CN102237746B - Balance structure of rotary compressor and rotary compressor comprising same - Google Patents
Balance structure of rotary compressor and rotary compressor comprising same Download PDFInfo
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- CN102237746B CN102237746B CN 201010173579 CN201010173579A CN102237746B CN 102237746 B CN102237746 B CN 102237746B CN 201010173579 CN201010173579 CN 201010173579 CN 201010173579 A CN201010173579 A CN 201010173579A CN 102237746 B CN102237746 B CN 102237746B
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Abstract
The invention provides a balance structure of a rotary compressor and a rotary compressor comprising the same. The balance structure of the rotary compressor comprises an eccentric motor rotor, a crank shaft eccentric part, a first balance block and a second balance block, wherein the eccentric motor rotor is arranged at one end of a crank shaft of a compressor rotor component; the crank shaft eccentric part is arranged close to the other end of the crank shaft; and the first balance block and the second balance block are arranged at the two ends of the eccentric motor rotor respectively. According to the balance structure of the rotary compressor, the eccentric motor rotor is adopted, and corresponding balance blocks are arranged at the two ends of the eccentric motor rotor according to the used eccentric motor rotor and crank shaft eccentric part, so that an ideal dynamic balance effect can be realized in a variable-frequency compressor, and the vibration and noise of the compressor are reduced.
Description
Technical field
The present invention relates to compressor field, be specifically related to 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 down unbalance response in working order in rotor-support-foundation system, therefore need to 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, consists of thus the balanced structure of compressor rotor system.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 section 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 vibration and the noise of compressor are larger.
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.
For 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 arranged on the end of bent axle of compressor drum parts; Crankshaft eccentric section is arranged near the other end of bent axle; The first balance weight and the 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 the first balance weight and the 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 the first balance weight or the 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 section 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 section 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 of balanced structure carried out model analysis, determine the crooked modal parameters in bent axle corresponding to rotor barycenter the first rank
The crooked modal parameters in bent axle the first rank that the first balance weight barycenter is corresponding
The bent axle first rank crooked modal parameters corresponding with the second balance weight barycenter
The bent axle first rank crooked modal parameters corresponding with crankshaft eccentric section barycenter
C) the offset m of definition rotor
me
m, the first balance weight offset m
pe
p, the second balance weight offset m
ae
aWith the offset m of crankshaft eccentric section
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, the first balance weight offset m
pe
p, the second balance weight offset m
ae
aOffset m with crankshaft eccentric section
ee
eBetween relation;
Wherein, m
pBe the quality of the first balance weight, m
aBe the quality of the second secondary balance weight, m
mBe the quality of rotor, m
eBe the quality of crankshaft eccentric section, e
pBe eccentric throw, the e of the first balance weight
aBe eccentric throw, the e of the second balance weight
mBe the eccentric throw of rotor, e
eEccentric throw for crankshaft eccentric section.
Further, according to the balanced structure of rotary compressor of the present invention, wherein, at step c) in, set as follows the initial value of offset: the initial value of the offset of the first balance weight is set to m
pe
p=m
ee
e, the initial value of the offset of the 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, steps d) in, the offset m of rotor
me
m, the first balance weight offset m
pe
p, the second balance weight offset m
ae
aOffset m with crankshaft eccentric section
ee
eBetween relation limit by following relational expression:
Qualitative restrain: Min (m
p+ m
a)
The constraint equation group:
Boundary constraint:
Wherein, L
pBe that the barycenter of the first balance weight is to the distance of the barycenter of crankshaft eccentric section, L
aBe that the barycenter of the second balance weight is to the distance of the barycenter of crankshaft eccentric section, L
mBe the barycenter of the eccentric motor rotor distance to the barycenter of crankshaft eccentric section, L
p, L
a, L
mValue determine according to the installation site of described the first balance weight and described the 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 all 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 eccentric motor rotor used and crankshaft eccentric section, at the two ends of eccentric motor rotor, corresponding balance weight is set, the dynamic balancing effect that can realize ideal in frequency-changeable compressor thus, 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, and purpose is for to the claimed further instruction that the invention provides.
Description of drawings
Accompanying drawing consists of the part of this specification, is used for helping further to understand the present invention.These accompanying drawings illustrate some embodiments of the present invention, and are used for illustrating principle of the present invention together with specification.Identical parts represent with identical label in the accompanying drawings.In accompanying drawing:
Figure 1A to Fig. 1 C shows respectively the schematic diagram according to three kinds of execution modes of the balanced structure of rotary compressor of the present invention;
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 to balanced structure of the present invention simultaneously below in conjunction with instantiation.
The dynamic balancing design of rotary compressor balanced structure of the prior art in the situation that invariable frequency compressor can be regarded bent axle as rigid body, thinks namely that bent axle is indeformable mainly for invariable frequency compressor, carries out on this basis the dynamic balancing design.Two constraint equations of the general employing of this balanced structure, and only comprise the parameter about rotor, crankshaft eccentric section and one of them balance weight in equation, and for frequency-changeable compressor, this design just can not be suitable for, utilize this mode to carry out the dynamic balancing design to frequency-changeable compressor and can't obtain desirable counterbalance effect, vibrations and noise are all larger.
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 section are arranged on respectively the opposite end of bent axle, 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 section 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 arranged on the end of bent axle 20 of compressor drum parts; Crankshaft eccentric section 30 is arranged near the other end of bent axle 10; And first balance weight 40 and the 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, in three embodiment that the below will describe in detail, all adopt from the mode of internal rotor borehole.Simultaneously, for the first balance weight and the second balance weight arrangement with respect to the eccentric motor rotor, the compressor model for 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 in Figure 1A to 1C.In the balanced structure shown in Figure 1A, the barycenter of the first balance weight 40 and the 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 simultaneously the barycenter of crankshaft eccentric section 30 also is positioned at this opposite side of the face A of longitudinal center.
In embodiment shown in Figure 1B and Fig. 1 C, the barycenter of the first balance weight 40 or the 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 the 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 the second balance weight 50 and eccentric motor rotor 10 and crankshaft eccentric section 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 the 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 the second balance weight 50 and crankshaft eccentric section 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 section 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 bent axle face A of longitudinal center.
According to principle of the present invention, the set-up mode of the eccentric part of the first balance weight 40, the second balance weight 50, eccentric motor rotor 10, crankshaft eccentric section 30 can be determined according to the concrete model of compressor.Compressor for different model, the size (corresponding mass) of the first balance weight 40, the 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 section 30 as rigid body, but consider the distortion of crankshaft eccentric section 30, employing is introduced the parameter relevant to distortion in constraint equation, simultaneously with the first balance weight 40, the second balance weight 50, the eccentric part of eccentric motor rotor 10, the offset of crankshaft eccentric section 30 is all introduced constraint equation, utilize corresponding optimized algorithm to determine rotor 10 offsets, first, the second balance weight 40, 50 offset and crankshaft eccentric section 30 eccentric the relationship between quantities, determine thus the concrete layout of balanced structure, be eccentric motor rotor 10 and first, the 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 of balanced structure carried out model analysis, determine the crooked modal parameters in the first rank of eccentric motor rotor 10
The crooked modal parameters in the first rank of the first balance weight 40
With the crooked modal parameters in the first rank of the second balance weight 50
With the crooked modal parameters in the first rank of crankshaft eccentric section 30
C) the offset m of definition eccentric motor rotor 10
me
m, the first balance weight 40 offset m
pe
p, the second balance weight 50 offset m
ae
aWith the offset m of crankshaft eccentric section 30
ee
e, and set the initial value of above-mentioned these offsets;
D) carry out modal balancing and check, utilize specifically the offset m of the above-mentioned parameter of determining (comprising the first crooked modal parameters and offset) optimization eccentric motor rotor 10
me
m, the first balance weight 40 offset m
pe
p, the second balance weight 50 offset m
ae
aOffset m with crankshaft eccentric section 30
ee
eBetween relation, namely optimization satisfies eccentric motor rotor 10, first balance weight 40 of equilibrium constraint, the offset of the second balance weight 50.
If check result satisfies default constraint equation and condition, export corresponding optimum results; Otherwise return to step c) in again check.
In above-mentioned parameter, m represents the quality of each part of balanced structure, wherein, and m
pBe the quality of the first balance weight, m
aBe the quality of the second secondary balance weight, m
mBe the quality of rotor, m
eQuality for crankshaft eccentric section; E represents the eccentric throw (being that barycenter is to the distance of the face A of longitudinal center of bent axle 10) of each part of balanced structure, e
pBe eccentric throw, the e of the first balance weight
aBe eccentric throw, the e of the second balance weight
mBe the eccentric throw of rotor, e
eEccentric throw for crankshaft eccentric section.M and e product both namely is defined as the offset me of corresponding component.
Preferably, at step c) in, set as follows the initial value of the offset of each part of balanced structure: the initial value of the offset of the initial value of the offset of the initial value of the offset of the first balance weight 40, the second balance weight 50, rotor 10 all is set to identical with the offset of crankshaft eccentric section 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 section 30
ee
eCan determine according to 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, the first balance weight 40 offset m
pe
p, the second balance weight 50 offset m
ae
aOffset m with crankshaft eccentric section 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 the first balance weight 40, m
aBe the quality of the second balance weight 50, m
mBe the quality of rotor 10, m
eBe the quality of crankshaft eccentric section 30, L
pBe that the barycenter of the first balance weight 40 is to the distance of the barycenter of crankshaft eccentric section 30, L
aBe that the barycenter of the second balance weight 50 is to the distance of the barycenter of crankshaft eccentric section 30, L
mBe the barycenter of eccentric motor rotor 10 distance to the barycenter of crankshaft eccentric section 30, symbol
The expression vector.Particularly, the eccentric throw of all 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 face A of the longitudinal center right side that shows in figure be defined as on the occasion of, and the left side is defined as negative value, the constraint equation of this moment just can be write as:
Above-mentioned empirical equation is to set for frequency-changeable compressor specially, the qualitative restrain condition Min m that wherein adopts
p+ m
aBe the basic purpose of vibration shape method dynamic balancing design, namely satisfy the requirement for dynamic balance of rotor part with the balance weight of minimum mass.Simultaneously, boundary constraint used
Be an experimental constraint formula, its purpose is the eccentric position that guarantees to choose suitable balance weight, rotor suitably is set to make simultaneously the size of these parts not too large.
Below, adopt an instantiation to above-mentioned steps d) in optimization method describe.Therefore describe with embodiment shown in Fig. 2, adopt the constraint equation (2) after above-mentioned distortion.
Model and inner concrete member according to compressor carry out model analysis, determine the crooked modal parameters of phase I of all parts, and modal parameters as crooked in the phase I of certain concrete compressor is as follows:
Determine simultaneously the offset m of crankshaft eccentric section 30
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, 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 the 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 relationship are complementary, as long as their offset satisfies the above-mentioned relation formula, 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.
These are only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.All any modifications of doing within the spirit and principles in the present invention, be equal to replacement, improvement etc., within protection scope of the present invention all should be included in.
Claims (9)
1. the balanced structure of rotary compressor, is characterized in that, comprising:
Eccentric motor rotor (10) is arranged on the end of bent axle (20) of compressor drum parts;
Crankshaft eccentric section (30) is arranged near the other end of described bent axle;
The first balance weight (40) and the second balance weight (50) are separately positioned on the two ends of described eccentric motor rotor;
The layout of described balanced structure adopts the following steps design:
A) set up the Mode Shape model of described balanced structure;
B) model analysis is carried out on the vibration shape model of described balanced structure, determined the crooked modal parameters in bent axle corresponding to described rotor barycenter first rank
The crooked modal parameters in bent axle the first rank that described the first balance weight barycenter is corresponding
The bent axle first rank crooked modal parameters corresponding with described the second balance weight barycenter
The bent axle first rank crooked modal parameters corresponding with described crankshaft eccentric section barycenter
C) the offset m of the described rotor of definition
me
m, described the first balance weight offset m
pe
p, the second balance weight offset m
ae
aOffset m with described crankshaft eccentric section
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 the first balance weight offset m
pe
p, the second balance weight offset m
ae
aOffset m with described crankshaft eccentric section
ee
eBetween relation;
Wherein, m
pBe the quality of the first balance weight, m
aBe the quality of the second balance weight, m
mBe the quality of rotor, m
eBe the quality of crankshaft eccentric section, e
pEccentric throw, e for described the first balance weight
aEccentric throw, e for described the second balance weight
mBe the eccentric throw of described rotor, e
eEccentric throw for described crankshaft eccentric section.
2. the balanced structure of rotary compressor according to claim 1, it is characterized in that, the barycenter of described the first balance weight and the 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 the first balance weight or the 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 section 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 section lays respectively at the both sides of described bent axle longitudinal center face.
6. the balanced structure of rotary compressor according to claim 1, is characterized in that, at described step c) in, set as follows the initial value of offset:
The initial value of the offset of described the first balance weight is set to m
pe
p=m
ee
e, the initial value of the offset of described the 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
7. the balanced structure of rotary compressor according to claim 1, is characterized in that, described steps d) in, the offset m of described rotor
me
m, described the first balance weight offset m
pe
p, described the second balance weight offset m
ae
aOffset m with described crankshaft eccentric section
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 the first balance weight distance to the barycenter of described crankshaft eccentric section, L
aBe that the barycenter of the second balance weight is to the distance of the barycenter of described crankshaft eccentric section, L
mBe the barycenter of the described eccentric motor rotor distance to the barycenter of described crankshaft eccentric section, L
p, L
a, L
mValue determine according to the installation site of the first balance weight and the second balance weight.
8. the balanced structure of rotary compressor according to claim 7, is characterized in that, the not homonymy that the eccentric throw of all parts of described balanced structure is in described bent axle longitudinal center face according to corresponding component get on the occasion of or negative value.
9. a rotary compressor, is characterized in that, comprises according to the described balanced structure of any one in aforementioned claim 1-8.
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|---|---|---|---|
| CN 201010173579 CN102237746B (en) | 2010-05-07 | 2010-05-07 | Balance structure of rotary compressor and rotary compressor comprising same |
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|---|---|---|---|
| CN 201010173579 CN102237746B (en) | 2010-05-07 | 2010-05-07 | Balance structure of rotary compressor and rotary compressor comprising same |
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| CN102237746B true CN102237746B (en) | 2013-05-15 |
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| CN104728118B (en) * | 2015-04-01 | 2017-06-16 | 广东美芝制冷设备有限公司 | Rotary compressor |
| JP6090405B1 (en) * | 2015-10-16 | 2017-03-08 | ダイキン工業株式会社 | 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 |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62284983A (en) * | 1986-06-04 | 1987-12-10 | Hitachi Ltd | Rotary compressor |
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2010
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Non-Patent Citations (1)
| Title |
|---|
| JP昭62-284983A 1987.12.10 |
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