Vane rotary compressor having hinge receiving portions formed on an outer peripheral surface of a rotor with a plurality of vanes including a hinge portion and a blade portion

Abstract

Disclosed herein is a vane rotary compressor in which a fluid such as a refrigerant is compressed while a volume of a compression chamber is reduced during rotation of a rotor. There is provided a vane rotary compressor capable of preventing a delay of rotation operation of a vane by respectively forming oil films on both sides of a hinge portion of the vane in a rotation direction thereof and smoothly sliding the hinge portion.

Claims

1. A vane rotary compressor comprising: a housing having a hollow cylinder formed therein; a rotor rotatingly disposed in the cylinder and coupled to a rotary shaft, the rotor including a plurality of slots and a plurality of hinge receiving portions formed on an outer peripheral surface of the rotor; and a plurality of vanes dividing the cylinder into a plurality of compression chambers, each of the plurality of vanes including a hinge portion and a blade portion extending outwardly from the hinge portion, the hinge portion received within one of the plurality of slots, the blade portion biasing towards an inner peripheral surface of the cylinder, each of the plurality of hinge receiving portions enclosing a circumference of the hinge portion of each of the plurality of vanes, the hinge portion of each of the plurality of vanes contacts the rotor at a friction point inwardly spaced from an end of each of the plurality of hinge receiving portions, the end of each of the plurality of hinge receiving portions extending beyond an extension line passing through a central point of the rotor and a central point of the hinge portion, each of the plurality of hinge receiving portions extending along the circumference of the hinge portion in a direction of rotation of the rotor.

2. The vane rotary compressor of claim 1, wherein an obtuse angle formed between the extension line extending between the central point of the rotor and the central point of the hinge portion and a line extending from the central point of the hinge portion and along the end of one of the plurality of hinge receiving portions is between 180 degrees and 230 degrees.

3. The vane rotary compressor of claim 1, wherein a gap is formed between the hinge portion and each of the plurality of hinge receiving portions on each side of the friction point, and wherein an oil film forms in each of the gaps.

4. The vane rotary compressor of claim 1, wherein the friction point divides a gap formed between an inner peripheral surface of each of the plurality of hinge receiving portions and an outer peripheral surface of the hinge portion into a plurality of oil film formation spaces.

5. A vane rotary compressor comprising: a housing having a hollow cylinder formed therein; a rotor rotatingly disposed in the cylinder and coupled to a rotary shaft, the rotor including a plurality of slots formed on an outer peripheral surface of the rotor; and a plurality of vanes dividing the cylinder into a plurality of compression chambers, each of the plurality of vanes including a hinge portion and a blade portion extending outwardly from the hinge portion, the hinge portion received within one of the plurality of slots, the blade portion biasing towards an inner peripheral surface of the cylinder, the hinge portion contacting an inner peripheral surface of the rotor at a friction point, the friction point disposed on an extension line passing through a central point of the rotor and a central point of the hinge portion.

6. The vane rotary compressor of claim 5, wherein a plurality of hinge receiving portions are formed on the outer peripheral surface of the rotor, each of the plurality of hinge receiving portions enclosing a circumference of the hinge portion of each of the plurality of vanes.

7. The vane rotary compressor of claim 6, wherein a gap is formed between an inner peripheral surface of each of the plurality of hinge receiving portions and an outer peripheral surface of the hinge portion of each of the plurality of vanes, a plurality of oil film formation spaces formed in each of the gaps.

8. The vane rotary compressor of claim 7, wherein the plurality of oil film formation spaces are separated from each other by the friction point.

9. The vane rotary compressor of claim 6, wherein a gap is formed between the hinge portion of each of the plurality of vanes and each of the plurality of hinge receiving portions on each side of the friction point, and wherein an oil film forms in each of the gaps.

10. The vane rotary compressor of claim 5, wherein a hinge portion imaginary circle extends along an outer peripheral surface of the hinge portion of each of the plurality of vanes and a rotor imaginary circle extends along the outer peripheral surface of the rotor, and wherein the hinge portion imaginary circle is disposed in an inner region of the rotor imaginary circle.

11. The vane rotary compressor of claim 5, wherein a hinge portion imaginary circle extends along an outer peripheral surface of the hinge portion of each of the plurality of vanes and a rotor imaginary circle extends along the outer peripheral surface of the rotor, and wherein the hinge portion imaginary circle is disposed in an outer region of the rotor imaginary circle.

12. A vane rotary compressor comprising: a housing having a hollow cylinder formed therein; a rotor rotatingly disposed in the cylinder and coupled to a rotary shaft, the rotor including a plurality of slots formed on an outer peripheral surface of the rotor, each of the slots having a hinge portion receiving groove formed inwardly from the outer peripheral surface of the rotor, the rotor further including a plurality of hinge receiving portions formed on the outer peripheral surface of the rotor; and a plurality of vanes dividing the cylinder into a plurality of compression chambers, each of the plurality of vanes including a hinge portion and a blade portion extending outwardly from the hinge portion, the hinge portion received within one of the plurality of slots, the blade biasing towards an inner peripheral surface of the cylinder, a circumference of the hinge portion received inside the outer peripheral surface of the rotor, the hinge portion of each of the plurality of vanes contacts the rotor at a friction point inwardly spaced from an end of each of the plurality of hinge receiving portions, the end of each of the plurality of hinge receiving portions extending beyond an extension line passing through a central point of the rotor and a central point of the hinge portion, each of the plurality of hinge receiving portions extending along the circumference of the hinge portion in a direction of rotation of the rotor.

13. The vane rotary compressor of claim 12, wherein each of the plurality of hinge receiving portions encloses the circumference of the hinge portion of each of the plurality of vanes.

14. The vane rotary compressor of claim 13, wherein an obtuse angle formed between the extension line extending between the central point of the rotor and the central point of the hinge portion and a line extending from the central point of the hinge portion and along an end of one of the plurality of hinge receiving portions is between 180 degrees and 230 degrees.

15. The vane rotary compressor of claim 12, wherein a gap is formed between the hinge portion and each of the plurality of hinge receiving portions on each side of the friction point, and wherein an oil film forms in each of the gaps.

16. The vane rotary compressor of claim 12, wherein the friction point is disposed on the extension line passing through the central point of the rotor and the central point of the hinge portion.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) The above and other objects, features and other advantages of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:

(2) FIG. 1 is a vertical cross-sectional view illustrating a conventional vane rotary compressor;

(3) FIG. 2 is a cross-sectional view taken along line A-A in FIG. 1;

(4) FIG. 3 is a horizontal cross-sectional view illustrating a conventional curved blade type vane rotary compressor;

(5) FIG. 4 is a partially enlarged view schematically illustrating forces acting on the vane during the rotation of a rotor in FIG. 3;

(6) FIG. 5 is a vertical cross-sectional view illustrating a vane rotary compressor according to an embodiment of the present invention;

(7) FIG. 6 is a view schematically illustrating a hinge portion of a vane and a hinge receiving portion of a rotor according to the embodiment of the present invention;

(8) FIG. 7 is a partially enlarged view illustrating a state in which oil films are formed on both sides of a friction point of the vane hinge portion in FIG. 6 according to the embodiment of the present invention; and

(9) FIG. 8 is a partial view schematically illustrating an example of a hinge receiving portion according to another embodiment of the present invention.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS OF THE INVENTION

(10) Hereinafter, a vane rotary compressor according to exemplary embodiments of the present invention will be described with reference to the accompanying drawings. In the description, the thickness of each line or the size of each component illustrated in the drawings may be exaggerated for convenience of description and clarity.

(11) In addition, the terms used herein are terms defined in consideration of functions of the present invention, and these may vary with the intention or practice of a user or an operator. Therefore, such terms should be defined based on the entire content disclosed herein.

(12) Moreover, the following embodiments are for the purposes of illustratively describing the components set forth in the appended claims only and are not intended to limit the spirit and scope of the invention. More particularly, various variations and modifications are possible in concrete constituent elements of the embodiments, and it is to be understood that differences relevant to the variations and modifications fall within the spirit and scope of the present disclosure defined in the appended claims.

Embodiments

(13) FIG. 5 is a vertical cross-sectional view illustrating a vane rotary compressor according to an embodiment of the present invention.

(14) As illustrated in FIG. 5, the overall external appearance of a vane rotary compressor, which is designated by reference numeral 100 (hereinafter, referred to as a compressor), according to an embodiment of the present invention is defined by coupling of a housing 200 and a rear head 500.

(15) The housing 200 includes a cylinder portion 210 which is formed therein with a space portion, and a front head portion 220 which closes the front of the space portion of the cylinder portion 210. The front head portion 220 is integrally formed with the cylinder portion 210 in the axial front thereof. In accordance with another example of the present invention, a housing may be integrally formed by the cylinder portion 210 and the rear head 500 to be described later and a separate front head may also be coupled to the front of the housing.

(16) The space portion of the cylinder portion 210 is equipped with a hollow cylinder 300. In addition, the cylinder 300 is provided therein with a rotary shaft 310 which rotates by the power of a drive source (not shown), a rotor 400 which rotates along with the rotary shaft 310 by receiving torque from the rotary shaft 310, and a plurality of vanes 600 which are hinge-coupled to the outer peripheral surface of the rotor 400 to be rotatable in the radial direction of the rotor 400.

(17) The rear head 500 is coupled to the axial rear of the housing 200 to close the rear of the space portion of the cylinder portion 210. A mounting groove 510 is formed at the inside center of the rear head 500, and the rear end of the rotary shaft 310 is inserted into and rotatably supported by the mounting groove 510. The front end of the rotary shaft 310 is rotatably supported by the hollow of the front head portion 220.

(18) Meanwhile, the outer peripheral surface of the first head portion 220 of the housing 200 is provided with a suction port (not shown) for suction of a refrigerant from the outside and a discharge port (not shown) for discharge of a high-pressure refrigerant compressed within the cylinder 300 to the outside, which are circumferentially spaced apart from each other.

(19) In addition, the front center of the first head portion 220 is extendedly formed with a pulley coupling portion 240 so as to couple a pulley 230 of an electronic clutch (not shown) thereto.

(20) FIG. 6 is a view schematically illustrating a hinge portion 610 of the vane 600 and a hinge receiving portion 420 of the rotor 400 according to the embodiment of the present invention. FIG. 7 is a partially enlarged view illustrating a state in which oil films 700 are formed on both sides of a friction point Pf of the vane hinge portion 610 in FIG. 6 according to the embodiment of the present invention.

(21) As illustrated in FIG. 6, the cylinder 300 is equipped therein with the rotary shaft 310 and the rotor 400 which are rotated by power of the drive source.

(22) The rotor 400 is coupled to the rotary shaft 310, which is connected to a clutch (not shown) driven by a drive motor (not shown) or an engine belt (not shown), to axially rotate along with the rotary shaft 310. The rotary shaft 310 is mounted along the central axis of the cylinder 300.

(23) The vanes 600 are spaced apart from each other and are hinge-coupled to the outer peripheral surface of the rotor 400. Each of the vanes 600 includes the hinge portion 610 which is hinge-coupled to one side of the outer peripheral surface of the rotor 400 and a blade portion 620 extending from one side of the hinge portion 610.

(24) In this case, each compression chamber 320 is divided and formed by a space defined by the pair of adjacent vanes 600, the outer peripheral surface of the rotor 400, and the inner peripheral surface of the cylinder 300. The front and rear of the compression chamber 320 are sealed by the front head portion 220 (see FIG. 5) and the rear head 500 (see FIG. 5), respectively.

(25) During the rotation of the rotor 400, the tip of the blade portion 620 of each of the vanes 600 rotates together in the rotation direction of the rotor 400 along the hollow inner peripheral surface of the cylinder 300. In this case, as the tip of the blade portion 620 of the vane 600 is close from an inlet (not shown) to an outlet (not shown), a gap between the outer peripheral surface of the rotor 400 and the hollow inner peripheral surface of the cylinder 300 is gradually narrowed, with the consequence that the volume of the compression chamber 320 is reduced and the refrigerant in the compression chamber 320 is compressed. For example, the hollow inner peripheral surface of the cylinder 300 may be formed in the form of an involute curve in which the width thereof is gradually decreased as being close from the inlet to the outlet.

(26) In this case, in order to maximally reduce the volume of the compression chamber 320 during a compression stroke, one side of the outer peripheral surface of the rotor 400 preferably comes into close contact with the hollow inner peripheral surface of the cylinder 300 in the vicinity of the outlet. To this end, the outer peripheral surface of the rotor 400 is formed with a plurality of slots 410 which are formed in the same number as that of the vanes 600 to receive the vanes 600 and are spaced apart from each other in the circumferential direction. The vanes 600 are fully received in the slots 410 on the outer peripheral surface of the rotor 400 in the vicinity of the outlet.

(27) Each of the slots 410 includes the hinge portion receiving groove 411 to which the hinge portion 610 of each vane 600 is hinge-coupled and a blade portion receiving groove 412 on which the blade portion 620 of the vane 600 is seated.

(28) The hinge portion receiving groove 411 has a circular arc section shape such that the circle section shaped hinge portion 610 is inserted into and coupled to the hinge portion receiving groove 411. The blade portion receiving groove 412 has a shape corresponding to the blade portion 620 and is recessed on the outer peripheral surface of the rotor 400.

(29) In accordance with the embodiment of the present invention, the hinge portion receiving groove 411 is radially inwardly spaced apart from the outer peripheral surface of the rotor 400. Thus, the overall circumference of the hinge portion 610 of the vane 600, which is hinge-coupled to the hinge portion receiving groove 411, is received inside the outer peripheral surface of the rotor 400. That is, a hinge portion imaginary circle Ch, which forms an outer peripheral surface of the hinge portion 610, is formed in an inner region of a rotor imaginary circle Cr, which forms the outer peripheral surface of the rotor 400, as illustrated in FIG. 6.

(30) In this case, a hinge receiving portion 420 is extendedly formed on one side of the outer peripheral surface of the rotor 400 so as to enclose a radially outward circumference of the hinge portion receiving groove 411. Accordingly, the hinge portion 610 of the vane 600 is received radially inward of the hinge receiving portion 420.

(31) Thus, the oil films 700 by oil viscosity are formed on both sides of the friction point, at which the hinge portion 610 comes into contact with the hinge receiving portion 420, so as to reduce friction resistance applied to the hinge portion 610 of the vane 600. Hereinafter, this description will be given in more detail.

(32) When the vane 600 is unfolded during beginning of an intake stroke, the sum of forces acting on the vane 600 is concentrated on the friction point Pf at which the outer peripheral surface of the hinge portion 610 of the vane 600 comes into contact with the inner peripheral surface of the hinge portion receiving groove 411.

(33) In the related art, since the friction point Pf between the hinge portion 4a and the hinge portion receiving groove 2a is formed at the end of the inner peripheral surface of the hinge portion receiving groove 2a as illustrated in FIG. 4, it is difficult to form the oil film 7 by the sliding surface and friction resistance is increased. Accordingly, this causes rotation operation of the vane 4 through the sliding motion of the hinge portion 4a to be delayed.

(34) In accordance with the embodiment of the present invention, the friction point Pf of the hinge portion 610 is formed on an imaginary extension line l joining a central point Mr of the rotor 400 and a central point Mh of the hinge portion 610, and an end portion of the hinge receiving portion 420 passes the extension line l from one side of the outer peripheral surface of the rotor 400 in the rotation direction of the rotor 400 and extends to enclose the outside of the hinge portion 610.

(35) That is, the friction point Pf, at which the outer peripheral surface of the hinge portion 610 comes into contact with the inner peripheral surface of the hinge portion receiving groove 411, is circumferentially inwardly spaced apart from an end Pe of the inner peripheral surface of the hinge portion receiving groove 411 by a predetermined interval.

(36) In addition, a predetermined gap is formed between the outer peripheral surface of the hinge portion 610 and the inner peripheral surface of the hinge portion receiving groove 411, and the gap is divided into a plurality of oil film formation spaces on the basis of the friction point Pf.

(37) On the basis of the friction point Pf, lubricant oil is preferably introduced into gaps of the front and rear of the hinge portion 610 in the rotation direction thereof so as to respectively from the oil films 700 in the gaps.

(38) That is, in accordance with the embodiment of the present invention, the oil films 700 are formed by viscosity of the sliding surfaces on both sides of the friction point Pf so that the hinge portion 610 may smoothly slide, thereby preventing rotation operation of the vane 600 from being delayed.

(39) Meanwhile, an angle , which is formed by the central point Mr of the rotor 400 and the end Pe of the inner peripheral surface of the hinge receiving portion 420 with respect to the central point Mb of the hinge portion 610, is preferably an obtuse angle between more than 180 and equal to or less than 230. This is because it is difficult to form the oil films on both sides of the friction point Pf when the angle is equal to or less than 180 and a rotatable angle of the vane 600 is restricted by the hinge receiving portion 420 to reduce compression efficiency when the angle is more than 230.

(40) As described above, in accordance with the embodiment of the present invention, since the hinge receiving portion 420 is formed to enclose the outside of the hinge portion 610, the friction point Pf at which the outer peripheral surface of the hinge portion 610 comes into contact with the inner peripheral surface of the hinge portion receiving groove 411 is circumferentially inwardly spaced apart from the end Pe of the inner peripheral surface of the hinge portion receiving groove 411 by a predetermined interval. In this case, since the oil films 700 are respectively formed on both sides of the friction point Pf, the hinge portion 610 may smoothly slide and rotation operation of the vane 600 may be prevented from being delayed.

(41) Meanwhile, FIG. 8 is a partial view schematically illustrating an example of three binge receiving portion 420 according to another embodiment of the present invention.

(42) In the above-mentioned embodiment, the overall region of the hinge portion 610 is received inside the outer peripheral surface of the rotor 400 and this state may be identified by the hinge portion imaginary circle Ch being formed in the inner region of the rotor imaginary circle Cr, as illustrated in FIG. 6.

(43) In accordance with another embodiment of the present invention, the overall region of the hinge portion 610 may also be arranged outside the outer peripheral surface of the rotor 400 as illustrated in FIG. 8. That is, a hinge portion imaginary circle Ch may also be formed in an outer region of a rotor imaginary circle Cr. In this case, the hinge receiving portion 420 protrudes outward from the outer peripheral surface of the rotor 400 and encloses the circumference of the hinge portion 610.

(44) In accordance with another embodiment of the present invention, the friction point Pf between the hinge portion 610 and the hinge receiving portion 420 is formed on the extension line l joining the central point Mr of the rotor 400 and the central point Mh of the hinge portion 610. Accordingly, oil films are respectively formed in the front and rear of the hinge portion 610 in the rotation direction thereof on the basis of the friction point Pf, thereby enabling a reduction in the hinge friction force B1 (see FIG. 4) of the vane 600.

INDUSTRIAL APPLICABILITY

(45) In accordance with the vane rotary compressor 100 according to an embodiment of the present invention, the oil films 700 are formed on both sides of the friction point Pf between the hinge portion 610 of the vane 600 and the hinge receiving portion 420 of the rotor 400.

(46) In this case, since two sliding surfaces are formed on each of the both sides of the friction point Pf, it may be possible to reduce friction force by the oil films 700 and to prevent generation of strike noise due to a delay of rotation operation of the vane 600.

(47) Moreover, it may be possible to enhance performance of the compressor by preventing an inner leakage due to the delay of rotation operation of the vane.

(48) Various embodiments have been described in the best mode for carrying out the invention. Although the present invention has been described with respect to the illustrative embodiments, it will be apparent to those skilled in the art that various variations and modifications may be made without departing from the spirit and scope of the invention as defined in the following claims.