KR20130011658A - Scroll compressor - Google Patents

Abstract

PURPOSE: A scroll compressor is provided to separate oil contained in refrigerant when the refrigerant circulating along a guide wall collides with an inner wall of a cover housing. CONSTITUTION: A scroll compressor comprises a compression unit, a cover housing(100), and a discharge hole. The compression unit sucks refrigerant, and compresses the refrigerant by a fixing scroll and a rotary scroll. The cover housing is installed at one side of the compression unit, and forms a discharge port(300) which discharges the compressed refrigerant to an outer cooling circuit. The discharge hole connects the compression unit to the cover housing. In the cover housing, a high pressure chamber is formed between the discharge hole and the discharge port. The high pressure chamber is divided by a plurality of guide walls, and a plurality of fluid paths is formed by the guide walls. One or more oil-separation grooves(236) are formed at one side of the guide wall. The plurality of paths is separated from each other at the center of the cover housing, and comprises a plurality of curved fluid paths with predetermined curvatures.

Description

[0001] SCROLL COMPRESSOR [0002]

The present invention relates to a scroll compressor, and more particularly, to a scroll compressor in which a refrigerant is compressed by relative rotation of a fixed scroll and a swing scroll, wherein the scroll compressor can separate and recover oil from the compressed refrigerant. .

In general, the compressor used in the air conditioning system of the automobile sucks the working fluid from the evaporator to the high temperature and high pressure which is easy to liquefy, and delivers it to the condenser.

In such a compressor, there is a reciprocating type that actually compresses the working fluid to perform compression while reciprocating, and a rotary type that performs compression while rotating.

The reciprocating type includes a crank type for transmitting a driving force of a drive source to a plurality of pistons using a crank, a swash plate type for transmitting to a rotating shaft provided with a swash plate, and a wobble plate type using a wobble plate.

The rotary type includes a rotary type using a rotating rotary shaft and a vane type, and a scroll type using a rotating scroll and a fixed scroll.

1 shows an example of a scroll compressor according to the prior art in cross section. According to this, the scroll compressor 1 largely comprises a drive unit 3, a control unit 5, and a compression unit 7.

Here, the driving unit 3 is a driving source for generating the rotational power of the compressor 1, and as shown in FIG. 1, the driving unit housing 31 and the intermediate housing 32 forming the outer body, and the driving unit housing 31 and It consists of a stator 33 installed in the intermediate housing 32 and a rotor 34 rotating inside the stator 33.

At this time, the drive unit housing 31 is a portion forming the outer body of the drive unit 3, it is generally formed in a cylindrical shape as shown, the intermediate housing 32 may be interposed between the control unit 5, the middle A bearing housing 35 protrudes from the bottom surface of the housing 32, and a bearing 36 for rotatably supporting the rotating shaft 37 of the rotor 34 of the driving unit 3 is rotatably formed on the bearing housing 35. It is fixedly installed. In addition, the intermediate housing 32 is formed with a suction port 38 for sucking the refrigerant through one side of the circumferential surface.

The stator 33 is a driving part that generates a rotational driving force together with the rotor 34 coaxially mounted inside, and is a stator core 33a fixedly mounted on the inner circumferential surface of the drive housing 31 by press fitting or the like as an electromagnet. And a bundle of coils 33b wound around the stator core 33a.

In addition, as described above, the rotor 34 is coaxially mounted inside the stator 33 to be driven to rotate, and is rotatably inserted into a hole in the center of the stator core 33a of the stator 33. And a rotating shaft 37 arranged long along the central axis, and a permanent magnet (not shown) attached to the outer circumferential surface of the rotating shaft 37.

Therefore, the rotor 34 is driven to rotate by interaction with the stator 33 in accordance with the driving principle of the motor when the stator 33 is excited, the rotary shaft 37 is driven through the bearing 36 drive housing ( 31 is rotatably supported and rotates together with the rotor 34.

On the other hand, the control unit 5 is a part for controlling the operation of the drive unit 3, is electrically connected to the stator 33 of the drive unit 3, by rotating the stator 33 to drive the rotor 34 to rotate Or it is stopped, for this purpose, the control unit 5 is a head housing 51 coupled to one side of the intermediate housing 32, the PCB 52 mounted inside the head housing 51, and on the PCB 52 It comprises a variety of electronic components such as a plurality of elements mounted on.

The compression unit 7 is a portion compressing the refrigerant by rotating by the rotational driving force generated by the driving unit 3, and is connected to the rear end of the rotation shaft 37 of the driving unit 3 as shown in FIG. 1.

In this case, the compression unit 7 includes a swing scroll 71 rotatably mounted at the rear end of the drive unit housing 31, and a fixed scroll 72 paired with the swing scroll 71 to compress the refrigerant. The refrigerant flowing into the compression chamber 73 formed therebetween is compressed by the relative rotation of the turning scroll 71 and the fixed scroll 72.

Looking in more detail, the turning scroll 71 is formed in the spiral spiral curved wrap wrap (71a) protruding on the rear side to converge toward the center, the center of the turning scroll wrap (71a) of the drive unit (3) The rear end of the rotary shaft 37 is engaged to rotate in synchronization with the rotor 34.

In addition, the fixed scroll 72 is fixedly installed at the inner rear end of the drive unit housing 31, and the fixed scroll wrap 72a curved in a spiral shape so as to match with the swing scroll wrap 71a of the swing scroll 71 is the center It is formed to converge toward.

Therefore, when the turning scroll 71 rotates, the rotating scroll 71 and the fixed scroll 72 that are matched with each other are driven by the interaction of the turning and fixed scroll wraps 71a and 72a, respectively. The refrigerant sucked into the outer edges of the swing and fixed scroll wrap (71a, 72a) is compressed to the center portion, the refrigerant compressed at a high pressure is a cover housing (to be described later through the discharge port 72b formed through the fixed scroll 72 ( It is discharged to the high pressure chamber 75 in 74.

At this time, the cover housing 74 is coupled to the rear end of the drive housing 31 so that one side opening is toward the rear of the fixed scroll 72, the discharge on the one side of the cover housing 74 to discharge the compressed refrigerant to the outside Port 76 is formed through.

That is, the refrigerant compressed in the compression chamber 73 is discharged into the high pressure chamber 75 through the discharge port 72b, and the high pressure refrigerant discharged into the high pressure chamber 75 is the cover housing (as shown in FIG. 2). It flows along the flow path 82 partitioned by the guide wall 81 in 74, and is finally supplied to the outside through the discharge port 76.

At this time, the high pressure refrigerant introduced into the high pressure chamber 75 and discharged to the outside through the discharge port 76 includes not only a high pressure refrigerant gas but also a large amount of lubricating oil supplied for smooth operation of the scroll compressor 1. It is contained.

Therefore, the conventional scroll compressor has a high oil content in the compressed refrigerant, which lowers the heat exchange efficiency of the refrigerant and, as the oil is discharged to the outside of the scroll compressor together with the refrigerant, continuously supplies oil to the scroll compressor, thus wasting oil. There are many problems.

The present invention has been made to solve the above problems, an embodiment of the present invention, by forming an oil separation groove on one side of the guide wall in contact with the inner wall of the cover housing, the refrigerant impinging on the inner wall of the cover housing It is associated with a scroll compressor that separates oil from the oil.

At this time, the oil separation groove is connected to the other side of the guide wall along the inner wall of the cover housing, when the refrigerant flows along the guide wall and collides with the inner wall of the cover housing, the oil contained in the refrigerant flows into the oil separation groove The pressure is separated to the other side of the guide wall.

According to a preferred embodiment of the present invention, the cover housing is provided with a compression unit for sucking the refrigerant to compress by the fixed scroll and the swing scroll, and a discharge port is installed on one side of the compression unit, the discharge port for the compressed refrigerant is discharged to the external refrigeration circuit And a discharge port communicating with the compression section and the cover housing, wherein the cover housing has a high pressure chamber formed between the discharge port and the discharge port, wherein the high pressure chamber is divided by a plurality of guide walls and a plurality of guide walls. Two flow paths are formed, and at least one oil separation groove is formed at one side of the guide wall forming the outermost flow path among the flow paths.

Here, the plurality of flow paths may include a plurality of curved flow paths formed at a predetermined curvature to be spaced apart from each other in the radial direction at the central portion of the cover housing.

In addition, the plurality of flow passages may include a plurality of straight passages each extending from the one side of the central portion of the cover housing to a plurality of curved passages spaced apart from each other at predetermined intervals.

According to the scroll compressor according to an embodiment of the present invention, as the oil is separated from the refrigerant supplied to the outside of the scroll compressor through the discharge port, there is an effect that the heat exchange efficiency of the refrigerant is improved compared to the conventional.

In addition, since it is possible to reuse the separated oil, it is possible to prevent waste of oil and increase the amount of oil remaining in the scroll compressor, thereby improving the durability of the scroll compressor.

1 is a cross-sectional view showing the configuration of a scroll compressor according to the prior art.
Figure 2 is a schematic view showing the configuration of a cover housing according to the prior art.
3 is a schematic view showing a configuration of a cover housing to which the oil separation structure is applied according to an embodiment of the present invention.
Figure 4 is a use state showing the state that the refrigerant passes through a plurality of flow paths formed in the cover housing according to an embodiment of the present invention.

Hereinafter, a preferred embodiment of a scroll compressor according to an embodiment of the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation.

In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

In addition, the following embodiments are not intended to limit the scope of the present invention, but merely as exemplifications of the constituent elements set forth in the claims of the present invention, and are included in technical ideas throughout the specification of the present invention, Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

Example

As shown in FIG. 1, in the case of the scroll compressor 1, refrigerant introduced into the inside of the suction port 38 provided on one side of the driving unit housing 31 is formed of the fixed scroll 72 and the turning scroll 71. After compression in the compression chamber 73 by relative rotation, it is supplied to the outside through the discharge port 76.

At this time, one side of the fixed scroll 72 is formed by the combination of the cover housing 74 having a space therein, the high pressure chamber 75 is formed. In the center of the fixed scroll 72, a discharge port 72b is formed to communicate with the compression chamber 73 and the high pressure chamber 75.

Accordingly, the refrigerant compressed in the compression chamber 73 is introduced into the high pressure chamber 75 in the cover housing 74 through the discharge port 72b, and the discharge port 76 penetrated through one side of the cover housing 74 is opened. Supplied through the outside.

Here, in the scroll compressor according to an embodiment of the present invention, an oil separation structure is formed at one side of the cover housing 74. That is, the oil contained in the refrigerant is separated while the refrigerant flowing into the high pressure chamber 75 of the cover housing 74 through the discharge port 72b flows to the discharge port 76 in the high pressure chamber 75. .

3 is a schematic view showing a configuration of a cover housing to which an oil separation structure is applied according to an embodiment of the present invention.

As shown in FIG. 3, the cover housing 100 to which the oil separation structure is applied according to an embodiment of the present invention has a discharge port 300 formed at one side such that the refrigerant is discharged to the outside, and the space inside thereof has a high pressure. The yarn 75 (see Fig. 1) is formed.

In addition, at least one flow path (A to F) is formed in the cover housing 100 by at least one or more guide walls partitioning the high pressure chamber. In this case, each of the flow paths A to F extend from one side of the central portion 110 of the cover housing 100 corresponding to the discharge port 72b (see FIG. 1) to one side of the discharge port 300.

The high pressure chamber is divided into a plurality of spaces by the guide walls, and the divided spaces become flow paths A to F that respectively guide the flow direction of the refrigerant. In this case, the number of passages formed in the partition may be appropriately selected in consideration of the size of the cover housing 100 and the performance of the compressor.

The guide wall partitioning the high pressure chamber into a plurality of spaces may include a blocking wall 210, a straight guide wall 221 ˜ 226, and a curved guide wall 231 ˜ 234.

Here, the blocking wall 210 serves to prevent the refrigerant introduced into the high pressure chamber through the discharge port from being immediately discharged through the discharge port 300 without passing through a separate flow path. To this end, a blocking wall 210 is formed between the central portion 110 and the discharge port 300 of the cover housing 100 facing the discharge port.

Preferably, the blocking wall 210 is formed in an arc shape having a predetermined angle spaced apart from the center of the cover housing 100 in the discharge port 300 direction.

The linear guide walls 221 to 226 guide the refrigerant introduced into the high pressure chamber through the discharge ports to the respective flow paths A to F. To this end, straight guide walls 221 to 226 from one side of the central portion 110 of the cover housing 100 facing the discharge port to the curved guide walls 231 to 234 or the inner wall 120 of the cover housing 100 to be described later. This extends.

In addition, since the linear guide walls 221 to 226 are formed to be spaced apart from each other by a predetermined interval, the space between the linear guide walls 221 to 226 and the linear guide walls 221 to 226 adjacent to each other is a straight channel A1 to F1. The straight flow paths A1 to F1 communicate with the curved flow paths A2 to F2 each formed of a space between the curved guide walls 231 to 234 and the curved guide walls 231 to 234 described later.

At this time, the refrigerant flowing into the high pressure chamber through the discharge port is preferably uniformly distributed in each of the flow path (A ~ F).

Therefore, each of the straight passages A1 to F1 is preferably spaced apart from each other along a circumference of an imaginary circle whose radius is the distance from the center of the cover housing 100 to the blocking wall 210. It may be formed parallel to each other or radially.

In this case, the straight guide walls 221 and 222 formed closest to the blocking wall 210 form straight flow paths A1 and B1 together with one end of the blocking wall 210, and are formed farthest from the blocking wall 210. The straight guide walls 225 and 226 extend to the inner wall 120 of the cover housing 100.

The curved guide walls 231 to 234 serve to guide the refrigerant introduced into the high pressure chamber through the discharge port to the discharge port 300 and are spaced apart from each other in the radial direction at the center of the cover housing 100 to have a predetermined curvature. .

Therefore, the curved flow paths A2 to F2 formed of the space between the curved guide walls 231 to 234 and the curved guide walls 231 to 234 adjacent to each other are also spaced apart from each other in the radial direction at the center of the cover housing 100. It is formed with a curvature of, and each of the straight passages A1 to F1 communicate with each of the curved passages A2 to F2.

In this case, the curved guide walls 231 and 232 formed closest to the center of the cover housing 100 form the curved flow paths A2 and B2 together with the blocking wall 210 described above and are farthest from the center of the cover housing 100. The formed curved guide walls 233 and 234 form curved flow paths E2 and F2 together with the inner wall 120 of the cover housing 100.

According to one embodiment of the present invention, the oil separation groove 236 is formed on one side of the straight guide walls 225, 226 extending to abut on the inner wall 120 of the cover housing 100.

In more detail, the straight guide walls 225 and 226 formed farthest from the blocking wall 210 extend to abut against the inner wall 120 of the cover housing 100 to form straight flow paths E1 and F1. The flow paths E1 and F1 are connected to the curved flow paths E2 and F2 formed by the curved guide walls 233 and 234 formed farthest from the center of the cover housing 100 and the inner wall 120 of the cover housing 100.

At this time, one end of the oil separation groove 236 is formed on one side of the straight guide wall (225,226) in contact with the inner wall 120 of the cover housing 100, the other end of the oil separation groove 236 of the cover housing 100 Passing through the inner wall 120 is formed on the other side of the straight guide wall (225,226).

In other words, the straight guide walls 225 and 226 abutting against the inner wall 120 of the cover housing 100 are interposed therebetween, and the cover housing 100 passes through the inner wall of the cover housing 100 at one side of the curved passages E2 and F2. Oil separation groove 236 is formed to the bottom of the central portion 110).

Accordingly, the refrigerant flowing into the straight passages E1 and F1 along the straight guide walls 225 and 226 extending to abut against the inner wall 120 of the cover housing 100 is before entering the curved passages E2 and F2. The oil is separated while colliding with the inner wall 120 of the cover housing 100, and the separated oil flows into one end of the oil separation groove 236.

In this case, a relatively high dynamic pressure is formed at a portion where the refrigerant collides with the inner wall 120 of the cover housing 100, and the oil in the oil separation groove 236 passes through the other end of the oil separation groove 236. It is discharged to the lower end of the central portion 110 of the cover housing 100.

The separated and recovered oil may be discharged or recovered through, for example, a recovery port (not shown) formed through one side of the lower end of the central portion 110 of the cover housing 100.

On the other hand, one side of the cover housing 100 is formed with a discharge port 300 to supply the compressed refrigerant to the outside, the inside of the discharge port 300 each of the above-described curved flow path (A2 ~ F2) is in communication Attenuation space 400 is formed.

At this time, at the ends of the curved guide walls 231 to 234 extending to the attenuation space 400, a protrusion 235 is formed in the flow path direction so that the space between the protrusions 235 can form the shape of a nozzle. The shape of the nozzle formed by the protrusion 235 may be formed at the end portions of the straight guide walls 221 to 226 contacting the central portion 110 of the cover housing 100.

In addition, based on the imaginary straight line L connecting the center of the cover housing 100 and the discharge port 300, the respective curved flow paths (A2 to F2) are formed on both left and right sides, respectively. A2 to F2) are formed asymmetrically different in length from each other.

This is to allow the discharge pulsations transmitted through the curved passages A2 to F2 to reach the attenuation space 400 in a timed manner by varying the lengths of the curved passages A2 to F2. Therefore, the pulsations having different phase differences are finally canceled in the attenuation space 400, and the pulsation of the refrigerant supplied to the outside through the discharge port 300 is reduced.

At this time, on the basis of the virtual straight line (L), the oil separation groove 236 is preferably formed in a pair one by one in the outermost flow path (E, F) on both sides.

4 is a state diagram showing the use of the refrigerant passing through a plurality of flow paths formed in the cover housing according to an embodiment of the present invention.

In the present embodiment, but shown an example in which a total of six flow paths (A to F) are formed, each of the left and right three, is not limited thereto, and the number of flow paths may be appropriately selected in consideration of the size of the cover housing 100 and the performance of the compressor. Can be.

Hereinafter, the present invention will be described with reference to the embodiment of FIG. 4.

Three curved flow paths A2 to F2 are formed on the left and right sides of the cover housing 100 based on an imaginary straight line L connecting the center of the cover housing 100 and the discharge port 300. At this time, since each of the curved passages A2 to F2 is formed asymmetrically with respect to the imaginary straight line L, the lengths of the respective passages A to F including the straight passages A1 to F1 are different from each other ( L _A <L _B <L _C <L _D <L _E <L _F ).

In addition, the oil separation grooves 236 are formed at one side of the linear guide walls 225 and 226 of the outermost flow paths E and F, which are formed at the left and right sides on the basis of the virtual straight line L, respectively. When the refrigerant flowed into the inner wall 120 of the cover housing 100 collides with the oil, the oil contained in the refrigerant is separated, and the separated oil passes through the oil separation groove 236 at the bottom of the central portion of the cover housing 100. Is discharged.

Meanwhile, the pulsating pressures of the refrigerant flowing into the attenuation space 400 through each of the flow paths A to F cancel each other so that each flow path A can be uniformly supplied to the outside through the discharge port 300. It is preferable that the quantity of the refrigerant flowing through ˜F) is the same.

Therefore, the longer the length of the flow paths A to F, the higher the flow resistance and the lower the flow rate of the fluid. Therefore, the cross-sectional area of the longest flow path F is the largest and the cross-sectional area of the shortest flow path A is increased. It is preferable to make the smallest (A _A <A _B <A _C <A _D <A _E <A _F ).

According to one embodiment of the invention, the flow of refrigerant and separation of oil proceeds as follows.

The refrigerant flows into the drive housing 31 through the suction port 38 provided at one side of the drive housing 31. By the rotational movement of the revolving scroll 71, the fixed scroll wrap 72a of the fixed scroll 72 and the revolving scroll wrap 71a of the revolving scroll 71 center the space of the compression chamber 73 therebetween. The refrigerant is compressed while being gradually reduced toward the oil, and the compressed refrigerant is discharged into the high pressure chamber 75 through the discharge port 72b.

At this time, the refrigerant flows into the central portion 110 of the cover housing 100 corresponding to the discharge port 72b in the high pressure chamber 75, and does not flow directly to the discharge port 300 due to the blocking wall 210. It flows in and flows into the flow paths A-F.

Each of the flow paths A to F includes a straight path A1 to F1 and a curved path A2 to F2, and the curved paths A2 to F2 are spaced apart from each other in a radial direction at the center of the cover housing 100. It is formed with a predetermined curvature, and the straight passages A1 to F1 are formed to be spaced apart from each other along a circumference of an imaginary circle whose radius is the distance from the center of the cover housing 100 to the blocking wall 210.

In this case, an oil separation groove 236 is formed at one side of the outermost flow paths E and F which are formed farthest from the center of the cover housing 100, and the coolant collides with the inner wall 120 of the cover housing 100. The separated oil is discharged or introduced into the bottom of the central portion 110 of the cover housing 100 through the oil separation groove 236.

A-F: Euro
A1 ~ F1: Straight flow path A2 ~ F2: Curved flow path
100: cover housing
110: center portion 120: inner wall
210: barrier wall
221 ~ 226: straight guide wall 231 ~ 234: curved guide wall
235: protrusion 236: oil separation groove
300: discharge port
400: attenuation space

Claims (3)

A compression unit 7 which sucks the refrigerant and compresses it by the fixed scroll 72 and the swing scroll 71;
A cover housing 100 installed at one side of the compression unit 7 and having a discharge port 300 through which compressed refrigerant is discharged to an external refrigeration circuit;
Discharge port 72b for communicating the compression section 7 and the cover housing 100,
In the scroll compressor, the high pressure chamber 75 is formed between the discharge port 72b and the discharge port 300 in the cover housing 100,
The high pressure chamber 75 is partitioned by a plurality of guide walls and a plurality of flow paths A to F are formed by the guide walls.
Scroll compressor, characterized in that at least one oil separation groove 236 is formed on one side of the guide wall (225,226) forming the outermost flow path of the flow path (E, F).
The method according to claim 1, wherein the plurality of flow path (A to F),
Scroll center, characterized in that it comprises a plurality of curved passages (A2 ~ F2) formed in a predetermined curvature spaced apart from each other in the radial direction in the center of the cover housing (100).
The method according to claim 2, wherein the plurality of flow path (A to F),
Scroll compressor, characterized in that it comprises a plurality of straight passages (A1 ~ F1) extending from the one side of the central portion 110 of the cover housing 100 to each of the plurality of curved passages (A2 ~ F2) spaced apart from each other at predetermined intervals. .

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