CN103032328B - The rotary compressor of multi cylinder - Google Patents
The rotary compressor of multi cylinder Download PDFInfo
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- CN103032328B CN103032328B CN201110304349.0A CN201110304349A CN103032328B CN 103032328 B CN103032328 B CN 103032328B CN 201110304349 A CN201110304349 A CN 201110304349A CN 103032328 B CN103032328 B CN 103032328B
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Abstract
A kind of rotary compressor of multi cylinder, motor and compressing mechanism is provided with in the housing of sealing, compressing mechanism comprises the first cylinder with first piston, with the second cylinder of the second piston and the central diaphragm between the first cylinder and the second cylinder, eccentric crankshaft drives first piston and the second piston rotation simultaneously, main bearing and supplementary bearing for supporting eccentric crankshaft are separately positioned on the side of the first cylinder and the second cylinder, eccentric crankshaft comprises main shaft, the first eccentric shaft connected with first piston, the second eccentric shaft connected with the second piston and countershaft, first eccentric shaft and the second eccentric shaft are connected by coupling shaft, jack shaft is provided with in coupling shaft, the intermediate bearing for supporting jack shaft is provided with in central diaphragm.The present invention not only goes for the rotary compressor of twin-tub, but also goes for the rotary compressor of three cylinders or multi-cylinder, and it has feature simple and reasonable, that flexible operation, Energy Efficiency Ratio are high, applied widely.
Description
Technical field
The present invention relates to a kind of rotary compressor, particularly a kind of rotary compressor of multi cylinder.
Background technique
In order to improve with twin-tub reliability and the efficiency of the rotary compressor of the multi cylinder being representative, except the main bearing in conventional art and supplementary bearing, added the 3rd axle and as jack shaft and intermediate bearing.In addition, in order to make effective length of intermediate bearing maximum, dull and stereotyped form central diaphragms with 2 or several.
In the Large Copacity rotary compressor be made up of many inflators, not only the compression load of compression chamber increases, and the axial length between main bearing to supplementary bearing can be elongated, so there is the problem of the axle rigidity deficiency of this part.Its result, because the incorrect operation of eccentric shaft abrasion and piston can reduce by generation efficiency.
In recent years, rotary compressor is mounted in domestic air conditioning, and progressively improve in the popularity rate in the whole world, on the other hand, in business air conditioner, medium-sized large revolving compressor is also improving.Such Large Copacity rotary compressor needs to adopt the multi-cylinder modes such as twin-tub.
Japanese documentation 1 Unexamined Patent 10 (1998)-213087 rotary compressor.
Chinese patent literature 2CN00249769.7.
Chinese patent literature 3CN00126311.0.
The bent axle of a Chinese patent literature 4CN2813935Y high rigid double-cylinder rotor type compressor.
Summary of the invention
Object of the present invention aims to provide a kind of rotary compressor of simple and reasonable, multi cylinder that flexible operation, Energy Efficiency Ratio are high, applied widely, to overcome deficiency of the prior art.
The rotary compressor of a kind of multi cylinder designed by this object, motor and compressing mechanism is provided with in the housing of sealing, compressing mechanism comprises the first cylinder with first piston, with the second cylinder of the second piston and the central diaphragm between the first cylinder and the second cylinder, eccentric crankshaft drives first piston and the second piston rotation simultaneously, main bearing and supplementary bearing for supporting eccentric crankshaft are separately positioned on the side of the first cylinder and the second cylinder, eccentric crankshaft comprises main shaft, the first eccentric shaft connected with first piston, the second eccentric shaft connected with the second piston and countershaft, its structure characteristic is that the first eccentric shaft and the second eccentric shaft are connected by coupling shaft, jack shaft is provided with in coupling shaft, the intermediate bearing for supporting jack shaft is provided with in central diaphragm.
Described central diaphragm comprises more than one flat board, this flat board comprises two parallel side planes, intermediate bearing be positioned at a side plane central authorities and towards the perforate of opposite side plane, center hole be positioned at opposite side plane central authorities and towards the inside of intermediate bearing and a side plane perforate.
Be provided with snubber between described intermediate bearing and center hole, this snubber is for limiting the knee-action of the jack shaft supported by intermediate bearing.
The external diameter of described jack shaft is larger than the external diameter of either party in the first eccentric shaft and the second eccentric shaft.
The gap formed between the external diameter of described jack shaft and the internal diameter of intermediate bearing is more than 2/1000 of the external diameter of jack shaft, and jack shaft and intermediate bearing are contactless state.
The rotary compressor of described multi cylinder is applied in air conditioner, refrigerating machine or water heater.
A kind of rotary compressor of multi cylinder, motor and compressing mechanism is provided with in the housing of sealing, compressing mechanism comprises more than three respectively with the cylinder of piston and the central diaphragm between cylinder, eccentric crankshaft drives each piston rotation simultaneously, main bearing and supplementary bearing are for supporting eccentric crankshaft, coupling shaft and countershaft that eccentric crankshaft comprises main shaft, drives the eccentric shaft of each piston, connects adjacent two eccentric shafts, its structure characteristic is provided with jack shaft in coupling shaft; One is had at least to be supported by the intermediate bearing that arranges in described central diaphragm in described jack shaft.
The rotary compressor of described multi cylinder is applied in air conditioner, refrigerating machine or water heater.
As for three with the concrete structure of the central diaphragm in the rotary compressor of upper cylinder and intermediate bearing, substantially identical with the concrete structure with the central diaphragm in the rotary compressor of twin-tub and intermediate bearing, therefore do not repeat in detail in the claims to record.
The present invention arranges jack shaft in the centre of the coupling shaft of connection first eccentric shaft and the second eccentric shaft, and is supported jack shaft by the intermediate bearing be arranged in central diaphragm; Jack shaft is made up of two flat boards, and the intermediate bearing that external diameter becomes large, axial length is longer just completes.
The present invention is by adding the 3rd bearing; namely be increased in the intermediate bearing except main bearing and supplementary bearing; significantly improve rigidity and the vibration of eccentric crankshaft, piston, slide plate not only can normally slide, and can also improve eccentric crankshaft and vibrate the wear-out failure and compression efficiency reduction that cause.
The present invention not only goes for the rotary compressor of twin-tub, but also goes for the rotary compressor of three cylinders or multi-cylinder, and it has feature simple and reasonable, that flexible operation, Energy Efficiency Ratio are high, applied widely.
Accompanying drawing explanation
Fig. 1 is the broken section structural representation of the rotary compressor R that the embodiment of the present invention 1 is relevant.
Fig. 2 is longitudinal broken section structural representation of the compressing mechanism relevant to embodiment 1.
Fig. 3 is the structural representation of the eccentric crankshaft relevant to embodiment 1.
Fig. 4 is the structural representation of second flat board relevant to embodiment 1.
Fig. 5 is the horizontal sectional structure schematic diagram of Fig. 4.
Fig. 6-Fig. 7 is second flat board relevant to the embodiment 1 assembling procedure figure relative to eccentric crankshaft.
Fig. 8 is that the assembling of the central diaphragm relevant to embodiment 1 completes figure.
Fig. 9 is the structural representation of the second dull and stereotyped M2 that embodiment 2 is relevant.
Figure 10 is the horizontal sectional structure schematic diagram of Fig. 9.
Figure 11 is that second flat board relevant to embodiment 1 is to the assembling procedure figure of eccentric crankshaft.
Figure 12 is that the assembling of the central diaphragm relevant to embodiment 2 completes figure.
Figure 13 is that the assembling of the first jack shaft that embodiment 3 is relevant and central diaphragm completes figure.
Figure 14 is that the assembling of central diaphragm that embodiment 4 is relevant and the first jack shaft completes figure.
Figure 15 is the structural representation of central diaphragm that embodiment 5 is relevant and the first jack shaft.
In figure: R is rotary compressor, H is motor, 2 is housing, P is compressing mechanism, 13a is the first cylinder, 13b is the second cylinder, 16a is first piston, 16b is the second piston, 21 is main bearing, 22 is supplementary bearing, 26 is upper bolt, 27 is lower bolt, S is eccentric crankshaft, 31 is main shaft, E1 is the first eccentric shaft, E2 is the second eccentric shaft, 33 is countershaft, 36 is oil supply, G is coupling shaft, G1 is the first jack shaft, G3 is the second jack shaft, M is central diaphragm, M1 is the first flat board, M2 is the second flat board, M3 is the 3rd flat board, M4 is the 4th flat board, F is intermediate bearing, 41 is gap, 43 is assembling pin-and-hole, hole centered by 44, groove centered by 45, 46 is snubber, 62 is assembling pin.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
Embodiment 1
See Fig. 1, it is the internal structure of rotary compressor R.Rotary compressor R is configured with compressing mechanism P and motor H in seal casinghousing, and they are fixed on the inwall place of housing.First cylinder 13a and the second cylinder 13b of compressing mechanism P are distinguished by central diaphragm M.
See Fig. 2, it is the detail drawing of compressing mechanism P.In the first cylinder 13a forming compressing mechanism P and the second cylinder 13b, being configured with first piston 16a and the second piston 16b, also having and the slide plate (without scheming) of its synchronous reciprocating action.The central diaphragm M be made up of the first dull and stereotyped M1 and the second dull and stereotyped M2 distinguishes these cylinders between two cylinders.
The coupling shaft G being configured in the eccentric crankshaft S at compressing mechanism P center is the axle of connection first eccentric shaft E1 and the second eccentric shaft E2, and the centre of coupling shaft G constitutes the first jack shaft G1.Intermediate bearing F is configured with in the central authorities of central diaphragm M.Therefore, the main shaft 31 of eccentric crankshaft S, countershaft 33 and jack shaft G1 are supported by main bearing 21, supplementary bearing 22 and intermediate bearing F respectively.The constituent parts of compressing mechanism P, after aligning, is connected with lower bolt 27 by bolt 26 on 5 groups.
See Fig. 3, eccentric crankshaft S is made up of the first jack shaft G1 arranged in the middle of main shaft 31, first eccentric shaft E1, coupling shaft G and the second eccentric shaft E2, countershaft 33.Coupling shaft G is the axle of connection first eccentric shaft E1 and the second eccentric shaft E2, and the scope of coupling shaft G is G.Coupling shaft G is made up of the second jack shaft G3 of the first jack shaft G1 and its both sides.
The width of the second jack shaft G3 is W, when being assembled as central diaphragm M by the second dull and stereotyped M2 and the first dull and stereotyped M1 as described later, just becomes the passage of these flat boards.Therefore, need to strengthen W size when the width of central diaphragm M or the first jack shaft G1 strengthens.And in the scope that the external diameter of the second jack shaft G3 does not exceed eccentric shaft external diameter and jack shaft G1 external diameter, the external diameter that expand the second jack shaft G3 improves the rigidity of coupling shaft G.
Here, the external diameter of the first jack shaft G1 coaxial with main shaft 31 is D1, and the width of the first jack shaft G1 is T.In embodiment 1, the external diameter of main shaft 31 and countershaft 33 is equal, and the outer diameter D 2 of the first eccentric shaft E1 and the second eccentric shaft E2 is equal respectively with eccentric amount e.The outer diameter D 2 of the outer diameter D 1=second eccentric shaft E2 of the first jack shaft G1.
The outer diameter D 1 of the first jack shaft G1 and width T, equally with central diaphragm M can be optimized by free variation.The oil supply 36 possessed in first jack shaft G1, the face that the compression being arranged on 2 cylinders causes is pressed in minimum scope.
See Fig. 4-Fig. 5, represent the detail drawing of the second dull and stereotyped M2 forming central diaphragm M.Second dull and stereotyped M2 is symmetrical.Second dull and stereotyped M2 forms by 2 planes of being strict with and at the center hole 44 that the internal diameter that the central part of this plane is through is d1 by planeness and parallelism.
By the center hole 44 of the second dull and stereotyped M2 and the first dull and stereotyped M1 wherein the heart be packed together to the intermediate bearing F that internal diameter is d3, intermediate bearing F is the bearing for supporting the first jack shaft G1.Second dull and stereotyped M2 is provided with 2 groups of assembling pin-and-holes 43, this assembling pin-and-hole 43 uses when the dull and stereotyped M1 of combination first is connected as central diaphragm M with the second dull and stereotyped M2.In addition, assembling pin-and-hole 43 is aligning holes when being arranged on cylinder by central diaphragm M.5 holes on the periphery of the second dull and stereotyped M2 are the assembly hole of lower bolt 27.
The internal diameter d1 of center hole 44 is the internal diameter d3 of intermediate bearing F, therefore d1=d3.Very little gap c is only had between the internal diameter d3 of intermediate bearing F and the outer diameter D 1 of the first jack shaft G1.Therefore, d1=d3=D1+c.This gap c due to oil viscosity or intermediate bearing F different with or without bushing bearing, reference value is the scope of 1 ~ 2/1000 of the outer diameter D 1 of the first jack shaft G1.In addition, as mentioned above, D1=D2, therefore d1=D2+c, the internal diameter of center hole 44 has gap c can through eccentric shaft.
Next, Fig. 6-Fig. 7 represents in the second dull and stereotyped M2 insertion eccentric crankshaft S, carries out the operation of assembling in central diaphragm M.In Fig. 6, the center of center hole 44 is consistent with the center of the second eccentric shaft E2, just becomes Fig. 7 when the second dull and stereotyped M2 is moved by the external diameter upward direction of the second eccentric shaft E2.In the figure 7, in order to keep the center of center hole 44 consistent with the center of main shaft 31, transverse shifting e size.Then, the second dull and stereotyped M2 is set on the periphery of the first jack shaft G1.
Equally, when being inserted from the upper end of main shaft 31 by the first dull and stereotyped M1, as shown in Figure 8,2 dull and stereotyped assembly projects terminate for the first dull and stereotyped M1 and the second dull and stereotyped M2 compact siro spinning technology.After assembling pin 62 being installed in assembling pin-and-hole 43, just complete the assembling of central diaphragm M.At this moment, in the intermediate bearing F formed in central diaphragm M, the first jack shaft G1 is supported across gap c.
Gap between the upper end of the first eccentric shaft E1 and main bearing 21 reduces by embodiment 1, due to the lower end of the second eccentric shaft E2 and the plane contact of supplementary bearing 22, can limit the scope of the knee-action of eccentric crankshaft S.Therefore, can prevent the top and bottom of the first jack shaft G1 from flying out from the perforate end of intermediate bearing F, interference with piston flat surface slide part.
Embodiment 2
See Fig. 9-Figure 10, in the present embodiment 2, be the central channel 45 of d2 at the center configuration internal diameter of the second dull and stereotyped M2, offer at the medial plane of central channel 45 center hole 44 that internal diameter is d1.
In embodiment 2, the internal diameter d3 of central channel 45 is the internal diameter of intermediate bearing F, therefore d2=d3.D2=d1+2e, constitutes the push stopping part 46 of thin-walled, sees Figure 10 in the bottom of central channel 45.In the same manner as in Example 1, d2=d3=D1+c.And, d1=D2+c.
See Figure 11, represent and the second dull and stereotyped M2 is inserted in eccentric crankshaft S, the technique of assembling central diaphragm M.Identical with embodiment 1, as Figure 11 when the second dull and stereotyped M2 is moved by the periphery upward direction of the second eccentric shaft E2.And, in order to ensure that the center of center hole 44 is consistent with the center of main shaft 31, the distance of transverse shifting e, again upward direction to move.Then, as Figure 12 after equally the first dull and stereotyped M1 being inserted from the upper end of main shaft 31.
Thereafter, after having installed assembling pin 62, the assembling of central diaphragm M has finished, and in intermediate bearing F, the first jack shaft G1 is supported by gap c.At the snubber 46 with the eccentric amount e equivalent size of eccentric shaft that is vertically disposed with of the first jack shaft G1.After first piston 16a inserts the first eccentric shaft E1, the plane of first piston 16a and contacting and can slide above of snubber 46.
Like this, embodiment 2 passes through on central diaphragm M, arrange the central channel 45 larger than center hole 44,
(1) snubber 46 of restriction eccentric crankshaft S knee-action is set in intermediate bearing F, the problem that the top and bottom of the first jack shaft G1 contact with the slip plane of first piston can be prevented; (2) the first jack shaft G1 and intermediate bearing F that internal diameter is larger than the outer diameter D 2 of the second eccentric shaft can be configured, the rigidity of bearing reliability and coupling shaft G can be improved; (3) even if expand the external diameter of the first jack shaft G1 and intermediate bearing F, the internal diameter d1 of center hole 44 and the slip plane of first piston can not change, and can not reduce so feature is compression efficiency.And the snubber 46 of embodiment 2 can use as the thrust surface of eccentric crankshaft S, substitute the push stopping part of above-mentioned eccentric shaft.
All the other are not stated part and see embodiment 1, no longer repeat.
Embodiment 3
See Figure 13, the present embodiment 3 forms central diaphragm M by 1 piece of flat board, therefore compared with the embodiment 1 forming central diaphragm M by 2 flat boards or embodiment 2, processing and the assembling with central diaphragm M are relatively easy to advantage, shortcoming is that the width of intermediate bearing F or bearing length can reduce by half.But the condition increasing the width W of the second jack shaft G3 can realize.And in embodiment 3, the outer diameter D 1 of the first jack shaft G1 and the outer diameter D 2 of the second eccentric shaft have to be same.I.e. D1 ≈ D2.
All the other are not stated part and see embodiment 1, no longer repeat.
Embodiment 4
See Figure 11,2 the 4th dull and stereotyped M4 that the central diaphragm M of the present embodiment 4 is configured by 1 the 3rd dull and stereotyped M3, its both sides are formed.The internal diameter of the center hole of through 4th dull and stereotyped M4 and the through hole of the 3rd dull and stereotyped M3 is equivalent to d1, d2 and d3 in embodiment 2 respectively.Therefore, the relation of d2=d3=D1+c sets up.Here, the internal diameter of through hole is suitable with the internal diameter d3 of intermediate bearing F.Embodiment 4 has the effect suitable with embodiment 2.And, as embodiment 2, central diaphragm M can be formed by 1 the 3rd dull and stereotyped M3 and 1 the 4th dull and stereotyped M4.
All the other are not stated part and see embodiment 1, no longer repeat.
Embodiment 5
The present invention can reach by the first jack shaft G1 the effect significantly improving coupling shaft G rigidity.Therefore, between the periphery of the first jack shaft G1 and the intermediate bearing F of central diaphragm M, wide arc gap to be set and avoid them to contact, the rigidity of coupling shaft G can be improved.According to above-mentioned purpose, in embodiment 5 as shown in figure 15, between the internal diameter of the intermediate bearing F of the dull and stereotyped central diaphragm M formed of the periphery of the first jack shaft G1 and 2, be provided with gap 41, contact to avoid them.
All the other are not stated part and see embodiment 1, no longer repeat.
According to the announcement technology of embodiment 1 to embodiment 5, its feature and effect are described.
(1) by adding the bearing of configuration coupling shaft G and Supporting connectivity axle G in the centre being compressed counteractive first eccentric shaft and the second eccentric shaft, the vibration of whole eccentric crankshaft S can significantly reduce, so, main shaft and countershaft concentric are arranged, and piston can rotate on normal track.Therefore, reliability and the efficiency of compressor can be improved.
Be provided with the bearing of coupling shaft G and Supporting connectivity axle G between (2) first eccentric shafts and the second eccentric shaft, even if therefore expand 2 cylinders thickness, increase the discharge capacity of compression chamber, the load that coupling shaft G is out of shape also does not expand substantially.Therefore, the Large Copacity rotary compressor can not accomplished in conventional art can carry out commercialization.
(3) by central diaphragm M is divided into several flat board, the Effective face width of the first jack shaft G1 and intermediate bearing F can be expanded.
(4) central diaphragm M is provided with the center hole 44 of bearing surface of piston and the intermediate bearing F larger than the external diameter of this center hole 44, therefore can arrange the snubber of restriction eccentric crankshaft S knee-action.
(5) jack shaft G not only can connect the first eccentric shaft and the second eccentric shaft, also has both the effect of the means improving eccentric crankshaft S rigidity.
And the restriction of the technical scope that the present invention can not disclose to embodiment 5 by above embodiment 1, can also expand application area in its main scope.Above-mentioned all announcement technology are also such as feasible from three cylinders to the application of multi-cylinder rotary compressor.Rotary compressor in the present invention can be used widely at air conditioner, refrigerating machine or water heater etc.
Claims (5)
1. the rotary compressor of a multi cylinder, motor (H) and compressing mechanism (P) is provided with in the housing of sealing, compressing mechanism (P) comprises the first cylinder (13a) with first piston (16a), with the second cylinder (13b) and the central diaphragm (M) that is positioned between the first cylinder (13a) and the second cylinder (13b) of the second piston (16b), eccentric crankshaft (S) drives first piston (16a) and the second piston (16b) to rotate simultaneously, main bearing (21) and supplementary bearing (22) for supporting eccentric crankshaft (S) are separately positioned on the side of the first cylinder (13a) and the second cylinder (13b), eccentric crankshaft (S) comprises main shaft (31), the first eccentric shaft (E1) connected with first piston (16a), the second eccentric shaft (E2) connected with the second piston (16b) and countershaft (33), it is characterized in that the first eccentric shaft (E1) and the second eccentric shaft (E2) are connected by coupling shaft (G), jack shaft is provided with in coupling shaft (G), the intermediate bearing (F) for supporting jack shaft is provided with in central diaphragm (M),
Described central diaphragm (M) comprises more than one flat board, this flat board comprises two parallel side planes, intermediate bearing (F) be positioned at a side plane central authorities and towards the perforate of opposite side plane, center hole (44) be positioned at opposite side plane central authorities and towards the inside of intermediate bearing (F) and a side plane perforate;
Snubber (46) is provided with, the knee-action of the jack shaft that this snubber (46) is supported by intermediate bearing (F) for restriction between described intermediate bearing (F) and center hole (44);
The gap formed between the internal diameter of the external diameter of described jack shaft and intermediate bearing (F) is more than 2/1000 of the external diameter of jack shaft, and jack shaft and intermediate bearing (F) are contactless state.
2. the rotary compressor of multi cylinder according to claim 1, is characterized in that the external diameter of described jack shaft is larger than the external diameter of either party in the first eccentric shaft (E1) and the second eccentric shaft (E2).
3., according to the rotary compressor of the arbitrary described multi cylinder of claim 1 to 2, it is characterized in that the rotary compressor of described multi cylinder is applied in air conditioner, refrigerating machine or water heater.
4. the rotary compressor of a multi cylinder, motor (H) and compressing mechanism (P) is provided with in the housing of sealing, compressing mechanism (P) comprises more than three respectively with the cylinder of piston and the central diaphragm between cylinder (M), eccentric crankshaft (S) drives each piston rotation simultaneously, main bearing (21) and supplementary bearing (22) are for supporting eccentric crankshaft (S), eccentric crankshaft (S) comprises main shaft (31), drive the eccentric shaft of each piston, connect coupling shaft (G) and the countershaft (33) of adjacent two eccentric shafts, it is characterized in that being provided with jack shaft in coupling shaft (G), one is had at least to be supported by the intermediate bearing (F) arranged in described central diaphragm (M) in described jack shaft,
Described central diaphragm (M) comprises more than one flat board, this flat board comprises two parallel side planes, intermediate bearing (F) be positioned at a side plane central authorities and towards the perforate of opposite side plane, center hole (44) be positioned at opposite side plane central authorities and towards the inside of intermediate bearing (F) and a side plane perforate;
Snubber (46) is provided with, the knee-action of the jack shaft that this snubber (46) is supported by intermediate bearing (F) for restriction between described intermediate bearing (F) and center hole (44);
The gap formed between the internal diameter of the external diameter of described jack shaft and intermediate bearing (F) is more than 2/1000 of the external diameter of jack shaft, and jack shaft and intermediate bearing (F) are contactless state.
5. the rotary compressor of multi cylinder according to claim 4, is characterized in that the rotary compressor of described multi cylinder is applied in air conditioner, refrigerating machine or water heater.
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| CN201110304349.0A CN103032328B (en) | 2011-09-30 | 2011-09-30 | The rotary compressor of multi cylinder |
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| CN201110304349.0A CN103032328B (en) | 2011-09-30 | 2011-09-30 | The rotary compressor of multi cylinder |
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| CN1763374A (en) * | 2004-10-21 | 2006-04-26 | 乐金电子(天津)电器有限公司 | Assembly structure for reducing bearing force of compressor crankshaft |
| CN101372970A (en) * | 2007-08-22 | 2009-02-25 | 泰州乐金电子冷机有限公司 | Sealed compressor |
| CN201771766U (en) * | 2010-08-06 | 2011-03-23 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN201991778U (en) * | 2011-03-09 | 2011-09-28 | 广东美芝制冷设备有限公司 | Baffle structure of variable capacity compressor |
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| CN103032328A (en) | 2013-04-10 |
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