KR101529928B1 - Rotary compressor - Google Patents

Abstract

The present invention relates to a rotary compressor. The rotary compressor according to the present invention can improve the performance of the compressor by sealing the upper and lower sides of the vane with sealing members to seal the vane and the upper and lower bearings between the vane and the vane to reduce leakage of the refrigerant between the bearing and the vane. Further, it is possible to improve the performance of the compressor by connecting the sealing member to the front end surface of the vane and reducing the leakage of the refrigerant between the vane and the rolling piston. Also, since the sealing members are made of a material having a low coefficient of friction, the frictional loss is reduced and the input to the compressor is reduced, so that the performance of the compressor can be improved. Further, the sealing member coupled to the end surface of the vane may be press-fitted, insert molded or insert die casted to facilitate machining of the rolling piston and the vane, thereby reducing manufacturing costs.

Rolling piston, vane, sealing, friction

Description

ROTARY COMPRESSOR

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly, to a rotary compressor capable of remarkably reducing a leakage amount of refrigerant and reducing manufacturing cost when a vane is integrally coupled to a rolling piston.

Generally, a refrigerant compressor is applied to a vapor compression refrigeration cycle such as a refrigerator or an air conditioner (hereinafter abbreviated as a refrigeration cycle). The refrigerant compressor is a constant velocity compressor driven at a constant speed or an inverter-type compressor whose rotation speed is controlled.

The refrigerant compressor is generally called a hermetic compressor in which a driving motor, which is a motor, and a compression unit that is operated by the driving motor are installed together in an internal space of a hermetically sealed casing. In the case where the driving motor is separately provided outside the casing, It can be called a compressor. Most of the refrigeration appliances for home use or commercial use are hermetically sealed compressors. The refrigerant compressor may be classified into a reciprocating type, a scroll type, and a rotary type according to a method of compressing a refrigerant.

The rotary compressor includes a cylinder and a rolling piston which eccentrically rotates in a compression space formed by an upper bearing and a lower bearing that cover both upper and lower sides of the cylinder, and a rolling piston which reciprocates in contact with an outer circumferential surface of the rolling piston, And a refrigerant is compressed by using a vane which is divided into a suction region and a discharge region. Recently, a structure has been proposed in which the vane is inserted into a rolling piston and integrally joined to prevent the refrigerant from leaking between the rolling piston and the vane. In this case, when a high-pressure refrigerant such as R410A is applied, the sealing force of the vane that distinguishes between the suction region and the discharge region may be an important factor in the performance of the compressor, and therefore research has been extensively conducted to integrally join the vane to the rolling piston.

However, in the conventional rotary compressor as described above, the refrigerant leakage generated between the rolling piston and the vane can be effectively blocked, but the leakage of the refrigerant generated between the vane and the upper and lower bearings is maintained to improve the performance of the compressor. . In particular, since the upper and lower side bearings and the vane are portions for friction movement, if the vane is excessively brought into close contact with the vane, the vane may be unstable and the suction region and the discharge region may not be partitioned. On the contrary, The refrigerant leakage is increased. Therefore, the tolerance between the vane and the bearing needs to be precisely controlled in the order of several micrometers, which may complicate the machining operation and increase the defect rate, thereby increasing manufacturing costs.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary compressor capable of effectively preventing the refrigerant from leaking between the vane and the upper and lower bearings, And has the object of the present invention.

In order to accomplish the object of the present invention, there is provided a cylinder in which a vane slot is formed; A pair of bearings for covering upper and lower sides of the cylinder and forming a compression space on both sides of the vane slot so that the suction port and the discharge port communicate with each other; A rolling piston supported by the pair of bearings and swirling in the compression space; And a vane slidably coupled to the vane slot of the cylinder in a radial direction to divide the compression space of the cylinder into a suction region and a discharge region together with the rolling piston, A first sealing groove is formed in a moving direction of the surface, and a first sealing member is inserted in the first sealing groove so as to face the bearing.

The rotary compressor according to the present invention is characterized in that a seal member having good lubrication is provided on both upper and lower sides of the vane so that the clearance between the vane and the bearings can be made narrower and the leakage of the refrigerant compressed thereby is reduced, Can be improved. Further, since a sealing member having a good lubricating property is provided between the vane and the bearing, the frictional loss between the vane and the bearing is reduced, and the input to the compressor is reduced, so that the performance of the compressor can be improved. Also, since the sealing member is provided at the end of the vane and is integrally coupled to the rolling piston, the refrigerant leakage between the rolling piston and the vane is effectively reduced, thereby further improving the performance of the compressor.

The rotary compressor of the present invention will be described in detail based on the embodiment shown in the accompanying drawings.

As shown in FIG. 1, in the rotary compressor according to the present invention, the transmission portion 200 and the compression portion 300 are installed together in an internal space of the closed container 100.

The electromotive unit 200 includes a stator 210 wound with a coil and fixed to the hermetic container 100, a rotor 220 rotatably installed inside the stator 210, And a crankshaft 230 which is press-fitted into the crankshaft 220 and rotates together.

The compression unit 300 includes a cylinder 310 formed in an annular shape, an upper bearing 320 for covering the upper side of the cylinder 310, a lower bearing 330 for covering the lower side of the cylinder 310, A rolling piston 340 rotatably coupled to an eccentric portion of the crankshaft 230 and disposed in a compression space of the cylinder 310 and a piston 310 rotatably coupled to the rolling piston 340, And a vane 350 coupled to the vane slot 312 to reciprocate linearly. A first sealing member 361 and a second sealing member 362 interposed between the vane 350 and the bearings 320 and 330 to reduce the leakage of the refrigerant and the rolling piston 340 and the vane 350 And a second sealing member 370 interposed between the first sealing member 370 and the second sealing member 370 to reduce refrigerant leakage.

The cylinder 310 has a suction port 311 radially formed on one side thereof and a vane slot 312 is radially formed on one side of the suction port 311 so that the vane 350 is slidably inserted.

A discharge port 321 is formed at one side of the upper bearing 320 so that the refrigerant compressed in the compression space is discharged to the inner space of the hermetic container 100. The upper bearing 320 and the lower bearing 330 are formed at their centers with journal bearing surfaces 322 and 331 so as to support the crank shaft 230 in a radial direction and journal bearing surfaces 322 and 331, The thrust surfaces 323 and 332 are formed on the vertical surface of the crankshaft 230 so as to support the crankshaft 230, the rolling piston 340 and the vane 350 in the axial direction.

In the figure, reference numeral 110 denotes a suction pipe, 120 denotes a discharge pipe, and 130 denotes an accumulator.

When the rotor 220 is rotated by the power applied to the stator 210 of the driving unit 200, the crankshaft 230 rotates together with the rotor 220, And transmits the rotational force of the driving unit 200 to the rolling piston 340 of the compression unit 300. The rolling piston 340 is pivotally moved by the crankshaft 230 and the refrigerant is moved from the suction region to the discharge region while the vane 350 is closed to compress the refrigerant, And is discharged to the inner space of the closed vessel 100 through the discharge port 321.

At this time, the vane 350 is inserted into the vane slot 312 of the cylinder 310 so that the vane 350 is axially moved with respect to the thrust surface 323 of the upper bearing 320 and the thrust surface 332 of the lower bearing 330 And reciprocates in a substantially radial direction along the pivoting motion of the rolling piston 340 in a supported state. Therefore, there is a certain tolerance between the vane 350 and the bearings 320 and 330. However, if the tolerance is too small, the behavior of the vane 350 becomes unstable, and if it is too large, the refrigerant leakage occurs.

In order to reduce both the friction loss and the refrigerant leakage between the vane 350 and the bearings 320 and 330, the first and second sealing members 330 and 330 are provided on both upper and lower sides of the vane 350, (361) and (362).

As shown in FIGS. 2 to 5, the vane 350 has a hexahedral shape and a body 351 is formed. A first sealing groove 351a and a first sealing groove 351b are formed at both upper and lower sides of the body portion 351 so as to allow the first sealing members 361 and 362 to be inserted into the body portion 351, .

3 and 4, the length of the first sealing grooves 351a and 351b is not shorter than the moving distance of the vane 350, more preferably longer than the moving distance of the vane 350 In the compression space S, as close as possible to the end of the rolling piston 340 at the end of the rolling piston 340 and at the opposite end to the end of the vane slot 312 (as far as possible) so that the first sealing members 361, As shown in Fig. For example, the first sealing grooves 351a and 351b are formed such that both ends of the first sealing grooves 351a and 351b are in contact with or inserted into the inner circumferential surface of the cylinder 310 and the outer circumferential surface of the rolling piston 340, The sealing force can be increased.

The first sealing members 361 and 362 are inserted into the first sealing grooves 351a and 351b so that both ends of the first sealing members 361 and 362 can be inserted into the inner circumferential surface of the cylinder 310 and the rolling piston 340, It is preferable that the sealing member is formed to have a length at least tangent to or inserted into the outer peripheral surface of the sealing member.

The first sealing members 361 and 362 may be formed of Teflon having a friction coefficient lower than that of the bearings 320 and 330 or the vane 350 or may be formed of an engineer plastic or aluminum material such as a peak . When the first sealing members 361 and 362 are made of aluminum, aluminum (Al) is 85 to 92wt%, tin (Sn) is 5 to 7.5wt%, silicon (Si) An aluminum material having a copper (Cu) content of 0.8 to 1.5 wt% may be utilized.

5, the depth of the first sealing grooves 351a and 351b is not greater than the axial height of the first and second sealing members 361 and 362, (362) can always protrude from both the upper and lower sides of the vane (350).

However, when the first sealing members 361 and 362 float in the first sealing grooves 351a and 351b and are brought into contact with the upper and lower bearing surfaces of the first and second sealing members 361 and 362, The directional height may be smaller than the depth of the first sealing groove 351a. 6, a portion of the refrigerant compressed in the compression space S or a portion of the refrigerant discharged to the closed container 100 may be connected to the upper and lower ends of the upper and lower sides of the vane 350, The refrigerant guide grooves 351c and 351d may communicate with the first sealing grooves 351a and 351b so that a part of the refrigerant may flow into the first sealing groove 351a.

In the reciprocating compressor according to the present invention as described above, the vane 350 reciprocates almost linearly along the rolling motion of the rolling piston 340 and compresses the compression space S into the suction region V1 and the discharge region V2). Since the pressure of the discharge region V2 is considerably higher than the pressure of the suction region V1, the refrigerant in the discharge region V2 flows into the suction region V2 through the space between the vane 350 and the bearings 320, (V1). However, since the first sealing members 361 and 362 are provided on both upper and lower sides of the vane 350, it is possible to effectively prevent the refrigerant from leaking from the discharge region V2 to the suction region V1. In particular, even when a high-pressure refrigerant such as R410a is applied, it is possible to effectively prevent the refrigerant from leaking from the discharge region V2 to the suction region V1, thereby improving the performance of the compressor.

When the first sealing members 361 and 362 are formed of a material having a lubricating property such as Teflon more than the vane 350, the first sealing members 361 and 362 may be connected to the upper bearing 320 The frictional loss does not increase even when the lower bearing 330 is brought into intimate contact with the lower bearing 330. Therefore, the first sealing member 361 can be brought into close contact with the surfaces of both the thrust bearings as tight as possible,

Since the first sealing members 361 and 362 are installed on both upper and lower sides of the vane 350, it is not necessary to precisely control the machining error of the vane 350, so that the vane 350 can be easily processed . This is because even though the first sealing members 361 and 362 are formed of a material having a good lubricating property and the first sealing members 361 and 362 are closely contacted with the both side bearings 320 and 330 The loss does not increase.

Meanwhile, the vane 350 may be inserted into the rolling piston 340 with its front end surface inserted into the rolling piston 340. And in this case, the vane 350 may be integrally coupled to the rolling piston 340, or may be rotatably coupled. 3 to 6, it is preferable that the one end of the first sealing member 361, 362, that is, the end of the rolling piston 340 side is inserted into the inside of the rolling piston 340, Can be effectively reduced. The other end of the first sealing members 361 and 362, that is, the end of the cylinder 310 at the side of the cylinder 310, is always formed in the vane slot 312, so that leakage of the refrigerant can be effectively reduced.

4 and 5, the vane 350 may be rotatably coupled to the second sealing groove 341 of the rolling piston 340 by providing a second sealing member 370 at an end thereof have. To this end, the vane 350 has a fixing portion 352 for fixing the second sealing member 370 at the tip end thereof.

As described above, the fixing portion 352 gradually moves from the portion of the main body portion 351 accommodated in the second sealing groove 341 of the rolling piston 340 toward the end of the rolling piston 340 The width is formed to be wider. Here, the starting end position of the fixing portion 352 may be within a range of being accommodated in the second sealing groove 341.

In the fixing portion 352, coupling grooves 353 may be formed on both sides in the vertical direction. That is, the coupling groove 353 must have a shape that allows the sealing member 360 to generate a kind of resistance force with respect to the moving direction of the vane 350, As shown in Fig. In this case, the coupling groove 353 may be formed in a variety of shapes such as a rectangular cross section or a semicircular groove.

In this case, the rolling piston 340 is formed in an annular shape and is rotatably coupled to the eccentric portion of the crank shaft 230, and is formed at one side of the outer circumferential surface of the rolling piston 340, The second sealing groove 341 is formed to be long in the axial direction so that a part of the vane 350, more precisely the second sealing member 370, can be inserted. It is preferable that the second sealing groove 341 is formed larger than a half circle cross-section at the time of a flat projection, so that the second sealing member 370 can support the second sealing member 370 in the radial direction.

4, the second sealing groove 341 is formed inside the outer circumferential surface of the rolling piston 340, and the vane 350 is rotated to the outside of the second sealing groove 341 A fan-shaped rotation guide groove 342 may be further formed. Here, the rotation center of the rotation guide groove 342 may be formed to coincide with the rotation center of the second sealing groove 341. In this case, the second sealing groove 341 may be formed such that the arc angle thereof is substantially equal to or larger than the arc angle of the second sealing member 370.

The second sealing member 370 is press-fitted into the end of the vane 350, that is, the fixing portion 352 of the vane 350, or is coupled by insert molding or insert die casting. The material of the second sealing member 370 may be the same material as the first sealing member 361 or 362 or a peak having a lower friction coefficient than the rolling piston 340 or the vane 350 It can be made of engineer plastic or aluminum material. When the second sealing member 370 is aluminum, the first sealing member 361 and the second sealing member 362 may be formed of aluminum (Al) in an amount of 85 to 92% by weight, tin (Sn) in an amount of 5 to 7.5% , Aluminum (Si) in an amount of 5 to 6.5 wt%, and copper (Cu) in an amount of 0.8 to 1.5 wt%.

The second sealing member 370 is coupled to the end of the vane 350, that is, the fixing portion 352 of the vane 350, and the second sealing member 370, Is inserted into the second sealing groove (341) of the rolling piston (340), the rolling piston (340) is angularly moved in a predetermined angle along the pivotal motion, 310 reciprocate in the vane slot 311. [

At this time, the sealing area between the second sealing groove 341 of the rolling piston 340 and the outer circumferential surface of the second sealing member 360 is increased, so that the sealing area is increased in the discharging area V2 The leakage of the compressed high-pressure refrigerant into the suction region V1 can be minimized. Also, even when a high-pressure refrigerant such as R410a is applied as in the case of the first sealing members 361 and 362, it is possible to effectively prevent the refrigerant from leaking from the discharge region V2 to the suction region V1, Can be improved. In addition, since the second sealing member 360 is formed of a material having a low coefficient of friction, the frictional loss between the rolling piston 340 and the second sealing member 360 can be reduced, thereby reducing the input to the compressor So that the performance of the compressor can be further improved.

The rotary compressor according to the present invention can be easily processed in comparison with the conventional rotary compressor. That is, in order to assemble the rolling piston and the vane integrally, the sealing groove of the rolling piston and the sealing protrusion of the vane have to be precisely machined to several micrometers in the above-described embodiment. However, The sealing member of the rolling piston is manufactured in a large quantity using a metal mold and is press-fitted into the fixed portion of the vane or combined with an insert molding or an insert die casting method having high dimensional accuracy, Thereby reducing the manufacturing cost of the compressor.

Meanwhile, another embodiment of the rotary compressor according to the present invention is as follows.

That is, in the above-described embodiment, the vane is inserted into the rolling piston so as to be integrally coupled. However, in this embodiment, even when the vane is coupled to the outer circumferential surface of the rolling piston, Member can be installed.

For example, when the compression space S is divided into the suction area V1 and the discharge area V2 by contacting the front end face of the vane 350, that is, the outer peripheral face of the rolling piston 340, Step portions 354 and 354 are formed on both upper and lower sides of the vane 350 and the first sealing groove 351a is formed on both upper and lower surfaces between the step portions 354 and 354 351b, respectively.

The first and second seal members 361 and 362 are not engaged with each other in the longitudinal direction of the vane 350 at a predetermined distance from both the bearings 320 and 330 The second sealing members 361 and 362 may be formed to be higher than both end portions of the vane 350 in the longitudinal direction so as to closely contact the bearings 320 and 330.

Also in this case, since sealing members 361 and 362 having good lubricating properties are provided on both upper and lower sides of the vane 350, the frictional loss between the vane 350 and the bearings 361 and 362 is not increased The sealing force can be increased.

The rotary compressor according to the present invention can be equally applied to a single rotary compressor as well as a double rotary compressor in which a cylinder is installed in a multi-layered manner as described above. The present invention is equally applicable to a compressor of a refrigeration apparatus to which the above rotary compressor is applied.

1 is a longitudinal sectional view showing a rotary compressor according to the present invention,

FIG. 2 is a perspective view of a rolling piston, a vane and a first sealing member in a rotary compressor according to FIG. 1,

FIGS. 3 and 4 are plan views showing the assembled state of the rolling piston and the vane in the rotary compressor of FIG. 2,

5 is a sectional view taken along the line "I-I" in Fig. 4,

FIG. 6 is a sectional view showing another embodiment of the vane according to FIG. 3;

FIG. 7 is a plan view showing another embodiment of a coupling method of a rolling piston and a vane in the rotary compressor according to FIG. 1;

8 is a sectional view taken along the line "II-II" in Fig.

Description of Reference Numerals in Main Parts of the Drawings

310: cylinder 311: vane slot

340: rolling piston 341: sealing groove

342: rotation guide groove 350: vane

351: main body portion 352:

361, 362: first sealing member 370: second sealing member

Claims (12)

A cylinder in which a vane slot is formed; A pair of bearings for covering upper and lower sides of the cylinder and forming a compression space on both sides of the vane slot so that the suction port and the discharge port communicate with each other; A rolling piston supported by the pair of bearings and swirling in the compression space; And And a vane slidably coupled to the vane slot of the cylinder in a radial direction to divide the compression space of the cylinder into the suction area and the discharge area together with the rolling piston, A first sealing groove is formed in at least one of the axially opposite side surfaces of the vane in a moving direction, a first sealing member is inserted into the first sealing groove so as to face the bearing, The vane is inserted and coupled to the outer circumferential surface of the rolling piston at a predetermined depth so that both ends of the vane can contact or be inserted into the outer circumferential surface of the rolling piston, The rotary compressor being formed. delete delete The method according to claim 1, Wherein the axial height of the first sealing member is greater than or equal to the depth of the first sealing groove. delete The method according to claim 1, And the gas guide groove communicates with at least one of the ends of the first sealing groove so as to guide a high-pressure gas between the bottom surface of the first sealing groove and the bottom surface of the first sealing member. The method according to claim 6, Wherein a height of the first sealing member in the axial direction is smaller than or equal to a depth of the first sealing groove. A cylinder in which a vane slot is formed; A pair of bearings for covering upper and lower sides of the cylinder and forming a compression space on both sides of the vane slot so that the suction port and the discharge port communicate with each other; A rolling piston supported by the pair of bearings and swirling in the compression space; And And a vane slidably coupled to the vane slot of the cylinder in a radial direction to divide the compression space of the cylinder into the suction area and the discharge area together with the rolling piston, A first sealing groove is formed in at least one of the axially opposite side surfaces of the vane in a moving direction, a first sealing member is inserted into the first sealing groove so as to face the bearing, And a second sealing member is integrally coupled to an end of the vane and the second sealing member is rotatably coupled to an outer circumferential surface of the rolling piston. 9. The method of claim 8, And a second sealing groove is formed on an outer circumferential surface of the rolling piston so as to be axially long so that the second sealing member can be rotatably engaged. 10. The method of claim 9, Wherein one end of the first sealing member is located inside the rolling piston and the other end of the first sealing member is located inside the vane slot even when the vane is drawn out most from the vane slot. A cylinder in which a vane slot is formed; A pair of bearings for covering upper and lower sides of the cylinder and forming a compression space on both sides of the vane slot so that the suction port and the discharge port communicate with each other; A rolling piston supported by the pair of bearings and swirling in the compression space; And And a vane slidably coupled to the vane slot of the cylinder in a radial direction to divide the compression space of the cylinder into the suction area and the discharge area together with the rolling piston, A first sealing groove is formed in at least one of the axially opposite side surfaces of the vane in a moving direction, a first sealing member is inserted into the first sealing groove so as to face the bearing, The end of the vane is in contact with the outer circumferential surface of the rolling piston. A stepped surface is formed on both upper and lower sides of the vane at a predetermined height. A first sealing groove is formed in the stepped surface to insert the first sealing member Rotary compressor. A cylinder in which a vane slot is formed; A pair of bearings for covering upper and lower sides of the cylinder and forming a compression space on both sides of the vane slot so that the suction port and the discharge port communicate with each other; A rolling piston supported by the pair of bearings and swirling in the compression space; And And a vane slidably coupled to the vane slot of the cylinder in a radial direction to divide the compression space of the cylinder into the suction area and the discharge area together with the rolling piston, A first sealing groove is formed in at least one of the axially opposite side surfaces of the vane in a moving direction, a first sealing member is inserted into the first sealing groove so as to face the bearing, Wherein the first sealing member is formed of a material having better lubricating property than the vane.

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