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 f 1 and discharge flow path f 2 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 r 1 which is formed in a circular shape having a predetermined thickness and has a convex curved surface, a lower concave curved surface portion r 2 having a concave curved surface, and a connection curved surface portion r 3 for connecting the upper convex curved surface portion r 1 and lower concave curved surface portion r 2 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 f 2 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 1 50 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 121 a and 122 a and compression regions 121 b and 122 b. 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 121 a and 122 a and compression regions 121 b and 122 b 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 121 a and 122 a 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.