CN103982433B - Rotary compressor - Google Patents
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- CN103982433B CN103982433B CN201410188783.0A CN201410188783A CN103982433B CN 103982433 B CN103982433 B CN 103982433B CN 201410188783 A CN201410188783 A CN 201410188783A CN 103982433 B CN103982433 B CN 103982433B
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- rotary compressor
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Abstract
The invention discloses a kind of rotary compressor, comprising: housing, compressing mechanism and motor.Compressing mechanism comprises main bearing and bent axle, and bent axle runs through main bearing.Motor is configured to generation electromagnetic unbalance power, and electromagnetic unbalance masterpiece is used on bent axle, the direction of electromagnetic unbalance power and the contrary with the deformation direction of the part of rotor contact of bent axle.According to rotary compressor of the present invention, decrease the amount of deformation of bent axle, reduce the contact even avoiding the upper end of bent axle and main bearing, decrease the strength of the upper end of main bearing, slow down the bending deflection degree of the component such as bent axle, main bearing, improve the reliability of compressor, the decentraction situation between running rotor and stator can be improved, lifting motor efficiency, improve noise, reduce the fluctuation of load of compressing mechanism and motor, reduce the vibrations in rotary compressor running, ensure that rotary compressor can run by high frequency.
Description
Technical field
The present invention relates to refrigerating field, especially relate to a kind of rotary compressor.
Background technique
Current rotary compressor has obtained common application in enormous quantities, but the load cycling that rotary compressor produces because of periodic compression brings problems to the design of compressor, application.
Periodic gas load is carry during rotary compressor running, this gas load makes bent axle occur bending and deformation, deflection of crankshaft distortion causes being fixed on the rotor on bent axle and stator decentraction when operating, produce electromagnetic unbalance power, electromagnetic unbalance power further increases crankshaft deformation, iterates thus to gas load power, electromagnetic unbalance power, crankshaft deformation stress and reaches state of equilibrium.Due to above-mentioned crankshaft deformation cause compressor to run well in there is the deficiencies such as, vibration large, noise high, electric efficiency low, inordinate wear high into power.Along with the expansion of compressor purposes, under the service conditions such as High Pressure Difference, heavy load, high rotating speed, the performance of this adverse effect is more obvious.
Summary of the invention
The present invention is intended to solve one of technical problem in correlation technique at least to a certain extent.For this reason, one object of the present invention is to propose a kind of rotary compressor, and reduce crankshaft deformation amount, lifting motor efficiency, decreases the strength of the upper end of main bearing.
According to the rotary compressor of the embodiment of the present invention, comprising: housing, compressing mechanism, described compressing mechanism comprises main bearing and bent axle, and described bent axle runs through described main bearing, motor, described motor is located in described housing, described motor comprises stator and is located at the rotor in described stator, be enclosed within outside described rotor on described bent axle, on the inwall that described stator is located at described housing and the periphery wall of described stator is provided with the trimming extended on the axial direction of described stator, circulation passage is limited between the inwall of described trimming and described housing, described stator comprises stator iron core and is wrapped in the winding on described stator iron core, described stator iron core is provided with multiple stator slot spaced apart in the circumferential direction of described stator iron core, wherein said motor is configured to generation electromagnetic unbalance power, described electromagnetic unbalance masterpiece is used on described bent axle, and the direction of described electromagnetic unbalance power and the contrary with the deformation direction of the part of described rotor contact of described bent axle.
According to the rotary compressor of the embodiment of the present invention, by an electromagnetic unbalance power pre-buried in motor, electromagnetic unbalance masterpiece is used in bent axle, and the direction of electromagnetic unbalance power and bent axle is contrary with the deformation direction of the part of rotor contact, decrease the amount of deformation of bent axle, reduce the contact even avoiding the upper end of bent axle and main bearing, thus the frictional force that can reduce between bent axle and main bearing, reduce the abrasion of bent axle, decrease the strength of the upper end of main bearing, slow down the bending deflection degree of the component such as bent axle, main bearing, improve the reliability of compressor.Simultaneously because the amount of deformation of bent axle reduces, thus the decentraction situation can improved between running rotor and stator, lifting motor efficiency, improve noise, reduce the fluctuation of load of compressing mechanism and motor simultaneously, reduce the vibrations in rotary compressor running, ensure that rotary compressor can run by high frequency.
In addition, rotary compressor according to the above embodiment of the present invention can also have following additional technical characteristics:
Preferably, the size of described electromagnetic unbalance power is the 1%-80% of the gas load power of bearing of described bent axle.
In some embodiments of the invention, the central axis of described stator and the central axis of described rotor spaced apart.
In other embodiments of the present invention, on described stator iron core, through the both sides of the first plane of the center line of the slide plate of the center of described stator and described compressing mechanism, the winding on described stator iron core is different.
Particularly, the both sides of described first plane on described stator iron core, at least one in the number of turns of the winding of described stator iron core, wire diameter, material, major-minor phase number of turns ratio is different.
In some embodiments more of the present invention, on described stator iron core, through the both sides of the first plane of the center line of the slide plate of the center of described stator and described compressing mechanism, the shape of cross section of described stator iron core is different.
Alternatively, the both sides of described first plane on described stator iron core, the shape of described stator slot is different.
Alternatively, the both sides of described first plane on described stator iron core, the position of the described trimming of described stator and/or the shape difference of described trimming.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the rotary compressor according to the embodiment of the present invention;
Fig. 2 is according to the activity chart of piston in cylinder in the rotary compressor of the embodiment of the present invention and traditional rotary compressor;
Fig. 3 is the location diagram according to the stators and rotators in the rotary compressor of the present invention's concrete example;
Fig. 4 is the stressed schematic diagram of bent axle during rotary compressor off-duty shown in Fig. 3;
Fig. 5 is the stressed schematic diagram of the bent axle when rotary compressor shown in Fig. 3 runs;
Fig. 6 is the stressed schematic diagram of the bent axle in traditional rotary compressor;
Fig. 7 is the force-deflection schematic diagram of the bent axle in traditional rotary compressor;
Fig. 8 is the graph of relation of the thrust load that crank angle in traditional rotary compressor and bent axle are subject to;
Fig. 9 is main bearing support force, the graph of relation between supplementary bearing support force and contact force that crank angle in traditional rotary compressor and bent axle are subject to;
Figure 10 is the graph of relation between the unbalanced magnetic pull that is subject to of the rotor in traditional rotary compressor and the monolateral bias of rotor.
Reference character:
Rotary compressor 100,
Housing 1,
Compressing mechanism 2, main bearing 20, bent axle 21, cylinder 22, piston 23, slide plate 24, air aspiration cavity 25, exhaust cavity 26, supplementary bearing 27
Motor 3, stator 30, rotor 31
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.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", " counterclockwise ", " 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 mechanical connection, also can be electrical connection; 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.
First the stressing conditions of the bent axle 21 ' of traditional rotary compressor is described with reference to figure 2, Fig. 6-Figure 10 below.
Traditional rotary compressor comprises: housing, compressing mechanism and motor, wherein, compressing mechanism and motor are located in housing respectively, compressing mechanism comprises cylinder 22 ', piston 23 ', bent axle 21 ', main bearing 20 ', supplementary bearing 27 ', bent axle 21 ', through main bearing 20 ', cylinder 22 ' and supplementary bearing 27 ', is enclosed within bent axle 21 ' and goes up and the compression chamber being positioned at cylinder 22 ' outside piston 23 '.The rotor 31 ' that motor comprises stator 30 ' and is located in stator 30 '.
Piston 23 ' is driven to rotate by bent axle 21 ' in compressor operation, in piston 23 ' rotation process, air aspiration cavity 25 ' volume expands gradually, exhaust cavity 26 ' volume reduces gradually, exhaust cavity 25 ' pressure raises gradually simultaneously, gas load masterpiece is used for bent axle 21 ', and as shown in Figure 8, wherein piston 23 ' rotates 360 degree is single press cycles to the gas load power (i.e. thrust load) that bent axle 21 ' is subject in single press cycles.
As shown in Figure 6, bent axle 21 ' is in the effect of load gas, bent axle 21 ' is subject to gas load power F, main bearing support force SB2 and supplementary bearing support force SB1, bent axle 21 ' produces bending deflection (as shown in Figure 7) under gas load power F, main bearing support force SB2 and supplementary bearing support force SB1 effect, bent axle 21 ' after distortion contacts with main bearing 20 ' in main bearing 20 ' upper end, produce the direction of contact force SB3, contact force SB3 as shown in figures 6 and 7.Therefore, in the process of compressor operating, bent axle 21 ' weares and teares at active force SB1, SB2 and SB3 place usually.
Fig. 9 is that the active force (i.e. main bearing support force SB2, supplementary bearing support force SB1 and contact force SB3) that is subject to of the bent axle 21 ' in traditional rotary compressor is in one cycle with the variation relation figure of bent axle 21 ' corner.As can be seen from Figure 9, main bearing support force SB2 and supplementary bearing support force SB1 is the main body of bearings power, and the size of contact force SB3 is more stable, is about 25% of main bearing support force SB2.
Bent axle 21 ' can cause rotor 31 ' the structure run-off the straight be connected on bent axle 21 ' after being out of shape, thus makes to occur monolateral eccentric d1 between the stator 30 ' of motor and rotor 31 ', as shown in Figure 7.
What those skilled in the art understood is, when motor stator 30 ' and rotor 31 ' decentraction, there will be air gap flux density inequality, rotor 31 ' can be subject to the unbalanced magnetic pull shown in left side in Fig. 7 freely, as shown in Figure 10, the scope of the monolateral eccentric d1 usually caused by unbalanced magnetic pull is between 0.05mm-0.5mm for the relation of unbalanced magnetic pull and monolateral eccentric d1.Unbalanced magnetic pull can be coupled with main bearing support force SB2, supplementary bearing support force SB1 and contact force SB3, increases contact force SB3 and supplementary bearing support force SB1, increases bent axle 21 ' bending deflection simultaneously.
From upper analysis, gas load power F can make bent axle 21 ' occur bending and deformation, cause motor stator 30 ' and rotor 31 ' disalignment to produce unbalanced magnetic pull, unbalanced magnetic pull turn increases bent axle 21 ' and is out of shape, this phenomenon can produce vibration, noise, electric efficiency are low, the adverse effects such as bent axle 21 ' wearing and tearing.
Therefore, in order to solve the problems referred to above existed in traditional rotary compressor, present applicant proposes by an electromagnetic unbalance power TF pre-buried in motor, carrying out the unbalanced force of partial equilibrium compressing mechanism with this electromagnetic unbalance power TF.
Below with reference to Fig. 1-Fig. 5, the rotary compressor 100 according to the embodiment of the present invention is described, wherein rotary compressor 100 can also can be duplex cylinder compressor for single cylinder compressor, all be described for single cylinder compressor in describing the invention, but what be worth understanding is, when rotary compressor 100 is duplex cylinder compressor, the stressing conditions of bent axle 21 is identical with the stressing conditions of single cylinder compressor, is just not described in detail here.
As depicted in figs. 1 and 2, the rotary compressor 100 according to the embodiment of the present invention comprises: housing 1, compressing mechanism 2 and motor 3, and wherein, compressing mechanism 2 comprises main bearing 20 and bent axle 21, and bent axle 21 runs through main bearing 20.What be certainly worth understanding is, compressing mechanism 2 also comprises the elements such as supplementary bearing 27, cylinder 22, piston 23, slide plate 24, main bearing 20 and supplementary bearing 27 are located at upper surface and the lower surface of cylinder 22 respectively, being enclosed within outside piston 23 on bent axle 21 and being positioned at the compression chamber of cylinder 22, slide plate 24 is located in the vane slot on cylinder 22 and one end of slide plate 24 movably and contacts all the time with the periphery wall of piston 23.
Drive piston 23 to rotate by bent axle 21 in compressor operation, in piston 23 rotation process, air aspiration cavity 25 volume expands gradually, and exhaust cavity 26 volume reduces gradually, and exhaust cavity 25 pressure raises gradually simultaneously, and gas load power F acts on bent axle 21.
Motor 3 is located in housing 1, the rotor 31 that motor 3 comprises stator 30 and is located in stator 30, be enclosed within bent axle 21 outside rotor 31, on the inwall that stator 30 is located at housing 1 and the periphery wall of stator 30 is provided with the trimming (scheming not shown) extended on the axial direction of stator 30, circulation passage is limited between the inwall of trimming and housing 1, stator 30 comprises stator iron core (scheming not shown) and is wrapped in the winding (scheming not shown) on stator iron core, stator iron core is provided with multiple stator slots spaced apart in the circumferential direction of stator iron core, wherein motor 3 is configured to generation electromagnetic unbalance power TF, electromagnetic unbalance power TF acts on bent axle 21, and the direction of electromagnetic unbalance power TF is contrary with the deformation direction of the part contacted with rotor 31 of bent axle 21, that is, a pre-buried electromagnetic unbalance power TF in motor 3, now under the effect of electromagnetic unbalance power TF, the part contacted with rotor 31 of bent axle 21 is subject to one and deformation direction opposite effect power, thus the amount of deformation of bent axle 21 can be reduced.
Specifically, because the direction of electromagnetic unbalance power TF is contrary with the deformation direction of the part contacted with rotor 31 of bent axle 21, thus the amount of deformation of bent axle 21 can be reduced, reduce the contact of the upper end even avoiding bent axle 21 and main bearing 20, thus the contact force SB3 between the upper end can reducing bent axle 21 and main bearing 20, particularly, the direction of electromagnetic unbalance power TF is identical with the direction of contact force SB3.In other words, the part or all of equilibrium contact power SB3 of electromagnetic unbalance power TF, namely contact force SB3 is partly or entirely transferred on pre-buried electromagnetic unbalance power TF.
Wherein, what needs were described is, any means can be adopted to improve motor 3, as long as ensure motor 3 after mounting (when namely rotor 31 does not rotate) self can produce an electromagnetic unbalance power TF, and the deformation direction of the direction of electromagnetic unbalance power TF and the part contacted with rotor 31 of bent axle 21 is on the contrary.
According to the rotary compressor 100 of the embodiment of the present invention, by an electromagnetic unbalance power TF pre-buried in motor 3, electromagnetic unbalance power TF acts on bent axle 21, and the direction of electromagnetic unbalance power TF is contrary with the deformation direction of the part contacted with rotor 31 of bent axle 21, decrease the amount of deformation of bent axle 21, reduce the contact of the upper end even avoiding bent axle 21 and main bearing 20, thus the frictional force that can reduce between bent axle 21 and main bearing 20, reduce the abrasion of bent axle 21, decrease the strength of the upper end of main bearing 20, slow down bent axle 21, the bending deflection degree of component such as main bearing 20 grade, improve the reliability of compressor 100.Simultaneously because the amount of deformation of bent axle 21 reduces, thus the decentraction situation can improved between running rotor 31 and stator 30, lifting motor efficiency, improve noise, reduce the fluctuation of load of compressing mechanism 2 and motor 3 simultaneously, reduce the vibrations in rotary compressor 100 running, ensure that rotary compressor 100 can run by high frequency.
The gas load power F wherein born due to bent axle 21 detects by adopting existing detection means, and in some embodiments of the invention, the size of electromagnetic unbalance power TF is defined as the 1%-80% of the gas load power F born of bent axle 21.Now can ensure under the effect of electromagnetic unbalance power TF, bent axle 21 hardly with the upper-end contact of main bearing 20, namely now contact force SB3 close to 0.
In specific embodiments more of the present invention, can adopt following three kinds of technological means pre-buried electromagnetic unbalance power TF in motor 3 according to the rotary compressor 100 of the embodiment of the present invention, the first wherein following plane is the plane of the center line of slide plate 24 through the center of stator 30 and compressing mechanism 2.Simultaneously following angular range is 0 degree of reference with the center line of slide plate 24, in compressor operation with motor 3 sense of rotation and gas compression direction for postive direction.
First kind of way: the central axis of stator 30 and the central axis of rotor 31 spaced apart.Specifically, making the gap of motor 3 under reset condition between stator 30 and rotor 31 uneven when designing motor 3, namely making stator 30 and rotor 31 decentraction.Such as shown in Figure 3 and Figure 4, gap, left side is greater than gap, right side, produces eccentricity values m.In other words, stator 30 and rotor 31 are reserved when designing is out of shape reciprocal decentraction with bent axle 21, and such as, when bent axle 21 is out of shape left, now the central axis of rotor 31 is positioned at the right side of the central axis of stator 30.In the example of fig. 3, motor 3 is greater than 0 degree of gap to 180 degree of sides in angle range 180 degree of gaps to 360 degree of sides.
Now due to the central axis of stator 30 and the central axis of rotor 31 spaced apart, thus stator 30 and rotor 31 limit spatially, the gap of the both sides that are positioned at the first plane is different, cause both sides air gap flux density different, stator 30 pairs of rotors 31 produce the electromagnetic unbalance power TF of direction in 0 degree to 180 degree interval, and electromagnetic unbalance power TF is identical with contact force SB3 direction.
Thus electromagnetic unbalance power TF makes motor 3 in operation process, eccentric slot m superposes with bent axle 21 amount of deformation, can ensure stator 30 and rotor 31 concentricity, effectively reduces contact force SB3 and bent axle 21 amount of deformation.
As shown in Figure 5, in motor 3 operation process, compared with traditional rotary compressor 100, the decentraction amount d2 of motor 3 is reduced, and contact force SB3 is balanced.
The second way: on stator iron core, through the both sides of the first plane of the center line of the slide plate 24 of the center of stator 30 and compressing mechanism 2, the winding on stator iron core is different.Particularly, the both sides of the first plane on stator iron core, at least one in the number of turns of the winding of stator iron core, wire diameter, material, major-minor phase number of turns ratio is different.That is, now in 180 degree to 360 degree sides of stator 30, place the winding unequal with offside, because both sides winding difference causes both sides air gap flux density difference, produce electromagnetic unbalance power TF.
The third mode: on stator iron core, through the both sides of the first plane of the center line of the slide plate 24 of the center of stator 30 and compressing mechanism 2, the shape of cross section of stator iron core is different.Particularly, the both sides of the first plane on stator iron core, the shape difference of stator slot, the position of the trimming of stator 30 and/or the shape difference of section.That is, in 180 degree to 360 degree sides of stator 30, the sectional shape of stator iron core is different from offside, and the sectional shape difference due to both sides stator iron core causes both sides air gap flux density difference, produces electromagnetic unbalance power TF.
Wherein, it will be appreciated that, stator iron core is made up of multiple stator punching (scheming not shown) superposed successively on the axial direction of stator 30, because multiple stator punching shape is identical, now the shape of cross section difference of stator iron core can be understood as the sectional shape difference of stator punching.
Owing to adopting multiple button point to fasten between upper and lower two stator punchings, the groove that each button point comprises salient point and coordinates with salient point, its bumps is located in one of them in two stator punchings, and groove is located on another in two stator punchings.
Therefore, in examples more of the present invention, the cross section difference of stator punching can comprise the button point difference of stator punching.
Certainly be worth understanding, above-mentioned three kinds of modes can be used alone or combinationally use.
According to the rotary compressor 100 of the embodiment of the present invention, because motor 3 is configured to generation electromagnetic unbalance power TF, the direction of electromagnetic unbalance power TF is contrary with the deformation direction of the part contacted with rotor 31 of bent axle 21, and therefore tool has the following advantages:
1, the stressed reduction of the axle of bent axle 21, can reduce friction, improving energy efficiency, reduction abrasion, life-saving.
2, the major axis amount of deformation of bent axle 21 is reduced, and can improve vibration, realizes the running of compressor high frequency.
3, the decentraction situation between rotor 31 and stator 30 that operates is improved, and electric efficiency can promote to some extent, and compressor electromagnetism sound proportion can reduce.
In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary mediate contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.
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 above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.
Claims (8)
1. a rotary compressor, is characterized in that, comprising:
Housing;
Compressing mechanism, described compressing mechanism comprises main bearing and bent axle, and described bent axle runs through described main bearing;
Motor, described motor is located in described housing, described motor comprises stator and is located at the rotor in described stator, be enclosed within outside described rotor on described bent axle, on the inwall that described stator is located at described housing and the periphery wall of described stator is provided with the trimming extended on the axial direction of described stator, circulation passage is limited between the inwall of described trimming and described housing, described stator comprises stator iron core and is wrapped in the winding on described stator iron core, described stator iron core is provided with multiple stator slot spaced apart in the circumferential direction of described stator iron core, wherein said motor is configured to generation electromagnetic unbalance power, described electromagnetic unbalance masterpiece is used on described bent axle, and the direction of described electromagnetic unbalance power and the contrary with the deformation direction of the part of described rotor contact of described bent axle.
2. rotary compressor according to claim 1, is characterized in that, the size of described electromagnetic unbalance power is the 1%-80% of the gas load power of bearing of described bent axle.
3. rotary compressor according to claim 1, is characterized in that, the central axis of described stator and the central axis of described rotor spaced apart.
4. rotary compressor according to claim 1, is characterized in that, on described stator iron core, through the both sides of the first plane of the center line of the slide plate of the center of described stator and described compressing mechanism, the winding on described stator iron core is different.
5. rotary compressor according to claim 4, is characterized in that, the both sides of described first plane on described stator iron core, and at least one in the number of turns of the winding of described stator iron core, wire diameter, material, major-minor phase number of turns ratio is different.
6. rotary compressor according to claim 1, is characterized in that, on described stator iron core, through the both sides of the first plane of the center line of the slide plate of the center of described stator and described compressing mechanism, the shape of cross section of described stator iron core is different.
7. rotary compressor according to claim 6, is characterized in that, the both sides of described first plane on described stator iron core, and the shape of described stator slot is different.
8. rotary compressor according to claim 6, is characterized in that, the both sides of described first plane on described stator iron core, the position of the described trimming of described stator and/or the shape difference of described trimming.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410188783.0A CN103982433B (en) | 2014-05-06 | 2014-05-06 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410188783.0A CN103982433B (en) | 2014-05-06 | 2014-05-06 | Rotary compressor |
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| CN103982433A CN103982433A (en) | 2014-08-13 |
| CN103982433B true CN103982433B (en) | 2016-03-16 |
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| CN201410188783.0A Expired - Fee Related CN103982433B (en) | 2014-05-06 | 2014-05-06 | Rotary compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2738260B2 (en) * | 1993-05-07 | 1998-04-08 | 三菱電機株式会社 | Scroll compressor |
| JPH0842472A (en) * | 1994-07-28 | 1996-02-13 | Mitsubishi Heavy Ind Ltd | Rolling piston type compressor |
| WO2009145232A1 (en) * | 2008-05-28 | 2009-12-03 | 東芝キヤリア株式会社 | Enclosed compressor and refrigeration cycle device |
| JP2011144758A (en) * | 2010-01-15 | 2011-07-28 | Panasonic Corp | Sealed type motor-driven compressor |
| CN202612115U (en) * | 2012-05-09 | 2012-12-19 | 广东美的电器股份有限公司 | Control device for improving sound quality of single-rotor compressor of variable frequency air conditioner |
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