KR102318124B1 - Scroll compressor - Google Patents

Abstract

A scroll compressor according to the present invention includes a first end plate in which a bearing hole through which a rotating shaft passes and a discharge port is formed around the bearing hole, and a first wrap protruding from one side of the first end plate a first scroll to; and a second end plate in which a rotating shaft coupling portion is formed so that the rotating shaft passing through the bearing hole of the first scroll is eccentrically coupled to the central portion, the second end plate is formed protruding from one side of the second end plate, and is engaged with the first lap to form a compression chamber together a second scroll including a second lap forming; wherein the first lap has a limiting range of stiffness coefficient defined as a reciprocal of a lap height divided by a lap thickness, and the value multiplied by a radius of curvature of the first lap. By forming it to be 0.005 mm or more, it is possible to suppress the deformation of the lap to prevent friction loss and abrasion and to prevent breakage of the lap.

Description

Scroll Compressor {SCROLL COMPRESSOR}

The present invention relates to a scroll compressor, and more particularly, to a compressor in which a compression unit is located below a transmission unit.

A scroll compressor is a compressor that engages with a plurality of scrolls and performs a relative rotational motion while forming a compression chamber composed of a suction chamber, an intermediate pressure chamber, and a discharge chamber between both scrolls. Such a scroll compressor can obtain a relatively high compression ratio compared to other types of compressors, and a stable torque can be obtained by smoothly performing refrigerant suction, compression, and discharge strokes. Accordingly, scroll compressors are widely used for refrigerant compression in air conditioners and the like. Recently, a high-efficiency scroll compressor with an operating speed of 180 Hz or higher by reducing the eccentric load has been introduced.

The scroll compressor may be divided 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 communicates directly with a compression chamber. Accordingly, the low-pressure type driving part is installed in the suction space of the low-pressure part, whereas the high-pressure type driving part is installed in the discharge space of the high-pressure part.

Such a scroll compressor can be divided into an upper compression type and a lower compression type depending on the positions of the driving unit and the compression unit. When the compression unit is located above the driving unit, it is called an upper compression type. On the contrary, when the compression unit is located below the driving unit, it is called a bottom compression type.

In a scroll compressor, as the pressure in the compression chamber increases, the orbiting scroll receives a gas force in a direction away from the fixed scroll. Then, as the orbiting scroll moves away from the fixed scroll, leakage between the compression chambers occurs and the compression loss increases.

In consideration of this, in the scroll compressor, a tip seal method of inserting a sealing member into the front end surfaces of the fixed wrap and the orbiting wrap is applied, or a back pressure chamber forming an intermediate pressure or a discharge pressure is formed on the rear surface of the orbiting scroll or the fixed scroll to form the back pressure chamber. The back pressure method is applied in which the orbiting scroll or the fixed scroll is pressurized by the opposing scroll with the pressure of

In particular, in the back pressure method, a method is known in which a sealing member is installed between the rear surface of the orbiting scroll (or the rear surface of the fixed scroll) and a frame corresponding thereto so that a back pressure chamber is formed inside or outside the sealing member. In the back pressure method using such a sealing member, an annular groove is formed in one member constituting the thrust surface, and an annular sealing member having a square cross-section is inserted into the annular groove. Then, the medium pressure refrigerant compressed in the compression chamber during operation of the compressor flows into the annular groove, and the sealing member is lifted up by the intermediate pressure pressure and is in close contact with the opposing member, thereby forming a back pressure chamber.

However, in the conventional scroll compressor as described above, as the discharge port is formed in the central portion of the fixed scroll, the back pressure and gas force applied to the central portion of the fixed lap and the orbiting lap are greater than the back pressure and gas force received by the edge portion. The central portion of the wrap or the orbiting wrap is deformed while being bent toward the edge, so that severe friction loss or wear occurs between the fixed wrap or the orbiting wrap and the scroll facing it, thereby reducing compressor efficiency.

Also, in the conventional scroll compressor as described above, in the case of a so-called through-axis scroll compressor in which the rotary shaft overlaps the compression chamber in the radial direction, the rotary shaft penetrates and engages the central portion of the fixed scroll, so that the discharge end of the fixed wrap is connected to the rotary shaft. This could not extend to the center of the fixed scroll sufficiently, and thus the rigidity of the discharge end of the fixed lap was weakened, so that the fixed lap was severely bent or the discharge end of the fixed lap was broken. Furthermore, as disclosed in Korean Patent Registration No. 10-1059880, when the compression ratio of the compression chamber is increased by changing the fixed wrap and the orbiting wrap to an atypical shape, the discharge end of the fixed wrap is more severely deformed and damaged. In this case, even when the lap support force is increased by forming a protrusion at the discharge end of the fixed lap, the lap deformation due to the increase in the compression ratio cannot be completely suppressed, and the reliability of the compressor may be lowered due to friction loss or wear or rupture of the lap.

In addition, in the conventional scroll compressor as described above, as disclosed in Japanese Patent Laid-Open No. 2000-257573, deformation or breakage of the wrap (particularly, the fixed wrap) is suppressed by changing the shape of the wrap. However, when the root of the lap is thickly formed in this way, the same groove must be formed at the lap tip of the scroll facing each other to make the manufacturing process of the lap more complicated, and the lap thickness from the middle of the lap to the lap tip becomes thin. There was a limit that could not solve the problem of deformation or breakage.

In addition, in consideration of this, when the overall thickness of the wrap is formed to be thick, the size of the scroll is increased to secure the turning radius, thereby increasing the size of the compressor, or conversely, the turning radius may decrease and thus the volume of the compression chamber may be reduced. This can be considered to have occurred as the lap shape was arbitrarily changed without specific consideration of the lap stiffness.

Korean Patent No. 10-1059880 Japanese Publication No. 2000-257573

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor capable of preventing friction loss or wear while optimizing the rigidity of the discharge end of the lap and excessively close contact with the head plate of the scroll facing the discharge end of the lap.

Another object of the present invention is to provide a scroll compressor capable of suppressing fracture while excessively deforming the vicinity of the discharge end of the lap by optimizing the rigidity of the discharge end of the lap.

In addition, another object of the present invention is to optimize the rigidity of the discharge end of the fixed wrap even when the rotating shaft passes through the fixed scroll and overlaps the compression chamber in the radial direction to prevent excessive deformation or breakage of the discharge end of the fixed wrap. It is intended to provide a scroll compressor capable of increasing the efficiency and reliability of the compressor through this.

In order to achieve the object of the present invention, there can be provided a scroll compressor capable of preventing the wrap from being excessively deformed or broken by optimizing the rigidity of the discharge side of the wrap formed on one of the two members that slide with each other. .

Here, the stiffness of the wrap may limit the range of the stiffness coefficient defined based on the height and thickness of the wrap and the radius of curvature.

And, the stiffness coefficient may be determined by the lap load + option value by the inclination of the lap × the gas force.

In addition, in order to achieve the object of the present invention, a first lap having a discharge end at the center and a suction end at the edge, each 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, respectively, a plurality of curves are connected from the discharge end to the suction end, and a rotating shaft coupling portion is formed at the discharge end so that the rotating shaft overlaps with the first wrap and is coupled a second wrap formed and engaged with the first wrap to form a compression chamber moving toward the center together with the first wrap while rotating with respect to the first wrap; including, the first wrap and the second wrap For a specific section of at least one lap among the laps, a first value is obtained by dividing the average height of the lap in the specific section by the average thickness of the lap, and a second value is obtained by multiplying the first value by the average radius of curvature of the lap, A scroll compressor may be provided, characterized in that it is formed using a stiffness coefficient defined as a reciprocal to the second value.

Here, the stiffness coefficient limit range may be formed to be greater than or equal to the limit line limit range defined by [(0.0001 to 0.0003) × lap load (N) + (7.0000 to 8.0000)].

And, the limit line limit range may be defined as [0.0002 × lap load (N) + 7.5202].

And, when the center side of the first wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 0°, the specific section is in the 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 part, and a concave portion for decreasing the thickness of the second wrap is formed in a section between the arc compression surface and the outer surface of the rotation shaft coupling part, and the first wrap is discharged. A protrusion may be formed in a section near the end to engage the concave portion 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, a first end plate portion in which a bearing hole through which the rotation shaft passes is formed in the center and a discharge port is formed around the bearing hole, and a first protruding portion formed on one side of the first end plate portion a first scroll comprising a wrap; and a second end plate in which a rotating shaft coupling portion is formed so that a rotating shaft passing through the bearing hole of the first scroll is eccentrically coupled to the central portion, and is formed to protrude from one side of the second end plate and engage with the first lap to form a compression chamber together. a second scroll including a second lap forming; wherein the first lap has a limiting range of stiffness coefficient defined as a reciprocal of a lap height divided by a lap thickness, and the value multiplied by a radius of curvature of the first lap. A scroll compressor may be provided, characterized in that it is formed to be 0.005 mm or more.

Here, the stiffness coefficient limiting range is defined for a section between any two points along the traveling direction of the lap in the first lap, and the lap height, lap thickness, and lap curvature radius are the average lap height and average of the lap section. It can be defined as the lap thickness, the average lap radius of curvature.

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

And, in the section from the end of the first lap adjacent to the outlet to any one point or at any one point in the section, the stiffness coefficient limiting range is [(0.0001 to 0.0003) × lap load (N) + (7.0000). ~ 8.0000)] and may be formed beyond the limit line limit.

In addition, in order to achieve the object of the present invention, a casing in which oil is stored in the inner space; a driving motor provided in the inner space of the casing; a rotating shaft coupled to the driving motor; a frame provided under the driving motor; a first scroll provided under the frame, having a first wrap formed on one side thereof, a bearing hole through which the rotation shaft passes, and a discharge port formed around the bearing hole; and a second wrap engaged with the first wrap is formed, the rotation axis is eccentrically coupled to overlap the second wrap in a radial direction, and a pivoting motion with respect to the first scroll is formed between the first scroll and the first scroll. a second scroll forming a compression chamber; It is provided between the frame and the second scroll to separate the interval between the frame and the second scroll into an inner space on the center side and an outer space on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure a sealing member for forming a seal, wherein the first lap divides the average lap height from the end adjacent to the outlet to the first point by the average lap thickness, and multiplies this value by the average lap radius of curvature. A scroll compressor may be provided, characterized in that it is formed such that the limiting range of the stiffness coefficient defined by multiplying the reciprocal by an arbitrary value of 1000 mm is 5 or more.

Here, the stiffness coefficient limit range may be formed to be greater than or equal to the limit line limit range defined by [(0.0001 to 0.0003) × lap load (N) + (7.0000 to 8.0000)].

And, the limit line limit range may be defined as [0.0002 × lap load (N) + 7.5202].

And, when the center side of the first wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 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 part, and a concave portion for decreasing the thickness of the second wrap is formed in a section between the arc compression surface and the outer surface of the rotation shaft coupling part, and the first wrap is discharged. A protrusion may be formed in a section near the end to engage the concave portion of the second lap, and at least a portion of the section in which the protrusion is formed may be formed to satisfy the rigidity coefficient limitation range.

The scroll compressor according to the present invention is formed by optimizing the lap rigidity of the portion adjacent to the discharge end of the fixed lap or the orbiting lap, thereby minimizing lap deformation of the discharging end at the center side receiving relatively high back pressure and gas force. It is possible to prevent excessive contact with the opposing scrolls, thereby reducing friction loss or abrasion between the scrolls, thereby increasing compressor efficiency.

In addition, by optimizing and forming the lap rigidity of the portion adjacent to the discharge end of the fixed lap or the orbiting lap, it is possible to suppress the discharge end of the fixed lap or the orbiting lap from being bent and deformed in the radial direction toward the outside. Through this, it is possible to increase the compressor efficiency by suppressing leakage from the compression chamber, and at the same time to suppress the breakage of the wrap, thereby increasing the reliability of the compressor.

In addition, even when the discharge end of the fixed lap is located far from the center of the fixed scroll because the rotating shaft passes through the center of the fixed scroll, the lap rigidity in the portion adjacent to the discharge end is optimized, thereby preventing friction or wear between the fixed lap and the scroll. It is possible to increase the efficiency and reliability of the compressor by preventing deformation or breakage of the fixed wrap.

1 is a longitudinal cross-sectional view showing a lower compression type scroll compressor according to the present invention;
2 is a cross-sectional view showing the compression part in FIG. 1;
Figure 3 is a front view showing a part of the rotation shaft to explain the sliding part in Figure 1,
4 is a longitudinal sectional view showing the oil supply passage between the back pressure chamber and the compression chamber in FIG. 1;
5 is a schematic diagram showing the amount of deformation in the vicinity of the discharge end of the first lap in the scroll compressor according to FIG. 1 analyzed for each part;
6 is a schematic view showing the shape of the wrap in the portion with the largest amount of deformation in FIG. 5 from the front;
7 is a schematic diagram showing the specification for the discharge end of the lap according to the present embodiment;
8 is a graph analyzing the amount of lap deformation according to various specifications and operating speed for the first lap;
9 is a cross-sectional view showing the amount of deformation with respect to the discharge end of the lap having a limited range of the stiffness coefficient of the lap according to the present embodiment compared with the prior art.

Hereinafter, a scroll compressor according to the present invention will be described in detail based on an embodiment shown in the accompanying drawings. However, hereinafter, for convenience, in a lower compression type scroll compressor in which the compression part is located below the transmission part, a scroll compressor of a type in which the rotation shaft overlaps on the same plane as the orbiting wrap will be described as a representative example. This type of scroll compressor is known to be suitable for application to a refrigeration cycle under high-temperature and high-compression ratio conditions.

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

Referring to FIG. 1 , in the lower compression scroll compressor according to the present embodiment, an electric part 20 that forms a driving motor and generates a rotational force is installed inside the casing 10 , and the lower side of the electric part 20 is A compression unit 30 for compressing the refrigerant by receiving the rotational force of the electric part 20 with a predetermined space (hereinafter, referred to as an intermediate space) 10a may be installed.

The casing 10 includes a cylindrical shell 11 constituting an airtight container, an upper shell 12 that covers the upper portion of the cylindrical shell 11 to form an airtight container, and a lower portion of the cylindrical shell 11 to form an airtight container together. At the same time, it may be formed of a lower shell 13 forming a storage space 10c.

The refrigerant suction pipe 15 penetrates through the side of the cylindrical shell 11 to directly communicate with the suction chamber of the compression unit 30, and the upper portion of the upper shell 12 communicates with the upper space 10b of the casing 10 A refrigerant discharge pipe 16 may be installed. The refrigerant discharge pipe 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 is 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. And in some cases, an oil separator (not shown) that separates oil mixed with the refrigerant is installed in the inside of the casing 10 including the upper space 10b or in the upper space 10b by connecting to the refrigerant suction pipe 16. can be

The electric part 20 includes a stator 21 and a rotor 22 rotating inside the stator 21 . The stator 21 has teeth and slots forming a plurality of coil winding parts (unsigned) along the circumferential direction on its inner circumferential surface, so that the coil 250 is wound, and between the inner circumferential surface of the stator and the outer circumferential surface of the rotor 22 . _{A second refrigerant passage P G2} is formed by combining the gap and the coil winding portion. Accordingly, the refrigerant discharged to 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 a second refrigerant passage formed in the transmission unit 20 (} P _G2 ) is moved to the upper space (10b) formed on the upper side of the transmission unit (20).

And a plurality of decut (D-cut) surfaces 21a are formed on the outer peripheral surface of the stator 21 in the circumferential direction, and the decut surfaces 21a are formed so that oil passes between the inner peripheral surface of the cylindrical shell 11 and the inner peripheral surface of the cylindrical shell 11. One oil passage P _O1 may be formed. Accordingly, the oil separated from the refrigerant in the upper space 10b moves to the lower space 10c through _{the first oil passage P O1} and the second oil passage P _{O2 to be described later.}

On the lower side of the stator 21 , a frame 31 constituting the compression part 30 at a predetermined interval may be fixedly coupled to the inner circumferential surface of the casing 10 . The frame 31 may be fixedly coupled to the outer circumferential surface by shrink-fitting or welding the outer circumferential surface to the inner circumferential surface of the cylindrical shell 11 .

And an annular frame side wall part (first side wall part) 311 is formed at the edge of the frame 31, and a plurality of communication grooves 311b are formed on the outer peripheral surface of the first side wall part 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 to be described later.

In addition, a first bearing portion 312 for supporting the main bearing portion 51 of the rotation shaft 50 to be described later is formed in the center of the frame 31 , and the main bearing portion of the rotation shaft 50 is formed in the first bearing portion. The first bearing hole 312a may be formed through in the axial direction so that the 51 is rotatably inserted and 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 an orbiting scroll (hereinafter, referred to as a second scroll) 33 eccentrically coupled to the rotating shaft 50 therebetween. The first scroll 32 may be fixedly coupled to the frame 31 , or may be coupled to be movable in the axial direction.

Meanwhile, in the first scroll 32 , a fixed end plate portion (hereinafter, referred to as a first end plate portion) 321 is formed in a substantially disk shape, and the edge of the first end plate portion 321 is coupled to the lower surface edge of the frame 31 . A scroll sidewall portion (hereinafter, referred to as a second sidewall portion) 322 may be formed.

A suction port 324 through which the refrigerant suction pipe 15 and the suction chamber communicate is formed through one side of the second side wall portion 322, and the central portion of the first end plate portion 321 communicates with the discharge chamber to discharge the compressed refrigerant. Discharge holes 325a and 325b may be formed. Only one discharge port 325a and 325b may be formed to communicate with both the first and second compression chambers V1 and V2, which will be described later, but are independent of each of the compression chambers V1 and V2. A plurality may be formed to communicate with the .

And the communication groove 322b described above is formed on the outer circumferential surface of the second side wall part 322, and the communication groove 322b is the communication groove 311b of the first side wall part 311 and the oil recovered together with the lower space. _{A second oil passage P O2} for guiding to (10c) is formed.

Also, a discharge cover 34 for guiding the refrigerant discharged from the compression chamber V to a refrigerant passage to be described later may be coupled to the lower side of the first scroll 32 . The discharge cover 34 has an inner space that accommodates the discharge ports 325a and 325b, and at the same time receives the refrigerant discharged from the compression chamber V through the discharge ports 325a and 325b in the upper space of the casing 10 ( 10b), more precisely, it may be formed to accommodate the inlet of _{the first refrigerant passage P G1} guiding into the space between the transmission unit 20 and the compression unit 30 .

Here, the first refrigerant flow path ( _PG1 ) is the inside of the flow path separation unit 40, that is, the second side wall portion 322 of the fixed scroll 32 on the inner side of the flow path separation unit 40 from the side of the rotation shaft 50 side. and the first sidewall portion 311 of the frame 31 may be sequentially formed. Accordingly, on the outside of the flow path separation unit 40 , the above-described second oil flow path P _O2 is formed to communicate with the first oil flow _{path P O1 .}

And on the upper surface of the first end plate portion 321, a fixed wrap (hereinafter, referred to as a first wrap) 323 may be formed in engagement with a turning wrap (hereinafter, referred to as a second wrap) 33 to be described later to form a compression chamber V. have. The first wrap 323 will be described later along with the second wrap 332 .

In addition, a second bearing part 326 for supporting a sub-bearing part 52 of the rotation shaft 50 to be described later is formed in the center of the first head plate part 321 , and the second bearing part 326 is provided in the axial direction. A second bearing hole 326a may be formed therethrough to support the sub-bearing part 52 in a radial direction.

Meanwhile, in the second scroll 33 , the orbiting end plate portion (hereinafter, referred to as the second end plate portion) 331 may be formed in a substantially disk shape. A second wrap 332 may be formed on a lower surface of the second end plate 331 to be engaged with the first wrap 322 to form a compression chamber.

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 shown in FIG. 2 , the second wrap 332 has a shape in which a plurality of arcs having different diameters and origins are connected, and the outermost curve may be formed in an approximately elliptical shape having a major axis and a minor axis. . The first wrap 323 may likewise be formed.

In the central portion of the second end plate 331, the inner end of the second wrap 332 is formed, and an eccentric portion 53 of the rotation shaft 50, which will be described later, is rotatably inserted and coupled to the rotation shaft coupling portion 333. direction may be formed through.

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

In addition, the rotation shaft coupling portion 333 is formed to have a height overlapping with the second wrap 332 on the same plane, so that the eccentric portion 53 of the rotation shaft 50 overlaps with the second wrap 332 on the same plane. can be placed in Through this, the repulsive force and the compressive force of the refrigerant are applied to the same plane with respect to the second end plate and cancel each other out, so that the inclination of the second scroll 33 due to the action of the compressive force and the repulsive force can be prevented.

In addition, the rotation shaft coupling portion 333 has a concave portion 335 engaged with the protrusion 328 of the first wrap 323 to be described later is formed on an outer peripheral portion opposite to the inner end of the first wrap 323 . One side of the concave portion 335 is formed with an increasing portion 335a increasing in thickness from the inner periphery to the outer periphery of the rotary shaft coupling portion 333 on the upstream side along the formation direction of the compression chamber V. This lengthens the compression path of the first compression chamber V1 just before discharge, and consequently makes it possible to increase the compression ratio of the first compression chamber V1 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 , and will be described later separately from the second compression chamber V2 .

The other side of the concave portion 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 inner end thickness (ie, the thickness of the discharge end) of the first wrap 323 and the turning radius of the second wrap 332 , the inner side of the first wrap 323 . When the end thickness is increased, the diameter of the arc compression surface 335b is increased. Due to this, 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 lengthened so that the compression ratio of the second compression chamber V2 may be increased accordingly.

In addition, in the vicinity of the inner end (suction end or start end) of the first wrap 323 corresponding to the rotation shaft coupling portion 333, a projection 328 protruding toward the outer periphery of the rotation shaft coupling portion 333 is formed, the projection ( A contact portion 328a that protrudes from the protrusion and engages with the concave portion 335 may be formed in the 328 . That is, the inner end of the first wrap 323 may be formed to have a greater thickness than other portions. Due to this, the lap strength of the inner end that receives the greatest compressive force among the first laps 323 may be improved, and thus durability may be improved.

Meanwhile, the compression chamber V is formed between the first end plate portion 321 and the first wrap 323 , and between the second wrap 332 and the second end plate portion 331 , and is sucked along the moving direction of the wrap. The chamber, the intermediate pressure chamber, and the discharge chamber may be continuously formed.

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

That is, the first compression chamber (V1) includes a compression chamber formed between the two contact points (P11, P12) formed by contacting the inner surface of the first wrap 323 and the outer surface of the second wrap 332, and , the second compression chamber (V2) includes a compression chamber formed between the two contact points (P21, P22) generated 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) just before the discharge is the center of the eccentric, that is, the center of the rotation shaft coupling portion (O) and the two lines connecting the two contact points (P11, P12), respectively, the angle having a larger value among the angles When α is α, α < 360° at least immediately before the start of discharge, and the distance ℓ between the normal vectors at the two contact points P11 and P12 also has a value greater than 0.

Due to this, since the first compression chamber immediately before discharge has a smaller volume compared to the case in which the fixed lap and the orbital lap made of the involute curve have a smaller volume, the sizes of the first lap 323 and the second lap 332 are not increased. Both the compression ratio of the first compression chamber V1 and the compression ratio of the second compression chamber V2 may be improved without the need to do so.

Meanwhile, as described above, the second scroll 33 may be pivotably installed between the frame 31 and the fixed scroll 32 . An Oldham ring 35 for preventing rotation of the second scroll 33 is installed between the upper surface of the second scroll 33 and the lower surface of the frame 31 corresponding thereto. A sealing member 36 forming the back pressure chamber S1 to be performed may be installed.

In addition, an intermediate pressure space is formed outside the sealing member 36 by the oil supply hole 321a provided in the second scroll 32 . This intermediate pressure space communicates with the intermediate compression chamber V and may serve as a back pressure chamber as the intermediate pressure refrigerant is filled. Accordingly, the back pressure chamber formed inside the sealing member 36 as the center may be referred to as a first back pressure chamber S1 , and the intermediate pressure space formed outside the sealing member 36 may be referred to as a second back pressure chamber S2 . After all, the back pressure chamber S1 is a space formed by the lower surface of the frame 31 and the upper surface of the second scroll 33 with the sealing member 36 as the center. will be explained again with

On the other hand, the flow path separation unit 40 is installed in the intermediate space 10a, which is a gas oil 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 is It serves to prevent interference with the oil moving from the upper space 10b of the electric part 20, which is the oil separation space, to the lower space 10c of the compression part 30, which is the storage space.

To this end, the flow path separation unit 40 according to the present embodiment separates the first space 10a into a space in which the refrigerant flows (hereinafter referred to as a refrigerant flow space) and a space through which oil flows (hereinafter, an oil flow space). Euro guide included. The flow guide may separate the first space 10a into a refrigerant flow space and an oil flow space with only the flow guide itself, but in some cases, a plurality of flow guides may be combined to serve as a flow guide.

The flow path separation 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 extending 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 a refrigerant flow space and an oil flow space.

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

The first flow guide 410 includes a first round wall part 411 extending upward from the outside, a second round wall part 412 extending upward from the inside, and a first round wall part 411 and a second round wall part 412 ) consists of a circular surface portion 413 extending in the radial direction to connect between. The first round wall portion 411 is formed higher than the second round wall portion 412, and the refrigerant hole is formed in the round surface portion 413 so that the refrigerant hole communicating from the compression unit 30 to the intermediate space 10a communicates. can

And, the balance weight 26 is located inside the second round wall portion 412, that is, in the direction of the rotation axis, the balance weight 26 is coupled to the rotor 22 or the rotation shaft 50 and rotates. At this time, the balance weight 26 can stir the refrigerant while rotating, but it prevents the refrigerant from moving toward the balance weight 26 by the second round wall 412 so that the refrigerant is stirred by the balance weight 26 can be suppressed

The second flow guide 420 may include a first extension portion 421 extending downwardly from the outside of the insulator and a second extension portion 422 extending downwardly from the inside of the insulator. The first extension portion 421 is formed to overlap the first round wall portion 411 in the axial direction, and serves to separate the refrigerant flow space and the oil flow space. The second extension 422 may not be formed as needed, but even if it is formed, it does not overlap with the second round wall 412 in the axial direction or is formed at a sufficient distance in the radial direction so that the refrigerant can sufficiently flow even if it overlaps. It is preferable to be

On the other hand, the upper portion of the rotation shaft 50 is coupled to the center of the rotor 22, while the lower portion is coupled to the compression unit 30 may be supported in the radial direction. As a result, the rotation shaft 50 transmits the rotational force of the transmission unit 20 to the orbiting scroll 33 of the compression unit 30 . Then, the second scroll 33 eccentrically coupled to the rotation shaft 50 rotates with respect to the first scroll 32 .

A main bearing part (hereinafter, the first bearing part) 51 is formed in the lower half of the rotation shaft 50 so as to be inserted into the first bearing hole 312a of the frame 31 and supported in the radial direction, and the first bearing part ( A sub-bearing part (hereinafter, referred to as a second bearing part) 52 may be formed at a lower side of the first scroll 32 to be inserted into the second bearing hole 326a of the first scroll 32 and supported in the radial direction. And an eccentric part 53 may be formed between the first bearing part 51 and the second bearing part 52 to be inserted into and coupled to the rotation shaft coupling part 333 .

The first bearing part 51 and the second bearing part 52 are formed on a coaxial line to have the same axial center, and the eccentric part 53 is attached to the first bearing part 51 or the second bearing part 52 . It may be formed eccentric in the radial direction with respect to the. The second bearing part 52 may be formed to be eccentric with respect to the first bearing part 51 .

The eccentric part 53 must be formed to have an outer diameter smaller than the outer diameter of the first bearing part 51 and larger than the outer diameter of the second bearing part 52 so that the rotating shaft 50 is connected to each of the bearing holes 312a and 326a. It may be advantageous for coupling through the rotation shaft coupling portion 333 . However, when the eccentric portion 53 is not integrally formed 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 . It can be coupled by inserting the rotation shaft (50).

In addition, an oil supply passage 50a for supplying oil to each bearing portion and the eccentric portion may be formed in the rotation shaft 50 along the axial direction. The oil supply passage 50a is approximately at the lower end or intermediate height of the stator 21 from the lower end of the rotary shaft 50 as the compression unit 30 is located below the transmission unit 20, or the first bearing unit 31 It can be formed by a groove digging to a position higher than the top of the . Of course, in some cases, it may be formed to pass through the rotation shaft 50 in the axial direction.

In addition, an oil feeder 60 for pumping oil filled in the lower space 10c may be coupled to a lower end of the rotation shaft 50 , that is, a lower end of the second bearing unit 52 . The oil feeder 60 is composed of an oil supply pipe 61 inserted into and coupled to the oil supply passage 50a of the rotating shaft 50, and a blocking member 62 that accommodates the oil supply pipe 61 and blocks the intrusion of foreign substances. can The oil supply pipe 61 may pass through the discharge cover 34 and be positioned so as to be submerged in the oil of the lower space 10c.

On the other hand, as shown in Fig. 3, each of the bearing parts 51 and 52 and the eccentric part 53 of the rotating shaft 50 is connected to the oil supply passage 50a to supply oil to each sliding part. A channel F1 is formed.

The sliding part oil supply passage F1 includes a plurality of oil supply holes 511, 521 and 531 that penetrate from the oil supply passage 50a toward the outer circumferential surface of the rotary shaft 50, and each bearing portion 51 and 52. and a plurality of oil supply grooves 512 (512) ( 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 is formed 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 oblique direction.

And, between the first bearing part 51 and the eccentric part 53, and between the eccentric part 53 and the second bearing part 52, the first connecting groove 541 and the second connecting groove each having an annular shape. 542 are respectively formed. The first connection groove 541 is connected to the lower end of the first oil supply groove 512 , and the second connection groove 542 is connected to the upper end of the second oil supply groove 522 . Accordingly, a portion of the oil lubricating the first bearing part 51 through the first oil supply groove 512 flows down to the first connection groove 541 and is collected, and this oil is transferred to the first back pressure chamber S1. It flows in 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 . They may be gathered and introduced into the compression unit 30 through the front end surface of the rotation shaft coupling unit 333 and the first end plate 321 .

And a small amount of oil sucked in the upper end direction of the first bearing unit 51 flows out of the bearing surface from the upper end of the first bearing unit 312 of the frame 31 and flows along the first bearing unit 312 along the frame 31 ), after flowing down to the upper surface 31a of the frame 31 (or a groove communicating from the upper surface to the outer circumferential surface) of the frame 31 and the oil passage P _O1 continuously formed on the outer peripheral surface of the first scroll 32 ) (P O1 ) (P _O2 ) through the lower space (10c) is recovered.

In addition, oil discharged from the compression chamber (V) to the upper space (10b) of the casing (10) together with the refrigerant is separated from the refrigerant in the upper space (10b) of the casing (10), on the outer peripheral surface of the electric part (20) It is recovered to the lower space 10c through the formed first oil passage P _{O1 and the second oil passage P O2} formed on the outer peripheral surface of the compression unit 30 . At this time, the flow path separation unit 40 is provided between the electric part 20 and the compression part 30, and the oil separated from the refrigerant in the upper space 10b and moved to the heart space 10c is transferred to the compression part 20 ) and does not interfere with the refrigerant moving to the upper space 10b and do not _remix , and each oil flows through different passages [(P O1 )(P _O2 )][(P _G1 )(P _G2 )] into the lower space At (10c), the refrigerant can move to the upper space (10b).

On the other hand, the compression chamber oil supply passage F2 for supplying the oil sucked through the oil supply passage 50a to the compression chamber V is formed in the second scroll 33 . 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 between the oil supply passage 50a and a second back pressure chamber S2 forming an intermediate pressure space, a second back pressure chamber S2 and It may be made of a second oil supply passage 372 communicating with the intermediate pressure chamber of the compression chamber (V).

Of course, the compression chamber oil supply passage may be formed to directly communicate 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 flow path connecting the second back pressure chamber S2 and the intermediate pressure chamber V must be separately provided, and for supplying oil to the Oldham ring 35 located in the second back pressure chamber S2. A separate oil path must be provided. As a result, the number of passages increases and processing becomes complicated. Therefore, in order to reduce the number of passages by unifying the refrigerant passage and the oil passage, as in the present embodiment, the oil supply passage 50a and the second back pressure chamber S2 are communicated, and the second back pressure chamber S2 is connected to the intermediate pressure chamber. It may be desirable to communicate with (V).

To this end, in the first oil supply passage 371 , a first turning passage portion 371a formed from the lower surface of the second end plate 331 to the middle in the thickness direction is formed, and in the first turning passage portion 371a A second turning passage part 371b is formed toward the outer circumferential surface of the second head plate part 331 , and a third turning passage part penetrating from the second turning passage part 371b toward the upper surface of the second end plate part 331 . (371c) is formed.

Further, the first turning passage portion 371a is formed at a position belonging to the first back pressure chamber S1 , and the third turning passage portion 371c is formed at a position belonging to the second back pressure chamber S2 . And a pressure reducing rod 375 in the second turning passage part 371b to lower the pressure of 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. Accordingly, the cross-sectional area of the second turning passage part 371b excluding the pressure reducing rod 375 is formed to be small in the first turning passage part 371a, the third turning passage part 371c, and the second turning passage part 371b.

Here, when the end of the third revolving passage portion 371c is formed to be located inside the Oldham ring 35, that is, between the Oldham ring 35 and the sealing member 36, the first oil supply passage 371 ), the oil moving through the Oldham ring 35 is clogged and cannot smoothly move to the second back pressure chamber S2. Accordingly, in this case, the fourth turning passage part 371d may be formed from the end of the third turning passage part 371c toward the outer peripheral surface of the second end plate part 331 . The fourth turning passage part 371d may be formed as a groove on the upper surface of the second end plate part 331 as shown in FIG. 4 , or may be formed as a hole inside the second end plate part 331 .

The second oil supply passage 372 has a first fixed passage portion 372a formed on the upper surface of the second side wall portion 322 in the thickness direction, 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 that communicates from the second fixed passage portion 372b to the intermediate pressure chamber V is formed.

In the drawings, an unexplained reference numeral 70 denotes an accumulator.

The lower compression type scroll compressor according to the present embodiment as described above operates as follows.

That is, when power is applied to the electric part 20, rotational force is generated in the rotor 21 and the rotating shaft 50 to rotate, and as the rotating shaft 50 rotates, the orbiting scroll eccentrically coupled to the rotating shaft 50 (33) is rotated by the Oldham ring (35).

Then, the refrigerant supplied from the outside of the casing 10 through the refrigerant suction pipe 15 flows into the compression chamber V, and the volume of the compression chamber V is reduced by the orbiting scroll 33's orbiting motion. As it decreases, it is compressed and discharged into the inner space of the discharge cover 34 through the discharge ports 325a and 325b.

Then, the refrigerant discharged into the inner space of the discharge cover 34 circulates in the inner space of the discharge cover 34, and after the noise is reduced, it moves to the space between the frame 31 and the stator 21, and this refrigerant is moved to the upper space of the electric part 20 through the gap between the stator 21 and the rotor 22 .

Then, after the oil is separated from the refrigerant in the upper space of the electric part 20, the refrigerant is discharged to the outside of the casing 10 through the refrigerant discharge pipe 16, while the oil is separated from the inner circumferential surface of the casing 10 and the stator ( 21) through the flow path and the flow path between the inner circumferential surface of the casing 10 and the outer circumferential surface of the compression part 30, a series of processes of recovery to the lower space 10c, which is the oil storage space of the casing 10, are repeated.

At this time, the oil in the lower space 10c is sucked through the oil supply passage 50a of the rotary shaft 50, and this oil is supplied through each oil supply hole 511, 521, 531 and oil supply groove 512, 522. ) 532 to lubricate the first bearing part 51 , the second bearing part 52 , and the eccentric part 53 , respectively.

Among them, the oil lubricating the first bearing part 51 through the first oil supply hole 511 and the first oil supply groove 512 is a first connection groove between the first bearing part 51 and the eccentric part 53 . 541, and this oil flows into the first back pressure chamber S1. This oil almost forms a discharge pressure, so that the pressure in the first back pressure chamber S1 also almost forms a discharge pressure. Accordingly, the central portion of the second scroll 33 can be supported in the axial direction by the discharge pressure.

Meanwhile, the oil in the first back pressure chamber S1 moves to the second back pressure chamber S2 through the first oil supply passage 371 due to the pressure difference with the second back pressure chamber S2 . At this time, a pressure reducing rod 375 is provided in the second swirl passage portion 371b constituting the first oil supply passage 371 , and the pressure of oil directed to the second back pressure chamber S2 is reduced to an intermediate pressure.

And, the oil moving to the second back pressure chamber (intermediate pressure space) S2 supports the edge of the second scroll 33 and at the same time, according to the pressure difference with the intermediate pressure chamber V, the second oil supply passage 372 is moved to the intermediate pressure chamber (V). However, when the pressure in the intermediate pressure chamber V becomes higher than the pressure in the second back pressure chamber S2 during the operation of the compressor, the refrigerant flows into the second back pressure chamber S2 through the second oil supply passage 372 in the intermediate pressure chamber V. ) will move towards In other words, the second oil supply passage 372 serves as a passage through which the refrigerant and the oil cross move according to the pressure difference between the pressure in the second back pressure chamber S2 and the intermediate pressure chamber V.

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

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, and the first back pressure chamber is formed between the second scroll and the frame, and the second back pressure chamber is formed between the second scroll and the frame and the first scroll, respectively. is formed

Accordingly, 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 revolving motion of the second scroll. In addition, since the sealing member seals in the axial direction while floating by pressure while being inserted into the sealing member insertion groove provided in the second scroll, it is preferable to be formed of a material and structure that can float quickly even at low pressure.

Meanwhile, as described above, as the first back pressure chamber, which is the central part of the second scroll, forms the discharge pressure, and the second back pressure chamber, which is the edge part, forms an intermediate pressure, the back pressure at the center of the second scroll, which is the orbiting scroll, increases from the edge part. A pressure higher than the back pressure of Meanwhile, the central portion of the second scroll is pressed more in the direction of the first scroll than the edge portion, and accordingly, the discharge end of the first lap positioned at the central portion of the first scroll is excessively pressed to the second end plate. At the same time, the central portion of the first wrap forms a discharge end to receive a discharge pressure, and the discharge end of the first wrap receives a strong gas force in the edge direction by the discharge pressure.

Accordingly, the discharge end of the first lap receives a pressing force from the central portion of the second scroll in the axial direction by the high back pressure of the first back pressure chamber, and at the same time receives a radial pressing force by the gas force of the discharge pressure. , as a result, the discharge end of the first lap may be bent outward from the root of the lap toward the front end of the lap, that is, in the height direction of the lap.

Such a phenomenon may seriously occur when the second bearing hole through which the rotation shaft passes 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 lap, which is a fixed lap, 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, so that the lap rigidity at the discharging end is lowered and the lap deformation increases.

And this phenomenon may occur more severely when the compression ratio is increased by changing the first wrap and the second wrap to an atypical shape as in the present embodiment. However, in this embodiment, the protrusion is formed at the discharge end of the first lap, so that the lap bearing force is improved to a certain extent. However, the lap bearing force does not increase as much as the compression ratio increases, so friction loss due to lap deformation at the discharging end of the first lap. However, there may be concerns about abrasion or rupture of the lap. FIG. 5 is a schematic view showing the amount of deformation around the discharge end of the first lap analyzed for each part to explain this, and FIG. 6 is a schematic diagram showing the shape of the wrap in the portion with the greatest amount of deformation in FIG. 5 from the front.

As shown in FIG. 5 , in the case of the first wrap 323 , the amount of deformation at the discharge end 323a is the largest by about 0.018 mm to 0.02 mm, and the amount of deformation gradually decreases from the discharge end 323a toward the suction end. can be seen doing In addition, it can be seen that the deformation amount of the first end plate portion 321 including the vicinity of the discharge end 323a of the first wrap 323 is approximately -0.003 mm to -0.005 mm. This can be seen that the first end plate portion 321 is slightly deformed by receiving a force in the opposite direction to the deformation of the first lap 323 .

Accordingly, as shown in FIG. 6 , the front end surface around the discharge end 323a receives a gas force and is bent from the right side of the drawing, that is, from the center to the edge, and the inner edge 323a1 of the discharge end 323a is the highest point. It faces the lower surface of the second end plate 331 while forming.

At the same time, the second scroll is moved by being pressed downward in the drawing by receiving the back pressure. However, as the discharge end 323a of the first wrap 323 is bent outwardly and deformed, the upper surface 321b of the first end plate 321 and the front end surface 332c of the second wrap 332 exert a back pressure. The discharge end 323a of the first wrap 323 and the lower surface 331b of the second end plate 331 first come into contact with each other before they come into contact with each other. That is, the distance t1 between the top surface of the first end plate part 321 and the front end surface 332c of the second wrap 332 is the discharge end 323a of the first wrap 323 and the second end plate part 331 . ) is larger than the interval t2 between the lower surfaces 331b. Accordingly, in a process in which the gap t2 between the front end surface 323c of the first wrap 323 and the lower surface 331b of the second end plate 331 is removed by the back pressure, the 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 consideration of this, in this embodiment, by optimizing the lap stiffness in the vicinity of the discharge end, even if the lap receives an axial force generated by a back pressure and a radial force generated by a gas force, the lap deformation can be minimized. And, through this, it is possible to suppress friction loss or abrasion between the lap and the end plate portion, or breakage of the lap.

The first lap according to the present embodiment may be implemented as the lap stiffness in the vicinity of the discharge end is formed so that the range of the stiffness coefficient defined as follows satisfies the optimal limit line range.

That is, referring to FIG. 7 , the stiffness coefficient (A) in the vicinity of the discharge end (hereinafter, the center of the lap) for the first lap is the average height (h) of the central section of the lap as the average thickness (t) of the center section of the lap. A second value obtained by dividing the first value and multiplying the first value by the average radius of curvature (R), which is the distance between the center line of the first lap from the center of the rotation axis for the central section of the lap (ie, the center of the second bearing hole) A value is obtained, and the stiffness coefficient may be defined as the reciprocal of the second value. Here, since the height of the first lap 323 is formed such that the height of the lap gradually decreases from the suction end to the discharge end, the lap height in the central section of the lap is formed differently along the progress direction of the lap. Therefore, ideally, in order to accurately calculate the lap height in the corresponding section (lap center section), it is preferable to obtain and substitute the average lap height as described above. However, since the lap height difference is very small, it can be ignored and substituted by generalizing the lap height. And this can be substituted by generalizing the radius of curvature of the lap to the radius of curvature of the lap for the same reason. For reference, the radius of curvature of the wrap is approximately 10 to 20 mm.

That is, if we express this as Equation (1),

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

same as Here, an arbitrary value of 1000 mm can be multiplied.

However, the height and thickness of the lap can be defined as the average lap height, average lap thickness, and average radius of curvature of a certain section as described above, but in some cases, It can also be defined by lap height, lap thickness, and lap curvature radius. However, in general, it may be advantageous in terms of processing to define each element based on a certain section.

For example, in the present embodiment, if the section showing the greatest amount of lap deformation is 0 to 60° (here, 0° is the discharge end), the corresponding section is 0 to 60°, more precisely, 0 to 45°. The stiffness modulus can also be calculated using the average lap height and the average lap thickness.

Here, it is preferable that the limiting range for the stiffness coefficient (A) in the corresponding section be approximately 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 value obtained by dividing the average lap height by the average lap thickness is 10 or more, the lap height is too high compared to the lap thickness, so that the lap rigidity is very weak, and lap breakage occurs. Therefore, (h/t) is preferably formed to be 10 or less. The minimum value does not need to be limited because the greater the lap thickness compared to the lap height, the greater the stiffness.

In addition, the average radius of curvature of the lap is approximately 10 to 20 mm. Since the lap rigidity increases as the lap radius of curvature is as small as possible, there is no need to limit the case where the lap radius of curvature is small even in this case. Therefore, if the average radius of curvature of the lap is 20 mm and substituted into the above equation (1), the stiffness coefficient (A) = 1/((10) × 20). Therefore, the stiffness coefficient becomes 0.005 mm, and if this is multiplied by an arbitrary value of 1000 mm, the stiffness coefficient becomes 5. Since this corresponds to the minimum stiffness coefficient value, it is preferable to form the limiting range of the stiffness coefficient for the discharge end of the lap to be 5 or more.

In addition, it is possible to determine an appropriate lap shape of the discharge end based on this rigidity coefficient limiting range. 8 is a graph analyzing the amount of lap deformation according to various standards and operating speeds of the first lap.

As shown, in the case of model①, the lap deformation amount is 20㎛, in the case of the model②, the lap deformation amount is 31㎛, in the case of the model③, the lap deformation amount is 79㎛, in the case of the model④, the lap deformation amount is 60㎛, And in the case of model ⑤, it can be seen that the amount of lap deformation is about 67㎛.

Among these models, it can be seen that the vicinity of the discharge end of the lap is broken in Model③ and Model⑤, which have relatively large amount of lap deformation, whereas in the other models ①, ②, and ④, the vicinity of the discharge end of the lap is maintained without being damaged. Therefore, the line connecting the model ③ and the model ⑤ is defined as a limit line, and the lap stiffness can be limited based on the limit line so that the amount of lap deformation belongs to the right side.

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

Meanwhile, in the present embodiment, the stiffness coefficient limiting range for optimizing the lap stiffness in the vicinity of 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 other sections of the first lap (or the second lap), the stiffness coefficient limit range in the section may be defined according to the newly calculated limit line limit range.

As described above, by optimizing and forming the lap rigidity of a portion adjacent to the discharge end of the first lap (or second lap), the center side discharge end receives a relatively high back pressure and gas force (and centrifugal force) as shown in FIG. 9 . can be minimized compared to the conventional (dotted line), and through this, the first wrap 323 is prevented from excessively adhering toward the second end plate 331 of the second scroll 33 facing each other. It is possible to increase compressor efficiency by reducing friction loss or wear between the first lap 323 and the second end plate portion 331 (or between the second lap and the first end plate portion).

In addition, by optimizing and forming the lap rigidity of the portion adjacent to the discharge end of the first lap 323 (or second lap), the central discharge end of the first lap 323 (or second lap) faces outward. It is possible to suppress deformation by bending radially toward the direction, thereby increasing compressor efficiency by suppressing leakage between the compression chambers V1 and V2, and at the same time suppressing breakage of the discharge end of the lap, thereby increasing the reliability of the compressor. .

In addition, even when the discharging end of the first wrap 323 is located far from the center of the first scroll 32 because the rotation shaft 50 passes through the center of the first scroll 32 , the wrap at a portion adjacent to the discharging end By optimizing the rigidity, friction or abrasion between the first wrap 323 (or the second wrap) and the corresponding second end plate 331 is prevented, or deformation or breakage of the fixed wrap is prevented, thereby increasing the efficiency and reliability of the compressor. can

10: casing 20: electric part
30: compression unit 31: frame
32: first scroll 323: first lap
323a: discharge end 33: second scroll
332: second lap 40: flow path separation unit
50: rotation shaft 50a: oil supply passage
51: first bearing part 52: second bearing part
53: eccentric part 60: oil feeder
70: accumulator S1: first back pressure chamber
S2: second back pressure chamber V: compression chamber

Claims (14)

a casing in which oil is stored in the inner space;
a driving motor provided in the inner space of the casing;
a rotating shaft coupled to the driving motor;
a frame provided under the driving motor;
a first scroll having a discharge end at the center and a suction end at the edge, each having a first wrap formed by connecting a plurality of curves from the discharge end to the suction end; and
The center has a discharge end and the edge has a suction end, respectively, a plurality of curves are connected from the discharge end to the suction end, and a rotation shaft coupling portion is formed at the discharge end so that the rotation shaft overlaps with the first wrap and is coupled. a second scroll having a second wrap engaged with the first wrap and forming a compression chamber moving toward the center together with the first wrap while performing a pivoting motion with respect to the first wrap; and
It is provided between the frame and the second scroll to separate the gap between the frame and the second scroll into an inner gap on the center side and an outer gap on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure a sealing member for forming a seal;
A first oil supply passage communicating between the inner gap and the outer gap is formed in the second scroll or the frame, and a second oil supply passage communicating between the outer gap and the compression chamber is formed in the first scroll,
A specific section of at least one of the first lap and the second lap includes:
A first value is obtained by dividing the average height of the lap in the specific section by the average thickness of the lap, a second value is obtained by multiplying the first value by the average radius of curvature of the lap, and the stiffness defined as a reciprocal of the second value A scroll compressor, characterized in that it is formed using a coefficient. According to claim 1,
The scroll compressor, characterized in that the stiffness coefficient limiting range is formed to be 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)]. 3. The method of claim 2,
The scroll compressor, characterized in that the limit line limit range is defined as [0.0002 × lap load (N) + 7.5202]. 3. The method of claim 2,
When the central portion of the first wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 0°,
The specific section is a scroll compressor, characterized in that the range of 0 ~ 45 ° with respect to the rotation angle of the rotation shaft. 5. The method according to any one of claims 1 to 4,
An arc compression surface is formed on one side of the rotating shaft coupling part,
A concave portion for decreasing the thickness of the second lap is formed in a section between the arc compression surface and the outer surface of the rotating shaft coupling portion, and in a section near the discharge end of the first lap to engage the concave portion of the second lap A protrusion is formed,
At least a portion of the section in which the protrusion is formed is formed to satisfy the range of the stiffness coefficient. a casing in which oil is stored in the inner space;
a driving motor provided in the inner space of the casing;
a rotating shaft coupled to the driving motor;
a frame provided under the driving motor;
a first scroll including a first end plate in which a bearing hole through which a rotation shaft passes and a discharge port is formed around the bearing hole, and a first wrap protruding from one side of the first end plate;
A second end plate portion having a rotation shaft coupling portion formed thereon so that a rotation shaft passing through the bearing hole of the first scroll is eccentrically coupled to the central portion, and formed to protrude from one side of the second end plate portion and engage with the first lap to form a compression chamber together a second scroll comprising a second wrap; and
It is provided between the frame and the second scroll to separate the interval between the frame and the second scroll into an inner space on the center side and an outer space on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure a sealing member for forming a seal;
A first oil supply passage communicating between the inner gap and the outer gap is formed in the second scroll or the frame, and a second oil supply passage communicating between the outer gap and the compression chamber is formed in the first scroll,
The first lap is formed such that the limiting range of the stiffness coefficient is 0.005 mm or more,
The limiting range of the stiffness coefficient is defined as a reciprocal number obtained by multiplying a value obtained by dividing a lap height by a lap thickness by a radius of curvature of the first lap. 7. The method of claim 6,
The stiffness coefficient limiting range is defined for a section between any two points along the traveling direction of the lap in the first lap,
The lap height, lap thickness, and lap radius of curvature are defined as an average lap height, average lap thickness, and average lap radius of curvature of a corresponding section. 7. The method of claim 6,
The stiffness coefficient limiting range is defined for any one point in the first lap,
The lap height, lap thickness, and lap radius of curvature are defined by the lap height, lap thickness, and lap radius of curvature at the corresponding point. 9. The method of claim 7 or 8,
In the section from the end of the first lap adjacent to the outlet to a point or at any point in the section, the stiffness coefficient limiting range is [(0.0001 to 0.0003) × lap load (N) + (7.0000 to 8.0000)], a scroll compressor characterized in that it is formed beyond the limit line limit. a casing in which oil is stored in the inner space;
a driving motor provided in the inner space of the casing;
a rotating shaft coupled to the driving motor;
a frame provided under the driving motor;
a first scroll provided under the frame, having a first wrap formed on one side thereof, a bearing hole through which the rotation shaft passes, and a discharge port formed around the bearing hole; and
A second wrap that engages with the first wrap is formed, and a rotary shaft coupling portion is formed in the center so that the rotary shaft is eccentrically coupled with the second wrap in a radial direction. a second scroll forming a compression chamber between the first scroll and the scroll;
It is provided between the frame and the second scroll to separate the gap between the frame and the second scroll into an inner gap on the center side and an outer gap on the edge side, and the oil sucked through the rotation shaft flows into the inner gap and back pressure Including; sealing member to form a seal;
A first oil supply passage communicating between the inner gap and the outer gap is formed in the second scroll or the frame, and a second oil supply passage communicating between the outer gap and the compression chamber is formed in the first scroll,
The first lap is formed such that the limiting range of the stiffness coefficient from the end of the side adjacent to the outlet to the first point is 5 or more,
The limiting range of the stiffness coefficient is defined by multiplying a reciprocal of a value obtained by dividing an average lap height by an average lap thickness by an average lap radius of curvature by 1000 mm. 11. The method of claim 10,
The scroll compressor, characterized in that the stiffness coefficient limiting range is formed to be 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)]. 12. The method of claim 11,
The scroll compressor, characterized in that the limit line limit range is defined as [0.0002 × lap load (N) + 7.5202]. 11. The method of claim 10,
When the central portion of the first wrap is referred to as a discharge end based on the rotation angle of the rotation shaft, and the discharge end is 0°,
The first point is a scroll compressor, characterized in that any one point within the range of 0 to 60 ° with respect to the rotation angle of the rotation shaft. 11. The method of claim 10,
An arc compression surface is formed on one side of the rotating shaft coupling part,
A concave portion for decreasing the thickness of the second lap is formed in a section between the arc compression surface and the outer surface of the rotating shaft coupling portion, and in a section near the discharge end of the first lap to engage the concave portion of the second lap A protrusion is formed,
At least a part of the section in which the protrusion is formed is formed to satisfy the rigidity coefficient limitation range.

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