CN102237746A - Balance structure of rotary compressor and rotary compressor comprising same - Google Patents
Balance structure of rotary compressor and rotary compressor comprising same Download PDFInfo
- Publication number
- CN102237746A CN102237746A CN2010101735793A CN201010173579A CN102237746A CN 102237746 A CN102237746 A CN 102237746A CN 2010101735793 A CN2010101735793 A CN 2010101735793A CN 201010173579 A CN201010173579 A CN 201010173579A CN 102237746 A CN102237746 A CN 102237746A
- Authority
- CN
- China
- Prior art keywords
- balance weight
- barycenter
- offset
- rotor
- balanced structure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000009434 installation Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 8
- 238000000034 method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000005457 optimization Methods 0.000 description 3
- 230000000295 complement effect Effects 0.000 description 1
- 239000013604 expression vector Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a balance structure of a rotary compressor and the rotary compressor comprising the same. The balance structure of the rotary compressor comprises: an eccentric motor rotor installed on one end of a crankshaft of the compressor rotor part; a crankshaft eccentric portion provided near the other end of the crankshaft; and the first balance weight and the second balance weight are respectively arranged at two ends of the eccentric motor rotor. The balance structure of the rotary compressor adopts the eccentric motor rotor, and the corresponding balance blocks are arranged at the two ends of the eccentric motor rotor according to the eccentric motor rotor and the eccentric part of the crankshaft, thereby realizing ideal dynamic balance effect in the variable frequency compressor and reducing vibration and noise of the compressor.
Description
Technical field
The present invention relates to compressor field, be specifically related to the balanced structure and the rotary compressor of rotary compressor.
Background technology
Usually, rotary compressor (for example, the DC frequency-changing rotary compressor for refrigerant) comprise the rotor-support-foundation system that is made of bent axle, roller and rotor in, there is unbalance response in working order down in rotor-support-foundation system, therefore need carry out the dynamic balancing design to rotor-support-foundation system.Usually the mode that adopts in the dynamic balancing design is that balance weight is installed on rotor, constitutes the balanced structure of compressor drum system thus.Existing compressor dynamic balancing theory is regarded bent axle as rigidity, and designs corresponding balance weight, with the unbalance response that reduces to be caused by crankshaft eccentric portion rotating inertia force.Yet the mode of this dynamic balancing design is difficult to the dynamic balancing effect of realizing ideal in frequency-changeable compressor, and the vibration and the noise of compressor are bigger.
Summary of the invention
The balanced structure that the purpose of this invention is to provide a kind of rotary compressor, it can be applied to frequency-changeable compressor, and the dynamic balancing effect of realizing ideal.
At above-mentioned purpose, a kind of balanced structure of rotary compressor is provided according to an aspect of the present invention, comprising: the eccentric motor rotor is installed on the end of bent axle of compressor drum parts; Crankshaft eccentric portion is arranged near the other end of bent axle; First balance weight and second balance weight are separately positioned on the two ends of eccentric motor rotor.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the barycenter of first balance weight and second balance weight all is positioned at the same side of longitudinal center's face of bent axle, and the barycenter of rotor is positioned at the opposite side of longitudinal center's face of bent axle.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the barycenter of first balance weight or second balance weight and the barycenter of rotor lay respectively at the both sides of longitudinal center's face of bent axle.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the barycenter of the barycenter of rotor and crankshaft eccentric portion is positioned at the same side of bent axle longitudinal center face.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the barycenter of the barycenter of rotor and crankshaft eccentric portion lays respectively at the both sides of bent axle longitudinal center face.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the layout of balanced structure designs in the following way:
A) vibration shape model of equilibrium establishment structure;
B) vibration shape model to balanced structure carries out model analysis, determines the crooked vibration shape parameter in bent axle first rank of rotor barycenter correspondence
The crooked vibration shape parameter in bent axle first rank of the first balance weight barycenter correspondence
With the crooked vibration shape parameter in bent axle first rank of the second balance weight barycenter correspondence
With the corresponding crooked vibration shape parameter in bent axle first rank of crankshaft eccentric portion barycenter
C) the offset m of definition rotor
me
m, first balance weight offset m
pe
p, second balance weight offset m
ae
aWith the offset m of crankshaft eccentric portion
ee
e, and set the initial value of these offsets;
D) utilize the above-mentioned parameter of determining, determine the offset m of rotor based on optimized Algorithm
me
m, first balance weight offset m
pe
p, second balance weight offset m
ae
aOffset m with crankshaft eccentric portion
ee
eBetween relation;
Wherein, m
pBe first mass of balance block, m
aBe the second secondary mass of balance block, m
mBe the quality of rotor, m
eBe the quality of crankshaft eccentric portion, e
pBe eccentric throw, the e of first balance weight
aBe eccentric throw, the e of second balance weight
mBe the eccentric throw of rotor, e
eEccentric throw for crankshaft eccentric portion.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, in step c), set the initial value of offset as follows: the initial value of the offset of first balance weight is set to m
pe
p=m
ee
e, the initial value of the offset of second balance weight is set to m
ae
a=m
ee
e, the initial value of the offset of rotor is set to m
me
m=m
ee
e
Further, according to the balanced structure of rotary compressor of the present invention, wherein, and in the step d), the offset m of rotor
me
m, first balance weight offset m
pe
p, second balance weight offset m
ae
aOffset m with crankshaft eccentric portion
ee
eBetween relation limit by following relational expression:
Qualitative restrain: Min (m
p+ m
a)
The constraint equation group:
Boundary constraint:
Wherein, L
pBe the distance of the barycenter of first balance weight to the barycenter of crankshaft eccentric portion, L
aBe the distance of the barycenter of second balance weight to the barycenter of crankshaft eccentric portion, L
mBe the barycenter of eccentric motor rotor distance, L to the barycenter of crankshaft eccentric portion
p, L
a, L
mValue determine according to the installation site of described first balance weight and described second balance weight.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, the not homonymy that the eccentric throw of each parts of balanced structure is in longitudinal center's face according to corresponding component get on the occasion of or negative value.
A kind of rotary compressor is provided according to a further aspect in the invention, and it has the balanced structure according to first aspect present invention.
The present invention has following technique effect:
Balanced structure according to rotary compressor of the present invention, wherein adopted eccentric rotor, and according to used eccentric motor rotor and crankshaft eccentric portion, at the two ends of eccentric motor rotor corresponding balance weight is set, the dynamic balancing effect that can in frequency-changeable compressor, realize ideal thus, the vibration and the noise of minimizing compressor.
Should be appreciated that above generality is described and the following detailed description is all enumerated and illustrative, purpose is for to the claimed further instruction that the invention provides.
Description of drawings
Accompanying drawing constitutes the part of this specification, is used to help further understand the present invention.These accompanying drawings illustrate some embodiments of the present invention, and are used for illustrating principle of the present invention with specification.Identical in the accompanying drawings parts are represented with identical label.In the accompanying drawing:
Figure 1A to Fig. 1 C shows the schematic diagram according to three kinds of execution modes of the balanced structure of rotary compressor of the present invention respectively;
Fig. 2 shows the balance vibration shape schematic diagram of balanced structure according to an embodiment of the invention;
Fig. 3 shows the design flow diagram according to balanced structure of the present invention.
Embodiment
Describe with reference to the execution mode of accompanying drawing simultaneously below in conjunction with instantiation balanced structure of the present invention.
The dynamic balancing design of rotary compressor balanced structure of the prior art is primarily aimed at invariable frequency compressor, under the situation of invariable frequency compressor, can regard bent axle as rigid body, thinks that promptly bent axle is indeformable, carries out the dynamic balancing design on this basis.Two constraint equations of the general employing of this balanced structure, and only comprise parameter in the equation about rotor, crankshaft eccentric portion and one of them balance weight, and for frequency-changeable compressor, this design just can not be suitable for, utilize this mode that frequency-changeable compressor is carried out the dynamic balancing design and can't obtain desirable counterbalance effect, vibrations and noise are all bigger.
In order to address the above problem, the present invention transforms existing balanced structure, change the structure of rotor, the rotor of original eccentric configuration is designed to eccentric structure, eccentric rotor and crankshaft eccentric portion are installed in the opposite end of bent axle respectively, arrange major and minor balance weight at the two ends of eccentric motor rotor simultaneously.The result of practical application shows, the dynamic balancing effect of the crankshaft eccentric portion that can realize ideal by above-mentioned this balance vibration shape structure.
According to above-mentioned basic principle of the present invention, a kind of balanced structure of rotary compressor is provided, it comprises: eccentric motor rotor 10, it is installed on the end of bent axle 20 of compressor drum parts; Crankshaft eccentric portion 30 is arranged near the other end of bent axle 10; And first balance weight 40 and second balance weight 50, it is separately positioned on two end faces of eccentric motor rotor 10.
Particularly, the eccentric motor rotor can have multiple make, for example, at the position borehole at rotor (being generally rotary body) internal deviation center or directly remove the material of a part of rotor body, among three embodiment that will describe in detail below, all adopt from the mode of internal rotor borehole.Simultaneously, for first balance weight and second balance weight arrangement with respect to the eccentric motor rotor, the compressor model at different can have multiple choices, and concrete arrangement can be described in three exemplary embodiments below equally.
Three examples according to the balanced structure of rotary compressor of the present invention have been shown among Figure 1A to 1C.In the balanced structure shown in Figure 1A, the barycenter of first balance weight 40 and second balance weight 50 all is positioned at the same side of the face A of longitudinal center of bent axle 20, and the barycenter of eccentric motor rotor 10 is positioned at the opposite side of the face A of longitudinal center, and the barycenter of crankshaft eccentric portion 30 also is positioned at this opposite side of the face A of longitudinal center simultaneously.
Among the embodiment shown in Figure 1B and Fig. 1 C, the barycenter of first balance weight 40 or second balance weight 50 and the barycenter of eccentric motor rotor 10 lay respectively at the both sides of the face A of longitudinal center of bent axle 30.In Figure 1B, the barycenter of first balance weight 40 is positioned at the side of the face A of longitudinal center, and the barycenter of the barycenter of the barycenter of second balance weight 50 and eccentric motor rotor 10 and crankshaft eccentric portion 20 all is positioned at the opposite side of the face A of longitudinal center of bent axle 30.In Fig. 1 C, the barycenter of the barycenter of first balance weight 40 and eccentric motor rotor 10 is positioned at the same side of the face A of longitudinal center, and the barycenter of the barycenter of second balance weight 50 and crankshaft eccentric portion 30 is positioned at the opposite side of the face A of longitudinal center of bent axle 30.
By top description as can be known, the barycenter of the barycenter of eccentric motor rotor 10 and crankshaft eccentric portion 30 can all be positioned at the same side of the face A of longitudinal center of bent axle 10, also can lay respectively at the both sides of the face A of bent axle longitudinal center.
According to principle of the present invention, the eccentric part of first balance weight 40, second balance weight 50, eccentric motor rotor 10, the set-up mode of crankshaft eccentric portion 30 can be determined according to the concrete model of compressor.Compressor at different model, first balance weight 40, the size (corresponding mass) of second balance weight 50, position, and the eccentric position of eccentric motor rotor 10 establishes a capital respective change really, and concrete arrangement can be determined by method as described below.
In above-mentioned balanced structure according to the present invention, no longer regard crankshaft eccentric portion 30 as rigid body, but the distortion of consideration crankshaft eccentric portion 30, employing is introduced the parameter relevant with distortion in the constraint equation, simultaneously with first balance weight 40, second balance weight 50, the eccentric part of eccentric motor rotor 10, the offset of crankshaft eccentric portion 30 is all introduced constraint equation, utilize corresponding optimized Algorithm to determine rotor 10 offsets, first, second balance weight 40, the relation of 50 offset and crankshaft eccentric portion 30 offsets, determine the concrete layout of balanced structure thus, promptly eccentric motor rotor 10 and first, second balance weight 40,50 quality and set-up mode.
Below, with reference to Fig. 3 the design cycle of balanced structure of the present invention is described.The design of balanced structure is as follows:
A) vibration shape model of equilibrium establishment structure (vibration shape model as shown in Figure 2);
B) vibration shape model to balanced structure carries out model analysis, determines the crooked vibration shape parameter in first rank of eccentric motor rotor 10
The crooked vibration shape parameter in first rank of first balance weight 40
With the crooked vibration shape parameter in first rank of second balance weight 50
With the crooked vibration shape parameter in first rank of crankshaft eccentric portion 30
C) the offset m of definition eccentric motor rotor 10
me
m, first balance weight 40 offset m
pe
p, second balance weight 50 offset m
ae
aWith the offset m of crankshaft eccentric portion 30
ee
e, and set the initial value of above-mentioned these offsets;
D) carry out modal balancing and check, utilize the offset m of the above-mentioned parameter of determining (comprising first crooked vibration shape parameter and the offset) optimization eccentric motor rotor 10 specifically
me
m, first balance weight 40 offset m
pe
p, second balance weight 50 offset m
ae
aOffset m with crankshaft eccentric portion 30
ee
eBetween relation, just optimization satisfies eccentric motor rotor 10, first balance weight 40 of balance constraints, the offset of second balance weight 50.
If check result satisfies preset restriction equation and condition, then the result is optimized in output accordingly; Check once more otherwise return in the step c).
In the above-mentioned parameter, m represents the quality of each part of balanced structure, wherein, and m
pBe first mass of balance block, m
aBe the second secondary mass of balance block, m
mBe the quality of rotor, m
eQuality for crankshaft eccentric portion; E represents the eccentric throw (being the distance of barycenter to the face A of longitudinal center of bent axle 10) of each part of balanced structure, e
pBe eccentric throw, the e of first balance weight
aBe eccentric throw, the e of second balance weight
mBe the eccentric throw of rotor, e
eEccentric throw for crankshaft eccentric portion.The two product of m and e promptly is defined as the offset me of corresponding component.
Preferably, in step c), set the initial value of the offset of each part of balanced structure as follows: all be set to the initial value of the offset of the initial value of the offset of the initial value of the offset of first balance weight 40, second balance weight 50, rotor 10 identical with the offset of crankshaft eccentric portion 30, that is m,
pe
p=m
ee
e, m
ae
a=m
ee
e, m
me
m=m
ee
eAccording to present general means, the offset m of crankshaft eccentric portion 30
ee
eCan determine according to the model and the performance of compressor.
Preferably, according to design philosophy of the present invention, above-mentioned steps d) in, the offset m of eccentric motor rotor 10
me
m, first balance weight 40 offset m
pe
p, second balance weight 50 offset m
ae
aOffset m with crankshaft eccentric portion 30
ee
eBetween relation limit by following relational expression:
Qualitative restrain: Min (m
p+ m
a)
Constraint equation:
Boundary constraint:
Wherein, m
pBe the quality of first balance weight 40, m
aBe the quality of second balance weight 50, m
mBe the quality of rotor 10, m
eBe the quality of crankshaft eccentric portion 30, L
pBe the distance of the barycenter of first balance weight 40 to the barycenter of crankshaft eccentric portion 30, L
aBe the distance of the barycenter of second balance weight 50 to the barycenter of crankshaft eccentric portion 30, L
mBe the barycenter of eccentric motor rotor 10 distance, symbol to the barycenter of crankshaft eccentric portion 30
The expression vector.Particularly, the eccentric throw of each parts of the balanced structure not homonymy that is in longitudinal center's face according to corresponding component get on the occasion of or negative value.For example, in vibration shape model embodiment illustrated in fig. 2, with the eccentric throw on the longitudinal center face A right side that shows among the figure be defined as on the occasion of, and the left side is defined as negative value, then Ci Shi constraint equation just can be write as:
Above-mentioned empirical equation is to set at frequency-changeable compressor specially, wherein the qualitative restrain condition Min m of Cai Yonging
p+ m
aBe the basic purpose of vibration shape method dynamic balancing design, promptly use the balance weight of minimum mass to satisfy the requirement for dynamic balance of rotor part.Simultaneously, used boundary constraint
Be an experimental constraint formula, its purpose is to guarantee to choose suitable balance weight, suitably the eccentric position of rotor is set, and makes that simultaneously the size of these parts is not too large.
Below, adopt an instantiation to come to above-mentioned steps d) in optimization method describe.Therefore describe with embodiment shown in Fig. 2, adopt the constraint equation (2) after the above-mentioned distortion.
Model and inner concrete member according to compressor carry out model analysis, determine the crooked vibration shape parameter of phase I of each parts, and be as follows as crooked vibration shape parameter of the phase I of certain concrete compressor:
Determine the offset m of crankshaft eccentric portion 30 simultaneously
ee
e=639.8g*mm (these numerical value are measured, calculated according to the actual components of compressor).With the constraint equation group above the substitution of above-mentioned parameter value, the result is as follows:
Qualitative restrain: Min m
p+ m
a
The constraint equation group:
Boundary constraint:
To above-mentioned equation solution, determine rotor offset m
me
m, the first balance weight offset m
pe
p, the offset m of second balance weight
ae
aWith crankshaft eccentric amount m
ee
eFollowing relation is arranged:
m
me
m＝1.5～3m
ee
e；
m
pe
p＝1.5～3m
ee
e；
m
ae
a＝0.6～1.2m
ee
e
Thus just can be according to actual needs, choose balance weight and rotor that quality, position relation are complementary, as long as their offset satisfies the above-mentioned relation formula, then just can obtain comparatively ideal dynamic balancing effect.
In addition, according to principle of the present invention, also provide a kind of rotary compressor, it comprises aforesaid balanced structure of the present invention.
Be the preferred embodiments of the present invention only below, be not limited to the present invention, for a person skilled in the art, the present invention can have various changes and variation.All any modifications of being done within the spirit and principles in the present invention, be equal to replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. the balanced structure of rotary compressor is characterized in that, comprising:
Eccentric motor rotor (10) is installed on the end of bent axle (20) of compressor drum parts;
Crankshaft eccentric portion (30) is arranged near the other end of described bent axle;
First balance weight (40) and second balance weight (50) are separately positioned on the two ends of described eccentric motor rotor.
2. the balanced structure of rotary compressor according to claim 1, it is characterized in that, the barycenter of described first balance weight and second balance weight all is positioned at the same side of longitudinal center's face (A) of described bent axle, and the barycenter of described rotor is positioned at the opposite side of longitudinal center's face of described bent axle.
3. the balanced structure of rotary compressor according to claim 1 is characterized in that, the barycenter of described first balance weight or second balance weight and the barycenter of described rotor lay respectively at the both sides of longitudinal center's face of described bent axle.
4. the balanced structure of rotary compressor according to claim 1 is characterized in that, the barycenter of the barycenter of described rotor and described crankshaft eccentric portion is positioned at the same side of described bent axle longitudinal center face.
5. the balanced structure of rotary compressor according to claim 1 is characterized in that, the barycenter of the barycenter of described rotor and described crankshaft eccentric portion lays respectively at the both sides of described bent axle longitudinal center face.
6. according to the balanced structure of each described rotary compressor among the claim 1-5, it is characterized in that the layout of described balanced structure designs in the following way:
A) set up the Mode Shape model of described balanced structure;
B) vibration shape model to described balanced structure carries out model analysis, determines the crooked vibration shape parameter in bent axle first rank of described rotor barycenter correspondence
The crooked vibration shape parameter in bent axle first rank of the described first balance weight barycenter correspondence
With the crooked vibration shape parameter in bent axle first rank of the described second balance weight barycenter correspondence
With the corresponding crooked vibration shape parameter in bent axle first rank of described crankshaft eccentric portion's barycenter
C) the offset m of the described rotor of definition
me
m, described first balance weight offset m
pe
p, second balance weight offset m
ae
aWith the offset m of described crankshaft eccentric portion
ee
e, and set the initial value of these offsets;
D) utilize the above-mentioned parameter of determining, determine the offset m of described rotor based on optimized Algorithm
me
m, described first balance weight offset m
pe
p, second balance weight offset m
ae
aOffset m with described crankshaft eccentric portion
ee
eBetween relation;
Wherein, m
pBe first mass of balance block, m
aBe the second secondary mass of balance block, m
mBe the quality of rotor, m
eBe the quality of crankshaft eccentric portion, e
pEccentric throw, e for described first balance weight
aEccentric throw, e for described second balance weight
mBe the eccentric throw of described rotor, e
eEccentric throw for described crankshaft eccentric portion.
7. the balanced structure of rotary compressor according to claim 6 is characterized in that, in described step c), sets the initial value of offset as follows:
The initial value of the offset of described first balance weight is set to m
pe
e=m
ee
e, the initial value of the offset of described second balance weight is set to m
ae
a=m
ee
e, the initial value of the offset of described rotor is set to m
me
m=m
ee
e
8. the balanced structure of rotary compressor according to claim 6 is characterized in that, in the described step d), and the offset m of described rotor
me
m, described first balance weight offset m
pe
p, described second balance weight offset m
ae
aOffset m with described crankshaft eccentric portion
ee
eBetween relation limit by following relational expression:
Qualitative restrain: Min (m
p+ m
a)
The constraint equation group:
Boundary constraint:
Wherein, L
pBe the barycenter of described first balance weight distance, L to the barycenter of described crankshaft eccentric portion
aBe the distance of the barycenter of second balance weight to the barycenter of described crankshaft eccentric portion, L
mBe the barycenter of described eccentric motor rotor distance, L to the barycenter of described crankshaft eccentric portion
p, L
a, L
mValue determine according to the installation site of first balance weight and second balance weight.
9. the balanced structure of rotary compressor according to claim 8 is characterized in that, the not homonymy that the eccentric throw of each parts of described balanced structure is in described longitudinal center face according to corresponding component get on the occasion of or negative value.
10. a rotary compressor is characterized in that, comprises according to each described balanced structure among the aforementioned claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010173579 CN102237746B (en) | 2010-05-07 | 2010-05-07 | Balance structure of rotary compressor and rotary compressor comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010173579 CN102237746B (en) | 2010-05-07 | 2010-05-07 | Balance structure of rotary compressor and rotary compressor comprising same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102237746A true CN102237746A (en) | 2011-11-09 |
| CN102237746B CN102237746B (en) | 2013-05-15 |
Family
ID=44888088
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010173579 Active CN102237746B (en) | 2010-05-07 | 2010-05-07 | Balance structure of rotary compressor and rotary compressor comprising same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102237746B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104728118A (en) * | 2015-04-01 | 2015-06-24 | 广东美芝制冷设备有限公司 | Rotary type compressor |
| CN106655606A (en) * | 2016-11-24 | 2017-05-10 | 兰州飞行控制有限责任公司 | Direct current brushless motor rotor structure |
| CN107949701A (en) * | 2015-10-16 | 2018-04-20 | 大金工业株式会社 | Compressor |
| CN108631500A (en) * | 2017-03-15 | 2018-10-09 | 三菱电机(广州)压缩机有限公司 | Compressor and its rotor assembly |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62284983A (en) * | 1986-06-04 | 1987-12-10 | Hitachi Ltd | Rotary compressor |
| CN1160127A (en) * | 1995-12-11 | 1997-09-24 | 运载器有限公司 | Counterweight drag eliminator |
| CN201437775U (en) * | 2009-07-01 | 2010-04-14 | 松下·万宝(广州)压缩机有限公司 | rotary compressor |
-
2010
- 2010-05-07 CN CN 201010173579 patent/CN102237746B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62284983A (en) * | 1986-06-04 | 1987-12-10 | Hitachi Ltd | Rotary compressor |
| CN1160127A (en) * | 1995-12-11 | 1997-09-24 | 运载器有限公司 | Counterweight drag eliminator |
| CN201437775U (en) * | 2009-07-01 | 2010-04-14 | 松下·万宝(广州)压缩机有限公司 | rotary compressor |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104728118A (en) * | 2015-04-01 | 2015-06-24 | 广东美芝制冷设备有限公司 | Rotary type compressor |
| CN107949701A (en) * | 2015-10-16 | 2018-04-20 | 大金工业株式会社 | Compressor |
| CN107949701B (en) * | 2015-10-16 | 2021-08-13 | 大金工业株式会社 | Compressor |
| CN106655606A (en) * | 2016-11-24 | 2017-05-10 | 兰州飞行控制有限责任公司 | Direct current brushless motor rotor structure |
| CN108631500A (en) * | 2017-03-15 | 2018-10-09 | 三菱电机(广州)压缩机有限公司 | Compressor and its rotor assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102237746B (en) | 2013-05-15 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105243172B (en) | A kind of Engine Mounting System optimization method considering dynamic rate and dynamic antivibration | |
| CN102237746B (en) | Balance structure of rotary compressor and rotary compressor comprising same | |
| CN102004823B (en) | Numerical value simulation method of vibration and acoustic characteristics of speaker | |
| RU2505424C1 (en) | Three-cylinder engine | |
| CN104417355B (en) | Vehicle powertrain mounting system and method of designing same | |
| CN103390073B (en) | A kind of vibration isolation design method of central air conditioner room | |
| RU2014141132A (en) | PIEZOELECTRIC DAMPER SYSTEM FOR AXIAL TURBO MACHINE ROTOR | |
| CN109990160A (en) | A kind of multidimensional viscous damping tuning quality shock bracket | |
| Liu et al. | Study on plate silencer with general boundary conditions | |
| Shi et al. | Influence of equipment excitation on flexible carbody vibration of EMU | |
| TW200730717A (en) | A method of vibration control supporting a cooling fan cover of a forced-air-cooled engine and forced-air-cooled engine with cooling air guide cover | |
| Chen et al. | Research of design and vibration reduction of dual mass flywheel with arc helix spring | |
| CN103742281A (en) | High-speed marine diesel cylinder sleeve support structure | |
| CN205136009U (en) | Rotor compressor, gleitbretter vibration system and air conditioner | |
| Pugachev | Application of gradient-based optimization methods for a rotor system with static stress, natural frequency, and harmonic response constraints | |
| Nagai et al. | Chaotic oscillations of a shallow cylindrical shell with a concentrated mass under periodic excitation | |
| Acar et al. | Nonlinear dynamics of flexible rotating shafts with centrifugal pendulum vibration absorbers | |
| US20190284993A1 (en) | Engine | |
| CN105275809B (en) | Rotor compressor, slip sheet vibration system and air conditioner | |
| CN108121166B (en) | Active vibration absorber and micropositioner | |
| KR20090057723A (en) | Dynamic damper of automobile | |
| JP5293856B2 (en) | Vibration reduction structure of multi-link engine | |
| CN109944904A (en) | Multi-modal suction vibrating isolation system and platform | |
| KR20180067293A (en) | Stock bridge damper design parameter selection apparatus and the method thereof | |
| CN203272570U (en) | Automobile front lower cantilever and multi-link shock-absorbing device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |