CN104454530B - Compressing mechanism and there is its rotary compressor for rotary compressor - Google Patents
Compressing mechanism and there is its rotary compressor for rotary compressor Download PDFInfo
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- CN104454530B CN104454530B CN201410734823.7A CN201410734823A CN104454530B CN 104454530 B CN104454530 B CN 104454530B CN 201410734823 A CN201410734823 A CN 201410734823A CN 104454530 B CN104454530 B CN 104454530B
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Abstract
The invention discloses a kind of compression mechanism for rotary compressor and there is its rotary compressor, compression mechanism includes: cylinder, two bearing parts, bent axle, piston and slide plate, cylinder is formed the first vane slot radially extending and connecting with compression chamber, it is provided with dividing plate between at least one and cylinder in two of which bearing, dividing plate is formed the second vane slot, second vane slot is corresponding with the first vane slot, and second vane slot and the first vane slot collectively form vane slot, slide plate is movably arranged in vane slot.The compression mechanism for rotary compressor according to the present invention, by offering the second vane slot, the problem that slide plate occurs bending and deformation can be improved, promote the overall efficiency of rotary compressor, and owing to the second vane slot is opened on dividing plate, the problem that can improve the assembling dislocation of slide plate and the second vane slot in the process of assembling, such that it is able to be effectively improved efficiency of assembling, it is simple to the popularization and application of compression mechanism.
Description
Technical field
The present invention relates to compressor apparatus field, especially relate to a kind of compression mechanism for rotary compressor and there is its rotary compressor.
Background technology
In the design of rotary compressor, owing to the pressure of the cold-producing medium at different parts place of compression mechanism is different, the difference force that slide plate bears mainly includes the first difference force and the second difference force, wherein the first difference force is the difference force that the part that slide plate extend in compression chamber is born, first difference force is mainly by the extension elongation of slide plate, the height of slide plate, and the pressure of suction muffler and discharge chamber determines, the difference force that wherein the second difference force is the inner of slide plate and the outer end of slide plate is born, second difference force is mainly by the width of slide plate, pressure in the height of slide plate and compression case body, the pressure of suction muffler and the pressure of discharge chamber together decide on.
Impact by the first difference force, slide plate can deform, in order to by the deformation amount controlling of slide plate within rational scope, then need to make slide plate ensure certain width, such as slide plate width is it is generally required to more than 3mm, but when the width of slide plate is thicker, second difference force can increase accordingly, thus indirectly adding the inner of slide plate and the contact force of piston, thus the power of compressor can be increased, affect the efficiency of rotary compressor, and when the extension elongation of slide plate is longer, and the total length of slide plate shorter time, by cause slide plate to stretch out rate bigger, thus the reliability of compressor will be affected, and hinder the flattening development of rotary compressor.
Summary of the invention
It is contemplated that at least solve one of technical problem of existence in prior art.For this, the invention reside in proposition a kind of compression mechanism for rotary compressor, the performance of described compression mechanism good and be easy to assemble.
The present invention also proposes a kind of rotary compressor with compression mechanism.
The compression mechanism for rotary compressor according to a first aspect of the present invention, including: cylinder assembly, described cylinder assembly includes cylinder and two bearings, said two bearing is respectively provided at the axial two ends of described cylinder, compression chamber is limited between described cylinder and said two bearing, described cylinder is formed the first vane slot radially extending and connecting with described compression chamber, it is provided with dividing plate between at least one and described cylinder in wherein said two bearings, described dividing plate is formed the second vane slot, described second vane slot is corresponding with described first vane slot, and described second vane slot and described first vane slot collectively form vane slot；Bent axle, described bent axle runs through described cylinder assembly, and described bent axle has eccentric part；Piston, described piston bush is located on described eccentric part and is positioned at described compression chamber；And slide plate, described slide plate is movably arranged in described vane slot, and the periphery wall of the inner and described piston of described slide plate only supports.
The compression mechanism for rotary compressor according to the present invention, by offering the second vane slot, the problem that slide plate occurs bending and deformation can be improved, promote the overall efficiency of rotary compressor, and owing to the second vane slot is opened on dividing plate, the problem that can improve the assembling dislocation of slide plate and the second vane slot in the process of assembling, such that it is able to be effectively improved efficiency of assembling, it is simple to the popularization and application of compression mechanism.
Alternatively, described dividing plate is two, and said two dividing plate is respectively provided between corresponding described bearing and described cylinder, said two dividing plate has been respectively formed on described second vane slot, and the two ends axially at described cylinder of wherein said slide plate are respectively received in described second vane slot of correspondence.
Alternatively, described second vane slot runs through described dividing plate along the thickness direction of described dividing plate.
Specifically, the width D of described slide plate meets: 0.5mm≤D≤3mm.
Further, the width D of described slide plate meets further: 1mm≤D≤2.5mm.
Specifically, the effective length L of described slide plate meets with the eccentric amount e of described bent axle: (2 × e) mm≤L≤2 × e+20mm.
Further, the effective length L of described slide plate meets further with the eccentric amount e of described bent axle: 2 × e+3mm≤L≤2 × e+8mm.
Specifically, the width of described second vane slot is equal with the width of described first vane slot.
Rotary compressor according to a second aspect of the present invention, including the compression mechanism for rotary compressor according to a first aspect of the present invention.
Rotary compressor according to the present invention, by arranging the compression mechanism for rotary compressor of above-mentioned first aspect, thus improve the overall performance of rotary compressor.
The additional aspect of the present invention and advantage will part provide in the following description, and part will become apparent from the description below, or is recognized by the practice of the present invention.
Accompanying drawing explanation
Fig. 1 is the explosive view of compression mechanism according to embodiments of the present invention；
Fig. 2 is the generalized section of the compression mechanism shown in Fig. 1.
Accompanying drawing labelling:
100: compression mechanism；101: vane slot；
1: cylinder；11: compression lumen pore；1a: air vent；1b: air entry；
11a: discharge chamber；11b: suction muffler；12: the first vane slots；
2: base bearing；3: supplementary bearing；
4: upper spacer；Vane slot on 41: the second；
5: lower clapboard；51: the second times vane slots；
6: piston；7: slide plate.
Detailed description of the invention
Being described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has the element of same or like function from start to finish.The embodiment described below with reference to accompanying drawing is illustrative of, it is intended to is used for explaining the present invention, and is not considered as limiting the invention.
Following disclosure provides many different embodiments or example for realizing the different structure of the present invention.In order to simplify disclosure of the invention, hereinafter parts and setting to specific examples are described.Certainly, they are only merely illustrative, and are not intended to the restriction present invention.Additionally, the present invention can in different examples repeat reference numerals and/or letter.This repetition is for purposes of simplicity and clarity, the relation between itself not indicating discussed various embodiment and/or arranging.Additionally, the example of the various specific technique that the invention provides and material, but those of ordinary skill in the art are it can be appreciated that the use of the property of can be applicable to of other techniques and/or other materials.
The compression mechanism 100 for rotary compressor of embodiment according to a first aspect of the present invention is described below with reference to Fig. 1 and Fig. 2.Wherein, rotary compressor can be vertical rotating formula compressor or horizontal rotary compressor, below, only illustrate for rotary compressor for vertical rotating formula compressor.
As it is shown in figure 1, according to a first aspect of the present invention embodiment for the compression mechanism 100 of rotary compressor, including cylinder assembly, bent axle, piston 6 and slide plate 7.
Specifically, cylinder assembly includes cylinder 1 and two bearings, and two bearings are respectively provided at the axial two ends of cylinder 1, limit compression chamber between cylinder 1 and two bearings.With reference to Fig. 1, cylinder 1 is formed the compression lumen pore 11 run through along its axis direction (such as the above-below direction described in Fig. 1), two bearing respectively base bearings 2 and supplementary bearing 3, wherein, base bearing 2 is arranged on the top on cylinder 1 axis direction, and directly or indirectly cover on the upper surface of compression lumen pore 11, supplementary bearing 3 is arranged on the lower section on cylinder 1 axis direction, and directly or indirectly cover on the lower surface of compression lumen pore 11, thus the upper surface of the lower surface of base bearing 2, supplementary bearing 3 limits compression chamber jointly with compression lumen pore 11.
Cylinder 1 is formed the first vane slot 12 radially extending and connecting with compression chamber.As depicted in figs. 1 and 2, first vane slot 12 can radially extending along cylinder 1, and first vane slot 12 can be directed away from the direction of cylinder 1 central axis by the part of sidewall for compression lumen pore 11 recessed, wherein, the upper surface of cylinder 1 is run through in the upper end of the first vane slot 12, and the lower surface of cylinder 1 is run through in the lower end of the first vane slot 12.
Being provided with dividing plate between at least one and cylinder 1 in two bearings, dividing plate is formed the second vane slot 101, the second vane slot 101 is corresponding with the first vane slot 12, and the second vane slot 101 and the first vane slot 12 collectively form vane slot 101.
That is, upper spacer 4 can be provided with between base bearing 2 and cylinder 1, second vane slot 101 can be one and be formed on upper spacer 4, now the second vane slot 101 is vane slot 41 on second, on second, the lower surface of vane slot 41 is opened wide, vane slot 41 also radially extending along cylinder 1 on second, and vane slot 41 and the first vane slot about 12 are just right on second, after upper spacer 4 and cylinder 1 are seated, on first vane slot 12 and second, the vane slot 41 projection in the plane being perpendicular to cylinder 1 axis is located along the same line, now vane slot 41 and the first vane slot 12 collectively form vane slot 101 on second.Now, compression chamber directly can be limited by upper spacer 4, cylinder 1 and supplementary bearing 3 further.
Lower clapboard 5 can be provided with between supplementary bearing 3 and cylinder 1, second vane slot 101 can also be one and be formed on lower clapboard 5, now the second vane slot 101 is second time vane slot 51, the upper surface of second time vane slot 51 is opened wide, second time vane slot 51 also radially extending along cylinder 1, and second time vane slot 51 and the first vane slot about 12 just right, after lower clapboard 5 and cylinder 1 are seated, the projection in the plane being perpendicular to cylinder 1 axis of first vane slot 12 and second time vane slot 51 is located along the same line, now second time vane slot 51 and the first vane slot 12 collectively form vane slot 101.Now, compression chamber directly can be limited by base bearing 2, cylinder 1 and lower clapboard 5 further.
Or, while being provided with upper spacer 4 between base bearing 2 and cylinder 1, lower clapboard 5 can be provided with between supplementary bearing 3 and cylinder 1, now, second vane slot 101 can also be two and not only formed on upper spacer 4, but also formed on lower clapboard 5, now, the vane slot 101 formed on upper spacer 4 is vane slot 41 on second, the vane slot 101 formed on lower clapboard 5 is second time vane slot 51, on second, 41, second time vane slot of vane slot 51 and the first vane slot 12 are just right up and down respectively, and collectively form vane slot 101.Now, compression chamber directly can be limited by upper spacer 4, cylinder 1 and lower clapboard 5 further.Below, only on the upper and lower dividing plate 5 of upper spacer 4, it is formed simultaneously with the second vane slot 101 to illustrate.In short, dividing plate is two, and two dividing plates are respectively provided between corresponding bearing and cylinder 1, and two dividing plates have been respectively formed on the second vane slot 101, and wherein the two ends axially at cylinder 1 of slide plate 7 are respectively received in the second vane slot 101 of correspondence.
Bent axle runs through cylinder assembly, and bent axle has eccentric part, and piston 6 is set on eccentric part and is positioned at compression chamber.As shown in Figure 1, bent axle sequentially runs through base bearing 2, upper spacer 4, cylinder 1, lower clapboard 5 and supplementary bearing 3, eccentric part is located on bent axle, and coordinate in compression chamber, piston 6 is formed generally as cylindrical shape and is set on eccentric part to coordinate in compression chamber, slide plate 7 coordinates in vane slot 101, the rotation axis of bent axle and the central axes of compression chamber, bent axle is in the process rotated, can pass through eccentric part drives piston 6 to roll along the inwall of compression chamber in compression chamber, when in the process that piston 6 rolls, the periphery wall of piston 6 linearly abuts with the inner circumferential sidewall of compression chamber all the time.
Slide plate 7 is movably arranged in vane slot 101.Such as in the example of fig. 1 and 2, the major part of slide plate 7 all coordinates in the first vane slot 12, the upper end of slide plate 7 coordinates on second in vane slot 41, and the lower end of slide plate 7 coordinates in second time vane slot 51, thus the height of slide plate 7 can more than the height of compression chamber.Here, it is to be understood that " highly " refer at cylinder 1 height axially.
The inner A1 of slide plate 7 only supports with the periphery wall of piston 6.Specifically, slide plate 7 can be slidably disposed in vane slot 101 by spring, wherein the outer end of spring is connected with cylinder 1, the inner of spring is connected with the outer end A2 of slide plate 7, wherein, spring is in compressive state all the time, thus the inner A1 of slide plate 7 can being promoted under the effect of the elastic force of spring to extend in compression chamber and being only against on the periphery wall of piston 6, so, in the process that crankshaft driving piston 6 rolls, slide plate 7 under piston 6 dual function with spring, motion of back and forth retreating can be done in vane slot 101.Here, it is to be understood that " the inner " refers to one end of contiguous cylinder 1 central axis, and its contrary one end is " outer end ", namely away from one end of cylinder 1 central axis.
In the process of slide plate 7 motion, owing to the outer end A2 of slide plate 7 is always positioned in vane slot 101, and the inner A1 of slide plate 7 closely abuts with the periphery wall of piston 6 all the time, thus compression chamber can be separated into the suction muffler 11b and discharge chamber 11a that are isolated from each other by slide plate 7 and piston 6, wherein suction muffler 11b can pass through air entry 1b suction cold-producing medium, discharge chamber 11a can pass through the cold-producing medium after air vent 1a discharges compression, roll at piston 6, in the process that slide plate 7 slides, the spatial volume of suction muffler 11b and discharge chamber 11a is continually changing, thus being compressed from the air entry 1b cold-producing medium flowed in suction muffler 11b, discharge from the air vent 1a discharge chamber 11a more afterwards.Here, it is necessary to explanation, cold-producing medium in the process of compression, the both sides of slide plate 7 respectively suction muffler 11b and discharge chamber 11a, make slide plate 7 be under pressure poor Fa owing to suction muffler 11b is different from the gas pressure in discharge chamber 11a.
Wherein, when piston 6 moves to top dead center position, namely when piston 6 is rolled into closest with the inner B1 of vane slot 101, the inner B1 of inner A1 and the first vane slot 12 of slide plate 7 is concordant, now, slide plate 7 is all formed constraint by the sidewall of the first vane slot 12 and the sidewall of the second vane slot 101, when piston 6 is rolled into and leaves top dead center position, the inner end of slide plate 7 extend into the inner side of the inner B1 of the first vane slot 12 and departs from the first vane slot 12, and the top and bottom of the inner end of slide plate 7 coordinate on second in vane slot 41 and second time vane slot 51 all the time, now, the inner end of slide plate 7 is not retrained by the sidewall of the first vane slot 12, and the upper end of the inner end of slide plate 7 is had effect of contraction by the sidewall of vane slot 41 on second, the lower end of the inner end of slide plate 7 is had effect of contraction by the sidewall of second time vane slot 51.
That is, slide plate 7 is in reciprocating process, the upper end of slide plate 7 is completely fitted on second in vane slot 41 all the time, the lower end of slide plate 7 is completely fitted in second time vane slot 51 all the time, thus vane slot 41 and second time vane slot 51 can support slide plate 7 effectively on second, to improve the problem on deformation of slide plate 7.
Here; it is understandable that; it is free to move back and forth and be easy to processing in order to ensure slide plate 7; on second, the minimum range S1 between the inner C11 and the inner B1 of the first vane slot 12 of vane slot 41 needs the maximum built-in length S be more than or equal to slide plate 7; it is to say, S1 >=S, and the minimum range S2 needs between the inner B1 of the inner C21 of second time vane slot 51 and the first vane slot 12 are be more than or equal to the maximum built-in length S of slide plate 7; it is to say, S2 >=S.Wherein, " the maximum built-in length of slide plate 7 " refers to piston 6 when being positioned at bottom dead center position, distance between the inner A1 and the inner B1 of vane slot 101 of slide plate 7, wherein " bottom dead center position " refers to piston 6 and is rolled into the inner B1 with vane slot 101 apart from maximum position.
So, by offering the second vane slot 101, slide plate 7 can be played effective supporting role, thus improving the force way of slide plate 7, it is similar to the force way being changed to simply supported beam by the force way of cantilever beam, slide plate 7 is avoided to occur bending and deformation, make to adopt thinner slide plate 7 to be possibly realized, namely the width of slide plate 7 can significantly be reduced, thus the contact force reduced between the inner A1 of slide plate 7 and piston 6, to avoid there is between the inner A1 of slide plate 7 and the outer end A2 of slide plate 7 bigger pressure reduction Fb, such that it is able to reduce the power of rotary compressor, promote the overall efficiency of rotary compressor.Additionally, by arranging the second vane slot 101, can so that the extension elongation of slide plate 7 is not stretched out the impact of rate by slide plate 7, such that it is able to increase the rate of stretching out of slide plate 7, reduce the total length of slide plate 7, increase the offset of bent axle so that the flattening of rotary compressor is designed to possibility.
Here, it will be appreciated that, " width " refers at the width being perpendicular on slide plate 7 moving direction, " length " refers to along the length on slide plate 7 moving direction, " extension elongation of slide plate 7 " refers to the length extending in compression chamber of slide plate 7, " the stretching out rate of slide plate 7 " refers to the ratio of the extension elongation of slide plate 7 and the total length of slide plate 7, " eccentric amount e of bent axle " can be understood as the distance between the central axis of piston 6 and the central axis of cylinder 1, and " central axis of cylinder 1 " is the central axis of compression chamber.
The compression mechanism 100 for rotary compressor according to embodiments of the present invention, by offering the second vane slot 101, the problem that slide plate 7 occurs bending and deformation can be improved, such that it is able to reduce the width of slide plate 7, increase the rate of stretching out of slide plate 7, reduce the offset of the overall length of slide plate 7, increase bent axle, to promote the overall efficiency of rotary compressor so that the flattening of rotary compressor is designed to possibility.
And owing to the second vane slot 101 is opened on dividing plate; in the process of assembling; the problem that will not cause the assembling dislocation of slide plate 7 and the second vane slot 101 due to regulation of mental activities operation; that is; can convenient and effectively ensure the depth of parallelism of the second vane slot 101 and the first vane slot 12, to guarantee that slide plate 7 can freely, successfully in vane slot 101 move, it is to avoid slide plate 7 moves card and waits indefinitely problem; such that it is able to be effectively improved efficiency of assembling, it is simple to the popularization and application of compression mechanism 100.
The width of the slide plate 7 in correlation technique is generally 3.2mm～5mm, owing to offering the second vane slot 101 on dividing plate, thus changing the force way of slide plate 7, improve the flexural deformation problem of slide plate 7, and then the width of slide plate 7 and vane slot 101 can be reduced further, such as the width of slide plate 7 can be reduced to 0.5mm～3mm, that is, offer in the cylinder assembly of the second vane slot 101, the width D of slide plate 7 can meet: 0.5mm≤D≤3mm, and preferably, the width D of slide plate 7 meets further: 1mm≤D≤2.5mm, so that the overall performance of processing and manufacturing and raising rotary compressor.
Along with the reduction of the width of slide plate 7, the width of vane slot 101 can also correspondingly reduce, and to ensure that slide plate 7 can reliably and stably in vane slot 101 move back and forth, avoids the problems such as leakage simultaneously.Preferably; the width of the second vane slot 101 and the width of the first vane slot 12 are equal; that is; on second, the width of 41, second time vane slot of vane slot 51 and the first vane slot 12 is equal respectively; consequently facilitating processing, and further ensure that slide plate 7 can reliably and stably in vane slot 101 move back and forth.
Owing to offering the second vane slot 101 on dividing plate, thus changing the force way of slide plate 7 so that the extension elongation of slide plate 7 is not stretched out the impact of rate by slide plate 7, such that it is able to increase the rate of stretching out of slide plate 7 further, reduce the total length of slide plate 7.Therefore, the effective length L of slide plate 7 and the eccentric amount e of bent axle can meet: (2 × e) mm≤L≤2 × e+20mm, and preferably, the effective length L of slide plate 7 and the eccentric amount e of bent axle meet further: 2 × e+3mm≤L≤2 × e+8mm, consequently facilitating the overall performance of processing and manufacture and raising rotary compressor.
Wherein, " effective length of slide plate 7 " can be understood as piston 6 when running to bottom dead center position, length between the inner A1 and effective outer end A3 of slide plate 7 of slide plate 7, wherein, " effective outer end " refers to piston 6 when running to bottom dead center position, the outermost end contacted with the first vane slot 12 of slide plate 7, such as in the figure 2 example, when the total length of slide plate 7 is shorter, piston 6 runs to bottom dead center position, the outer end A2 of slide plate 7 may be located at the inner side of the outer end B2 being namely positioned at the first vane slot 12 in the first vane slot 12, now the outer end A2 of slide plate 7 is effective outer end A3 of slide plate 7, namely the outer end A2 of slide plate 7 overlaps with effective outer end A3 of slide plate 7, when the total length of slide plate 7 is longer (not shown go out), piston 6 runs to bottom dead center position, the outer end A2 of slide plate 7 may be located at the outside of the outer end B2 of the first vane slot 12, the now outer end B2 that effective outer end A3 is vane slot 101 of slide plate 7, namely effective outer end A3 of slide plate 7 overlaps with the outer end B2 of vane slot 101, and it is respectively positioned on the inner side of the outer end A2 of slide plate 7.
Specifically, the second vane slot 101 runs through dividing plate along the thickness direction of dividing plate.Such as in the example of fig. 1 and 2, on second, vane slot 41 runs through upper spacer 4 along the vertical direction, second time vane slot 51 runs through lower clapboard 5 along the vertical direction, consequently facilitating the processing of upper spacer 4 and lower clapboard 5, and may insure that upper spacer 4 and the thinner thickness of lower clapboard 5, to be conducive to the flattening of rotary compressor further.
Certainly, the invention is not restricted to this, on second, vane slot 41 can also be formed by the lower surface of upper spacer 4 is upwardly recessed, and on second vane slot 41 not through the upper surface of upper spacer 4, second time vane slot 51 can also be downwardly concaved by the upper surface of lower clapboard 5 and form, and second time vane slot 51 is not through the lower surface of lower clapboard 5.
The rotary compressor (not shown go out) of embodiment according to a second aspect of the present invention, including the compression mechanism 100 for rotary compressor according to the above-mentioned first aspect embodiment of the present invention.It addition, rotary compressor according to embodiments of the present invention can also include: housing (not shown go out) and electric machine assembly (not shown go out).
Wherein, housing can include upper shell, middle casing and lower house, upper shell and lower house are connected to top and the bottom of middle casing, jointly to limit the cylindrical shell of sealing and hollow with middle casing, preferably, middle casing can adopt welding procedure be integrally fixed structure respectively with upper shell and lower house.It is, of course, understood that the structure of housing is not limited to this.
Further, electric machine assembly can be located at the top in housing, compression mechanism 100 can be located in housing and be positioned at the lower section of electric machine assembly, wherein, electric machine assembly can include stator and rotor, stator can be fixed together with the periphery wall of middle casing, rotor can be rotatably arranged in stator, the upper end of bent axle can be fixed together with rotor hot jacket, thus rotor can drive bent axle to rotate around the central axis of bent axle, compression mechanism 100 is run through in the bottom of bent axle, thus can cold-producing medium in compression compressors structure 100 in the process of crank rotation.
Rotary compressor according to embodiments of the present invention, by arranging the compression mechanism 100 for rotary compressor of above-mentioned first aspect embodiment, thus improve the overall performance of rotary compressor.
In describing the invention, it will be appreciated that, term " " center ", " length ", " width ", " highly ", " on ", D score, " vertically ", " level ", " top ", " end ", " interior ", " outward ", " axially ", " radially ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, it is for only for ease of the description present invention and simplifies description, rather than the device of instruction or hint indication or element must have specific orientation, with specific azimuth configuration and operation, therefore it is not considered as limiting the invention.
Additionally, term " first ", " second " are only for descriptive purposes, and it is not intended that indicate or imply relative importance or the implicit quantity indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or implicitly include one or more these features.In describing the invention, " multiple " are meant that two or more, unless otherwise expressly limited specifically.
In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, for instance, it is possible to it is fixing connection, it is also possible to be removably connect, or integral；Can be joined directly together, it is also possible to be indirectly connected to by intermediary, it is possible to be connection or the interaction relationship of two elements of two element internals.For the ordinary skill in the art, it is possible to understand above-mentioned term concrete meaning in the present invention as the case may be.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means in conjunction with this embodiment or example describe are contained at least one embodiment or the example of the present invention.In this manual, the schematic representation of above-mentioned term is necessarily directed to identical embodiment or example.And, the specific features of description, structure, material or feature can combine in one or more embodiments in office or example in an appropriate manner.Additionally, when not conflicting, the feature of the different embodiments described in this specification or example and different embodiment or example can be carried out combining and combining by those skilled in the art.
Although an embodiment of the present invention has been shown and described, it will be understood by those skilled in the art that: these embodiments can being carried out multiple change, amendment, replacement and modification when without departing from principles of the invention and objective, the scope of the present invention is limited by claim and equivalent thereof.
Claims (9)
1. the compression mechanism for rotary compressor, it is characterised in that including:
Cylinder assembly, described cylinder assembly includes cylinder and two bearings, said two bearing is respectively provided at the axial two ends of described cylinder, compression chamber is limited between described cylinder and said two bearing, described cylinder is formed the first vane slot radially extending and connecting with described compression chamber, it is provided with dividing plate between at least one and described cylinder in wherein said two bearings, described dividing plate is formed the second vane slot, described second vane slot is corresponding with described first vane slot, and described second vane slot collectively forms vane slot with described first vane slot；
Bent axle, described bent axle runs through described cylinder assembly, and described bent axle has eccentric part；
Piston, described piston bush is located on described eccentric part and is positioned at described compression chamber；And
Slide plate, described slide plate is movably arranged in described vane slot, and the periphery wall of the inner and described piston of described slide plate only supports.
2. the compression mechanism for rotary compressor according to claim 1, it is characterized in that, described dividing plate is two, and said two dividing plate is respectively provided between corresponding described bearing and described cylinder, said two dividing plate has been respectively formed on described second vane slot, and the two ends axially at described cylinder of wherein said slide plate are respectively received in described second vane slot of correspondence.
3. the compression mechanism for rotary compressor according to claim 1, it is characterised in that described second vane slot runs through described dividing plate along the thickness direction of described dividing plate.
4. the compression mechanism for rotary compressor according to claim 1, it is characterised in that the width D of described slide plate meets: 0.5mm≤D≤3mm.
5. the compression mechanism for rotary compressor according to claim 4, it is characterised in that the width D of described slide plate meets further: 1mm≤D≤2.5mm.
6. the compression mechanism for rotary compressor according to claim 1, it is characterised in that the effective length L of described slide plate is satisfied with the eccentric amount e of described bent axle: (2 × e) mm≤L≤2 × e+20mm.
7. the compression mechanism for rotary compressor according to claim 6, it is characterised in that the eccentric amount e of the effective length L of described slide plate and described bent axle meets further: 2 × e+3mm≤L≤2 × e+8mm.
8. the compression mechanism for rotary compressor according to any one of claim 1-7, it is characterised in that the width of described second vane slot is equal with the width of described first vane slot.
9. a rotary compressor, it is characterised in that include the compression mechanism for rotary compressor according to any one of claim 1-8.
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| JP2000170677A (en) * | 1998-12-02 | 2000-06-20 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| KR100404469B1 (en) * | 2001-11-06 | 2003-11-05 | 주식회사 엘지이아이 | Bearing plate structure for compressor |
| KR20040036973A (en) * | 2002-10-25 | 2004-05-04 | 엘지전자 주식회사 | Apparatus for reducing face pressor of enclossed compressor |
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| CN101240797A (en) * | 2008-03-07 | 2008-08-13 | 广东美芝制冷设备有限公司 | Rotation-type compressor sliding blade spring and uses thereof |
| CN101624986A (en) * | 2009-07-24 | 2010-01-13 | 广东美芝制冷设备有限公司 | Slip sheet control device of rotary compressor |
| CN204312331U (en) * | 2014-12-04 | 2015-05-06 | 广东美芝制冷设备有限公司 | For rotary compressor compressing mechanism and there is its rotary compressor |
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| CN104454530A (en) | 2015-03-25 |
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