KR20180124637A - Scroll compressor - Google Patents

Abstract

A scroll compressor includes: a driving motor including a stator fixed to an interior space of a casing and a rotor rotated in the interior of the stator and having an inner passage and an outer passage that extend axially; a rotary shaft coupled to the rotor of the driving motor to be rotated; a compression part including a first scroll provided on the lower side of the driving motor, and a second scroll coupled to the first scroll to form a compression chamber, in which the rotary shaft is eccentrically coupled to overlap the compressor chamber radially, and configured such that a refrigerant compressed by the compression chamber is discharged toward an interior space of the casing while the second scroll pivots with respect to the first scroll; a discharge pipe communicating with an upper space formed on the upper side of the driving motor in the interior space of the casing; and an oil separating unit provided in an upper space of the casing and configured to separate oil from a refrigerant before the refrigerant is discharged to the discharge pipe, and the oil separating unit includes: a porous member contacting the refrigerant in the upper space and configured to separate the oil from the refrigerant; and a heat emitting member provided to transfer heat to the porous member. Accordingly, the amount of oil discharged together with the refrigerant may be minimized.

Description

[0001] SCROLL COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly to a compressor in which a compression portion is located at a lower side of a transmission portion.

The scroll compressor is a compressor that engages with a plurality of scrolls to perform a relative orbiting motion and forms a compression chamber formed 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 as compared with other types of compressors, smoothly connecting suction, compression, and discharge strokes of the refrigerant, thereby obtaining stable torque. Therefore, the scroll compressor is widely used for refrigerant compression in an air conditioner or the like. Recently, a high-efficiency scroll compressor having an eccentric load lowered and an operation speed of 180 Hz or higher has been introduced.

The scroll compressor can be divided into a low-pressure type in which the suction pipe communicates with the internal space of the casing constituting the low-pressure portion, and a high-pressure type in which the suction pipe is in direct communication with the compression chamber. Accordingly, in the low-pressure type, the electric section is installed in the suction space which is the low-pressure section, while the high-pressure type is installed in the discharge space which is the high-

Such a scroll compressor may be classified into an upper compression type and a lower compression type depending on the positions of the driving portion and the compression portion. The upper compression type is a method in which the compression portion is located above the transmission portion, and the lower compression type is a method in which the compression portion is located below the transmission portion.

Generally, the compressor including the high-pressure scroll compressor is disposed away from the compression section so that the oil can be separated from the refrigerant in the internal space of the casing. Therefore, in the high pressure type scroll compressor of the upper compression type, the discharge tube is located between the driving portion and the compression portion, while in the lower compression type high pressure type scroll compressor, the discharge tube is located above the driving portion.

Accordingly, the refrigerant discharged from the compression section moves toward the discharge tube in the intermediate space between the transmission section and the compression section without moving to the transmission section. On the other hand, the lower compression type compressor moves the refrigerant discharged from the compression section toward the discharge tube in the oil separation space formed on the upper side of the transmission section after passing through the transmission section.

At this time, the oil separated from the refrigerant in the upper space, which is the oil separation space, passes through the transmission portion and moves to the oil storage space formed below the compression portion, and the refrigerant discharged from the compression portion also passes through the transmission portion and moves toward the oil separation space do.

However, in the conventional lower compression scroll compressor as described above, the refrigerant and oil moving to the upper space discharged from the compression unit are separated from the refrigerant while circulating in the space above, and the separated refrigerant is discharged through the discharge pipe, The oil is discharged to the outside while the oil is recovered to the lower space. However, the oil moving to the actual upper space is not sufficiently separated from the refrigerant, and is discharged to the outside of the compressor together with the refrigerant.

Further, in the conventional lower compression scroll compressor, when the motor is an inverter motor, there is a problem that reliability of the compressor is deteriorated because the oil separation degree is not the same depending on the operation speed. That is, when the motor is operated at a high speed (approximately 90 Hz or more based on the compressor) or at a low speed (approximately 40 to 50 Hz or less based on the compressor), the oil separation effect due to the centrifugal force can be expected. However, this depends on the centrifugal force generated by the rotor, so that the oil separation effect is not significantly improved. On the other hand, when the motor is operated at a medium speed (about 60 to 90 Hz based on the compressor), the oil separation effect due to the centrifugal force is reduced instead of the centrifugal force. However, conventionally, there is no separate mechanism for this purpose or there is a limit to improve the oil separation effect at medium speed.

Further, in the conventional lower compression scroll compressor, when applying to the refrigeration cycle system, superheat of the refrigerant can not be ensured during the cooling low-temperature operation or the startup operation, which is an intermediate speed operation condition, and liquid refrigerant is generated, It can not be separated by the centrifugal separation method or the gravity sedimentation method, so that a large amount of liquid refrigerant is discharged to the outside of the compressor, thereby lowering the efficiency of the entire refrigeration cycle system.

Further, in the conventional lower compression scroll compressor, the refrigerant discharge path and the oil return path are interfered with each other in the opposite direction, causing the refrigerant and the oil to mutually flow resistance. Particularly, the oil is not pumped by the high-pressure refrigerant and is not recovered to the oil storage space, resulting in oil shortage inside the casing, which may cause friction loss or abrasion due to oil shortage in the compression portion.

In addition, in the conventional lower compression scroll compressor, if the refrigerant discharge path and the oil recovery path interfere with each other as described above, oil separated from the internal space of the casing is mixed with the refrigerant discharged again and discharged to the outside of the compressor, The oil shortage of the oil is further increased.

In addition, in the conventional lower compression scroll compressor, the oil can be left on the upper side of the compression section without sufficiently securing the oil recovery passage for moving the oil collected between the drive section and the compression section to the lower space of the casing. This increases the possibility that the oil is mixed with the refrigerant and is discharged to the outside of the compressor after moving to the upper space of the casing, so that the oil shortage inside the compressor can be further increased.

It is an object of the present invention to provide a scroll compressor capable of effectively separating refrigerant and oil from the inside of a casing, thereby minimizing discharge of oil together with refrigerant.

It is another object of the present invention to provide a scroll compressor which is less affected by the operation speed of the drive unit and can increase the oil separation effect in all the drive bands.

Another object of the present invention is to provide a scroll compressor in which liquid refrigerant is separated from gas refrigerant in a compressor to suppress discharge of the refrigerant in a liquid state, thereby increasing the efficiency of the refrigeration cycle system.

It is another object of the present invention to provide a scroll compressor capable of smoothly moving oil separated from a refrigerant in an upper space of a casing to a lower space of a casing.

Another object of the present invention is to provide a scroll compressor in which oil separated from a refrigerant in an upper space of a casing can be prevented from mixing with a refrigerant moving from a space below the casing to an space above the casing.

Another object of the present invention is to provide a scroll compressor in which oil collected between a driving portion and a compression portion can be recovered to a space below the compressor without being mixed with a refrigerant discharged from the compression portion.

Another object of the present invention is to provide a scroll compressor capable of reliably separating a refrigerant passage and an oil passage from each other in a casing.

In order to achieve the object of the present invention, A driving unit provided in the inner space and having a stator coupled to the casing and a rotor rotatably installed in the stator; A compression unit provided below the driving unit; A rotating shaft for transmitting a driving force from the driving unit to the compression unit; An oil separating member provided on the upper side of the driving portion and made of mesh to separate refrigerant and oil; And a heater for heating the oil separating member.

Here, the heater may be embedded in the mesh or may be provided to contact the outer circumferential surface of the casing.

Further, a guide member for guiding the refrigerant and the oil to the oil separating member may be further provided between the oil separating member and the driving motor.

The apparatus may further include a flow path separating unit provided between the power transmitting section and the compression section for separating the refrigerant flow path and the oil flow path.

The flow path separating unit includes a first flow path guide coupled to the compression unit and a second flow path guide extending from the flow path unit, and the second flow path guide includes an insulator provided on the flow path, A flow path sealing member may further be provided between the first flow path guide and the second flow path guide.

In order to achieve the object of the present invention, A driving motor having a stator fixed to an inner space of the casing and an inner passage and an outer passage which are formed of a rotor rotating inside the stator and pass through in the axial direction; A rotating shaft coupled to and rotating with the rotor of the driving motor; A first scroll provided below the drive motor and a compression chamber formed by engaging with the first scroll, the rotation axis being eccentrically coupled with the compression chamber so as to overlap with the compression chamber in a radial direction, A compression unit including a second scroll such that the refrigerant compressed in the compression chamber is discharged toward the inner space of the casing; A discharge tube communicating with an upper space formed on the upper side of the drive motor in an inner space of the casing; And an oil separating unit provided in an upper space of the casing and separating the refrigerant from the refrigerant before the refrigerant is discharged to the discharge pipe, wherein the oil separating unit contacts the refrigerant in the upper space, A porous member for separating the oil; And a heat generating member provided to transmit heat to the porous member.

Here, the porous member may be formed to have at least two porosities.

The porous member may be formed in an annular shape so as to face the inner peripheral surface of the casing, and the porosity of the porous member may be smaller than the porosity of the outer side.

The porous member may be formed of a mesh.

The mesh may be formed by rolling a sheet having at least two voids in a drying direction.

The mesh may be formed by inserting a plurality of mesh portions each of which is made of a plurality of plate materials having different porosities from each other, and inserting a smaller porosity of the plurality of mesh portions into the larger porosity side.

Here, the heating member may include a first heating member contacting the porous member.

The heating member may further include a second heating member wound around an outer circumferential surface of the casing.

Here, the guide member may further include a guide member provided between the upper end of the drive motor and the lower end of the discharge pipe, for guiding the oil-mixed refrigerant to the oil separating member.

The guide member may be coupled to the rotor of the driving motor or the upper end of the rotating shaft to extend toward the inner circumferential surface of the casing, and may be spaced apart from the lower end of the discharge pipe.

The inlet of the discharge pipe may further include an oil separation plate extending radially from the outer circumference of the discharge pipe.

The motor-driven compressor includes a drive motor and a compression unit. The drive motor is connected to the compressor. The drive motor includes a compressor, . ≪ / RTI >

Further, in order to achieve the object of the present invention, there is provided an electric motor comprising: a driving unit including a stator and a rotor; A rotating shaft coupled to the rotor; Wherein a plurality of scrolls are engaged with each other, and the plurality of scrolls are coupled through a rotating shaft, wherein one of the plurality of scrolls receives rotational force of the driving portion by the rotation axis, A compression unit for compressing the fluid while performing the compression; And a second space communicating with the discharge pipe on the upper side of the driving unit and a second space communicating with the compression unit on the lower side of the compression unit, And a third space in which an oil feeder extending from a rotating shaft is accommodated; And a mesh member formed in an annular shape and fixed to the inner circumferential surface of the casing in the second space.

Here, the mesh member may include a first mesh facing the inner circumferential surface of the casing and a second mesh provided inside the first mesh, and the first mesh may have a larger porosity than the second mesh .

At least one of the first mesh and the second mesh may be provided so that the first hot wire is in contact with at least one of the first mesh and the second mesh.

Further, the outer circumferential surface of the casing may be provided so as to be in contact with the second hot wire.

The rotor or the rotary shaft may further include a plate-like guide member that rotates together with the rotor or the rotary shaft and extends toward the inner peripheral surface of the casing.

Meanwhile, the flow guide may further include a space between the transmission portion and the compression portion to divide the space between the transmission portion and the compression portion into a plurality of spaces along the radial direction.

In the scroll compressor of the present invention, the oil separating member including the mesh is provided on the inner circumferential surface of the casing, so that the refrigerant containing the oil passes through the oil separating member to separate the oil from the refrigerant, The amount of oil recovered can be increased by minimizing the discharge to the outside. This makes it possible to prevent friction loss or abrasion due to oil shortage inside the compressor.

In the scroll compressor according to the present invention, since the oil separating member is provided with the heating member such as hot wire, even if liquid refrigerant is generated, the liquid refrigerant can be vaporized by the heating member to effectively separate the oil from the refrigerant.

The scroll compressor according to the present invention is provided with a guide member for centrifugally separating the refrigerant containing oil at the upper side of the transmission portion so that most refrigerant and oil are guided to pass through the oil separation member to increase the oil separation effect And the effect that the refrigerant and the oil are centrifugally separated by the guide member can be expected. Accordingly, this embodiment can improve the oil separation effect even at medium speed as well as at low speed and high speed operation.

Further, in the scroll compressor according to the present invention, since the oil separation plate is provided at the inlet of the discharge pipe, the oil separation effect can be further enhanced.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view showing a lower compression type scroll compressor according to the present invention,
Figure 2 is a cross-sectional view of the compression section of Figure 1,
FIG. 3 is a front view showing a part of the rotating shaft for explaining the sliding section in FIG. 1,
Fig. 4 is a vertical sectional view for explaining the oil supply passage between the back pressure chamber and the compression chamber in Fig. 1,
Fig. 5 is a perspective view of the scroll compressor according to Fig. 1,
FIG. 6 is a longitudinal sectional view showing a state in which the oil separation unit according to FIG. 5 is assembled;
7 is a sectional view taken along the line " IV-IV " in Fig. 6,
FIG. 8 is a schematic view for explaining a process of circulating refrigerant and oil in the lower compression scroll compressor of FIG. 1,
9 is a graph showing the effect of the oil separation unit according to the present invention,
Fig. 10 and Fig. 11 are longitudinal sectional views showing another embodiment of the oil separation unit in the scroll compressor according to Fig. 1; Fig.

Hereinafter, a scroll compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings. For reference, the scroll compressor according to the present invention will be described as a representative example of a scroll compressor of a type in which a rotary shaft is overlapped on the same plane as a rotary wrap in a lower compression scroll compressor in which a compression portion is positioned below a transmission portion for convenience. This type of scroll compressor is known to be suitable for application to refrigeration cycles under high temperature and high compression ratio conditions.

FIG. 1 is a vertical sectional view showing a lower compression type scroll compressor according to the present invention, FIG. 2 is a transverse sectional view showing a compression part in FIG. 1, FIG. 3 is a front view showing a part of a rotary shaft, Fig. 4 is a vertical sectional view for explaining an oil supply passage between the back pressure chamber and the compression chamber in Fig. 1. Fig.

Referring to FIG. 1, the lower compression scroll compressor according to the present embodiment includes a casing 10 in which a driving unit 20 for generating a rotational force is provided, A compression section 30 for receiving the rotational force of the driving section 20 and compressing the refrigerant may be installed in a predetermined space (hereinafter referred to as an intermediate space) 10a.

The casing 10 includes a cylindrical shell 11 constituting a hermetically sealed container, an upper shell 12 covering the upper portion of the cylindrical shell 11 and constituting a hermetically sealed container together with the lower shell of the cylindrical shell 11, And a lower shell 13 for forming a low-pressure space 10c.

The refrigerant suction pipe 15 penetrates into the side surface of the cylindrical shell 11 and directly communicates with the suction chamber of the compression unit 30. The upper shell 12 is communicated 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 to the upper space 10b of the casing 10 from the compression unit 30 is discharged to the outside and the upper space 10b corresponds to a kind of oil separation space The refrigerant discharge pipe 16 can be inserted to the middle of the upper space 10b of the casing 10. [ An oil separator (not shown) for separating the oil mixed in the refrigerant may be connected to the refrigerant suction pipe 16 in the interior of the casing 10 or the upper space 10b including the upper space 10b, .

The electromotive section 20 comprises a stator 21 and a rotor 22 which rotates from the inside of the stator 21. The stator 21 has teeth and slots forming a plurality of coil winding portions (not shown) on the inner circumferential surface of the stator 21 in the circumferential direction so that the coils 25 are wound. The stator 21 is wound around the inner circumferential surface of the stator 21 and the outer circumferential surface of the rotor 22 And the second refrigerant passage P _G2 is formed by combining the space and the coil winding portion. The refrigerant discharged to the intermediate space 10c between the transmission portion 20 and the compression portion 30 through the first refrigerant passage _PG1 to be described later is discharged to the second refrigerant passage P _G2 to the upper space 10b formed on the upper side of the transmission portion 20. [

A plurality of D-cut faces 21a are formed on the outer circumferential surface of the stator 21 along the circumferential direction and the cut face 21a is formed so as to allow the oil to pass between the inner circumferential face of the cylindrical shell 11 1 oil passage P _O1 can be formed. Thus, the oil separated from the refrigerant in the upper space (10b) is moved to the lower side space (10c) through a first oil yuro (P _O1) and the second oil yuro (P _O2) which will be described later.

The frame 31 constituting the compression unit 30 can be fixedly coupled to the inner circumferential surface of the casing 10 at a predetermined distance below the stator 21. The outer circumferential surface of the frame 31 can be heat-shrunk or welded and fixedly coupled to the inner circumferential surface of the cylindrical shell 11.

An annular frame side wall portion (first side wall portion) 311 is formed at an edge of the frame 31. A plurality of communication grooves 311b are formed along the circumferential direction on the outer peripheral surface of the first side wall portion 311 . The communication groove 311b together with the communication groove 322b of the first scroll 32 to be described later forms the second oil passage P ₀₂ .

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

A fixed scroll (hereinafter referred to as a first scroll) 32 may be provided on the lower surface of the frame 31 with an orbiting scroll (hereinafter referred to as a second scroll 33) eccentrically connected to the rotary shaft 50 interposed therebetween. The first scroll 32 may be fixedly coupled to the frame 31, but may also be movably coupled in the axial direction.

The first scroll 32 has a fixed plate portion 321 (hereinafter, referred to as a first plate portion) 321 formed in a substantially circular plate shape. The edge of the first plate portion 321 is engaged with a bottom edge of the frame 31 (Hereinafter referred to as a second side wall portion) 322 may be formed.

A suction port 324 through which the refrigerant suction pipe 15 communicates with the suction chamber is formed at one side of the second side wall portion 322 and a compressed refrigerant is discharged through the central portion of the first hard plate portion 321 in communication with the discharge chamber And discharge ports 325a and 325b may be formed. The discharge ports 325a and 325b may be formed so as to communicate with both the first compression chamber V1 and the second compression chamber V2 to be described later. However, the discharge ports 325a and 325b may be independent of the compression chambers V1 and V2, As shown in FIG.

The communication groove 322b is formed on the outer circumferential surface of the second side wall portion 322. The communication groove 322b communicates with the communication groove 311b of the first side wall portion 311, And the second oil passage P _O2 for guiding to the second oil passage 10c.

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 portion of the first scroll 32. [ The discharge cover 34 receives the refrigerant discharged from the compression chamber V through the discharge openings 325a and 325b in the upper space of the casing 10 10b and more precisely the inlet of the first refrigerant passage P _G1 which guides the refrigerant to the space between the transmission portion 20 and the compression portion 30.

The first refrigerant passage P _G1 is connected to the second sidewall portion 322 of the fixed scroll 32 on the inner side of the flow path separation unit 40, that is, on the inner side of the rotary shaft 50, And the first sidewall portion 311 of the frame 31 in this order. Thus, the second oil passage P _O2 described above is formed outside the oil passage separating unit 40 so as to communicate with the first oil passage P _O1 . The flow separation unit will be described later in detail.

A fixed lap 323 (hereinafter referred to as a first lap) 323, which forms a compression chamber V, is formed on the upper surface of the first hard plate portion 321 to engage with a later-described wrapping lap have. The first wrap 323 will be described later with the second wrap 332.

A second shaft receiving portion 326 for supporting the sub bearing portion 52 of the rotating shaft 50 to be described later is formed at the center of the first hard plate portion 321 and a second shaft receiving portion 326 is formed in the second shaft receiving portion 326 in the axial direction The 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 a shape of a substantially circular plate in which the orbiting plate portion (hereinafter referred to as the second plate portion) 331 is formed. A second lap 332 may be formed on the lower surface of the second hard plate 331 to engage the first lap 322 to form a compression chamber.

The second wrap 332 may be formed in an involute shape with the first wrap 323, but may be formed in various other shapes. For example, as shown in FIG. 2, the second wrap 332 may have a shape in which a plurality of arcs having different diameters and origin points are connected to each other, and the outermost curve may be formed in a substantially oval shape having a major axis and a minor axis . This may also be done for the first wrap 323 as well.

A rotary shaft engaging portion 333 is formed on the central portion of the second hard plate portion 331 and serves as an inner end portion of the second wrap 332. The rotary shaft engaging portion 333 is rotatably inserted into the eccentric portion 53 of the rotary shaft 50, As shown in FIG.

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

The rotation axis connecting portion 333 is formed to have a height that overlaps the second wraps 332 on the same plane so that the eccentric portion 53 of the rotation axis 50 overlaps the second wraps 332 on the same plane As shown in FIG. As a result, the repulsive force and the compressive force of the refrigerant are canceled each other while being applied to the same plane with reference to the second longitudinal plate portion, so that the inclination of the second scroll 33 due to the action of the compressive force and the repulsive force can be prevented.

The rotary shaft engaging portion 333 is formed with a recess 335 which is engaged with the protrusion 328 of the first wrap 323 which will be described later on the outer peripheral portion opposite to the inner end of the first wrap 323. At one side of the recess 335, an increasing portion 335a is formed on the upstream side along the forming direction of the compression chamber V to increase the thickness from the inner peripheral portion to the outer peripheral portion of the rotary shaft engaging portion 333. This makes it possible to increase the compression ratio of the first compression chamber (V1) to be close to the pressure ratio of the second compression chamber (V2) as a result that the compression path of the first compression chamber (V1) immediately before discharge becomes long. 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 in a separate 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 thickness of the inner end of the first wrap 323 (i.e., 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 can be increased to ensure durability, and the compression path can be lengthened, thereby increasing the compression ratio of the second compression chamber V2.

A protrusion 328 is formed near the inner end (suction end or start end) of the first wrap 323 corresponding to the rotation shaft coupling portion 333 so as to protrude toward the outer peripheral portion of the rotation shaft coupling portion 333, 328 may be formed with a contact portion 328a that protrudes from the projection and engages with the recess 335. [ That is, the inner end of the first wrap 323 may be formed to have a larger thickness than the other portions. Thus, the lap strength at the inner end portion, which receives the greatest compressive force among the first laps 323, is improved, and the durability can be improved.

On the other hand, the compression chamber V is formed between the first hard plate portion 321 and the first lap 323, and between the second lap 332 and the second hard plate portion 331, An intermediate pressure chamber, and a discharge chamber may be continuously formed.

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 a second compression chamber (V2) 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, P12) formed by 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 two contact points P21 and P22 formed by the outer surface of the first wrap 323 and the inner surface of the second wrap 332 being in contact with each other.

Here, the first compression chamber (V1) immediately before discharge has an angle (?) Having a larger value among the angles formed by the two lines connecting the center O of the eccentric portion, that is, the center O of the rotary shaft coupling portion and the two contact points P11 and P12 The distance l between the normal vectors at the two contact points P11 and P12 also has a value larger than zero.

This makes it possible to increase the size of the first wrap 323 and the second wrap 332 since the first compression chamber immediately before discharge has a smaller volume than in the case where the first compression chamber has the fixed wrap and the orbiting wrap composed of involute curves 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 can be installed so as to be pivotable between the frame 31 and the fixed scroll 32. An ore ring 35 for preventing the rotation of the second scroll 33 is provided between the upper surface of the second scroll 33 and the lower surface of the frame 31 corresponding to the upper surface of the second scroll 33, A sealing member 36 for forming a back pressure chamber S1 for performing a back pressure operation can be provided.

The intermediate pressure space is formed by the oil supply hole 321a provided in the second scroll 32 on the outer side of the sealing member 36. [ The intermediate pressure space communicates with the intermediate compression chamber (V) and can function as a back pressure chamber as the intermediate pressure refrigerant is filled. Therefore, the back pressure chamber formed on the inner side around the sealing member 36 may be referred to as a first back pressure chamber S1, and the intermediate pressure space formed on the outside may be referred to as a second back pressure chamber S2. 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 about the sealing member 36. The back pressure chamber S1 is formed by a sealing member .

On the other hand, the flow path separating unit 40 is provided in the intermediate space 10a, which is a light oil space formed between the lower surface of the electromotive section 20 and the upper surface of the compression section 30 so that the refrigerant discharged from the compression section 30 And serves to prevent the oil from interfering with the oil moving from the upper space 10b of the electromotive section 20 which is the oil separation space to the lower space 10c of the compression section 30 which is 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 through which refrigerant flows (hereinafter referred to as a refrigerant flow space) and a space through which oil flows (hereinafter referred to as an oil flow space) Includes a Euro Guide. The flow guide may separate the first space 10a into the refrigerant flow space and the oil flow space by the flow guide alone. However, in some cases, a plurality of flow guides may be combined to serve as a flow guide.

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 extending downward. The first flow path guide 410 and the second flow path guide 420 are overlapped 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, and the second flow path guide 420 is inserted into the stator 21 to be extended from an insulator insulating the winding coils .

The first flow path guide 410 includes a first annular wall portion 411 extending upward from the outside, a second annular wall portion 412 extending upward from the inside, a first annular wall portion 411 and a second annular wall portion 412 And an annular surface portion 413 extending in the radial direction so as to connect between the two. The first annular wall portion 411 is formed higher than the second annular wall portion 412 and the refrigerant hole is formed in the annular surface portion 413 so that the coolant hole communicating with the intermediate space 10a in the compression portion 30 is communicated .

The first balance weight 261 is located inside the second annular wall portion 412 in the direction of the rotational axis and the first balance weight 261 is coupled to the rotor 22 or the rotational shaft 50 . At this time, although the first balance weight 261 can rotate and the refrigerant can be stirred, the refrigerant is prevented from moving toward the first balance weight 261 by the second annular wall portion 412 so that the refrigerant flows into the first balance weight 261 Can be suppressed from being stirred by the agitator.

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

Both spaces formed on the inner side and the outer side of the first space 10a are completely formed between the first annular wall portion 411 of the first flow guide 410 and the second extended portion 421 of the second flow guide 420 And a flow-through sealing member 430 for separating the fluid.

The upper portion of the rotary shaft 50 is press-fitted to the center of the rotor 22 while the lower portion is coupled to the compression portion 30 to be radially supported. Thus, the rotary shaft (50) transfers the rotational force of the electromotive unit (20) to the orbiting scroll (33) of the compression unit (30). Then, the second scroll 33 eccentrically coupled to the rotary shaft 50 is rotated with respect to the first scroll 32.

A main bearing portion (hereinafter referred to as a first bearing portion) 51 is formed in the lower half portion of the rotary shaft 50 so as to be inserted into the first bearing hole 312a of the frame 31 and radially supported, Bearing portion 52 (hereinafter referred to as a second bearing portion) may be formed on the lower side of the second scroll portion 51 so as to be inserted into the second bearing hole 326a of the first scroll 32 and radially supported. The eccentric portion 53 may be formed between the first bearing portion 51 and the second bearing portion 52 so as to be inserted into the rotary shaft engaging portion 333 and coupled therewith.

The first bearing portion 51 and the second bearing portion 52 are coaxially formed so as 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 Can be formed eccentrically in the radial direction. The second bearing portion 52 may be formed to be eccentric with respect to the first bearing portion 51.

The eccentric part 53 should be formed so as 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 rotary shaft 50 can be inserted into the respective bearing holes 312a, It may be advantageous to pass through and join the rotating shaft coupling portion 333. However, when the eccentric part 53 is formed integrally with the rotary shaft 50 but using a separate bearing, the outer diameter of the second bearing part 52 is not formed to be smaller than the outer diameter of the eccentric part 53 The rotation shaft 50 can be inserted and coupled.

An oil supply passage 50a for supplying oil to each bearing portion and the eccentric portion may be formed along the axial direction within the rotary shaft 50. The oil supply passage 50a is formed at the lower end or middle height of the stator 21 or at the lower end of the first bearing portion 31 at the lower end of the rotary shaft 50 as the compression portion 30 is positioned below the transmission portion 20, As shown in FIG. Of course, in some cases, it may be formed by penetrating the rotary shaft 50 in the axial direction.

An oil feeder 60 for pumping the oil filled in the lower space 10c may be coupled to the lower end of the rotary shaft 50, that is, the lower end of the second bearing portion 52. [ The oil feeder 60 includes an oil supply pipe 61 inserted into and coupled to the oil supply passage 50a of the rotary shaft 50 and a blocking member 62 for receiving the oil supply pipe 61 to block intrusion of foreign matter . The oil supply pipe 61 can be positioned so as to pass through the discharge cover 34 and immerse in the oil in the lower space 10c.

3, the bearing portions 51 and 52 and the eccentric portion 53 of the rotary shaft 50 are connected to the oil supply passage 50a, and a sliding portion for supplying oil to each sliding portion The flow path F1 is formed.

The wet sliding portion communication passage F1 has a plurality of oil supply holes 511, 521 and 531 penetrating from the oil supply passage 50a toward the outer peripheral surface of the rotary shaft 50, And a plurality of oil supply grooves 512 (521, 521) which communicate with the oil supply holes 511, 521, 531 and lubricate the bearing portions 51, 52 and the eccentric portion 53, respectively, 522) < / RTI >

For example, the first oil supply hole 511 and the first oil supply groove 512 are formed in the first bearing portion 51 and the second oil supply hole 521 and the second oil supply groove And a third oil supply hole 531 and a third oil supply groove 532 are formed in the eccentric portion 53, 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 shape in the axial or oblique direction.

Between the first bearing portion 51 and the eccentric portion 53 and between the eccentric portion 53 and the second bearing portion 52, a first connection groove 541 and an annular second connection groove 541, Respectively. The lower end of the first oil supply groove 512 communicates with the first connection groove 541 and the upper end of the second oil supply groove 522 is connected to the second connection groove 542. Accordingly, a part of the oil that lubricates the first bearing portion 51 through the first oil supply groove 512 flows down to the first connection groove 541 and is collected into the first back pressure chamber S1 Thereby forming a discharge pressure of the discharge pressure. The oil that lubricates the second bearing portion 52 through the second oil supply groove 522 and the oil that lubricates the eccentric portion 53 through the third oil supply groove 532 are connected to the second connection groove 542 And may be introduced into the compression section 30 through the space between the distal end surface of the rotary shaft coupling section 333 and the first hard plate section 321.

A small amount of oil sucked in the upper direction of the first bearing portion 51 flows out of the bearing surface at the upper end of the first bearing portion 312 of the frame 31 and flows along the first bearing portion 312 along the frame 31 The oil passages P _O1 and P P2 are continuously formed on the outer circumferential surface of the frame 31 (or the grooves communicating from the upper surface to the outer circumferential surface) and the outer circumferential surface of the first scroll 32, _O2 to the lower space 10c.

The oil discharged to the upper space 10b of the casing 10 together with the refrigerant in the compression chamber V is separated from the refrigerant in the upper space 10b of the casing 10 and is discharged to the outer peripheral surface of the transmission portion 20 And is collected into the lower space 10c through the first oil passage P _O1 formed and the second oil passage P _O2 formed on the outer peripheral surface of the compression portion 30. [ The oil separating unit 40 to be described later is provided between the transmission portion 20 and the compression portion 30 so that the oil separated from the refrigerant in the upper space 10b and moved to the lower space 10c is compressed (P _O1 ) (P _O2 )] [(P _G1 ) (P _G2 )] without being intermixed with the refrigerant discharged to the upper space 10b, The refrigerant can move to the lower space 10c and the refrigerant can move to the upper space 10b.

On the other hand, the second scroll (33) is provided with a compression chamber power distribution passage (F2) for supplying the oil sucked through the oil supply passage (50a) to the compression chamber (V). The compression chamber F2 is connected to the above-described sliding portion classifying passage F1.

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

Of course, the compression chamber lubrication passage may be formed so as to communicate directly from the oil supply passage 50a to the intermediate pressure chamber without passing through the second back pressure chamber S2. However, in this case, a refrigerant passage for communicating the second back pressure chamber S2 and the intermediate pressure chamber V must be separately provided, and a refrigerant passage for supplying oil to the oil sealing 35 located in the second back pressure chamber S2 An oil line must be provided separately. This increases the number of passageways and complicates the processing. Therefore, in order to reduce the number of passages by unitizing the refrigerant passage and the oil passage, the oil supply passage 50a and the second back pressure chamber S2 are communicated with each other and the second back pressure chamber S2 is communicated with the intermediate pressure chamber (V). ≪ / RTI >

To this end, the first-class oil passageway 371 is formed with a first swivel passage portion 371a formed to the middle in the thickness direction on the lower surface of the second rigid plate portion 331, and the first swivel passage portion 371a A second turning passage portion 371b is formed toward the outer circumferential surface of the second hard plate portion 331 and a third turning passage portion 371b penetrating from the second turning passage portion 371b toward the upper surface of the second hard plate portion 331, (371c) is formed.

The first swivel passage portion 371a is formed at a position belonging to the first back pressure chamber S1 and the third swivel passage portion 371c is formed at a position belonging to the second back pressure chamber S2. The second swing passage portion 371b is provided with a pressure reducing rod 375 so that 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 can be lowered. ) Is inserted. The sectional area of the second swivel passage portion 371b excluding the pressure-sensitive bar 375 is smaller than the first swivel passage portion 371a or the third swivel passage portion 371c and the second swivel passage portion 371b.

In the case where the end of the third swing passage portion 371c is formed so as to be located inside the art ring 35, that is, between the art ring 35 and the sealing member 36, the first oil passageway 371 Is blocked by the oil seal 35 and does not smoothly move to the second back pressure chamber S2. Therefore, in this case, the fourth swivel passage portion 371d may be formed at the end of the third swivel passage portion 371c toward the outer peripheral surface of the second hard plate portion 331. [ The fourth turning passage portion 371d may be formed as a groove on the upper surface of the second hard plate portion 331 as shown in FIG. 4 or may be formed as a hole in the second hard plate portion 331.

The second level communication passage 372 has a first fixed passage portion 372a formed in the thickness direction on the upper surface of the second sidewall portion 322 and a second fixed passage portion 372a formed in the first fixed passage portion 372a in the radial direction, And a third fixed passage portion 372c communicating with the intermediate pressure chamber V from the second fixed passage portion 372b is formed.

In the drawing, reference numeral 70 denotes an accumulator.

The lower compression scroll compressor according to this embodiment operates as follows.

That is, when power is applied to the electromotive unit 20, a rotational force is generated in the rotor 21 and the rotating shaft 50 and rotates. As the rotating shaft 50 rotates, (33) is swiveled by the alerting (35).

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 movement of the orbiting scroll 33 And is compressed and discharged to the inner space of the discharge cover 34 through the discharge ports 325a and 325b.

The refrigerant discharged to the inner space of the discharge cover 34 circulates through the inner 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 portion 20 through the gap between the stator 21 and the rotor 22. [

After the oil is separated from the refrigerant in the upper space of the transmission portion 20, the refrigerant is discharged to the outside of the casing 10 through the refrigerant discharge pipe 16, while the oil flows from the inner peripheral surface of the casing 10 to the stator 21 and the inner circumferential surface of the casing 10 and the outer circumferential surface of the compression section 30 to the lower space 10c which is the oil storage space of the casing 10. [

At this time, the oil in the lower space 10c is sucked up through the oil supply passage 50a of the rotary shaft 50. The oil is supplied to the respective oil supply holes 511, 521, 531 and the oil supply grooves 512 The first bearing portion 51, the second bearing portion 52 and the eccentric portion 53 are respectively lubricated through the first and second bearing portions 532 and 532.

The oil that lubricates the first bearing portion 51 through the first oil supply hole 511 and the first oil supply groove 512 is discharged through the first connection groove 51 between the first bearing portion 51 and the eccentric portion 53, (541), and this oil flows into the first back pressure chamber (S1). This oil almost forms the discharge pressure, so that the pressure in the first back pressure chamber S1 almost also forms the discharge pressure. Therefore, the center portion 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 level communication 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 swing passage portion 371b constituting the first-class oil passageway 371, so that the pressure of oil toward the second back pressure chamber S2 is reduced to an intermediate pressure.

The oil that moves to the second back pressure chamber (intermediate pressure space) S2 supports the edge portion of the second scroll 33, and at the same time, the second oil level communication passage 372 is moved in accordance with the pressure difference with the intermediate pressure chamber V, To the intermediate pressure chamber (V). However, if the pressure of the intermediate pressure chamber V becomes higher than the pressure of the second back pressure chamber S2 during the operation of the compressor, the refrigerant in the intermediate pressure chamber V flows through the second oil supply passage 372 into the second back pressure chamber S2 . In other words, the second-level communication passage 372 serves as a passage through which the refrigerant and the oil cross each other in accordance with the pressure difference between the second back pressure chamber S2 and the intermediate pressure chamber V.

At this time, as described above, the flow path separation unit 40 is installed in an intermediate space (hereinafter referred to as a first space) 10a which is a light oil space formed between the lower surface of the electric drive unit 20 and the upper surface of the compression unit 30 The refrigerant discharged from the compression section 30 is discharged to the lower space of the compression section 30 which is the oil storage space in the upper space 10b (hereinafter referred to as the second space 10b) of the transmission section 20, 3 space) 10c of the oil mist. Accordingly, the refrigerant and the oil are discharged together in the compression section 30 and pass through the transmission section 20, and the refrigerant and the oil that have passed through the transmission section 20 are separated from the refrigerant in the second space (10b) the oil is separated, the separated oil is collected in a third area (10c) low dielectric space via a first oil passage (P _O1) and the second oil passage (P _O2).

However, even if there is no separate oil separator in the second space 10b or a diaphragm oil separator, the oil separation effect is low, and the oil is likely to be discharged to the outside of the compressor together with the refrigerant. As a result, the amount of oil recovered into the third space 10c, which is the oil storage space of the compressor, is reduced and the amount of oil supplied to each sliding portion is reduced, resulting in friction loss and abrasion.

Particularly, the oil separation inside the compressor is deeply related to the flow rate of the refrigerant (hereinafter referred to as refrigerant oil) containing the oil. It is generally known that the centrifugation method is suitable when the flow rate of the refrigerant oil is low or high. This is because, although the collision between particles does not occur at a low speed, the degree of expansion of the refrigerant oil is weak and the particle size of the oil is increased, so that the oil separation effect by gravity sedimentation is improved. In the case of high speed, The oil particles are combined to receive a larger centrifugal force than the refrigerant, and the oil separation effect due to inertia is separated from the refrigerant.

However, in the case of medium speed, it is difficult to expect the oil separation effect due to gravity settling as in low speed or the oil separation effect due to inertia as in high speed. Therefore, in the case of medium speed, it is preferable to provide a separate oil separator rather than a centrifugal separator.

However, conventionally, as described above, oil is separated using a gravity sedimentation method or a centrifugal separation method using a space without a separate oil separator, so that a low speed or high speed operation of the compressor (actually, Although the flow rate can be expected based on the operation speed of the compressor for convenience, the oil separation effect can be expected as follows. However, since the oil separation effect is lowered at medium speed operation . However, when the second space is excessively enlarged in order to secure the oil separation space, the compressor becomes uneven and the width of the second space is limited. Therefore, the oil can not be sufficiently separated from the refrigerant oil flowing into the second space, and may be discharged to the outside of the compressor together with the refrigerant, resulting in oil shortage within the compressor. This will be described later with reference to FIG.

In view of this, in the lower compression scroll compressor according to the present embodiment, an oil separation unit capable of actively responding to the change in the operation speed of the compressor can be provided in the second space. 5 and 6 are views showing an example of such an oil separation unit.

Referring to FIG. 1, the oil separation unit 80 according to the present embodiment may be provided on the upper side of the transmission unit 20 so that oil can be separated from the refrigerant oil passing through the transmission unit 20.

5 and 6, the oil separation unit 80 includes a porous member 81 coupled to the inner circumferential surface of the casing 10 and a porous member 81 provided to contact the porous member 81 to heat the porous member 81 Or a heating member 82 for heating the liquid refrigerant mixed with the refrigerant oil.

The porous member 81 is a member that is in contact with the refrigerant oil to separate the refrigerant and the oil, and may be formed of a mesh formed by rolling in a cylindrical shape. However, the porous member does not necessarily need to have a mesh shape. That is, the porous member 81 may be formed of a cylinder having a plurality of fine holes in addition to the mesh. Therefore, in addition to the mesh, the porous member 81 may be an oil filter capable of separating the refrigerant and oil from the refrigerant oil. However, this embodiment will be described as a mesh representation for the sake of convenience.

The porous member 81, that is, the mesh may be formed to have a single porosity (i.e., roughness of the mesh) as a whole, but may be formed to have different porosity in the radial direction. For example, as shown in FIGS. 5 to 7, the mesh 81 includes a first mesh 811 located inside in accordance with the order of contact with the refrigerant oil, a first mesh 811 surrounding the outer periphery of the first mesh 811, And a second mesh 812 in contact with the inner circumferential surface of the cylindrical shell 11.

The first mesh 811 may have a porosity lower than that of the second mesh 812 so that the first mesh 811 may be formed more densely than the second mesh 812. As a result, the refrigerant oil is separated from the refrigerant and the oil while passing through the first mesh 811, and the separated oil flows along the second mesh 812 to be smoothly guided to the first oil passage P _O1 have.

The first mesh 811 and the second mesh 812 are formed by forming a first mesh 811 on the inner side and a second mesh 812 on the outer side according to the order in which a sheet is rolled up and dried . However, in a state where the first mesh 811 and the second mesh 812 are separately formed, the first mesh 811 can be inserted into the second mesh 812 and then assembled.

The mesh can be held in a cylindrical shape by being tightened with a plurality of long bolts 841 and nuts 842 while the upper and lower ends of the mesh are supported by the upper and lower support members 831 and 832, respectively.

The upper support member 831 and the lower support member 832 may be formed to correspond to each other. 5, the upper and lower support members 831 and 832 are annularly formed with body portions 831a and 832a, and the inner peripheral surface of the body portions 831a and 832a has a circumferential direction The support portions 831b and 832b may be formed in a protruding shape at regular intervals.

It is preferable that the body portions 831a and 832a are formed as thin as possible so that the oil filtered by the mesh 811 and 812 can flow down quickly to the first oil passage P _O1 . The bolt holes 831c and 832c for bolting the upper end support member 831 and the lower end support member 832 with bolts may be formed on both the support portions 831b and 832b.

6 and 7, the heating member 82 may be embedded between the first mesh 811 and the second mesh 812, which are made of heat and are the porous member 81. However, in some cases, Or may be provided on the outer peripheral surface or the inner peripheral surface of the porous member 81. [ However, in order to stably support the heating member 82, it may be preferable that the heating member 82 is installed inside the mesh 81.

The process of separating the refrigerant and the oil in the scroll compressor according to the present embodiment as described above is as follows.

8, the refrigerant discharged from the compression unit 30 is supplied to the second space 10b through the first refrigerant passage P _G1 and the second refrigerant passage P _G2 in a state of containing oil Movement.

Then, the refrigerant (dashed line arrow) and the oil (solid line arrow) which move to the second space 10b are centrifuged by the rotation of the rotor 22, and the centrifugal effect is generated in the second space 10b do. The refrigerant centrifugally separated in the second space 10b is guided to the discharge pipe 16 and discharged to the outside of the compressor. The separated oil collides with the inner circumferential surface of the casing 10, a down flow to the inner peripheral face of the ride (10) via a first oil passage (P _O1) and the second oil passage (P _O2), low dielectric space 3 is recovered into the space (10c).

However, the refrigerant oil in which the refrigerant and oil are not separated comes into contact with the porous member 81 constituting the oil separation unit 80 while circulating in the second space 10b.

Then, the refrigerant oil first contacts with the first mesh 811 constituting the porous member 81, and a part of the oil is separated from the refrigerant, and the refrigerant again passes through the second mesh 812 to separate most of the oil .

Then, the separated oil is collected in the second mesh 812 and the casing 10 is a third area (10c) down flows take the inner peripheral surface via a first oil passage (P _O1) and the second oil passage (P _O2) of The separated refrigerant passes through the second mesh 812 and moves to the upper side of the second space 10b and is discharged to the outside of the compressor through the discharge pipe 16. [

At this time, the refrigeration cycle system including the compressor may be operated under a medium load condition or liquid refrigerant may be generated at the initial stage of startup. However, if the porous member 81 is heated by the heating member 82 or the liquid refrigerant is heated by the heating member 82 The liquid refrigerant is vaporized and the oil can be easily separated from the refrigerant.

Here, the heating member 82 may be configured to be turned on / off in accordance with the operation speed of the compressor by a compressor control unit (not shown). In some cases, the pressure of the refrigerant discharged may be checked, And may control the heating member 82 to be turned on / off according to the determination.

As a result, the oil separation unit 80 according to the present embodiment can smoothly separate oil from the refrigerant even when the compressor operates at a high speed or a low speed as well as an intermediate speed. This is shown in FIG.

 As shown in FIG. 9, when the oil separating unit is not provided (conventionally), the oil separation rate (n%) rapidly decreases as the operation speed of the compressor increases. This means that the oil flow rate increases sharply as the operation speed increases.

However, when the oil separation unit 80 including the porous member 81 and the heat generating member 82 is provided as in the present embodiment, the oil separation rate (n%) as a whole is improved compared to the prior art in which the oil separation unit is not provided Can be seen. 9, since the oil separation unit 80 of the present embodiment includes the porous member 81 and the heating member 82, the oil separation rate (n%) in the middle speed (approximately 50 to 90 Hz) It can be seen that the oil separation rate (n%) in the region of high speed (about 90 Hz or more) or low speed (about 40 to 50 Hz or less) is also improved.

This is because the present embodiment adopts the filtration separation method based on the mesh as a basis, the oil separation rate (n%) is remarkably improved in the middle speed case, and even when the liquid refrigerant is included, ), So that the oil can be easily separated and the oil separation effect can be greatly improved.

In addition, even in the case of high speed or low speed, the refrigerant oil scattered to the inner circumferential surface of the casing 10 due to the centrifugal force comes into contact with the porous member 81 made of the mesh to improve the oil separation effect, The effect of oil separation can be further improved by being vaporized by the member 82.

Accordingly, in this embodiment, the refrigerant and the oil can be effectively separated regardless of the operating speed of the compressor, and the oil shortage in the compressor can be prevented in advance.

Meanwhile, another embodiment of the oil separation unit according to the present invention is as follows.

That is, in the above-described embodiment, the heating member is in contact with the mesh in the casing, such as between the first mesh and the second mesh, the inner circumferential surface of the first mesh or the inner circumferential surface of the second mesh or the middle of the first mesh or the second mesh. In this embodiment, the heating member is provided so as to contact the outer peripheral surface of the casing.

10, a first heating member 821 is provided on the inner side of the casing 10 and a second heating member 821 is provided on the outer side of the casing 10 822 may be respectively installed.

In this case, it is preferable that the first heating member 821 is provided so as to be in contact with the mesh 81, and the second heating member 822 is provided so as to be in contact with the outer peripheral surface of the casing 10.

The first heating member 821 and the second heating member 822 may be connected to separate power terminals, but the first heating member 821 and the second heating member 822 may be connected in parallel to the same power terminal It is possible.

The basic structure of the porous member in the oil separation unit according to the present embodiment as described above and the operation and effect of the same are the same as those of the above-described embodiment. However, since the second heating member 822 is further provided on the outer circumferential surface of the compressor casing, the liquid refrigerant can be effectively vaporized even when the amount of the liquid refrigerant is large, so that the oil separation effect can be enhanced.

Meanwhile, another embodiment of the oil separation unit according to the present invention is as follows.

That is, in the above-described embodiments, the porous member such as a mesh is provided in the casing to improve the oil separation effect during medium-speed operation. However, in this embodiment, the rotor 22 or the rotating shaft 50 A guide member 85 made of a circular plate is provided on the upper surface to increase the oil separation effect during high speed or low speed operation or to provide an oil separation plate 86 at the end of the discharge pipe 16 to enhance the gravity sedimentation separation effect.

For example, the guide member 85 according to the present embodiment can be coupled to the upper surface of the rotor 22, more precisely to the upper surface of the second balance weight 262 provided in the rotor 22. Of course, the guide member 85 may be coupled to the upper end of the rotary shaft 50 by extending the rotary shaft 50.

The guide member 85 is formed in a disk shape having a predetermined width and can be coupled to the upper surface of the second balance weight 262. [ Of course, the guide member 85 may extend in the axial direction of the rotary shaft 50 and be coupled to the upper end of the rotary shaft 50 thereof. This is different from the present embodiment only in the coupling position, but the basic operation and effect are the same, and a description thereof will be omitted. However, when the guide member is coupled to the rotary shaft, the eccentric load increases as the rotary shaft is extended, but the guide member can be more stably fixed as the center of the guide member is coupled to the rotary shaft.

Here, the basic configuration of the oil separating member according to the present embodiment and the operation and effect thereof are very similar to those of the above-described embodiments. Therefore, detailed description thereof will be omitted. However, in this embodiment, since the porous member 81 and the heating member 82 are provided on the inner peripheral surface of the casing 10 and the disc-like guide member 85 is provided on the rotor 22 or the rotary shaft 50 The refrigerant passing through the second refrigerant passage P _G2 and the oil are doubled in centrifugal force by the guide member 85 and the porous member 81 provided on the inner peripheral surface of the casing 10 and the heat- It is possible to move more toward the side 82. Accordingly, the centrifugal separation effect is further improved by the guide member 85 in the present embodiment compared with the above-described embodiment, and the oil separation effect by the porous member 81 and the heating member 82 is further improved .

Meanwhile, the present embodiment may further include an oil separation plate 86 having an annular shape near the inlet end of the discharge pipe 16. The oil separation rate (n%) is further improved by separating the oil that has not yet been separated by the filtration separation using the porous member 81 and the heating member 82 as well as the centrifugal separation in the second space 10b .

Accordingly, in this embodiment, the refrigerant and the oil can be effectively separated regardless of the operation speed of the compressor, and the oil that can not be separated by the centrifugal separation can be effectively separated even in the medium-speed operation, Oil deficiency can be prevented in advance.

In this embodiment, even if a large amount of liquid refrigerant is mixed in the refrigerant oil according to the operating condition of the refrigeration cycle system, the liquid refrigerant is vaporized by the heat generated in the heating member, so that the refrigerant and the oil can be more effectively separated.

10: casing 10a: intermediate space (first space)
10b: upper space (second space) 10c: lower space (third space)
20: Transmission section 21: Stator
22: Rotor 262: Second balance weight
26: insulator 30: compression section
32: first scroll 323: first wrap
33: second scroll 332: second wrap
40: flow path separation unit 50:
60: Oil feeder 70: Accumulator
80: Oil separation unit 81: Porous member (mesh)
811: first mesh 812: second mesh
82: heating member 821: first heating member
822: second heating member 85: guide member
86: oil separation plate V: compression chamber
F1 : Flooding flow path F2 : Compressed class distribution channel

Claims (18)

A casing in which an inner space is sealed;
A driving motor having a stator fixed to an inner space of the casing and an inner passage and an outer passage which are formed of a rotor rotating inside the stator and pass through in the axial direction;
A rotating shaft coupled to and rotating with the rotor of the driving motor;
A first scroll provided below the drive motor and a compression chamber formed by engaging with the first scroll, the rotation axis being eccentrically coupled with the compression chamber so as to overlap with the compression chamber in a radial direction, A compression unit including a second scroll such that the refrigerant compressed in the compression chamber is discharged toward the inner space of the casing;
A discharge tube communicating with an upper space formed on the upper side of the drive motor in an inner space of the casing; And
And an oil separation unit provided in an upper space of the casing and separating the refrigerant from the refrigerant before the refrigerant is discharged to the discharge pipe,
A porous member contacting the refrigerant in the upper space to separate oil from the refrigerant; And
And a heat generating member provided to transmit heat to the porous member. The method according to claim 1,
Wherein the porous member is formed to have at least two porosities. 3. The method of claim 2,
Wherein the porous member is formed in an annular shape so as to face along the inner circumferential surface of the casing,
Wherein the porosity of the porous member is smaller than the porosity of the outer side. The method according to claim 1,
Wherein the porous member is formed of a mesh. 5. The method of claim 4,
Wherein the mesh is formed by rolling a sheet of sheet having at least two voids in a running direction. 5. The method of claim 4,
Wherein the mesh is formed by inserting a plurality of mesh portions each of which is formed by rolling a plurality of plate materials having different porosity from each other and inserting a smaller porosity of the plurality of mesh portions into the larger porosity side. The method according to claim 1,
Wherein the heat generating member comprises a first heat generating member which is in contact with the porous member. 8. The method of claim 7,
Wherein the heating member is further provided with a second heating member wound around an outer circumferential surface of the casing. The method according to claim 1,
Further comprising a guide member provided between an upper end of the drive motor and a lower end of the discharge pipe, for guiding the oil-mixed refrigerant to the oil separating member. 10. The method of claim 9,
The guide member is coupled to the rotor of the drive motor or the upper end of the rotation shaft and extends toward the inner circumferential surface of the casing,
And is spaced from the lower end of the discharge pipe. The method according to claim 1,
And an oil separation plate extending in a radial direction from an outer circumferential surface of the discharge pipe is further provided at an inlet of the discharge pipe. 12. The method according to any one of claims 1 to 11,
And a flow path separation unit which is annularly formed between the drive motor and the compression unit and separates the space between the drive motor and the compression unit into an inner space communicating with the inner flow path of the drive motor and an outer space communicating with the outer flow path The scroll compressor comprising: A transmission section including stator and rotor;
A rotating shaft coupled to the rotor;
Wherein a plurality of scrolls are engaged with each other, and the plurality of scrolls are coupled through a rotating shaft, wherein one of the plurality of scrolls receives rotational force of the driving portion by the rotation axis, A compression unit for compressing the fluid while performing the compression;
And a second space communicating with the discharge pipe on the upper side of the driving unit and a second space communicating with the compression unit on the lower side of the compression unit, And a third space in which an oil feeder extending from a rotating shaft is accommodated; And
And a mesh member formed in an annular shape and fixed to the inner circumferential surface of the casing in the second space. 14. The method of claim 13,
Wherein the mesh member comprises:
A first mesh facing the inner circumferential surface of the casing, and a second mesh provided inside the first mesh,
Wherein the first mesh has a larger porosity than the second mesh. 15. The method of claim 14,
Wherein at least one of the first mesh and the second mesh is provided so that a first hot line is in contact with at least one of the first mesh and the second mesh. 16. The method of claim 15,
And a second hot wire is provided in contact with an outer circumferential surface of the casing. 17. The method of claim 16,
Wherein the rotor or the rotary shaft further includes a plate-like guide member which rotates together with the rotor or the rotary shaft and extends toward the inner peripheral surface of the casing. 18. The method according to any one of claims 13 to 17,
Further comprising: a flow guide disposed between the transmission portion and the compression portion to divide a space between the transmission portion and the compression portion into a plurality of spaces along a radial direction.

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