CN104454529A - Compression mechanism for rotary compressor and rotary compressor with same - Google Patents
Compression mechanism for rotary compressor and rotary compressor with same Download PDFInfo
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- CN104454529A CN104454529A CN201410729032.5A CN201410729032A CN104454529A CN 104454529 A CN104454529 A CN 104454529A CN 201410729032 A CN201410729032 A CN 201410729032A CN 104454529 A CN104454529 A CN 104454529A
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Abstract
The invention discloses a compression mechanism for a rotary compressor and the rotary compressor with the same. The compression mechanism comprises a cylinder, two bearing pieces, a crank shaft, a piston and a slip sheet, wherein the cylinder is provided with a first slip sheet groove which extends along the radial direction and is communicated with a compression cavity, at least one bearing is provided with a second slip sheet groove which is open towards the cylinder, and the second slip sheet groove corresponds to the first slip sheet groove; a slip sheet groove is formed by the second slip sheet groove and the first slip sheet groove, and the slip sheet is movably arranged in the slip sheet groove. According to the compression mechanism for the rotary compressor, at least one bearing is provided with the second slip sheet groove, so that the problem of bending deformation of the slip sheet is improved, the width of the slip sheet is decreased, and the protrusion rate of the slip sheet is increased; the length of the slip sheet is decreased, the eccentricity of the crank shaft is increased, and the integral energy efficiency of the rotary compressor is improved, and a flat design of the rotary compressor is possibly realized.
Description
Technical field
The present invention relates to compressor apparatus field, especially relate to a kind of compressing mechanism for rotary compressor and there is its rotary compressor.
Background technique
In the design of rotary compressor, because the pressure of the refrigeration agent at compressing mechanism different parts place is different, the difference force that slide plate bears mainly comprises the first difference force and the second difference force, wherein the first difference force difference force of bearing for part that slide plate extend in compression chamber, first difference force is primarily of the extrusion of slide plate, the height of slide plate, and the pressure of air aspiration cavity and exhaust cavity determines, the wherein outer end of the second difference force the inner that is slide plate and the slide plate difference force of bearing, second difference force is primarily of the width of slide plate, pressure in the height of slide plate and compressor housing, the pressure of air aspiration cavity and the pressure of exhaust cavity determine jointly.
By the impact of 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 generally needs to be greater than 3mm, but when the width of slide plate is thicker, second difference force can corresponding increase, thus indirectly add 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 extrusion of slide plate is longer, and the total length of slide plate shorter time, by causing, the rate of stretching out of slide plate is larger, thus will the reliability of compressor be affected, and hinder the flattening development of rotary compressor.
Summary of the invention
The present invention is intended at least to solve one of technical problem existed in prior art.For this reason, the invention reside in and propose a kind of compressing mechanism for rotary compressor, the performance of described compressing mechanism is good.
The present invention also proposes a kind of rotary compressor with compression mechanism.
The compressing mechanism for rotary compressor according to a first aspect of the present invention, comprise: cylinder assembly, described cylinder assembly comprises cylinder and two bearings, described two bearings are located at the axial two ends of described cylinder respectively, compression chamber is limited between described cylinder and described two bearings, described cylinder is formed with radial extension and the first vane slot be communicated with described compression chamber, at least one in wherein said two bearings is formed with the second vane slot opened wide towards described cylinder, described second vane slot is corresponding with described first vane slot, and described second vane slot and described first vane slot form vane slot jointly, bent axle, described bent axle runs through described cylinder assembly, and described bent axle has eccentric part, piston, described piston sleeve to be located on described eccentric part and to be positioned at described compression chamber, and slide plate, described slide plate is located in described vane slot movably, and the inner end of described slide plate and the periphery wall of described piston only support.
According to the compressing mechanism for rotary compressor of the present invention, by offering the second vane slot at least one bearing, the problem that slide plate occurs bending and deformation can be improved, thus the offset of the width of slide plate, the rate of stretching out increasing slide plate, the overall length reducing slide plate, increase bent axle can be reduced, to promote the overall efficiency of rotary compressor, the flattening of rotary compressor design is made to become possibility.
Alternatively, described two bearings are formed with respectively described second vane slot, being contained in respectively in corresponding described second vane slot at the two ends axially of described cylinder of wherein said slide plate.
Particularly, 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.
Particularly, the effective length L of described slide plate and the eccentric amount e of described bent axle meet: (2 × e) mm≤L≤2 × e+20mm.
Further, the effective length L of described slide plate and the eccentric amount e of described bent axle meet further: 2 × e+3mm≤L≤2 × e+8mm.
Alternatively, described second vane slot is formed to away from the direction of described cylinder is recessed by a part for a side end face of the described cylinder of the vicinity of described bearing.
Particularly, 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, comprises the compressing mechanism for rotary compressor according to a first aspect of the present invention.
According to rotary compressor of the present invention, by arranging the compressing mechanism for rotary compressor of above-mentioned first aspect, thus improve the overall performance of rotary compressor.
Additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present invention.
Accompanying drawing explanation
Fig. 1 and Fig. 2 is two explosive views of the compressing mechanism according to the embodiment of the present invention;
Fig. 3 is the generalized section of the compressing mechanism shown in Fig. 1 and Fig. 2.
Reference character:
100: compressing mechanism;
1: cylinder; 11: compression lumen pore; 1a: relief opening; 1b: intakeport;
11a: exhaust cavity; 11b: air aspiration cavity; 12: the first vane slots;
2: main bearing; Vane slot on 21: the second;
3: supplementary bearing; 31: the second times vane slots;
4: piston; 5: slide plate.
Embodiment
Be 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 element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.
Disclosing hereafter provides many different embodiments or example is used for realizing different structure of the present invention.Of the present invention open in order to simplify, hereinafter the parts of specific examples and setting are described.Certainly, they are only example, and object does not lie in restriction the present invention.In addition, the present invention can in different example repeat reference numerals and/or letter.This repetition is to simplify and clearly object, itself does not indicate the relation between discussed various embodiment and/or setting.In addition, the various specific technique that the invention provides and the example of material, but those of ordinary skill in the art can recognize the property of can be applicable to of other techniques and/or the use of other materials.
The compressing mechanism 100 for rotary compressor of embodiment is according to a first aspect of the present invention described below with reference to Fig. 1-Fig. 3.Wherein, rotary compressor can be vertical rotating formula compressor or horizontal rotary compressor, below, be only vertical rotating formula compressor with rotary compressor for example is described.
As shown in Figure 1, the compressing mechanism 100 for rotary compressor of embodiment according to a first aspect of the present invention, comprising: cylinder assembly, bent axle, piston 4 and slide plate 5.
Particularly, cylinder assembly comprises cylinder 1 and two bearings, and two bearings are located at the axial two ends of cylinder 1 respectively, limits compression chamber between cylinder 1 and two bearings.With reference to Fig. 1, cylinder 1 is formed with the compression lumen pore 11 run through along its axial direction (above-below direction such as described in Fig. 1), two bearings are respectively main bearing 2 and supplementary bearing 3, wherein, main bearing 2 is arranged on the upper end on cylinder 1 axial direction, and cover on the upper-end surface of compression lumen pore 11, supplementary bearing 3 is arranged on the lower end on cylinder 1 axial direction, and cover on the lower end surface of compression lumen pore 11, thus the upper-end surface of the lower end surface of main bearing 2, supplementary bearing 3 limits compression chamber jointly with compression lumen pore 11.
Cylinder 1 is formed with radial extension and the first vane slot 12 be communicated with compression chamber.As depicted in figs. 1 and 2, first vane slot 12 can extend along the radial direction of cylinder 1, and the first vane slot 12 can be recessed into towards the direction away from cylinder 1 central axis by a part for the sidewall of compression lumen pore 11, wherein, the upper-end surface of cylinder 1 is run through in the upper end of the first vane slot 12, and the lower end surface of cylinder 1 is run through in the lower end of the first vane slot 12.
At least one in two bearings is formed with the second vane slot opened wide towards cylinder 1, the second vane slot is corresponding with the first vane slot 12, and the second vane slot and the first vane slot 12 form vane slot jointly.
That is, second vane slot can be one and only be formed on main bearing 2, now the second vane slot is vane slot 21 on second, on second, the lower end surface of vane slot 21 is opened wide, on second, vane slot 21 also extends along the radial direction of cylinder 1, and on second vane slot 21 and the first vane slot about 12 just right, after main bearing 2 and cylinder 1 are seated, on first vane slot 12 and second, the projection of vane slot 21 in the plane perpendicular to cylinder 1 axis is located along the same line, and now vane slot 21 and the first vane slot 12 form vane slot jointly on second.
Second vane slot can also be one and only be formed on supplementary bearing 3, now the second vane slot is second time vane slot 31, the upper-end surface of second time vane slot 31 is opened wide, second time vane slot 31 also extends along the radial direction of cylinder 1, and second time vane slot 31 and the first vane slot about 12 just right, after supplementary bearing 3 and cylinder 1 are seated, first vane slot 12 and the second time projection of vane slot 31 in the plane perpendicular to cylinder 1 axis are located along the same line, and now second time vane slot 31 and the first vane slot 12 form vane slot jointly.
Or, second vane slot can also be two and not only be formed on main bearing 2, but also is formed on supplementary bearing 3, now, the vane slot be formed on main bearing 2 is vane slot 21 on second, the vane slot be formed on supplementary bearing 3 is second time vane slot 31, on second, vane slot 21, second time vane slot 31 and the first vane slot 12 are just right up and down respectively, and jointly form vane slot.Below, be only described to be formed with the second vane slot on main bearing 2 and on supplementary bearing 3 simultaneously.
Bent axle runs through cylinder assembly, and bent axle has eccentric part, and piston 4 to be set on eccentric part and to be positioned at compression chamber.As shown in Figure 1, bent axle runs through main bearing 2, cylinder 1 and supplementary bearing 3 in turn, eccentric part is located on bent axle, and be engaged in compression chamber, piston 4 is substantially formed as cylindrical shape and is set on eccentric part to be engaged in compression chamber, slide plate 5 is engaged in vane slot, the spin axis of bent axle and the central axes of compression chamber, bent axle is in the process of rotating, can be rolled along the inwall of compression chamber in compression chamber by eccentric part driven plunger 4, when in the process that piston 4 rolls, the periphery wall of piston 4 linearly abuts with the inner circumferential sidewall of compression chamber all the time.
Slide plate 5 is located in vane slot movably.Such as in the example of fig. 1 and 2, the major part of slide plate 5 is all engaged in the first vane slot 12, the upper end of slide plate 5 is engaged on second in vane slot 21, and the lower end of slide plate 5 is engaged in second time vane slot 31, thus the height of slide plate 5 can be greater than the height of compression chamber.Here, it is to be appreciated that " highly " refers at cylinder 1 height axially.
The inner A1 of slide plate 5 and the periphery wall of piston 4 only support.Particularly, slide plate 5 can be located in vane slot slidably by spring, the outer end of its medi-spring is connected with cylinder 1, the inner of spring is connected with the outer end A2 of slide plate 5, wherein, spring is in compressive state all the time, thus the inner A1 that can promote slide plate 5 under the effect of the elastic force of spring to extend in compression chamber and is only against on the periphery wall of piston 4, like this, in the process that crankshaft driving piston 4 rolls, slide plate 5 under piston 4 double action with spring, can do back and forth to retreat in vane slot and move.Here, it is to be appreciated that " the inner " refers to one end of contiguous cylinder 1 central axis, its contrary one end is " outer end ", namely away from one end of cylinder 1 central axis.
In the process that slide plate 5 moves, because the outer end A2 of slide plate 5 is positioned at vane slot all the time, and the inner A1 of slide plate 5 closely abuts with the periphery wall of piston 4 all the time, thus compression chamber can be separated into the air aspiration cavity 11b and exhaust cavity 11a that are isolated from each other by slide plate 5 and piston 4, wherein air aspiration cavity 11b can suck refrigeration agent by intakeport 1b, exhaust cavity 11a can discharge the refrigeration agent after compression by relief opening 1a, roll at piston 4, in the process that slide plate 5 slides, the spatial volume of air aspiration cavity 11b and exhaust cavity 11a constantly changes, thus compressed from the refrigeration agent that intakeport 1b flows in air aspiration cavity 11b, discharge from the relief opening 1a exhaust cavity 11a more afterwards.Here, it should be noted that, refrigeration agent is in the process of compression, and the both sides of slide plate 5 are respectively air aspiration cavity 11b and exhaust cavity 11a, makes slide plate 5 be under pressure poor Fa because air aspiration cavity 11b is different from the gas pressure in exhaust cavity 11a.
Wherein, when piston 4 moves to top dead center position, namely when piston 4 is rolled into nearest with the inner B1 of vane slot, the inner A1 of slide plate 5 is concordant with the inner B1 of the first vane slot 12, now, the sidewall of the first vane slot 12 and the sidewall of the second vane slot are all formed slide plate 5 and retrain, when piston 4 be rolled into leave top dead center position time, the inner end of slide plate 5 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 5 to be engaged on second in vane slot 21 and second time vane slot 31 all the time, now, the inner end of sidewall to slide plate 5 of the first vane slot 12 does not retrain, and the upper end of sidewall to the inner end of slide plate 5 of vane slot 21 has effect of contraction on second, the lower end of sidewall to the inner end of slide plate 5 of second time vane slot 31 has effect of contraction.
That is, slide plate 5 is in reciprocating process, the upper end of slide plate 5 to be engaged on second in vane slot 21 all the time completely, the lower end of slide plate 5 is engaged in second time vane slot 31 all the time completely, thus vane slot 21 and second time vane slot 31 can support slide plate 5, effectively to improve the problem on deformation of slide plate 5 on second.
Here; be understandable that; be free to move back and forth in order to ensure slide plate 5 and be convenient to processing; minimum range S1 on second between the inner C11 of the vane slot 21 and inner B1 of the first vane slot 12 needs the maximum built-in length S being more than or equal to slide plate 5; that is, S1 >=S, and the minimum range S2 between the inner B1 of the inner C21 of second time vane slot 31 and the first vane slot 12 needs the maximum built-in length S being more than or equal to slide plate 5; that is, S2 >=S.Wherein, " the maximum built-in length of slide plate 5 " refers to piston 4 when being positioned at bottom dead center position, distance between the inner A1 of the slide plate 5 and inner B1 of vane slot, wherein " bottom dead center position " refers to piston 4 and is rolled into the inner B1 of vane slot apart from maximum position.
In addition, it should be noted that, the length of the second vane slot can not be long, and the bent axle via hole on first on the inner B1 of vane slot and main bearing 2 needs spaced apart, bent axle via hole on second on the inner B1 of vane slot 21 and supplementary bearing 3 also needs spaced apart, to avoid the leakage problem of refrigeration agent.
According to the compressing mechanism 100 for rotary compressor of the embodiment of the present invention, by offering the second vane slot at least one bearing, effective supporting effect can be played to slide plate 5, thus improve the force way of slide plate 5, be similar to the force way being changed to simply supported beam by the force way of overhang, slide plate 5 is avoided to occur bending and deformation, make to adopt thinner slide plate 5 to become possibility, namely the width of slide plate 5 can significantly be reduced, thus the contact force reduced between the inner A1 of slide plate 5 and piston 4, to avoid that there is between the inner A1 of the slide plate 5 and outer end A2 of slide plate 5 larger pressure reduction Fb, thus the power of rotary compressor can be reduced, promote the overall efficiency of rotary compressor.In addition, by arranging the second vane slot, the extrusion of slide plate 5 can be made by slide plate 5 not stretch out the impact of rate, thus the offset of the rate of stretching out of slide plate 5, the total length reducing slide plate 5, increase bent axle can be increased, make the flattening of rotary compressor design become possibility.
Here, it will be appreciated that, described herein " width " refers to perpendicular to the width on slide plate 5 movement direction, " length " refers to along the length on slide plate 5 movement direction, " extrusion of slide plate 5 " refers to the length extend in compression chamber of slide plate 5, " the stretching out rate of slide plate 5 " refers to the ratio of the extrusion of slide plate 5 and the total length of slide plate 5, " eccentric amount e of bent axle " can be understood as the distance between the central axis of piston 4 and the central axis of cylinder 1, and " central axis of cylinder 1 " is the central axis of compression chamber.
The width of the slide plate 5 in correlation technique is generally 3.2mm ~ 5mm, due at least one in two bearings offering the second vane slot, thus change the force way of slide plate 5, improve the bending deflection problem of slide plate 5, and then the width of slide plate 5 and vane slot can be reduced further, the width of such as slide plate 5 can be reduced to 0.5mm ~ 3mm, that is, offer in the cylinder assembly of the second vane slot, the width D of slide plate 5 can meet: 0.5mm≤D≤3mm, and preferably, the width D of slide plate 5 meets further: 1mm≤D≤2.5mm, so that the overall performance of manufacturing and raising rotary compressor.
Along with the reduction of the width of slide plate 5, the width of vane slot also can correspondingly reduce, to ensure that slide plate 5 reliably and stably to-and-fro motion in vane slot, can avoid the problems such as leakage simultaneously.Preferably; the width of the second vane slot is equal with the width of the first vane slot 12; that is; on second, the width of vane slot 21, second time vane slot 31 and the first vane slot 12 is equal respectively; thus be convenient to processing, and guarantee that slide plate 5 can reliably and stably to-and-fro motion in vane slot further.
Due at least one in two bearings offering the second vane slot, thus change the force way of slide plate 5, make the extrusion of slide plate 5 not stretch out the impact of rate by slide plate 5, thus the rate of stretching out of slide plate 5, the total length of reduction slide plate 5 can be increased further.Therefore, the effective length L of slide plate 5 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 5 and the eccentric amount e of bent axle meet further: 2 × e+3mm≤L≤2 × e+8mm, thus are convenient to the overall performance processing and manufacture and improve rotary compressor.
Wherein, " effective length of slide plate 5 " can be understood as piston 4 when moving to bottom dead center position, length between the inner A1 of slide plate 5 and effective outer end A3 of slide plate 5, wherein, " effective outer end " refers to piston 4 when moving to bottom dead center position, the outermost end contacted with the first vane slot 12 of slide plate 5, such as in the figure 2 example, when the total length of slide plate 5 is shorter, after piston 4 moves to bottom dead center position, the outer end A2 of slide plate 5 can be positioned at the inner side that namely the first vane slot 12 is positioned at the outer end B2 of the first vane slot 12, now the outer end A2 of slide plate 5 is effective outer end A3 of slide plate 5, namely the outer end A2 of slide plate 5 overlaps with effective outer end A3 of slide plate 5, (scheme not shown) when the total length of slide plate 5 is longer, after piston 4 moves to bottom dead center position, the outer end A2 of slide plate 5 can be positioned at the outside of the outer end B2 of the first vane slot 12, now effective outer end A3 of slide plate 5 is the outer end B2 of vane slot, namely effective outer end A3 of slide plate 5 overlaps with the outer end B2 of vane slot, and be all positioned at the inner side of the outer end A2 of slide plate 5.
Preferably, the second vane slot is formed to away from the direction of cylinder 1 is recessed by a part for a side end face of the contiguous cylinder 1 of bearing.Such as in the example of fig. 1, on second, vane slot 21 is formed on the lower end surface of main bearing 2, and formed to being recessed on by a part for main bearing 2 lower end surface, second time vane slot 31 is formed on the upper-end surface of supplementary bearing 3, and is formed by a part for supplementary bearing 3 upper-end surface is recessed downwards.
The rotary compressor (scheming not shown) of embodiment, comprises the compressing mechanism 100 for rotary compressor according to the above-mentioned first aspect embodiment of the present invention according to a second aspect of the present invention.In addition, can also comprise according to the rotary compressor of the embodiment of the present invention: housing (scheming not shown) and electric machine assembly (scheming not shown).
Wherein, housing can comprise upper shell, middle casing and lower shell body, upper shell and lower shell body are connected to top and the bottom of middle casing, seal and the cylindrical shell of hollow jointly to limit with middle casing, preferably, middle casing can adopt welding procedure to be integrally fixed structure respectively with upper shell and lower shell body.Certainly, be understandable that, the structure of housing is not limited thereto.
Further, electric machine assembly can be located at the top in housing, compressing mechanism 100 can be located in housing and to be positioned at the below of electric machine assembly, wherein, electric machine assembly can comprise stators and rotators, stator can be fixed together with the periphery wall of middle casing, rotor can be located in stator rotationally, the upper end of bent axle can be fixed together with rotor hot jacket, thus rotor can driving crank flexing axle central axis rotate, compressing mechanism 100 is run through in the bottom of bent axle, thus can refrigeration agent in compression compressors structure 100 in the process of crank rotation.
According to the rotary compressor of the embodiment of the present invention, by arranging the compressing 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 ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, the implication of " multiple " is 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, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood 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 to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification or example and different embodiment or example can carry out combining and combining by those skilled in the art.
Although illustrate and describe embodiments of the invention, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present invention and aim, scope of the present invention is by claim and equivalents thereof.
Claims (9)
1. for a compressing mechanism for rotary compressor, it is characterized in that, comprising:
Cylinder assembly, described cylinder assembly comprises cylinder and two bearings, described two bearings are located at the axial two ends of described cylinder respectively, compression chamber is limited between described cylinder and described two bearings, described cylinder is formed with radial extension and the first vane slot be communicated with described compression chamber, at least one in wherein said two bearings is formed with the second vane slot opened wide towards described cylinder, described second vane slot is corresponding with described first vane slot, and described second vane slot and described first vane slot form vane slot jointly;
Bent axle, described bent axle runs through described cylinder assembly, and described bent axle has eccentric part;
Piston, described piston sleeve to be located on described eccentric part and to be positioned at described compression chamber; And
Slide plate, described slide plate is located in described vane slot movably, and the inner end of described slide plate and the periphery wall of described piston only support.
2. the compressing mechanism for rotary compressor according to claim 1, it is characterized in that, described two bearings are formed with respectively described second vane slot, being contained in respectively in corresponding described second vane slot at the two ends axially of described cylinder of wherein said slide plate.
3. the compressing mechanism for rotary compressor according to claim 1, is characterized in that, the width D of described slide plate meets: 0.5mm≤D≤3mm.
4. the compressing mechanism for rotary compressor according to claim 3, is characterized in that, the width D of described slide plate meets further: 1mm≤D≤2.5mm.
5. the compressing mechanism for rotary compressor according to claim 1, is characterized in that, the effective length L of described slide plate and the eccentric amount e of described bent axle meet: (2 × e) mm≤L≤2 × e+20mm.
6. the compressing mechanism for rotary compressor according to claim 5, is characterized in that, the effective length L of described slide plate and the eccentric amount e of described bent axle meet further: 2 × e+3mm≤L≤2 × e+8mm.
7. the compressing mechanism for rotary compressor according to claim 1, is characterized in that, described second vane slot is formed to away from the direction of described cylinder is recessed by a part for a side end face of the described cylinder of the vicinity of described bearing.
8. the compressing mechanism for rotary compressor according to any one of claim 1-7, is characterized in that, the width of described second vane slot is equal with the width of described first vane slot.
9. a rotary compressor, is characterized in that, comprises the compressing mechanism for rotary compressor according to any one of claim 1-8.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108252910A (en) * | 2017-11-30 | 2018-07-06 | 刘悦吟 | A kind of compressor |
| CN111287969A (en) * | 2018-12-10 | 2020-06-16 | 广东美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN111412175A (en) * | 2020-04-27 | 2020-07-14 | 中国科学院工程热物理研究所 | Distortion generating device for testing transient total pressure distortion of axial flow compressor |
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| 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 |
| CN204312330U (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 |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108252910A (en) * | 2017-11-30 | 2018-07-06 | 刘悦吟 | A kind of compressor |
| CN111287969A (en) * | 2018-12-10 | 2020-06-16 | 广东美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN111287969B (en) * | 2018-12-10 | 2022-02-18 | 广东美芝精密制造有限公司 | Compressor and refrigeration equipment |
| CN111412175A (en) * | 2020-04-27 | 2020-07-14 | 中国科学院工程热物理研究所 | Distortion generating device for testing transient total pressure distortion of axial flow compressor |
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