil drawn through the oil supply passage (50a) to the compression chamber (V). The compression chamber oil supply passage F2 is connected to the sliding part oil supply passage F1 described above.

The compression chamber oil supply passage F2 includes a first oil supply passage 371 communicating with the oil supply passage 50a and a second back pressure chamber S2 constituting an intermediate pressure space, and a second back pressure chamber S2. The second oil supply passage 372 communicates with the intermediate pressure chamber of the compression chamber (V).

Of course, the compression chamber oil supply passage may be formed so as to communicate directly with the intermediate pressure chamber from the oil supply passage (50a) without passing through the second back pressure chamber (S2). However, in this case, a refrigerant path for communicating the second back pressure chamber S2 and the intermediate pressure chamber V must be separately provided, and the oil is supplied to the old dam ring 35 positioned in the second back pressure chamber S2. Oil passages should be provided separately. This increases the number of passages, which complicates processing. Therefore, in order to reduce the number of passages by unifying the refrigerant passage and the oil passage, the oil supply passage 50a and the second back pressure chamber S2 communicate with each other as in the present embodiment, and the second back pressure chamber S2 is the intermediate pressure chamber. It may be desirable to communicate with (V).

To this end, the first oil supply passage 371 is formed with a first turning passage portion 371a which is formed in the thickness direction from the lower surface of the second hard plate portion 331 to the middle, and in the first turning passage portion 371a. The second turning passage portion 371b is formed toward the outer circumferential surface of the second hard plate portion 331, and the third turning passage portion penetrates from the second turning passage portion 371b toward the upper surface of the second hard plate portion 331. 371c is formed.

The first swing passage part 371a is formed at a position belonging to the first back pressure chamber S1, and the third swing passage part 371c is formed at a position belonging to the second back pressure chamber S2. In addition, the second turning passage part 371b includes a pressure reducing rod 375 to lower the pressure of the oil moving from the first back pressure chamber S1 to the second back pressure chamber S2 through the first oil supply passage 371. ) Is inserted. Thus, the cross-sectional area of the second swing passage portion 371b except for the pressure reducing rod 375 is formed to be small in the first swing passage portion 371a or the third swing passage portion 371c and the second swing passage portion 371b.

Here, when the end portion of the third turning passage portion 371c is formed to be located inside the old dam ring 35, that is, between the old dam ring 35 and the sealing member 36, the first oil supply passage 371. The oil moving through) is blocked by the old dam ring 35 and thus cannot be smoothly moved to the second back pressure chamber S2. Therefore, in this case, the fourth pivot passage part 371d may be formed from the end of the third pivot passage part 371c toward the outer circumferential surface of the second hard plate part 331. As shown in FIG. 4, the fourth pivot passage part 371d may be formed as a groove in the upper surface of the second hard plate part 331 or may be formed as a hole in the second hard plate part 331.

The second oil supply passage 372 has a first fixed passage 372a formed in the thickness direction on the upper surface of the second side wall portion 322, and a second fixed passage in the radial direction from the first fixed passage portion 372a. A portion 372b is formed, and a third fixed passage portion 372c communicating with the intermediate pressure chamber V from the second fixed passage portion 372b is formed.

Reference numeral 70 in the figure denotes an accumulator.

The lower compression scroll compressor according to the present embodiment as described above is operated as follows.

That is, when power is applied to the transmission unit 20, rotational force is generated by the rotor 22 and the rotating shaft 50 to rotate, and the rotating shaft 50 is eccentrically coupled to the rotating shaft 50 as the rotating shaft 50 rotates The 33 is swiveling by Oldham Ring 35.

Then, the coolant supplied through the coolant suction pipe 15 from the outside of the casing 10 flows into the compression chamber V, and the coolant flows in the volume of the compression chamber V by the swinging motion of the swing scroll 33. As it decreases, it is compressed and discharged into the inner space of the discharge cover 34 through the

discharge holes

325a and 325b.

Then, the refrigerant discharged into the internal space of the discharge cover 34 circulates through the internal space of the discharge cover 34 and moves to the space between the frame 31 and the stator 21 after the noise is reduced. Is moved to the upper space of the transmission unit 20 through the gap between the stator 21 and the rotor 22.

Then, after the oil is separated from the coolant in the upper space of the transmission unit 20, the coolant is discharged to the outside of the casing 10 through the coolant discharge pipe 16, while the oil is in the inner circumferential surface of the casing 10 and the stator ( 21 is repeated a series of processes to be recovered to the lower space (10c) of the storage space of the casing 10 through the flow path between the inner peripheral surface of the casing 10 and the outer peripheral surface of the compression unit 30.

At this time, the oil in the lower space (10c) is sucked through the oil supply passage (50a) of the rotating shaft 50, the oil is the oil supply holes 511, 521, 531 and the oil supply grooves (512) (522) 532 to lubricate the first bearing portion 51, the second bearing portion 52, and the eccentric portion 53, respectively.

Among these, the oil lubricated with the first bearing part 51 through the first oil supply hole 511 and the first oil supply groove 512 is the first connection groove between the first bearing part 51 and the eccentric part 53. At 541, the oil flows into the first back pressure chamber S1. This oil almost forms a discharge pressure, and the pressure of the 1st back pressure chamber S1 also forms almost a discharge pressure. Therefore, the center side of the second scroll 33 can be supported in the axial direction by the discharge pressure.

On the other hand, the oil in the first back pressure chamber (S1) is moved to the second back pressure chamber (S2) via the first oil supply passage 371 by the pressure difference with the second back pressure chamber (S2). At this time, the second turning passage portion 371b constituting the first oil supply passage 371 is provided with a decompression rod 375, and the pressure of the oil directed to the second back pressure chamber S2 is reduced to an intermediate pressure.

The oil moving to the second back pressure chamber (intermediate pressure space) S2 supports the edge of the second scroll 33 and the second oil supply passage 372 according to the pressure difference with the intermediate pressure chamber V. It moves to the intermediate pressure chamber (V) through. However, when the pressure in the intermediate pressure chamber V becomes higher than the pressure in the second back pressure chamber S2 during operation of the compressor, the refrigerant flows in the second back pressure chamber S2 through the second oil supply passage 372. Will move to). In other words, the second oil supply passage 372 serves as a passage through which the refrigerant and oil cross-move according to the pressure difference between the pressure in the second back pressure chamber S2 and the pressure in the intermediate pressure chamber V.

On the other hand, as described above, the back pressure chamber is formed on the rear surface of the second scroll, that is, the upper surface of the second scroll so as to prevent the second scroll from being pushed away by the pressure of the compression chamber and away from the first scroll.

That is, the back pressure chamber is provided with a sealing member on the lower surface of the frame and the upper surface of the second scroll, so that the first back pressure chamber between the second scroll and the frame, and the second back pressure chamber between the second scroll and the frame and the first scroll, respectively. Is formed.

Therefore, it is preferable that the sealing member has excellent sealing force between the frame and the second scroll and has excellent wear resistance in consideration of friction caused by the pivoting movement of the second scroll. In addition, the sealing member is formed of a material and a structure that can be quickly floated even at low pressure because the sealing member is sealed by the pressure in the state inserted into the sealing member insertion groove provided in the second scroll.

On the other hand, as described above, as the first back pressure chamber, which is the center of the second scroll, forms the discharge pressure, and the second back pressure chamber, which is the edge, forms the intermediate pressure, the back pressure at the center of the second scroll, which is the turning scroll, The pressure is higher than the back pressure of. In the meantime, the second scroll has a central portion pressed more in the first scroll direction than the edge portion, so that the discharge end of the first wrap located at the central portion of the first scroll is excessively in close contact with the second hard plate portion. At the same time, the center portion of the first wrap forms a discharge end to receive the discharge pressure, and the discharge end of the first wrap receives a strong gas force in the edge direction by the discharge pressure.

As a result, the discharge end of the first wrap receives the force of the central portion of the second scroll in the axial direction by the high back pressure of the first back pressure chamber while being pushed in the radial direction by the gas force of the discharge pressure. In other words, the discharging end of the first lap may be bent outward from the root of the lap toward the front end face of the lap, that is, in the height direction of the lap.

This phenomenon may occur severely when a second bearing hole through which a rotating shaft penetrates is formed in the center of the first scroll which is a fixed scroll as in the present embodiment. That is, when the second bearing hole is formed in the center of the first scroll, the discharge end of the first wrap, which is the fixed wrap, cannot be formed by extending to the center of the first scroll due to the second bearing hole. This is because the discharging end of is located far from the center of the scroll, and the lap stiffness at the discharging end is reduced by that amount, thereby increasing the lap deformation.

This phenomenon may occur more seriously when the compression ratio is increased by changing the first wrap and the second wrap to an amorphous shape as in the present embodiment. However, in the present embodiment, the protrusion is formed at the discharge end of the first wrap, the lap holding force is improved to a certain degree, but the frictional loss due to the deformation of the lap at the discharge end of the first lap is not increased due to the increase in the compression ratio. Abrasion or lap breakage may occur. FIG. 5 is a schematic view illustrating the deformation amount at the periphery of the discharge end of the first wrap for each part, and FIG. 6 is a schematic view of the wrap shape at the site where the deformation amount is the greatest in FIG.

As shown in FIG. 5, in the case of the first wrap 323, the deformation amount at the discharge end 323a is the largest, about 0.018 mm to 0.02 mm, and the deformation amount gradually decreases toward the suction end direction at the discharge end 323a. I can see that. In addition, the deformation amount of the first hard plate part 321 including the discharge end 323a of the first wrap 323 may be about −0.003 mm to −0.005 mm. This may be seen that the first hard plate portion 321 is finely deformed by the force in the opposite direction in which the first wrap 323 is deformed.

Accordingly, as shown in FIG. 6, the tip surface around the discharge end 323a is bent toward the edge at the right side, that is, the center of the drawing, while the inner edge 323a1 of the discharge end 323a is the highest point. To form a lower surface of the second hard plate portion 331 to face.

At the same time, the second scroll is pushed in the downward direction of the drawing by the back pressure. However, as the discharge end 323a of the first wrap 323 is bent outward and deformed, the upper surface 321b of the first hard plate portion 321 and the front end surface 332c of the second wrap 332 are back pressured. By contacting by the first contact with the discharge end 323a of the first wrap 323 and the lower surface 331b of the second hard plate portion 331 first. That is, the distance t1 between the upper surface of the first hard plate portion 321 and the front end surface 332c of the second wrap 332 is the discharge end 323a and the second hard plate portion 331 of the first wrap 323. ) Is larger than the interval t2 between the lower surfaces 331b. Therefore, the gap t2 between the front end surface 323c of the first wrap 323 and the lower surface 331b of the second hard plate portion 331 is removed by the back pressure. The friction loss or wear described above may occur between the upper surface 321b and the front end surface 332c of the second wrap 332, and the vicinity of the discharge end of the first wrap may be broken.

In view of this, in this embodiment, the lap stiffness in the vicinity of the discharge end is optimized, so that the lap deformation due to the axial force generated by the back pressure and the radial force generated by the gas force can be minimized. In this way, friction loss or abrasion or wrap breakage between the wrap and the hard plate portion can be suppressed.

The first wrap according to the present embodiment may be implemented as the lap stiffness near the discharge end is formed so as to satisfy the optimal limit line range.

That is, referring to FIG. 7, the stiffness coefficient A near the discharge end of the first lap (hereinafter referred to as lap center) is the average height h of the lap center section to the average thickness t of the lap center section. The second value obtained by dividing the first value and multiplied by the first value multiplied by the average radius of curvature R, which is the distance between the center of the rotation axis with respect to the center portion of the lap (ie, the center of the second axis hole) and the centerline of the first lap. The stiffness coefficient can be defined as the inverse of the second value. Here, the height of the first wrap 323 is formed so that the height of the lap gradually decreases from the suction end to the discharge end, the lap height in the center portion of the lap is formed differently along the direction of the wrap. Therefore, in order to accurately calculate the lap height in the corresponding section (lap center section), it is preferable to obtain and substitute the lap average height as described above. However, because the lap height difference is very small, you can ignore it and generalize it to lap height and substitute it. And this can be substituted by lap curvature radius generalized to lap curvature radius for the same reason. For reference, the radius of curvature of the lap is about 10-20 mm.

In other words, this is expressed by equation (1),

A = 1 / ((h / t) × R) ----------- Formula (1)

Same as It can be multiplied by any value 1000mm.

However, as described above, the height and thickness of the lap may be defined as the average lap height, the average lap thickness, and the average average curvature radius of a predetermined section, but in some cases, at a specific point based on the direction of the lap's progression, It can also be defined by lap height, lap thickness, and lap curvature radius. In general, however, it may be advantageous in terms of processing to define each element based on a certain interval.

For example, in the present embodiment, if the section showing the largest lap deformation amount is 0 to 60 ° (where 0 ° is the discharge end), the interval is 0 to 60 °, more precisely between 0 to 45 °. The stiffness coefficient can also be calculated using the lap average height and lap average thickness.

Here, it is preferable that the limit range for the stiffness coefficient A in the corresponding section is about 0.005 or more. That is, when the stiffness coefficient is obtained by referring to Equation (1) above, (h / t) does not exceed approximately 10. In general, when the average height of the lap divided by the average thickness of the lap is 10 or more, the lap stiffness becomes very weak and the lap stiffness is too high compared to the lap thickness, thereby causing lap fracture. Therefore, it is preferable to form (h / t) so that it may become 10 or less. The lowest value does not need to be limited as the stiffness increases as the lap thickness is larger than the lap height.

Moreover, the lap average curvature radius will be about 10-20 mm. Since the lap stiffness of the lap curvature increases as small as possible, there is no need to limit the case where the lap curvature radius is small. Therefore, when the lap average curvature radius is set to 20 mm and substituted into Equation (1), the stiffness coefficient A = 1 / ((10) x 20). Therefore, the stiffness coefficient is 0.005 mm, and the stiffness coefficient is 5. Since this corresponds to the minimum stiffness coefficient value, it is preferable that the limit range of the stiffness coefficient with respect to the discharge end of the wrap is 5 or more.

And the appropriate wrap shape of the discharge stage can be determined based on the stiffness coefficient limitation range. 8 is a graph analyzing the amount of deformation of the lab wrap according to various standards and operating speeds for the first lab.

As shown in this figure, in the case of the model ①, the deformation amount of the lap is 20 µm, in the case of the model ②, the deformation amount of the lap is 31 µm, in the case of the model ③, the deformation amount of the lap is 79 µm, In the case of model ⑤, it can be seen that the amount of lap strain is about 67 µm.

It can be seen that in the models ③ and model ⑤ where the amount of lap deformation is relatively large, the vicinity of the discharging end of the lap is broken, while in the remaining

models

①, ②, and ④, the vicinity of the discharging end of the lap is maintained without being damaged. Accordingly, the line connecting the model ③ and the model ⑤ may be defined as a limit line, and the lap stiffness such that the amount of lap deformation falls on the right side can be defined based on the limit line.

Here, when the limit line refers to FIG. 8, the slope of the limit line may range from about 0.0001 to 0.0003, and the offset amount may range from 7.0000 to 8.0000. Accordingly, it may be preferable that the stiffness coefficient is formed to be larger than at least [(0.0001 to 0.0003) x lap load (N) + (7.000 to 8.0000) by gas force]]. More precisely, the stiffness coefficient is preferably formed larger than [0.0002 x lap load (N) + 7.5202 by gas force].

Meanwhile, in the present embodiment, the range of the stiffness coefficient for optimizing the lap stiffness around the discharge end of the first lap has been described, but this may be applied to other sections of the first lap (or the second lap). However, since the limit line may be interpreted differently in another section of the first lap (or second lap), the stiffness coefficient limit in the section may be defined according to the newly calculated limit line limit.

As described above, by optimizing the stiffness of the portion adjacent to the discharge end of the first lap (or the second lap), as shown in Fig. 9, the discharge end of the center side receiving a relatively high back pressure and gas force (and centrifugal force) It is possible to minimize the deformation of the lap compared to the conventional (dotted line display), thereby preventing the first lap 323 from being in close contact with the second hard plate portion 331 of the second scroll 33 facing each other. Compressor efficiency can be improved by reducing friction loss or wear between the first wrap 323 and the second hard plate portion 331 (or the second wrap and the first hard plate portion).

In addition, by optimizing the stiffness of the portion adjacent to the discharge end of the first lap 323 (or the second lap), the discharge end of the center side of the first lap 323 (or the second lap) is extended outward. It is possible to suppress the deformation in the radial direction toward the top, thereby suppressing the leakage between the compression chamber (V1) (V2) to increase the compressor efficiency and at the same time suppress the breakage of the discharge end of the wrap to increase the reliability of the compressor. .

In addition, even when the rotating shaft 50 penetrates the center of the first scroll 32 so that the discharge end of the first wrap 323 is located far from the center of the first scroll 32, the wrap at the portion adjacent to the discharge end is performed. By stiffness, the efficiency and reliability of the compressor can be increased by preventing friction, wear or deformation or fracture of the fixed wrap between the first wrap 323 (or the second wrap) and the corresponding second hard plate portion 331. Can be.

Claims

A first wrap having a discharge end at a center portion and a suction end at an edge portion thereof, the first wrap being formed by connecting a plurality of curves from the discharge end to the suction end; And

It has a discharge end at the center and a suction end at the edge, respectively, a plurality of curves are formed from the discharge end to the suction end, the rotary shaft coupling portion is formed so that the rotary shaft is coupled to overlap the first wrap And a second wrap that engages with the first wrap and forms a compression chamber that moves toward the center with the first wrap while pivoting about the first wrap.

In a specific section of at least one of the first lap and the second lap, a lap average height in the specific lap is divided by a lap average thickness to obtain a first value, and the first value is multiplied by the average radius of curvature of the lap. And a second value is obtained and is formed using a stiffness coefficient defined by the inverse of the second value.
The method of claim 1,

And a limit range of the stiffness coefficient is greater than or equal to the limit line limit range defined by [(0.0001 to 0.0003) x lap load (N) + (7.0000 to 8.0000)].
The method of claim 2,

The limit line limit range is defined as [0.0002 × lap load (N) + 7.5202] scroll compressor.
The method of claim 2,

When the center side of the first lap is called an ejection end and the ejection end is 0 ° based on the rotation angle of the rotation shaft,

The specific section is a scroll compressor, characterized in that the range of 0 ~ 45 ° based on the rotation angle of the rotary shaft.
The method according to any one of claims 1 to 4,

One side of the rotating shaft coupling portion is formed with an arc compression surface,

A recess is formed in the section between the arc compression surface and the outer surface of the rotating shaft coupling portion to reduce the thickness of the second wrap, and in a section near the discharge end of the first wrap to engage the recess of the second wrap. Protrusions are formed,

At least a portion of the section in which the projection is formed is characterized in that the scroll compressor is formed to satisfy the range of the stiffness coefficient.
A first scroll including a first hard plate portion having a rotating shaft penetrating a rotation shaft at a central portion thereof, and a first wrap portion protruding from one side of the first hard plate portion; And

A second hard plate portion having a rotary shaft coupling portion formed therein so as to eccentrically engage a rotary shaft penetrating the bearing hole of the first scroll in a central portion thereof, and protruding from one side of the second hard plate portion and engaging the first wrap to form a compression chamber together; And a second scroll comprising a second wrap to

And the first lap is formed such that the lap height is divided by the lap thickness, and a limit of the stiffness coefficient defined by the inverse of the value of the lap thickness of the first lap is 0.005 mm or more.
The method of claim 6,

The stiffness limit range is defined for a section between any two points along the direction of travel of the lap in the first lap,

The lap height, lap thickness, lap curvature radius is a scroll compressor, characterized in that defined by the average lap height, average lap thickness, the average lap curvature radius.
The method of claim 6,

The stiffness limit is defined for any point in the first lap,

The lap height, lap thickness, lap radius of curvature is characterized in that the scroll height, lap thickness, lap radius of curvature of the point characterized in that the scroll compressor.
The method according to claim 7 or 8,

In the section from the end of the first lap to the point adjacent to the discharge port or at any point of the section, the limit of the stiffness coefficient is [(0.0001 to 0.0003) x lap load (N) + (7.0000 to 8.0000)], wherein the scroll compressor is formed beyond the limit line limit.
Casing in which the oil is stored in the inner space;

A drive motor provided in the inner space of the casing;

A rotating shaft coupled to the drive motor;

A frame provided below the drive motor;

A first scroll provided at a lower side of the frame and having a first wrap formed at one side thereof, a bearing hole through which the rotating shaft penetrates at a central portion thereof, and a discharge hole formed at a periphery of the bearing hole; And

A second lap is formed to engage the first lap, the rotation axis is eccentrically coupled so as to radially overlap the second lap, and is compressed between the first lap while pivoting with respect to the first scroll. A second scroll forming a thread;

It is provided between the frame and the second scroll and separates the interval between the frame and the second scroll into an inner interval on the central side and an outer interval on the edge side, oil sucked through the rotating shaft flows into the inner interval and back pressure Includes; sealing member to form a seal,

The first lap is a stiffness coefficient defined by multiplying the average lap height by the average lap thickness from the end of the side adjacent to the outlet to the first point, and multiplying this value by the reciprocal of the average lap curvature radius by an arbitrary value of 1000 mm. Scroll compressor, characterized in that formed so that the limit is 5 or more.
The method of claim 10,

And a limit range of the stiffness coefficient is greater than or equal to the limit line limit range defined by [(0.0001 to 0.0003) x lap load (N) + (7.0000 to 8.0000)].
The method of claim 11,

The limit line limit range is defined as [0.0002 × lap load (N) + 7.5202] scroll compressor.
The method of claim 10,

When the center side of the first lap is called an ejection end and the ejection end is 0 ° based on the rotation angle of the rotation shaft,

The first point is a scroll compressor, characterized in that any point within the range of 0 ~ 60 ° based on the rotation angle of the rotary shaft.
The method of claim 10,

One side of the rotating shaft coupling portion is formed with an arc compression surface,

A recess is formed in the section between the arc compression surface and the outer surface of the rotating shaft coupling portion to reduce the thickness of the second wrap, and in a section near the discharge end of the first wrap to engage the recess of the second wrap. Protrusions are formed,

At least a portion of the section in which the protrusion is formed is characterized in that the scroll compressor is formed to satisfy the limit of the stiffness coefficient.