CN104196728B - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN104196728B CN104196728B CN201410418248.XA CN201410418248A CN104196728B CN 104196728 B CN104196728 B CN 104196728B CN 201410418248 A CN201410418248 A CN 201410418248A CN 104196728 B CN104196728 B CN 104196728B
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- housing
- supplementary bearing
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Abstract
The invention discloses a kind of rotary compressor, comprising: housing, motor and compressing mechanism, described housing comprises lower shell body assembly; Motor is located in housing; Compressing mechanism is connected with motor and comprises cylinder, main bearing and supplementary bearing assembly, supplementary bearing assembly comprises hub portion and flange part, the transverse dimension of hub portion is less than the transverse dimension of flange part, wherein P1, P2 meet respectively: 0.1≤P1≤1.5,0.06≤P2≤1.1, wherein, P1=H1/H2, P1=H3/H4, H1 is the perpendicular distance between the center of hub portion lower surface and lower shell body assembly diapire, H2 is the height of supplementary bearing assembly, and H3 is the perpendicular distance between the edge of the lower surface of flange part and lower shell body assembly diapire, and H4 is the height of cylinder.According to rotary compressor of the present invention, improve the dissolving viscosity of refrigerator oil, add the reliability of rotary compressor.
Description
Technical field
The present invention relates to art of refrigeration units, especially relate to a kind of rotary compressor.
Background technique
Point out in correlation technique, part refrigerant after rotary compressor compression can dissolve in the refrigerator oil of its oil sump, refrigerator oil can be made like this to dissolve viscosity reduce, thus reduce the lubricating condition of moving element in rotary compressor, thus reduce reliability and the working efficiency 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, one object of the present invention is to propose a kind of rotary compressor, the coolant quantity be dissolved in refrigerator oil can be reduced in its oil sump, reduce air-conditioning system refrigerant enclosed volume, also rotary compressor fuel delivery and oil supplying quality can be ensured, thus rotary compressor performance can be improved, improve rotary compressor reliability.
According to rotary compressor of the present invention, comprising: housing, have oil sump in described housing, described housing comprises lower shell body assembly, motor, described motor is located in described housing, compressing mechanism, described compressing mechanism is connected with described motor, described compressing mechanism comprises cylinder, main bearing and supplementary bearing assembly, described main bearing and supplementary bearing assembly are located at the top of described cylinder and bottom respectively and make compression chamber with described limiting cylinder, described supplementary bearing assembly comprises the hub portion and flange part that are upwards connected successively vertically, the transverse dimension of described hub portion is less than the transverse dimension of described flange part, wherein P1, P2 meets respectively: 0.1≤P1≤1.5, 0.06≤P2≤1.1, wherein, P1=H1/H2, P1=H3/H4, described H1 is the perpendicular distance between the center of described hub portion lower surface and described lower shell body assembly diapire, described H2 is described supplementary bearing assembly height in the vertical direction, described H3 is the perpendicular distance between the edge of the lower surface of described flange part and described lower shell body assembly diapire, described H4 is described cylinder height in the vertical direction.
According to rotary compressor of the present invention, temperature in oil sump is improved, thus the refrigerant content be dissolved in the refrigerator oil of oil sump reduces, and in air-conditioning system, refrigerant enclosed volume reduces, improve the dissolving viscosity of refrigerator oil simultaneously, add the reliability of rotary compressor.
Alternatively, described lower shell body assembly has the lug boss protruded downwards, and described lug boss is relative up and down with described hub portion.
Or alternatively, the bottom surface of described lower shell body assembly is formed as plane.
Further, when the discharge volume of described compression chamber is less than or equal to 25cm
3during/rev, P1, P2 meet further: 0.1≤P1≤1.0,0.08≤P2≤0.8; When the discharge volume of described compression chamber is greater than 25cm
3during/rev, P1, P2 meet further: 0.1≤P1≤1.0,0.06≤P2≤0.4.
Alternatively, the refrigerant for refrigeration cycle in described rotary compressor is HC class combustible refrigerant.
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
Above-mentioned and/or additional aspect of the present invention and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the partial schematic diagram of the rotary compressor according to the embodiment of the present invention;
Fig. 2 is another schematic diagram of the rotary compressor shown in Fig. 1;
Fig. 3 is the graph of a relation being dissolved in refrigerant content in oil sump and P1, P2 in the rotary compressor shown in Fig. 1;
Fig. 4 is the graph of a relation of system energy efficiency according to the embodiment of the present invention and ability and P1, P2;
Fig. 5 is the supply capability of the bent axle of the rotary compressor shown in Fig. 1 and the graph of a relation of P2;
Fig. 6 is the coefficient of performance of the rotary compressor shown in Fig. 1 and the graph of a relation of P2;
Fig. 7 is the graph of a relation being dissolved in refrigerant content, systematic energy efficiency ratio, supply capability and the coefficient of performance in oil sump and P2 in the rotary compressor according to the embodiment of the present invention.
Reference character:
100: rotary compressor;
11: main casing; 12: lower shell body; 13: oil sump; 2: motor;
31: cylinder; 311: intakeport; 32: main bearing;
33: supplementary bearing; 331: hub portion; 332: flange part; 341: center oilhole.
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.Being exemplary below by the embodiment be described with reference to the drawings, only for explaining the present invention, and can not limitation of the present invention being interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " transverse direction ", " highly ", " thickness ", " on ", D score, " left side ", " right side ", " 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 describing the invention, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or connect integratedly; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, concrete condition above-mentioned term concrete meaning in the present invention can be understood.
Below with reference to Fig. 1-Fig. 7, the rotary compressor 100 according to the embodiment of the present invention is described.
As depicted in figs. 1 and 2, according to the rotary compressor 100 of the embodiment of the present invention, comprise housing, motor 2 and compressing mechanism.
See figures.1.and.2, housing is vertically arranged, now the central axis of housing is vertical with its holding plane, motor 2 and compressing mechanism are all located in housing, motor 2 is connected with compressing mechanism, to drive compressing mechanism to compress the refrigerant entered in the compression chamber of compressing mechanism, the bottom in housing has oil sump 13, and the such as refrigerator oil of the lubricant oil in oil sump 13 can enter each moving element of compressing mechanism to lubricate each moving element.
Be appreciated that, housing can comprise upper shell (scheming not shown), main casing 11 and lower shell body assembly, main casing 11 can be formed as the cylindrical shape that top and bottom are all opened wide substantially, upper shell and lower shell body assembly are located at top and the bottom of main casing 11 respectively, and this three limits the holding space for holding above-mentioned motor 2 and compressing mechanism jointly.Certainly, the concrete structure of housing can also according to the type of different rotary compressors 100 adaptive change, the present invention does not make particular determination to this.It should be noted that the lower shell body assembly in Fig. 1 and Fig. 2 is lower shell body 12, but when lower shell body 12 being provided with other parts and this parts are positioned at housing, that is, lower shell body assembly comprises lower shell body 12 and above-mentioned parts.
Particularly, as depicted in figs. 1 and 2, compressing mechanism comprises cylinder 31, main bearing 32 and supplementary bearing assembly, the top of cylinder 31 and bottom are all unlimited, main bearing 32 and supplementary bearing assembly are located at top and the bottom of cylinder 31 respectively, and main bearing 32, supplementary bearing assembly and cylinder 31 limit compression chamber, supplementary bearing assembly comprises the hub portion 331 and flange part 332 that are upwards connected successively vertically, hub portion 331 and flange part 332 are preferably coaxial to be arranged, wherein, the transverse dimension of hub portion 331 is less than the transverse dimension of flange part 332.Here, it should be noted that, supplementary bearing assembly in Fig. 1 and Fig. 2 is supplementary bearing 33, but, when exhaust port is formed on supplementary bearing 33, can arrange baffler (scheming not shown) in the side away from cylinder of supplementary bearing 33, in other words, supplementary bearing assembly comprises supplementary bearing 33 and baffler.
The application makes with cognitive the discovery of the following fact and problem based on inventor: inventor finds, when rotary compressor 100 runs, refrigerant (for gas mixture) in compression chamber after compression is discharged from the exhaust port main bearing 32, now can by the pasta disturbance because of oil sump 13 near exhaust port, splash and the elaioleucite of generation is taken out of together, the gap of these refrigerants between the stators and rotators of motor 2 flows to the upper space in housing, in the process, the refrigerator oil that gets off is deposited by the clearance backflow between stator and the inwall of housing in the oil sump 13 of housing bottom because of other factors such as motor 2 filtrations, and the relief opening that remaining elaioleucite continues to move up through case top together with gaseous coolant is discharged outside housing, such as enter air-conditioning system, another enters in compression chamber by the intakeport 311 of housing finally to follow refrigerant, carry out next circulation.And within the compressor, under the effect of the oiling blade of refrigerator oil in the center oilhole 341 of the bent axle of compressing mechanism near bottom oil sump 13, upwards pump oil, and each moving element of compressing mechanism is lubricated, compressing mechanism is discharged finally by the helical oil groove be arranged on main bearing 32, after this most of refrigerator oil flows to oil sump 13 downwards, and small part follows the refrigerant of discharging from compression chamber, upwards flows to flowing.
In above process, heated from the refrigerator oil of motor 2 upper return by motor 2, temperature is higher, from main bearing 32 flow out for the refrigerator oil lubricated between moving element, owing to absorbing a large amount of frictional heat, temperature is also higher.The refrigerator oil that this two-part temperature is higher flows to oil sump 13 downwards jointly, and carries out heat trnasfer downwards.And the refrigerator oil of oil sump 13 bottom can by housing and outside heat exchange, thus make the temperature of self lower.
Because the density of refrigerator oil and temperature exist certain relation: temperature is higher, density is less, therefore the refrigerator oil " floating " that oil sump 13 upper temp is higher is on the refrigerator oil that temperature of lower is lower, when the refrigerator oil temperature that temperature is higher declines, this part refrigerator oil also sinks because density increases.In whole oil circuit dynamic circulation, the higher refrigerator oil of temperature all the time " floating " on oil sump 13 upper strata, cryogenic freezing machine oil all the time " deposition " in oil sump 13 bottom.Like this, the refrigerating machine oil reservoir of different temperatures gradient is just defined at oil sump 13 longitudinal direction.In oil sump 13, this temperature contrast of refrigerator oil is generally about 5 DEG C ~ 10 DEG C, even larger.
Because the refrigerator oil in compressor and refrigerant mix, and there is corresponding relation in refrigerant meltage in refrigerator oil and pressure and temp: temperature is higher, and refrigerant solubility is less, and refrigerator oil dissolves viscosity to be increased, and reliability increases.That is, temperature is lower, and the solubility of refrigerant is larger, and the dissolving viscosity of refrigerator oil just reduces, thus the reliability of rotary compressor 100 just reduces.Particularly, the refrigerator oil of oil sump 13 bottom due to temperature lower, the refrigerant of discharging from compression chamber like this can be dissolved in this part refrigerator oil largely, thus reduce the efficiency of rotary compressor 100, and reduce due to the dissolving viscosity of refrigerator oil, be unfavorable for the lubrication between each moving element of compressing mechanism, frictional loss is serious, noise is large, and reduces the working life of rotary compressor 100.
It can thus be appreciated that, reduce the refrigerator oil that in rotary compressor 100, in oil sump 13, temperature is less than normal, just can reduce in rotary compressor 100 coolant quantity be dissolved in refrigerator oil well, thus the refrigerant enclosed volume in minimizing air-conditioning system, this has the combustible refrigerant of strict demand to be very important for refrigerant enclosed volume.
Thus, bent axle oil suction place (i.e. the lower end of bent axle) is made to assemble the refrigerator oil of comparative high temperature, the dissolving viscosity of carrying out the refrigerator oil lubricated can be improved like this, improve lubricating status between moving element, thus can coolant leakage be reduced, improve efficiency, in addition, the reliability of rotary compressor 100 also can improve.This can be realized by the distance of the bottom of conservative control compressor from bent axle lower end.
Particularly, as shown in Figure 2, P1, P2 meet respectively:
0.1≤P1≤1.5，0.06≤P2≤1.1
Wherein, P1=H1/H2, P2=H3/H4, H1 be the center of hub portion 331 lower surface and lower shell body assembly diapire (such as, the diapire of lower shell body 12 in Fig. 1 and Fig. 2) between perpendicular distance (i.e. perpendicular distance between center and this center projection on the diapire of housing of hub portion 331 lower surface), H2 be supplementary bearing assembly (such as, supplementary bearing 33 in Fig. 1 and Fig. 2) height in the vertical direction, H3 be the edge of the lower surface of flange part 332 and lower shell body assembly diapire (such as, the diapire of lower shell body 12 in Fig. 1 and Fig. 2) between perpendicular distance (i.e. perpendicular distance between edge and this edge projection on the diapire of housing of flange part 332 lower surface), H4 is cylinder 31 height in the vertical direction (i.e. the thickness of cylinder 31).
With reference to Fig. 2 composition graphs 3-Fig. 7, by adjusting diapire and the supplementary bearing 33 of housing, the size of the distance relation between cylinder 31 and supplementary bearing 33 and cylinder 31 self, drawn by test, as shown in Figure 3, the refrigerant content dissolved in refrigerator oil is along with P1, the increase of P2 numerical value and increasing, in other words, work as P1, when P2 is less, the refrigerant content dissolved in refrigerator oil is less, such as when the height of supplementary bearing 33 and cylinder 31 is constant, the distance H1 between the lower surface of the hub portion 331 of supplementary bearing 33 and the diapire of housing should be reduced as far as possible, and the perpendicular distance H3 between the edge of the lower surface of the flange part 332 of supplementary bearing 33 and shell bottom wall.
Preferably, as shown in Figures 2 and 3, lower shell body 12 comprises lug boss and joint, lug boss can be protruded downwards by the center of lower shell body 12 and be formed, joint is connected on the periphery of lug boss, and the plane at joint place is higher than the bottom surface of lug boss, and lug boss is relative with hub portion about 331, now H1 is the perpendicular distance between the center of the lower surface of hub portion 331 and the diapire of lug boss, and H3 is the perpendicular distance between the edge of the lower surface of flange part 332 and the upper surface of joint.Certainly, the present invention is not limited thereto, the bottom surface of lower shell body 12 can also be formed as plane.
Further, it can also be seen that from Fig. 3, when P1, P2 are less, the amplitude that the refrigerant content dissolved in refrigerator oil increases is little, and when P1, P2 are increased to a certain numerical value, the amplitude that the refrigerant content dissolved in refrigerator oil increases is larger.
Within air-conditioning systems, the variation relation of refrigerant enclosed volume is close with above-mentioned change.When the system of guarantee refrigerant enclosed volume is constant, (EER, EnergyEfficiencyRatio, namely the coefficient of performance of refrigerating of air conditioner, also claims Energy Efficiency Ratio to system energy efficiency, represents the specific power refrigerating capacity of air-conditioning system.EER value is higher, represent that evaporation in air-conditioning system absorbs the electricity that more heat or compressor consume less) and ability with P1, P2 variation tendency as shown in Figure 4, as can be seen from the figure, when P1, P2 are larger, the refrigerant content increase that machine oil dissolves in rotary compressor 100, is frozen, reduce for the coolant quantity of refrigeration cycle in system, system capability declines to some extent, and air-conditioning system efficiency is also under some influence, Comparatively speaking, when P1, P2 are less, system energy efficiency and ability higher.
In enclosure interior, because the lower end surface (i.e. the lower end surface of hub portion 331) of the lower end surface of bent axle and supplementary bearing 33 is usually roughly concordant, distance between the lower end of bent axle and the diapire of housing is substantially equal to above-mentioned distance H1, and this distance directly can affect supply capability and the quality of bent axle.Such as, distance H1 is too little, and due to the agitation that oiling blade rotates, the refrigerator oil of the lower end of center oilhole 341 can exist foam, and the quality of fuel feeding can be affected, and fuel delivery also has larger impact.In addition, in rotary compressor 100, the constraint due to the factor such as structure, design determines the requirement to supply capability, therefore, also must consider the impact of these factors on supply capability.As shown in Figure 5, along with the increase of P2, the supply capability of bent axle improved before this, after tend towards stability, when supply capability is greater than 2 grades, effectively could ensure lubrication, ensure the reliability of rotary compressor 100, therefore consider from rotary compressor 100 reliability perspectives, the numerical value of P2 must be greater than certain certain value, and namely when the thickness of cylinder 31 remains unchanged, the perpendicular distance between the edge of the lower surface of the flange part 332 of supplementary bearing 33 and shell bottom wall can not be too near.Here, it should be noted that, " 1 grade " in Fig. 5, " 2 grades ", " 3 grades " can represent that the fuel delivery of bent axle is respectively 10ml/min, 20ml/min, 50ml/min, certainly, the present invention is not limited thereto, the fuel delivery grade of bent axle specifically can also divide according to actual requirement, and the present invention does not make particular determination to this.
Because the supply capability of P2 and rotary compressor 100 exists certain relation, when supply capability is less, refrigerator oil between moving element is not enough, lubrication, sealing are deteriorated, coolant leakage between component increases, friction factor between friction pair increases, resistance increases, thus causes the COP (CoefficientofPerformance, the coefficient of performance) of whole rotary compressor 100 to decline.Relation between COP and the P2 of rotary compressor 100 as shown in Figure 6, as can be seen from the figure, relation between the supply capability of the relation between COP and P2 of rotary compressor 100 and bent axle and P2 is roughly the same, namely improve before this, after tend towards stability.
In conjunction with above-mentioned each influence factor, the numerical value of above-mentioned P1, P2 and the refrigerant content, the supply capability of rotary compressor 100, the COP of rotary compressor 100 that are dissolved in refrigerator oil can be known, system refrigerant enclosed volume, system energy efficiency etc. have close relationship, (in figure, illustrate only trend relation) as shown in Figure 7, the relation of comprehensive each influence factor, draw best P1, P2 number range, i.e. 0.1≤P1≤1.5,0.06≤P2≤1.1.
Thus, by the bottom such as lower shell body 12 of appropriate design housing, change the refrigerator oil content of refrigerator oil different temperatures in oil sump 13 in rotary compressor 100, thus reduce the refrigerant content be dissolved in refrigerator oil, and then reduce system refrigerant enclosed volume.Separately by appropriate design lower shell body 12, better can improve the quality of fuel feeding and refrigerator oil, reach and improve lubrication, improve rotary compressor 100 efficiency and reliability.
In addition, when at least one in the bottom of housing and the bottom of lower shell body 12 or supplementary bearing 33 being installed miscellaneous part, such as when exhaust port is located on supplementary bearing 33, can arrange baffler in the side away from cylinder 31 of supplementary bearing 33, now H3 is the perpendicular distance between baffler and the bottom of housing.Be appreciated that the concrete setting position of the parts be arranged on lower shell body 12 and supplementary bearing 33 can according to actual requirement specific design, correspondingly, the concrete size of H1 to H4 specifically can be determined according to above-mentioned definition, does not repeat them here.
According to the rotary compressor 100 of the embodiment of the present invention, temperature in oil sump 13 is improved, thus the refrigerant content be dissolved in the refrigerator oil of oil sump reduces, in air-conditioning system, refrigerant enclosed volume reduces (namely under identical refrigerant enclosed volume, system energy efficiency is improved), improve the dissolving viscosity of refrigerator oil simultaneously, add the reliability of rotary compressor 100.
Further, when the discharge volume of compression chamber is less than or equal to 25cm
3(namely the piston of compressing mechanism often rotates a circle to/rev, and the refrigerant volume of discharge is less than or equal to 25cm
3) time, P1, P2 meet further:
0.1≤P1≤1.0，0.08≤P2≤0.8；
When the discharge volume of compression chamber is greater than 25cm
3(namely the piston of compressing mechanism often rotates a circle to/rev, and the refrigerant volume of discharge is greater than 25cm
3) time, P1, P2 meet further:
0.1≤P1≤1.0，0.06≤P2≤0.4。
Here, it should be noted that, " the discharge volume of compression chamber " piston referred in the inner of the slide plate of compressing mechanism and compression chamber only supports and slide plate is accommodated in the vane slot of cylinder 31 completely time, the volume in the space limited between the inner circle wall of compression chamber inside cylinder 31 and the periphery wall of piston.Be appreciated that direction " interior " refers to towards the direction at cylinder 31 center.Wherein, because slide plate, vane slot etc. are known by those skilled in the art, be not described in detail here.
Thus, when the discharge volume of compression chamber (is namely greater than 25cm comparatively greatly
3/ rev) time, by by P2 design in a less scope, such as when the height of cylinder 31 remain unchanged, make the diapire of lower shell body 12 distance flange part 332 nearer time, refrigerator oil temperature in oil sump is higher, the coolant quantity be dissolved in refrigerator oil can be reduced in rotary compressor 100 so further, reduce air-conditioning system refrigerant enclosed volume, also rotary compressor 100 fuel delivery and oil supplying quality can be ensured, thus rotary compressor 100 performance can be improved further, improve rotary compressor 100 reliability.
Alternatively, the refrigerant for refrigeration cycle in rotary compressor 100 is flammable, such as, can be HC class combustible refrigerant, but be not limited thereto.Here, it should be noted that, HC class combustible refrigerant, known by those skilled in the art, is not described in detail here.
According to the rotary compressor 100 of the embodiment of the present invention, by housing bottom reasonable in design and each size of rotary compressor 100, can well achieve the above object.By relevant design and verification experimental verification, obtain rational H1, H2, H3, H4 number range, make the refrigerant that is dissolved in housing in refrigerator oil few, the supply capability of rotary compressor 100 is guaranteed, reliability is improved, and air-conditioning system refrigerant enclosed volume is few, efficiency is improved.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " 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, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
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 (5)
1. a rotary compressor, comprise housing, motor and compressing mechanism, in described housing, there is oil sump, described housing comprises lower shell body assembly, described motor is located in described housing, described compressing mechanism is connected with described motor, described compressing mechanism comprises cylinder, main bearing and supplementary bearing assembly, described main bearing and supplementary bearing assembly are located at the top of described cylinder and bottom respectively and make compression chamber with described limiting cylinder, described supplementary bearing assembly comprises the hub portion and flange part that are upwards connected successively vertically, the transverse dimension of described hub portion is less than the transverse dimension of described flange part, it is characterized in that, wherein P1, P2 meets respectively:
0.1≤P1≤1.5，0.06≤P2≤1.1
Wherein, P1=H1/H2, P2=H3/H4, described H1 is the perpendicular distance between the center of described hub portion lower surface and described lower shell body assembly diapire, described H2 is described supplementary bearing assembly height in the vertical direction, described H3 is the perpendicular distance between the edge of the lower surface of described flange part and described lower shell body assembly diapire, and described H4 is described cylinder height in the vertical direction.
2. rotary compressor according to claim 1, is characterized in that, described lower shell body assembly has the lug boss protruded downwards, and described lug boss is relative up and down with described hub portion.
3. rotary compressor according to claim 1, is characterized in that, the bottom surface of described lower shell body assembly is formed as plane.
4. the rotary compressor according to any one of claim 1-3, is characterized in that, when the discharge volume of described compression chamber is less than or equal to 25cm
3during/rev, P1, P2 meet further:
0.1≤P1≤1.0，0.08≤P2≤0.8；
When the discharge volume of described compression chamber is greater than 25cm
3during/rev, P1, P2 meet further:
0.1≤P1≤1.0，0.06≤P2≤0.4。
5. rotary compressor according to claim 1, is characterized in that, the refrigerant for refrigeration cycle in described rotary compressor is HC class combustible refrigerant.
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| CN201410418248.XA CN104196728B (en) | 2014-08-22 | 2014-08-22 | Rotary compressor |
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| CN201410418248.XA CN104196728B (en) | 2014-08-22 | 2014-08-22 | Rotary compressor |
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| CN104196728B true CN104196728B (en) | 2016-04-20 |
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| CN104632633B (en) * | 2015-01-06 | 2017-05-31 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN107313938A (en) * | 2017-08-22 | 2017-11-03 | 广东美的制冷设备有限公司 | Compressor assembly and the refrigeration system with it |
| CN107355381A (en) * | 2017-08-22 | 2017-11-17 | 广东美的制冷设备有限公司 | Compressor assembly and there is its refrigeration system |
| CN109356827A (en) * | 2018-12-11 | 2019-02-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor housing structure and compressor with it |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678566A (en) * | 2011-03-18 | 2012-09-19 | 乐金电子(天津)电器有限公司 | Rotary compressor |
| CN103912501A (en) * | 2014-04-22 | 2014-07-09 | 广东美芝制冷设备有限公司 | Single-cylinder rotary compressor and double-cylinder rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP3649796B2 (en) * | 1995-03-31 | 2005-05-18 | 三洋電機株式会社 | Rotary compressor |
| JP4288741B2 (en) * | 1999-03-12 | 2009-07-01 | 三菱電機株式会社 | Rotary compressor |
| JP2001355586A (en) * | 2000-06-14 | 2001-12-26 | Matsushita Electric Ind Co Ltd | Rotary compressor |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678566A (en) * | 2011-03-18 | 2012-09-19 | 乐金电子(天津)电器有限公司 | Rotary compressor |
| CN103912501A (en) * | 2014-04-22 | 2014-07-09 | 广东美芝制冷设备有限公司 | Single-cylinder rotary compressor and double-cylinder rotary compressor |
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