Abstract:
A vane structure for a compressor comprises: a Z-plate located in a cylinder assembly for dividing an inner space of the cylinder assembly into a plurality of compression spaces and notated by a driving unit to suck, compress, and discharge fluid; and vanes undergoing reciprocating movements by being contacted to both surfaces of the Z-plate for dividing the respective compression space into a suction area and a compression area, wherein the vane includes a vane roller which is rolling contacted to the Z-plate to reduce a friction resistance between the Z-plate and the vane, and thereby an abrasion can be minimized, a noise generation can be reduced, life spans of components can be increased, and a reliability of the compressor can be improved.

Description:
TECHNICAL FIELD  
         [0001]    The present invention relates a vane structure for a compressor in which a vane is in contact with a Z-plate, a rotation member, so that a fluid can be compressed in a compression chamber and discharged therefrom  
         BACKGROUND ART  
         [0002]    Generally, compressors convert a mechanical energy into a compression energy of an compressible fluid, of which a freezing compressor is classified into a reciprocating compressor, a scroll type compress, a centrifugal type compressor and rotary type compressor depending on a compression method.  
           [0003]    The present applicant has developed a compressor with a novel concept, which can be classified into the rotary compressor, and filed an application for the invention to the Korean Industrial Patent Office (Application No. 10-1999-0042381, Application date: Oct. 1, 1999), which has been laid open May 7, 2001 with a-publication number 2001-0035687.  
           [0004]    The former application invention of the same applicant will now be described with reference to FIG. 1.  
           [0005]    [0005]FIG. 1 is a vertical sectional view showing a compressor of the former application invention of the present invention.  
           [0006]    As shown in FIG. 1, a compressor of the former application invention of the present invention includes: a electric mechanism unit  4  consisting of a stator and a rotor  3  inside a casing  1  and generating a rotational force; and a compression mechanism unit  10  for compressing a fluid by a rotational force generated from the rotor  3  of the electric mechanism unit  4  and discharging it.  
           [0007]    [0007]FIG. 2 is a partial cut-out perspective view showing the compression mechanism unit  10 .  
           [0008]    With reference to FIGS. 1 and 2, the compression mechanism unit.  10  includes: a cylinder  11  fixed at a lower portion of the casing  1 ; a first bearing plate  13  and a second bearing plate  14  fixed at an upper surface and a lower surface of the cylinder  11  and forming a compression space (V) together with the cylinder  11 ; a rotational shaft  12  for transmitting a rotational driving force generated from the rotor  3  of the electric mechanism unit  4  to the compression mechanism unit; a Z-plate  15  coupled at the rotational shaft  12  and rotated, and dividing the compression space (V) of the cylinder  11  into a first space (V 1 ) and a second space (V 2 ); and a first vane  17  and a second vane  18  each being in contact with the upper surface and lower surface of the Z-plate and dividing the spaces V 1  and V 2  into suction areas (V 1   s  and V 2   s ) and compression area (V 1   p  and V 2   p ) when the Z-plate is rotated.  
           [0009]    The cylinder  11 , the first bearing plate  13  and the second bearing plate  14  are cylinder assembly forming the compression space (V).  
           [0010]    In FIG. 1, reference number  5  denotes a suction pipe through which a fluid is sucked into the casing  1 , and  6  denotes a discharge pipe through which a fluid is discharged.  
           [0011]    Reference numerals  11   a  and  11   b  denote suction passages through which a fluid is sucked into the compression space (V) of the cylinder  11 ,  13   a  and  14   a  denote discharge passages for discharging a compressed fluid, and  13   b  and  14   b  denote discharge valves.  
           [0012]    Reference numerals  19  and  20  denote discharge mufflers for reducing a discharge noise, and  19   a  and  20   a  denote discharge holes formed at the discharge mufflers  19  and  20 , through which a compressed fluid is discharged.  
           [0013]    Primary construction elements of the compressor will now be described in detail.  
           [0014]    The Z-plate  15  is formed as disk type when projected on plane so that its outer circumference face can slidably contact an inner circumferential face of the cylinder  11 , and its side is formed with a cam surface of a sine wave curve which has the same thickness from the inner circumferential face to the outer cicumferential face in its development, so that its upper dead point (R 1 ) is in contact with the lower surface of the first bearing plate  13  and rotated, and a lower dead point (R 2 ) is closely adhered to the upper surface of the second bearing plate  14  and rotated.  
           [0015]    As shown in FIG. 3, the first vane  17  and the second vane  18  are formed in square plate shape with a certain thickness, penetrating each bearing plate  13  and  14 , so that when the rotational shaft  12  is rotated the first vane  17  and the second vane  18  linearly and reciprocally moved in the axial direction along the cam surface of the Z-plate  17  while being in contact with the upper surface and lower surface of the Z-plate  15 , respectively.  
           [0016]    The first vane  17  and the second vane  18  receives an elastic force from springs  21  and  22  supplied by the bearing plates  13  and  14  at their rear portion  17   a  (refer to FIG. 1). An outer side  17   b  of each vane  17  and  18  is in contact with the inner circumferential face of the cylinder  11 , and an inner side of each vane  17  and  18  is in contact with the outer circumferential face of the rotational shaft  12 . A front end portion  17   d  of each vane  17  and  18  slidably contacts the upper surface and the lower surface of the Z-plate  15  (reference to FIG. 2).  
           [0017]    The operation process of the compressor of the former application invention constructed as described above will now be explained.  
           [0018]    When the rotational shaft  12  is rotated by a driving force of the electric mechanism unit  4 , the Z-plate  15  coupled at the rotational shaft  12  is simultaneously rotated in the cylinder  11 , thereby sucking, compressing and discharging a fluid.  
           [0019]    Namely, with reference to FIG. 2, the first space V 1  positioned at an upper portion of the Z-plate  15  is divided into a suction area V 1   s  and a compression area V 1   p  by taking the upper dead point (R 1 ) and the first vane  17  as a boundary, and the second space V 2  positioned at the lower portion of the Z-plate  15  is divided into a suction area (V 2   s ) and a compression area (V 2   p ) by taking the lower dead point (R 2 ) and the second vane  18  as a boundary.  
           [0020]    In this state, as the Z-plate  15  is rotated, the upper dead point (R 1 ) and the lower dead point (R 2 ) of the Z-plate  15  are moved to vary a volume of the suction area and the compression area of each space.  
           [0021]    At this time, the first vane  17  and the second vane  18  are reciprocally moved in the mutually opposite direction up to as high as the cam face of the Z-plate.  
           [0022]    Accordingly, a fresh fluid is simultaneously sucked into each suction area (V 1   s , V 2   s ) through each suction passage  11   a  and  11   b  of the first space V 1  and the second space V 2  and gradually compressed, and then, when the upper dead point R 1  or the lower dead point R 2  of the Z-plate reaches a discharge initiation point, the fluid is simultaneously discharged outwardly of the compression space (V) through the discharge passages  13   a  and  14   a  of each space V 1  and V 2 .  
           [0023]    However, in the compressor of the former application invention, as the vanes which are linearly and reciprocally moved are in contact with the upper surface and the lower surface of the Z-plate  15 , a sliding friction takes place at the contact side between the vanes  17  and  18  and the Z-plate  15 .  
           [0024]    Accordingly, a driving force loss is increased due to the friction resistance between the vanes  17  and  18  and the Z-plate  15 , and a friction noise is generated.  
           [0025]    In addition, as the friction face between the vanes  17  and  18  and the Z-plate  15  is abraded t shorten a life span of the parts, and especially, as the fluid at the side of the compression area is leaked toward the suction area, so that a compression efficiency is degraded.  
           [0026]    Technical Gist of the Pesent Invention  
           [0027]    Therefore, an object of the present invention is to provide a vane structure of a compressor that is capable of heightening an efficiency and a reliability of a compressor by reducing a friction loss and abrasion between a vane and a Z-plate.  
         DETAILED DESCRIPTION OF THE INVENTION  
         [0028]    In order to achieve the above objects, there is provided a vane structure for a compressor including a cylinder assembly having a suction passage and a discharge passage, a Z-plate dividing an inner space of the cylinder assembly into a plurality of compression spaces, and sucking, compressing and discharging a fluid while being rotated by a driving unit, and vanes being in contact with both sides of the Z-plate to make a reciprocal movement, and dividing each compression space into a suction area and a compression area, wherein the vane has a vane roller being in rolling-contact with the Z-plate.  
           [0029]    The vane includes a vane plate reciprocally moved along both sides of the Z-plate and a vane roller provided at the vane plate and being in a rolling-contact with the Z-plate.  
           [0030]    The vane plate includes a roller receiving hole into which the vane roller is inserted and mounted.  
           [0031]    In one embodiment of the present invention, the vane roller is formed having a bar structure with the same diameter on the whole, and the roller receiving hole is formed in a hole structure having the same inner diameter.  
           [0032]    An opened portion of the roller receiving hole so that the vane roller comes in contact with the Z-plate therethrough is smaller than a diameter of the vane roller to prevent the vane roller from releasing.  
           [0033]    At least one of both sides of the roller receiving hole has an opened structure.  
           [0034]    In another embodiment of the present invention, a roller support extended from the vane plate is formed at both sides of the roller receiving hole, and the vane roller can be rotatably supported by the roller support.  
           [0035]    The vane roller is installed at the roller support through a pin member.  
           [0036]    In still another embodiment of the present invention, the vane roller is formed in a bar structure with a tapering shape, and the roller receiving hole is formed in a tapering hole structure.  
           [0037]    The vane roller is positioned such that a side with a relatively smaller diameter is directed inward of the cylinder assembly and a side with a relatively greater diameter is directed outward of the cylinder assembly.  
           [0038]    The vane structure for a compressor of the present invention has effects that by mounting the vane roller being in rotatably contact with the Z-plate in the vane, a friction resistance between the Z-plate and the vane can be reduced when a compressor is operated, according to which a friction between the Z-plate and the vane can be minimized, a noise is restrained from generating, a durability of parts can be lengthened, and a reliability of the compressor can be heightened. 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0039]    [0039]FIG. 1 is a vertical-sectional view showing a compressor of a former application invention of the present invention;  
         [0040]    [0040]FIG. 2 is a partial cut-out perspective view showing a compression mechanism unit of a compressor of the former application invention of the present invention;  
         [0041]    [0041]FIG. 3 is a perspective view of a vane of the compressor of the former application invention of the present invention;  
         [0042]    [0042]FIG. 4 is a vertical-sectional view showing a compression mechanism unit of a compressor in accordance with the present invention;  
         [0043]    [0043]FIGS. 5 and 6 are a perspective view and an exploded perspective view showing a vane structure in accordance with a first embodiment of the present invention;  
         [0044]    [0044]FIGS. 7 and 8 are a perspective view and an exploded perspective view showing a vane structure in accordance with a second embodiment of the present invention;  
         [0045]    [0045]FIG. 9 is an exploded perspective view showing a vane structure and a vane installation structure in accordance with a third embodiment of the present invention; and  
         [0046]    [0046]FIG. 10 and FIG. 11 are explanatory side views showing a vane operation state of the third embodiment of the present invention. 
     
    
     MODE FOR CARRYING OUT THE PREFERRED EMBODIMENTS  
       [0047]    The present invention will now be described with reference to accompanying drawings.  
         [0048]    [0048]FIG. 4 is a vertical-sectional view showing a compression mechanism unit of a compressor in accordance with the present invention, and FIGS. 5 and 6 are a perspective view and an exploded perspective view showing a vane structure in accordance with a first embodiment of the present invention.  
         [0049]    The same reference numerals are given to the same and similar parts as in the former application invention as described above in the following descriptions.  
         [0050]    A compression mechanism unit  10  of a compressor where vanes are installed includes: a rotational shaft  12  coupled at a rotor of an electric mechanism unit provided inside a casing  1 ; a Z-plate  15  dividing the inner space of the cylinder assembly including the cylinder  11  coupled with the rotational shaft  12  into a first space V 1  and a second space V 2 ; and a first vane  50  and a second vane  55  respectively inserted into the first and second bearing plates  13  and  14  and linearly and reciprocally moved along the cam face of the Z-plate  15 .  
         [0051]    Especially, each vane  50  and  55  include vane rollers  52  and  57  at their front end portion so as to be in rolling-contact with the Z-plate  15 .  
         [0052]    In FIG. 4, reference number  5  is suction pipes through which a fluid is sucked into the casing  1 ,  19  and  20  denote discharge mufflers for reducing a discharge noise, and  19   a  and  20   a  denote discharge holes formed at the discharge mufflers  19  and  20 , through which a compressed fluid is discharged.  
         [0053]    Major constructional elements of the compression mechanism unit  10  will now be described.  
         [0054]    The first and second bearing plats  13  and  14  are respectively mounted at an upper side and a lower side of the cylinder  11 , which form a compression space of the cylinder assembly together with the cylinder  11 .  
         [0055]    The suction passages  11   a  and  11   b  are respectively formed at the cylinder  11 , communicating with the first space V 1  and the second space V 2 , in order to suck a fluid from outside. Discharge passages  13   a  and  14   a  are formed at each bearing plate  13  and  14 , which respectively include discharge valves  13   b  and  14   b.    
         [0056]    The Z-plate  15  is formed as a disk type when viewed from plane projection so that its outer circumferential surface can slidably contact the inner circumferential surface of the cylinder  11 , and the circumferential side is formed as a cam face of a sine wave curve having the same thickness from the inner circumferential face to the outer circumference face when the side is opened.  
         [0057]    In the first embodiment of the present invention, as shown in FIGS. 5 and 6, the first vane  50  and the second vane  55  include a vane plate  51  formed in a square plate structure with a certain thickness and area; and a vane roller  52  rotatably mounted at a front end portion of the vane plate  51  and being in rolling-contact with the upper surface and the lower surface of the Z-plate  15 .  
         [0058]    The vane plate  51  is supplied by springs  21  and  22  at its rear portion  51   a,  and both sides  51   b  and  51   c  are respectively in contact with the inner circumferential face of the cylinder and the outer circumferential face of the rotational shaft  12 .  
         [0059]    A long circular roller receiving hole  51   e  is formed at a front end portion  51   d  of the vane plat  51 , into which the vane roller  52  is inserted and mounted.  
         [0060]    The roller receiving hole  51   e  has a certain inner diameter as large as the vane roller  51  can be inserted. The roller receiving hole  51   e  is preferably formed in such a structure that both sides of the vane plate  51  are all opened, but according to a designing condition, either one side may be opened or both sides may not be opened.  
         [0061]    The vane roller  52  is formed in a circular bar structure with an outer diameter and length corresponding to the inner diameter and length of the roller receiving hole  51   e  and is in rolling-contact with the cam face constituted by upper and lower sides of the Z-plate  15 .  
         [0062]    The vane roller  52  is inserted and mounted in the roller receiving hole  51   e,  and at this time, the both end portions of the vane roller  52  may be mounted exposed outwardly of the roller receiving hole  51   e.    
         [0063]    The vanes  50  and  55  are respectively inserted into the vane slots of the first and second bearing plates  13  and  14 , so that the vane roller  52  of the front end portion  51   d  is in rolling-contact at the upper surface and the lower surface of the Z-plate, and the both sides  51   b  and  51   c  of the vane plate  51  are respectively in contact with the inner circumferential surface of the cylinder  11  and the outer circumferential surface of the rotational shaft  12 .  
         [0064]    At this time, the vanes  50  and  55  are positioned in a radial direction, directing to the center of the Z-plate, and positioned perpendicular to the rotational shaft  12 .  
         [0065]    The roller receiving hole  51   e  is formed such that a center of the circular section thereof is positioned at a rather inner side than the front end portion  51   d  of the vane plate  51  so that the vane rollers  52  and  57  are not released therefrom.  
         [0066]    That is, as shown in FIG. 5, the roller receiving hole  51   e  has a space (L) between both ends smaller than the diameter (D) of the vane rollers  52  and  57 .  
         [0067]    The operation and effect of the compressor having such a vane structure in accordance with the first embodiment of the present invention will now be described.  
         [0068]    When power is applied to the electric mechanism unit, the Z-plate  15  is rotated together with the rotational shaft  12 , and vanes  50  and  55  are vertically and reciprocally moved in the mutually opposite direction according to the height of the cam face of the Z-plate  15 .  
         [0069]    At this time, as for the vanes  50  and  55  being in contact with the upper and lower can face of the Z-plate  15 , the vane rollers  52  and  57  provided at the front end portion roratably contact along the cam face of the Z-plate  15  when the vane rollers  52  and  57  are rotated, so that a friction resistance between the Z-plate  15  and the vanes  50  and  55  can be considerably reduced.  
         [0070]    That is, the Z-plate  15  makes a rotational motion centering around the rotational shaft  12 , whereas the vanes  50  and  55  make a linear motion in an axial direction of the rotational shaft  12  while being in contact at the cam face of the Z-plate. Accordingly the motion direction of the Z-plate  15  and the vanes  50  and  55  makes 90°, causing a problem of generation of a severe friction at the mutual contact side.  
         [0071]    Comparatively, however, in the present invention, the vane rollers  52  and  57  are provided at the vanes  50  and  55 , to make a rolling motion between the vanes  50  and  55  and the Z-plate  15 , agreeing with the rotation direction of the Z-plate  15 . Thus, a friction resistance between the Z-plate  15  and the vanes  50  and  55  can be minimized.  
         [0072]    In order to mount the vane rollers  52  and  57 , the vane rollers  52  and  57  are pushed from the side and inserted into the roller receiving hole  51   e  formed at each vane plate  51 . Therefore, less number of parts are required to mount the vane rollers  52  and  57  and its assembly work is easy, so that a productivity degradation can be prevented.  
         [0073]    In addition, since the center of the roller receiving hole  51   e  for receiving the vane rollers  52  and  57  is formed at the inner side of the contact end of the front end portion, so that the vane rollers  52  and  57  can be prevented from releasing during operation.  
         [0074]    [0074]FIGS. 7 and 8 are a perspective view and an exploded perspective view showing a vane structure in accordance with a second embodiment of the present invention.  
         [0075]    Compared to the construction of the first embodiment of the present invention in which only the vane rollers are inserted into the roller receiving hole, the second embodiment of the present invention proposes a structure that both sides of vanes  60  and  65  are rotatably supported by vane plates  61  and  66 .  
         [0076]    That is, in the vane plates  61  and  66 , roller receiving holes  61   e  and  66   e  are formed at a front end portion being in contact with the Z-plate, of which both sides are not opened, and roller supports  61   b  and  66   b  are formed to rotatably support the vane rollers  62  and  67  by means of pin members  63  and  68 .  
         [0077]    Pin through holes  62   a,    67   a,    61   c  and  66   c  are formed at the vane rollers  62  and  67  and at the roller supports  61   b  and  66   b,  into which the pin members  63  and  68  are inserted.  
         [0078]    It is preferred that the size of the roller supports  61   b  and  66   b  is adjusted such that they are formed less protruded than the vane rollers  62  and  67  so as not directly to be in contact with the Z-plate.  
         [0079]    Meanwhile, though not presented in the drawings, protrusions may be formed at both ends of the vane rollers  62  and  67  and inserted and mounted into grooves of the roller supports  61   b  and  66   b,  without installing pin members.  
         [0080]    [0080]FIG. 9 is an exploded perspective view showing a vane structure and a vane installation structure in accordance with a third embodiment of the present invention, and FIG. 10 and FIG. 11 are explanatory side views showing a vane operation state of the third embodiment of the present invention.  
         [0081]    Unlike the vane rollers which are formed in a cylindrical structure with the same diameter as in the first and second embodiments as described above, a vane roller  72  in the third embodiment has a structure that it is tapering off.  
         [0082]    That is, a roller receiving hole  71 e of a vane plate  71  is form in a conical shape, for which the vane roller  72  inserted into the roller receiving hole  71   e  is also formed in a conical bar shape corresponding to the roller receiving hole  71   e.  The conical vane roller  72  is in rolling-contact with the Z-plate  15 .  
         [0083]    The vane roller  72  has a length corresponding to the length of the roller receiving hole  71   e  and different diameters at both end portions as it tapers off to form a conical bar shape.  
         [0084]    The roller receiving hole  71   e  is formed in a conical shape with different inner diameters at both ends, of which lower surface being in contact with the Z-plate is opened.  
         [0085]    The roller receiving hole  71 e is preferably formed from the side being in contact with an outer circumference of the rotational shaft  12  to the side being in contact with an inner wall of the cylinder  11 .  
         [0086]    Namely, the roller receiving hole  71   e  is preferably formed penetrating both sides of the vane plate  71 . In this respect, however, one side of the roller receiving hole  71   e  may penetrate one side of the vane plate  71  with some portion of the other side remaining, or otherwise, a roller support may be formed at both sides likewise in the second embodiment of the present invention.  
         [0087]    The center of the roller receiving hole  71   e  is to be formed inclined against the front end side of the vane plate  71 . The reason for this is to allow the contact surface of the tapering vane roller  72  inserted into the roller receiving hole  71   e  to tightly adhered onto the upper surface or the lower surface of the Z-plate  15 , being level therein without a gap.  
         [0088]    The tapering vane roller  72  is inserted such that the side with smaller diameter is positioned at the side of the rotational shaft  12  and the side with a larger diameter is positioned at the side of the inner wall of the cylinder  11 .  
         [0089]    As vane  70  is inserted into the vane slot  13   a  formed at the bearing plate  13 , the tapering vane roller  72  is in rolling-contact with the Z-plate and both sides of the vane plate  71  are respectively in contact with the outer circumferential face of the rotational shaft  12  and the inner circumferential face of the cylinder  11 .  
         [0090]    At this time, the vane  70  is positioned in a radial direction toward the center of the Z-plate  15  and positioned perpendicular to the rotational shaft  12 .  
         [0091]    The vane  70  is elastically supported by a spring coupled at one side of the bearing plate  13 . Accordingly, the vane  70  makes a rolling movement as the tapering vane roller is in line-contact with the Z-plate with an elastic force constantly.  
         [0092]    The vane slot  13   a,  into which the vane  70  is inserted, is penetratingly formed at the bearing plate  13 , having a width corresponding to the thickness of the vane  70  and a length corresponding to the length of the vane  70 .  
         [0093]    That is, the vane slot  13   a  has the same section and shape with the vane plate  71  of the vane  70 .  
         [0094]    The operation and effect of the vane structure in accordance with the third embodiment of the present invention will now be described.  
         [0095]    When a rotational shaft  12  is rotated upon receiving a driving force from the electric mechanism unit, the Z-plate  15  is rotated along with the rotational shaft  12 , to respectively and successively change the first and second spaces within the cylinder assembly into a suction area and a compression area together with vanes  70 , to suck and compress and discharge a fluid.  
         [0096]    In the above process, as the Z-plate  15  is rotated, vanes  70  being in contact with the waveform cam surface of the Z-plate are vertically moved along the cam surface, and at this time, the vane roller  72  of the vane  70  is rotated in a state of being in line-contact with the waveform curved surface of the Z-plate  15 .  
         [0097]    According to the rotation of the Z-plate  15 , the vane roller  72  of the vane  70  makes a rolling movement in a state of being in line-contact with the Z-plate  15 , changing the first and second space within the cylinder assembly consisting of the cylinder  11  and the bearing plate to each suction area and compression area. Hence, a friction resistance between the Z-plate  15  and the vane  70  can be minimized and movement of the vane  70  can be smoothly made.  
         [0098]    With reference to FIG. 10, there is a difference between a curvature of an inner curved line (a) of the Z-plate  15 , that is, the curved line where the rotational shaft  12  and the Z-plate  15  meet, and the inner diameter, and a curvature of an outer curved line (b) of the Z-plate  15  and the outer diameter. In this connection, if the vane roller  72  of the vane  70  is formed in a bar structure wholly having the same diameter, an infinitesimal gap may occur due to the curvature difference between the inner curved line (a) and the outer curved line (b) of the Z-plate  15 . Then, an infinitesimal pressure leakage may occur between the suction area and the compression are.  
         [0099]    However, if the vane roller  72  of the vane  70  is formed in a tapering bar shape, as shown in FIG. 11, such an infinitesimal gap possibly caused due to the curvature difference between the inner curved line (a) and the outer curved line (b) of the Z-plate  15  can be prevented from occurrence. Therefore, a friction resistance can be minimized and a pressure leakage can be prevented.  
       INDUSTRIAL APPLICABILITY  
       [0100]    As so far described, according to the vane structure for a compressor of the present invention, by mounting the vane roller being in rotatably contact with the Z-plate in the vane, a friction resistance between the Z-plate and the vane can be reduced when the compressor is operated. Thus, abrasion between the Z-plate and the vane can be minimized, a noise occurrence can be restrained, durability of parts can be lengthened, and accordingly, a reliability of the compressor can be heightened.