Compressor

Abstract

A compressor, capable of reducing friction among a vane and parts which perform relative motion with the vane in driving the compressor by using materials having thermal expansion coefficient of the vane as same as or higher than 2.5×10−5/° C., reducing consumption of activation energy and friction loss by gaining lower friction coefficient and higher abrasion resistance, reducing abrasion of the parts, controlling heat transfer, and increasing suction amount of refrigerant gas, can improve compression performance.

Description

TECHNICAL FIELD

[0001] The present invention relates to a compressor and particularly, to a vane of a compressor and mounting structure thereof, capable of minimizing friction loss and generation of frictional heat caused by relative motion in operating a compressor.

BACKGROUND ART

[0002] Generally, a compressor is an instrument for compressing gas such as refrigerant and the like. The compressor generally includes an electric mechanism unit for generating a driving force and a compression unit for compressing gas by receiving the driving force of the above electric mechanism unit and is classified into a rotary compressor, a reciprocating compressor and a scroll compressor according to the compression mechanism of the compression unit.

[0003] FIGS. 1 and 2 show an embodiment of the compressor, as shown therein, a rotational shaft 30 coupled with a rotor 21 of a driving motor 20 rotates when the driving motor 20 mounted in the hermetic container 10 is driven and according to rotation of the rotational shaft 30, an eccentric portion 31 provided on the rotational shaft 30 eccentrically rotates in a compression space (P) of a cylinder 40 positioned at the lower side of the driving motor 20.

[0004] As the eccentric portion 31 of the rotational shaft 30 eccentrically rotates in the compression space (P) of the cylinder 40, a rolling piston 50 which is coupled with the eccentric portion 31 is linearly contacted on an inner wall of the compression space (P) of the cylinder 40 and performs a circular movement in the compression space (P) of the cylinder 40 under the condition that it is linearly contacted on the vane which is coupled with a vane slot 41 formed in the cylinder 40.

[0005] As the rolling piston 50 performs a circular movement in the compression space (P) of the cylinder 40, as the compression space (P) of the cylinder 40 divided by a vane 60 is converted into a suction region (a) and a compression region (b), refrigerant gas is sucked through a suction port 42 provided on the cylinder 40, compressed and discharged through a discharge port 43 provided on the cylinder 40. The compressed refrigerant gas discharged through the discharge port 43 is discharged into the hermetic container 10 through a discharge through hole 71 formed in an upper bearing plate 70 among the upper bearing plate 70 and lower bearing plate 80 which are respectively covered and coupled at both sides of the cylinder 40, and refrigerant gas discharged into the hermetic container 10 of high temperature and pressure is discharged through a discharge pipe 11 which is coupled with the upper portion of the hermetic container 10.

[0006] At this time, as the compression space (P) of the cylinder 40 is divided into a suction region (a) and a compression region (b), an open/close means 90 coupled with the upper portion of the upper bearing plate 70 is operated together and the discharge through hole 71 is opened or closed.

[0007] Reference numeral 12 which is not described above designates a suction pipe, reference numeral 13 designates a combining bolt, 22 designates a stator and 91 designates a muffler.

[0008] On the other hand, the vane 60 which is inserted in the vane slot 41 of the cylinder 40 and is linearly contacted on the rolling piston 50 is, as shown in FIG. 3, formed by forming a contact curved surface portion 61 having a predetermined curvature on a side surface of the vane body having predetermined thickness and area.

[0009] The vane 60 is manufactured by processing a whole surface of a high-speed steel of a certain shape by lathe turning method.

[0010] The vane 60 is inserted in the vane slot of the cylinder 40 so that the contact curved surface portion 61 is contacted on the, rolling piston 50, and the other side of the contact curved surface portion 61 of the vane 60 is elastically supported by a spring S and coupled with the rolling piston 50 to be contacted.

[0011] However, in the above structure, as the rotational shaft 30 rotates in the operation, the vane 60 is linearly contacted on the rolling piston 50 and performs relative movement. The vane 60 has severe friction with the rolling piston 50 and the inner wall of the vane slot 41 as it divides the compression space (P) of the cylinder 40 into the suction region (a) and the compression region (b) performing linear reciprocating movement along the vane slot 41. Also, as the friction heat by the friction is generated, a relatively large input energy is required.

[0012] Particularly, in the initial state of activation, since supply of lubricating oil can not be smoothly done, large activation energy is needed by static friction coefficient and it is difficult to select a proper motor.

[0013] Also, friction heat by friction of the vane 60, and inner wall of the rolling piston 50 and vane slot 41 is transmitted to the cylinder 40, thus to heat the suction region (a) of the cylinder 40 and degrade compression efficiency of the refrigerant gas.

[0014] Particularly, the vane 60 is formed with high-speed steel having a relatively small thermal expansion coefficient and therefore, gas compression efficiency was further degraded since heating value generated in case of friction among the vane 60 formed with steel, and inner wall of the rolling piston 50 and vane slot 41.

DISCLOSURE OF THE INVENTION

[0015] Therefore, it is an object of the present invention to provide a compressor, capable of minimizing friction loss and generation of frictional heat caused by relative motion in operating a compressor.

[0016] To achieve these objects, there is provided a compressor, comprising: a cylinder assembly having a compression space; a rotation body which is inserted in the compression space of the cylinder assembly so that it can rotate; and a vane which is inserted in a vane slot formed in the cylinder assembly to be contacted on the rotation body, for dividing the compression space of the cylinder assembly into a suction region and a compression region performing relative motion according to rotation of the rotation body, wherein the vane of a compressor is formed with materials having a thermal expansion coefficient as same as or larger than 2.5×10−5/° C.

BRIEF DESCRIPTION OF THE DRAWINGS

[0017] FIG. 1 is a longitudinal sectional view showing a conventional compressor;

[0018] FIG. 2 is a plane sectional view showing the conventional compressor;

[0019] FIG. 3 is a perspective view showing a vane of FIG. 1;

[0020] FIG. 4 is a longitudinal sectional view showing a compression unit of a compressor in accordance with the present invention;

[0021] FIG. 5 is a plane sectional view showing the compression unit of the compressor of FIG. 4;

[0022] FIG. 6 is a perspective view showing a vane used in the compressor of the present invention;

[0023] FIG. 7 is a partial sectional view illustrating an operational state of the compressor of the present invention;

[0024] FIG. 8 is a longitudinal sectional view showing the compression unit of the compressor in case that the compressor of the present invention are applied to another compressor;

[0025] FIG. 9 is a plane sectional view showing the compression unit of the compressor in case that the compressor of the present invention are applied to another compressor; and

[0026] FIG. 10 is a partial perspective view showing the compression unit of the compressor shown in FIG. 8 in section.

MODES FOR CARRYING OUT THE PREFERRED EMBODIMENTS

[0027] Hereinafter, the compressor of the present invention will be described with reference to the embodiments shown in the accompanied drawings.

[0028] FIGS. 4 and 5 show embodiments of a compression unit of a compressor to which a vane of a compressor of the present invention are applied. As shown in the drawings, firstly, the compression unit of the compressor includes a cylinder assembly (K) having a compression space (P) therein, a rotational shaft 30 which penetrates and is inserted in the cylinder assembly (K) so that an eccentric portion 31 is provided on the compression space (P) of the cylinder assembly (K) by having the eccentric portion 31, and a rolling piston 50 which is inserted to the outside of the rotational shaft 30 and provided on the compression space (P) of the cylinder assembly (K).

[0029] The rotational shaft 30 is connected with an electric mechanism unit for generating a driving force and the rolling piston 50 and the eccentric portion 31 for a rotation body.

[0030] The cylinder assembly (K) includes a cylinder 40 in which a through hole is formed, an upper bearing plate 70 and lower bearing plate 80 for respectively supporting the rotational shaft 30 being covered-coupled with the both sides of the cylinder 40 to seal the through hole of the cylinder 40.

[0031] The compression space (P) is formed by the upper and lower bearing plates 70 and 80 which are covered and coupled with the through hole of the cylinder 40 both sides of the cylinder 40.

[0032] A suction port 42 which is penetrated at a side of the cylinder 40 is formed at a side of the cylinder 40, a discharge port 43 is formed at a side of the suction port 42, and a vane slot 41 which is penetrated to have a predetermined width between the suction port 42 and discharge port 43 is formed.

[0033] In addition, a discharge hole 71 penetrated and formed to be connected with the discharge port 43 of the cylinder 40 is formed in the upper bearing plate 70.

[0034] A vane 100 having a predetermined shape is inserted so that it can perform a linear movement in the vane slot 41 of the cylinder assembly (K), and the vane 100 is elastically supported by the spring S. Accordingly, a side of the vane 100 is linearly contacted on the circumferential surface of the rolling piston 50 provided on the compression space (P) of the cylinder assembly (K).

[0035] The rolling piston 50 is linearly contacted on the inner wall of the compression space (P) of the cylinder assembly (K), and the vane 100 is linearly contacted on the circumferential surface of the rolling piston 50, thus to divide the compression space (P).

[0036] As shown in FIG. 6, in the vane 100, a contact curved surface portion 102 is formed with curved surfaces, having a predetermined curvature in a side surface of the vane body 101 which has predetermined thickness and area, and is contacted on the circumferential surface of the rolling piston 50.

[0037] The vane 100 is made of materials having a thermal expansion coefficient higher than 2.5×10−5/° C. and it is desirable that the vane 100 is made of materials having a thermal expansion coefficient between 3.5×10−5/° C. and 5.0×10−5/° C.

[0038] On the other hand, the vane 100 is made of high polymer composite materials having a large thermal expansion coefficient and a small heat transfer coefficient, and it is desirable that it is made of polymer or polyamide as the high polymer composite materials.

[0039] Particularly, the polyamide has identical characteristics to the steel in terms of chemical resistance against refrigerant gas and has smaller friction coefficient and larger abrasion resistance.

[0040] In addition, the vane slot 41 in which the vane 100 made of materials having thermal expansion coefficient higher than 2.5×10−5/° C. is inserted is formed to have relatively larger assembly clearance with the vane 100.

[0041] That is, the vane slot 41 is in which the vane 60 formed with materials having a large thermal expansion coefficient is inserted and the vane 60 are formed to have a small assembly clearance in consideration of the thermal expansion coefficient (1.1×10−5/° C.) of the vane 60 formed with steel, but the vane slot 41 in which the vane 100 formed with materials having a high thermal expansion coefficient is inserted and vane 100 are formed to have a relatively large assembly clearance. Therefore, the assembly clearance among the vane 100 and vane slot 41 under the condition that the compressor is not driven is maintained large.

[0042] An open/close means 90 for opening and closing the discharging hole 71 is mounted in the upper bearing plate 70 of the cylinder assembly (K).

[0043] Reference numeral 10 which is not described designates a hermetic container, 12 designates a suction pipe, 13 designates a combining bolt and 91 designates a muffler.

[0044] The operation effect of the vane of the compressor in accordance with the present invention will be described as follows.

[0045] Firstly, the compression unit of the compressor revolves on the basis of the center of the shaft in the compression space (P) of the cylinder assembly (K) under the condition that the rolling piston 50 coupled with the eccentric portion 31 of the rotational shaft 30 by rotation of the rotational shaft 30 is contacted on the vane 100 when the rotational shaft 30 rotates by receiving a rotary force of the electric mechanism unit.

[0046] As the rolling piston 50 revolves and rotates, the volume of the compression space (P) of the cylinder assembly (K) is changed together with the linear reciprocating movement of the vane 100. That is, as the compression space (P) is converted into the suction region (a) and the compression region (b), refrigerant gas of low temperature and pressure is sucked to the compression space (P) of the cylinder assembly (K) through the suction pipe 12 and suction port 42, compressed and discharged through the discharge port 43 and discharge hole 71.

[0047] In the above process, the vane 100 receives a lateral pressure by pressure difference of the suction region (a) and the compression region (b) of the compression space (P) of the cylinder assembly (K) and performs linear reciprocating movement. The contact curved surface portion 102 of the vane is contacted on the circumferential surface of the rolling piston 50 being elastically supported on the circumferential surface.

[0048] At this time, the assembly clearance of the vane 100 and vane slot 41 in initially driving the compressor is maintained large and as shown in FIG. 7, the vane 100 is heated and expanded by heat generated in driving the compressor normally after the initial driving. Accordingly, the interval between the vane 100 and the vane slot 41 is maintained finely.

[0049] Therefore, due to the large interval between the vane 100 and the vane slot 41 in initially driving the compressor, little friction between the vane 100 and inner wall of the vane slot 41 is generated and accordingly little activation energy is consumed. Also, the interval between the vane 100 and vane slot 41 becomes shorter by expansion of the vane 100 in driving the compressor normally, thus to minimize leakage of gas.

[0050] Particularly, little friction is generated under the condition that sufficient oil is not supplied in initially driving, thus to substantially reduce waste of activation energy.

[0051] In addition, when the vane 100 is made of polymer or polyamide materials, heat transfer toward the suction region (a) of the compression space (P) of the cylinder assembly (K) is minimized since heating value is relatively small and heat transfer coefficient is small, when the friction is generated. Therefore, an amount of the sucked refrigerant gas is increased, thus to increase compression coefficient.

[0052] Also, the vane 100 formed with polymer or polyamide materials gains lower friction coefficient and larger friction resistance and lengthens life span of the vane 100.

[0053] Hereinafter, another compressor to which the vane of the compressor in accordance with the present invention are applied will be described with reference to FIGS. 8, 9 and 10.

[0054] As shown in FIGS. 8, 9 and 10, the compression unit of another compressor has a compression space (P) therein and a rotational shaft 110 is inserted penetrating the center of the compression space (P) of the cylinder assembly (K) in which the suction flow path f1 and discharge flow path f2 which are respectively connected to the compression space (P). The rotational shaft 110 is coupled with the electric mechanism unit for generating a driving force.

[0055] The cylinder assembly (K) includes a cylinder 120 in which a through hole in the circular shape is formed, an upper bearing plate 130 and a lower bearing plate 140 which are covered and coupled on the upper/lower surfaces of the cylinder 120, for forming the compression space (P) together with the cylinder 120 and supporting the rotational shaft 110.

[0056] At a side of the upper bearing plate 130 and the lower bearing plate 140, vane slots 131 and 141 which are penetrated and formed to have predetermined width and length are respectively formed.

[0057] The rotational shaft 110 includes a shaft portion 111 formed to have predetermined outer diameter and length and a dividing plate 150 which is lengthened and formed to have predetermined thickness and area at a side of the shaft portion 111, for dividing the compression space (P) of the cylinder assembly (K) into first and second spaces 121 and 122.

[0058] The dividing plate 150 of the rotational shaft 110 includes an upper convex curved surface portion r1 which is formed in a circular shape having a predetermined thickness and has a convex curved surface, a lower concave curved surface portion r2 having a concave curved surface, and a connection curved surface portion r3 for connecting the upper convex curved surface portion r1 and lower concave curved surface portion r2 in case of shown from the side and formed in a wave curved surface shape of a sine wave.

[0059] Also, vanes 100′ are respectively inserted in the vane slot 131 of the upper bearing plate 130 and vane slot 141 of the lower bearing plate 140, and elastic supporting means 160 for elastically supporting the vanes 100′ are coupled with the upper bearing plate 130 and lower bearing plate 140. Accordingly, the vane 100′ is abutted being linearly contacted on the dividing plate 150 by the elastic supporting means 160.

[0060] In the vane 100′, a contact curved surface portion 104 in the rounding shape being abutted on the wave curved surface of the dividing plate 150 is formed, and an outer curved surface portion 105 contacted on the inner wall of the compression space (P) of the cylinder assembly (K) and an inner curved surface portion 106 which is contacted on the circumferential surface of the rotational shaft 110 are formed on both surfaces of the vane body 103. The vane slots 131 and 141 in which the vane 100′ is inserted is formed in a square shape corresponding to the cross-sectional shape of the-vane 100′.

[0061] The vane 100′ is made of materials having thermal expansion coefficient as same as or higher than 2.5×10−5/° C. and it is desirable that the vane 100′ is made of materials having thermal expansion coefficient between 3.5×10−5/° C. and 5.0×10−5/° C.

[0062] On the other hand, the vane 100′ is made of high polymer composite materials having a large thermal expansion coefficient and small heat transfer coefficient, and it is desirable that it is made of polymer or polyamide as the composite materials.

[0063] Particularly, the polyamide has an identical characteristic as the steel in terms of chemical resistance against the refrigerant, and it has smaller friction coefficient and larger friction resistance than the vane which is formed with the steel.

[0064] That is, the vane slot 41 is in which the vane 60 formed with materials having a large thermal expansion coefficient is inserted and vane 60 are formed to have a small assembly clearance in consideration of the thermal expansion coefficient (1.1×10−5/° C.) of the vane 60 formed with steel, but the vane slots 131, 141 in which the vane 100′ formed with materials having a large thermal expansion coefficient is inserted and vane 100′ are formed to have a relatively large assembly clearance. Therefore, the assembly clearance among the vane 100′ and vane slots 131 and 141 under the condition that the compressor is not driven is maintained large.

[0065] In addition, an open/close means 170 for opening or closing the discharge flow path f2 is mounted on a side surface of the respective bearing plates 130 and 140 of the cylinder assembly (K).

[0066] Reference numeral 10 which is not described designates a hermetic container and 180 designates a muffler.

[0067] The operation effect of the compression unit of the above compressor to which the vane of the compressor in accordance with the present invention are applied will be described as follows.

[0068] Firstly, in the compression unit of the compressor, the dividing plate 150 of the rotational shaft 110 rotates in the compression space (P) of the cylinder assembly (K) when the rotational shaft 110 rotates by receiving a rotary force of the driving force of the electric mechanism unit.

[0069] As the dividing plate 150 of the rotational shaft 110 rotates in the compression space (P) of the cylinder assembly (K), vanes 100′ which are connected with the dividing plate 150 are moved together, a first and second spaces 121 and 122 of the compression space (P) divided by the dividing plate 150 are converted into the suction regions 121a and 122a and compression regions 121b and 122b. Then, refrigerant gas is sucked to first and second spaces 121 and 122 together with the operation of the open/close means 170, and such process is repeated.

[0070] As the dividing plate 150 of the rotational shaft 110 rotates in the compression space (P) of the cylinder assembly (K), under the condition that the vane 100′ which is positioned vertically and radially to the dividing plate 150 is elastically supported by the elastic supporting means 160, and the vane 100′ performs linear reciprocating movement upwards and downwards along the wave curved surface of the dividing plate 150.

[0071] In the above process, the vanes 100′ performs linear reciprocating movement receiving pressure to the lateral direction by pressure difference of the suction regions 121a and 122a and compression regions 121b and 122b of the compression space (P) of the cylinder assembly (K), and the contact curved surface portion 104 of the vane 100′ is elastically supported on the outer curved surface of the dividing plate 150 an contacted by the elastic supporting means 160.

[0072] At this time, in case of initially driving the compressor, the assembly clearance of the vane 100′ and vane slots 131 and 141 is maintained large and the vane 100′ is heated and expanded by heat generated in driving the compressor normally after the initial driving. Accordingly, the interval between the vane 100′ and the vane slots 131 and 141 can be maintained finely.

[0073] Therefore, as the clearance of the vane 100′ and vane slots 131 and 141 increases, little friction among the vane 100′ and inner wall of the vane slots 131 and 141 is occurred and little activation energy is consumed. Also, in case of driving the compressor normally, the clearance between the vane 100′ and vane slots 131 and 141 decreases by expansion of the vane 100′, thus to minimize leakage of refrigerant gas. Particularly, little friction is generated under the condition that oil is not sufficiently supplied and consumption of activation energy is substantially reduced.

[0074] In addition, in case the vane 100′ is formed with polymer or polyamide materials, heating value is relatively small in case of friction and heat transfer coefficient decreases. Accordingly, heat transfer to the suction regions 121a and 122a of the compression space (P) of the cylinder assembly (K) is minimized and amount of the sucked refrigerant gas is increased, thus to improve compression efficiency. Also, the vane 100′ formed with polymer or polyamide materials becomes to have a small friction coefficient and large abrasion resistance, thus to lengthen life span of the vane 100′.

[0075] As described above, the vane of the compressor can reduce friction the vane and parts which perform relative motion with the vane, reduce consumption of activation energy and friction loss, reduce abrasion of the parts and control heat transfer, thus to increase suction amount of the refrigerant gas and improve compression performance.

[0076] At the present invention may be embodied in several forms without departing from the spirit or essential characteristics thereof, if should also be understood that the above-described embodiments are not limited by any of the details of the foregoing description, unless otherwise specified, but rather should be constructed broadly within its spirit and scope as defined in the appended claims, and therefore all changes and modifications that fall within the meets and bounds of the claims, or equivalence of such meets and bounds are therefore intended to be embraced by appended claims.

Claims

1. A compressor, comprising: a cylinder assembly having a compression space; a rotation body which is inserted in the compression space of the cylinder assembly so that it can rotate; and a vane which is inserted in a vane slot formed in the cylinder assembly to be contacted on the rotation body, for dividing the compression space of the cylinder assembly into a suction region and a compression region performing relative motion according to rotation of the rotation body, wherein the vane of a compressor is formed with materials having a thermal expansion coefficient as same as or larger than 2.5×10−5/° C.

2. The compressor of claim 1, wherein the vane is made of a material having a thermal expansion coefficient between 3.5×10−5/° C. and 5.0×10−5/° C.

3. The compressor of claim 1, wherein the vane is made of polymer composite materials.

4. The compressor of claim 1, wherein the vane is made of polyamide.

5. The compressor of claim 1, wherein the assembly clearance between the vane and slot is set larger than an optimal assembly clearance in consideration of thermal expansion under the condition of normal driving.