CN202510384U - Cantilever type motor rotor for direct connection centrifugal compressors and direct connection centrifugal compressor - Google Patents
Cantilever type motor rotor for direct connection centrifugal compressors and direct connection centrifugal compressor Download PDFInfo
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- CN202510384U CN202510384U CN2012201513260U CN201220151326U CN202510384U CN 202510384 U CN202510384 U CN 202510384U CN 2012201513260 U CN2012201513260 U CN 2012201513260U CN 201220151326 U CN201220151326 U CN 201220151326U CN 202510384 U CN202510384 U CN 202510384U
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Abstract
The utility model discloses a cantilever type motor rotor for direct connection centrifugal compressors. The rotor is composed of an impeller installation portion, a front bearing installation portion, a rotor core installation portion and a rear bearing installation portion which are sequentially arranged along the axial direction of the rotor, a rotor core is installed on the rotor core installation portion, the total length of the rotor is L, the length of a rotor cantilever which is located at one end of the impeller installation portion is L1, and the ratio of the L1 to the L ranges from 0.15 to 0.35. The utility model further relates to a direct connection centrifugal compressor with the cantilever type motor rotor. According to the direct connection centrifugal compressor, a motor is used for directly driving an impeller to rotate, and a gear speed increasing box is omitted, so that the direct connection centrifugal compressor has the advantages of being high in rated efficiency, small, light and high in energy efficiency; and the structure of a rotation shaft is optimized, and accordingly, the compressor keeps small vibration at high rotation speeds.
Description
Technical field
The present invention relates to be used for the compressor of field of air conditioning, relate in particular to a kind of high rotating speed (rotating speed more than 6000 rev/mins) centrifugal compressor and rotor thereof with straight connection type rotating shaft.
Background technique
The centrifugal compressor of existing field of air conditioning, fixed AC motor or frequency-conversion alternating current motor frequently of employing brought up to design speed through overdrive gear with rotating speed usually, and the impeller rotation is to the acting of incoming flow gas, thus the raising gas pressure.Not enough below the compressor arrangement of this routine exists: (1) has increased the mechanical loss of compressor owing to have the intermediate gear speedup box, thereby increases the compressor power consumption, influences unit performance; (2) existence of gear-box increases the form structure of compressor greatly, makes casing seem huge, heavy, and cost also increases thereupon; (3) because the rotating speed of centrifugal compressor is very high, and gear up process noise is very big, therefore the noise of conventional centrifuge is commonly about 93 decibels, makes it in practical applications, need extra increase soundproof measures, causes engineering cost to increase.
In addition; Also have compressor impeller and the direct-connected straight connection type centrifugal compressor of motor shaft, the compressor of this form is because compressor impeller and the shared rotating shaft of motor; Both vibrations superpose in rotating shaft; Cause the vibration of compressor to increase, under high rotating speed, the increase of vibration is particularly evident.Owing to saved overdrive gear, the effect of the opposing axial force that original overdrive gear produces has also disappeared in addition, and the axial force that impeller produces is difficult to obtain balance, and this has further aggravated the vibration of compressor again.In order to suppress the vibration of straight connection type centrifugal compressor under high rotating speed; Existing means are normally improved the positioning device of its rotor, and like employing magnetic suspension bearing and axial thrust bearing etc., but rotor is the main motion parts in the compressor; Vibration performance to compressor plays a key effect; Only depend on and improve its positioning device, and the structural dimensions of rotor is not optimized, the improvement of the vibration performance that is obtained is very limited.
Summary of the invention
One object of the present invention is to improve the efficiency of compressor, reduces its boundary dimension, reduces its weight and noise.
Another object of the present invention is the structure optimization through compressor drum, reduces the vibration of compressor at high rotating speed operating conditions.
In order to realize above-mentioned purpose of the present invention; The technological scheme that is adopted is: a kind of direct connection centrifugal compressor is used the cantilever type rotor; Said rotor vertically in order be formed with impeller assembly department, fore bearing assembly department, rotor iron core assembly department, rear bearing assembly department, rotor iron core is installed on the rotor iron core assembly department, it is characterized in that: the arm length that is positioned at the rotor of impeller assembly department one end is L1; The total length of rotor is L, and wherein the ratio range of L1/L is 0.15～0.35.
Preferred embodiment as technique scheme; Said rotor also is provided with the auxilliary thrust disc of rotor between impeller assembly department and fore bearing assembly department; Between fore bearing assembly department and rotor iron core assembly department, also be provided with rotor main thrust dish; The motor fore bearing is installed in the fore bearing assembly department place between auxilliary thrust disc and main thrust dish, is set to biradial-twin shaft axial thrust bearing structure.
As the preferred embodiment of technique scheme, said biradial-twin shaft axial thrust bearing is a hydrodynamic sliding bearing.
As the preferred embodiment of technique scheme, said rear bearing is set to biradial-axial thrust bearing structure, thereby forms axially two thrust bearing structures of compressor drum.
As the preferred embodiment of technique scheme, the centre of support of the forward and backward bearing of rotor is apart from being L4, and wherein the ratio range of L1/L4 is 0.3～0.4.
As the preferred embodiment of technique scheme, the external diameter of rotor iron core is D, and the length of rotor iron core is L3, and the scope of the ratio D/L3 of the external diameter of rotor iron core and rotor iron core axial length is 0.25～0.35.
As the preferred embodiment of technique scheme, wherein the ratio range of L3/L is 0.35～0.55.
As the preferred embodiment of technique scheme, fore bearing assembly department diameter is d2, and auxilliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 1.6～1.9.
As the preferred embodiment of technique scheme, fore bearing assembly department width is L2, and wherein the ratio range of the width-diameter ratio L2/D2 of fore bearing is 1.5～1.8.
As the preferred embodiment of technique scheme, fore bearing assembly department diameter is d2, and main thrust dish external diameter is d3, and wherein the ratio range of d3/d2 is 1.8～2.5.
As the preferred embodiment of technique scheme, fore bearing assembly department diameter is d2, and auxilliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 0.9～1.1.
As the preferred embodiment of technique scheme, fore bearing assembly department diameter is d2, and rear bearing assembly department diameter is d4, and wherein the ratio range of d4/d2 is 1.6～1.9.
The present invention also further relates to a kind of straight connection type centrifugal compressor, and it has each described rotor like claim 1-12, and said compressor has one or more levels impeller.
As the preferred embodiment of technique scheme, said multi-stage impeller is arranged on the cantilever end of rotor in the same way in order.
As the preferred embodiment of technique scheme, the rotating speed of its rotor is more than 6000 rev/mins, and preferably more than 7000 rev/mins, said motor is the DC frequency-changing synchronous machine, and its power is between 150kw to 800kw.
Compressor of the present invention utilizes the rotation of motor direct-drive impeller, has saved gear speedup case, simultaneously the structure of straight connection type rotor is optimized, and compared with prior art, has the following advantages:
(1) owing to there is not the overdrive gear structure, eliminates the geared machine loss, improved the efficiency of centrifuge compressor; The compressor operating noise is very low, generally at 70～80 decibels; Compressor contour structure size and weight reduce greatly, and overall structure is compact more.
(2) owing to adopted the rotor structure that can suppress to vibrate, optimized the vibration performance of compressor greatly, very little in high-revolving vibration values, far below the 0.03mm of national Specification.
Description of drawings
Fig. 1 is the structural representation of bipolar impeller centrifugal compressor;
Fig. 2 is the structural representation of rotor;
Fig. 3 is the structural representation of single-stage impeller centrifugal compressor.
Description of reference numerals: 1-housing, 2-capacity controlling gear, 3-casing, 4-blade, 5-seal arrangement, 6-impeller, 7-fore bearing, 8-rotor, 9-motor, 10-rear bearing, 11-locking nut, 12-wheel cap, 13-bend, 14-return channel, 15-air supply passage, 16-lining, 17-first impeller, 18-second impeller, 801-impeller construction section, 802-step, 803-iron core assembly department, 804-rotor iron core, 805-fore bearing assembly department, 806-rear bearing assembly department.
Embodiment
Below in conjunction with accompanying drawing embodiments of the invention are elaborated:
Shown in Figure 1 is the structural representation of twin-stage centrifugal compressor, and centrifugal compressor mainly is made up of casing 3, housing 1, first impeller 17, second impeller 18, motor 9 and positioning device, and wherein, casing 3 is a casting structure, is used for fixing the most of component of compressor.Casing 3 is cast as one gas collector (spiral case), and casing 3 built-in asphalt channel and gas channels.This casing 3 compact structures, easy to process.The housing 1 that is used for fixing capacity controlling gear 2 and steering flow direction is connected with casing 3, and housing 1 forms the closed chamber with intakeport and relief opening with casing 3.
In closed chamber, be provided with first impeller 17 and second impeller, 18, the first impellers 17 are arranged on air-breathing oral-lateral, second impeller, 18 adjacent first impellers 17 are provided with, and 18 in first impeller 17 and second impeller are connected through rigidity lining 16.First impeller 17 is a unshrouded impeller, at impeller arranged outside wheel cap 12, forms accurate closed flow to cooperate impeller, and gas is carried out compressed action.First impeller, 17 exit flows guide to 18 imports of second impeller through bend 13, return channel 14.Return channel 14 at second impeller, 18 front ends processes middle air supply passage 15, and joins through the economizer of flange on the casing 3 and unit, when compressor operating, through middle tonifying Qi effect, reduces secondary import enthalpy, and the whole wasted work of compressor is reduced.
Motor 9 is installed on the casing 3, and its rotor 8 stretches in the closed chamber from the axis hole on the casing 3.First impeller 17 and second impeller, 18 hot chargings are on rotor 8; And lock through 11 pairs first impellers 17 of locking nut; Locking nut 11 hand of spirals are opposite with the impeller sense of rotation; Make impeller when high speed rotating, nut is more fastening, guarantees the stability of motor 9 direct impeller high speed rotating.In the present embodiment, impeller is a two-stage, but impeller also can be for one-level (as shown in Figure 3) or more than the two-stage.Impeller can be unshrouded impeller, also can be double shrouded wheel.
The motor 9 of present embodiment is the DC frequency-changing synchronous machine, and its power is between 150kW to 800kW, and rotating speed belongs to the high-power frequency conversion category greater than 10000 rev/mins.Owing to be synchronous machine, revolutional slip is 0, so rated efficiency is high.
Forward and backward bearing is used for there be not the axial force that the balance impeller is produced under the gear-driven situation.Forward and backward bearing all wraps the radial-axial thrust bearing that possesses radial support and axial thrust function simultaneously.The radial-axial thrust bearing both can be sliding bearing, also can be rolling bearing.The radial-axial thrust bearing both can be in rotor 8 one-sided settings; Be that rotor 8 one ends adopt radially-the twin shaft axial thrust bearing; The other end adopts radial bearing; Radially-and the twin shaft axial thrust bearing usually is positioned near impeller one end, also can adopt the two thrust bearings in both sides, and promptly the radial-axial thrust bearing is all adopted at rotor 8 two ends.Because present embodiment gearless speedup structure, be the axial force that balance impeller rotation is better brought, the two ends of rotating shaft respectively are provided with a radial-axial thrust bearing, and promptly two selection structures make structure more reliable.
The capacity controlling gear 2 that is used for adjustments of gas flow size is installed in the air-breathing oral-lateral of closed chamber, and is assemblied on the housing 1 through fastening piece.Capacity controlling gear 2 mainly is made up of with vane drive mechanism a plurality of blades 4, and 4 rotations change flow area thereby vane drive mechanism is according to the load driven vane.When the air-conditioning system load reduces, reduce the rotating speed of motor 9 earlier, when motor 9 rotating speeds reach liminal value, reduce blade 4 apertures of capacity controlling gear 2 again, reduce the flow that gets into the closed chamber intakeport; When the air-conditioning system load increases, open the blade 4 of capacity controlling gear 2 to maximum earlier, increase the incoming flow gas flow that gets into said closed chamber intakeport, when the incoming flow gas flow transfers to maximum, improve the rotating speed of motor 9 again through frequency variator.Make blade 4 apertures of capacity controlling gear 2 remain on a bigger aperture like this, reduce, improve the comprehensive part load performance of compressor owing to the too small restriction loss that brings of blade 4 apertures.
The structure of rotor is as shown in Figure 2; Rotor comprises rotor 8, impeller and rotor iron core 804, and the left end of rotor 8 has impeller assembly department 801, the first impellers 17, lining 16 and second impeller 18 and is installed on the impeller assembly department 801; The left end of first impeller 17 contacts with locking nut 11; The right-hand member of second impeller 18 contacts with step 802 on being formed on rotor 8, through the effect of locking nut 11 with step 802, first impeller 17 and second impeller 18 is locked on the axial direction of rotor 8.The part that rotor 8 is positioned at motor 9 has rotor iron core assembly department 803, and rotor iron core 804 is fixedly mounted on the rotor iron core assembly department 803, and together rotates with rotor 8.Also have on the rotor 8 and be used to install radially-fore bearing assembly department of twin shaft axial thrust bearing 7 805 and the rear bearing assembly department 806 that is used to install radial-axial thrust bearing 10.
The rotor profile adopts slim-lined construction, effectively reduces the desired structural strength of rotor material, and the motor profile is also smaller and more exquisite simultaneously.
For guaranteeing that rotor can reach design speed n≤0.8n
cCritical speed of rotation; With away from critical speed of rotation, make rotor operation requirement stably, the integral structure characteristic of rotor is distributed as follows: L:850mm～1650mm; D: φ 100mm～φ 400mm; L1:245～285mm, L4:600～750mm, each dimension scale concerns as follows: rotor iron core appearance proportion: D/L3:0.25～0.35; Arm length and bearings centre distance ratio L1/L4:0.3～0.4; The relative external diameter ratio of auxilliary thrust disc: d1/d2:1.6～1.9; Motor fore bearing width-diameter ratio L2/d2:1.5～1.8; The relative external diameter ratio of main thrust dish: d3/d2:1.8～2.5; Front and back bearings is installed not the relative external diameter of assembly department than d4/d2:0.9～1.1, wherein: d4 is a motor rear bearing assembly department diameter; Cantilever segment relative length ratio: L1/L:0.15～0.35; Iron core relative length ratio: L3/L:0.35～0.55.Wherein: L is the rotor length overall, and L1 is a cantilever segment length, and L2 is a motor fore bearing assembly department width; L3 is a rotor core length, and L4 is a bearings centre distance, and D is the rotor iron core external diameter; D1 is the auxilliary thrust disc external diameter of rotor; D2 is a motor fore bearing root diameter, and d3 is a rotor main thrust dish external diameter, and d4 is a motor rear bearing assembly department diameter;
The effect of each section is following:
Cantilever segment L1: for guaranteeing that the firsts and seconds impeller shaft is to installation dimension and the design of optimizing impeller channel.If the undersized meeting of L1 causes impeller shaft to reduce to installation dimension, influence impeller channel and overall construction design, make impeller performance not reach designing requirement; If L1 is oversize; With the length that increases cantilever segment, increase the amount of deflection of cantilever segment, and then influence the stability of rotor operation.
Motor fore bearing assembly department width L2: be used to guarantee the bearing capacity of bearing, too small, bearing capacity descends and do not reach requirement, and is excessive, can cause the rotor length lengthening, influences operation stability.
Rotor core length L3: optimize each other with the rotor iron core external diameter, guarantee the compressor operating power demand, crossing conference increases cost, and the low load with strong power phenomenon can occur, too small, does not reach power demand.
Bearings centre distance L4: the decision two bearings is in epitrochanterian support scope, and this scope can influence the stress of whole rotor under bearings.Too small, the rotor first critical speed is descended, do not reach design speed stable operation requirement, that is: n≤0.8n
cExcessive, can cause the corresponding increase of other length dimension, cost also can increase.
The rotor iron core D outer diameter: L optimizes jointly with rotor core length; Make power of motor reach requirement on the one hand; Avoid on the other hand that the iron core external diameter is excessive to cause that centrifugal force is to the influence of iron core under the high rotating speed because of changeing, because the rotor iron core external diameter is big more, suffered centrifugal force is just big more; Critical speed of rotation can be affected, and then influences the smooth operation of rotor.
Auxilliary thrust disc outside diameter d 1: guarantee that on the one hand impeller does not connect the required area of transmitting torque through there being key, restricts the generation that cantilever segment is scratched on the other hand.When cantilever segment was scratched, the oil film kinetic pressure through non axial thrust direction restricted the generation that cantilever segment is scratched, brought bearing and axle journal edge abrasion after avoiding the amount of deflection of axle to surpass limit value, thereby reached the purpose of raising rotor rigidity.
In addition, cantilever segment L1: for guaranteeing that the firsts and seconds impeller shaft is to installation dimension and the design of optimizing impeller channel.If the undersized meeting of L1 causes impeller shaft to reduce to installation dimension, influence impeller channel and overall construction design, make impeller performance not reach designing requirement; If L1 is oversize; With the length that increases cantilever segment, increase the amount of deflection of cantilever segment, and then influence the stability of rotor operation.
Motor fore bearing assembly department width L2: be used to guarantee the bearing capacity of bearing, too small, bearing capacity descends and do not reach requirement, and is excessive, can cause the rotor length lengthening, influences operation stability.
Rotor core length L3: optimize each other with the rotor iron core external diameter, guarantee the compressor operating power demand, crossing conference increases cost, and the low load with strong power phenomenon can occur, too small, does not reach power demand.
Bearings centre distance L4: the decision two bearings is in epitrochanterian support scope, and this scope can influence the stress of whole rotor under bearings.Too small, the rotor first critical speed is descended, do not reach design speed stable operation requirement, that is: n≤0.8n
cExcessive, can cause the corresponding increase of other length dimension, cost also can increase.
The rotor iron core D outer diameter: L optimizes jointly with rotor core length; Make power of motor reach requirement on the one hand; Avoid on the other hand that the iron core external diameter is excessive to cause that centrifugal force is to the influence of iron core under the high rotating speed because of changeing, because the rotor iron core external diameter is big more, suffered centrifugal force is just big more; Critical speed of rotation can be affected, and then influences the smooth operation of rotor.
Auxilliary thrust disc outside diameter d 1: guarantee that on the one hand impeller does not connect the required area of transmitting torque through there being key, restricts the generation that cantilever segment is scratched on the other hand.When cantilever segment was scratched, the oil film kinetic pressure through non axial thrust direction restricted the generation that cantilever segment is scratched, brought bearing and axle journal edge abrasion after avoiding the amount of deflection of axle to surpass limit value, thereby reached the purpose of raising rotor rigidity.
In the compressor operation process, along with the raising of rotating speed, rotational frequency is near its resonant frequency, and compressor has the trend of the resonance of producing, the vibration aggravation.And rotor is the main motion parts in the compressor; Its physical dimension is the principal element of decision compressor resonant frequency; If optimal design through rotor structure; The resonant frequency that makes compressor can guarantee then that away from its frequency of okperation compressor keeps lower level of vibration when running up.Through analyzing; The impeller assembly department of rotor 8 and rotor iron core assembly department 803 places are key positions of decision compressor resonant frequency; Because this two position is separately installed with impeller and rotor iron core; The quality of rotor mainly concentrates on this two positions, and the diameter of rotor iron core is bigger than other positions of rotor, and the rotary inertia of rotor mainly is this position.For these reasons, when optimizing the physical dimension of rotor, the ratio L1/L of the diameter D that selects rotor iron core 804 for use and the ratio D/L3 of length L 3 and cantilever segment length L 1 and rotor total length L is as main parameters optimization.
Based on the said structure parameter; Compressor to having the described structure of present embodiment is tested; Used structural parameter D/L3 to be respectively 0.19,0.31,0.77 rotor in the test; According to GB GB/T18430.1-2007 maximum load water temperature, compressor respectively 6000,7000,9000,10500, operation under the rotating speed of 12000rpm, through the vibration situation at place in before vibroscope test compression machine sucking pipe, outlet pipe, motor front support leg, motor rear supporting leg, the motor and in behind the motor; Outcome record is in table 1, table 2, table 3; Wherein table 1 is that D/L3 is 0.19 test result, and table 2 is that D/L3 is 0.31 test result, and table 3 is that D/L3 is 0.77 test result.
Table 1
Table 2
Table 3
From test result, when to adopt D/L3 be 0.77 rotor (referring to table 3), rotating speed during for 9000rpm vibration begin to strengthen; Bigger place is in leg place, motor front and back; When rotating speed was 12000rpm, motor rear supporting leg vibration values was 0.032, surpassed GB specified value 0.03mm; When to adopt D/L3 be 0.17 rotor (referring to table 1); The vibration situation is that 0.77 rotor is good than adopting D/L3 obviously, and maximum vibration is 0.026mm, is in motor front end neutral position and motor rear supporting leg place; Do not surpass GB specified value 0.03mm; But rotating speed is when 10500rpm, and vibration still has obvious increase phenomenon, and there is the trend of resonance in the system at this moment of explain; When to adopt D/L3 be 0.31 rotor (referring to table 2), vibrate bigger place and be in motor leg and suction, outlet pipe place, but numerical value be much little with respect to GB specified value 0.03mm, explains that compressor is more steady at the lower rotor part that runs up; Therefore the physical dimension of rotor is taken as optimum value at this moment, and promptly the ratio of the D outer diameter of the rotor iron core of present embodiment rotor and length L 3 gets 0.31.
More than be merely specific embodiment of the present invention, do not limit protection scope of the present invention with this; Not violating any replacement and the improvement of being done on the basis of the present invention, all belong to protection scope of the present invention.
Claims (15)
1. a direct connection centrifugal compressor is used the cantilever type rotor; Said rotor vertically in order be formed with impeller assembly department, fore bearing assembly department, rotor iron core assembly department, rear bearing assembly department; Rotor iron core is installed on the rotor iron core assembly department; It is characterized in that: the total length of rotor is L, and the arm length that is positioned at the rotor of impeller assembly department one end is L1, and wherein the ratio range of L1/L is 0.15～0.35.
2. rotor according to claim 1; It is characterized in that: said rotor also is provided with the auxilliary thrust disc of rotor between impeller assembly department and fore bearing assembly department; Between fore bearing assembly department and rotor iron core assembly department, also be provided with rotor main thrust dish; The motor fore bearing is installed in the fore bearing assembly department place between auxilliary thrust disc and main thrust dish, is set to radially-twin shaft axial thrust bearing structure.
3. rotor according to claim 2 is characterized in that: radially said-twin shaft axial thrust bearing is a hydrodynamic sliding bearing.
4. rotor according to claim 3 is characterized in that: said rear bearing is set to the radial-axial thrust bearing, thereby forms axially two thrust bearing structures of compressor drum.
5. rotor according to claim 4 is characterized in that: the forward and backward bearings centre distance of rotor is L4, and wherein the ratio range of L1/L4 is 0.3～0.4.
6. rotor according to claim 5 is characterized in that: the external diameter of rotor iron core is D, and the length of rotor iron core is L3, and the scope of the ratio D/L3 of the external diameter of rotor iron core and rotor iron core axial length is 0.25～0.35.
7. rotor according to claim 6 is characterized in that: wherein the ratio range of L3/L is 0.35～0.55.
8. rotor according to claim 3 is characterized in that: fore bearing assembly department diameter is d2, and auxilliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 1.6～1.9.
9. rotor according to claim 8 is characterized in that: fore bearing assembly department width is L2, and wherein the ratio range of the width-diameter ratio L2/d2 of fore bearing is 1.5～1.8.
10. rotor according to claim 3 is characterized in that: fore bearing assembly department diameter is d2, and main thrust dish external diameter is d3, and wherein the ratio range of d3/d2 is 1.8～2.5.
11. rotor according to claim 3 is characterized in that: fore bearing assembly department diameter is d2, and auxilliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 0.9～1.1.
12. rotor according to claim 11 is characterized in that: fore bearing assembly department diameter is d2, and rear bearing assembly department diameter is d4, and wherein the ratio range of d4/d2 is 1.6～1.9.
13. a straight connection type centrifugal compressor, it has each described rotor like claim 1-12, and said compressor has one or more levels impeller.
14. straight connection type centrifugal compressor according to claim 13 is characterized in that: said multi-stage impeller is arranged on the cantilever end of rotor in the same way in order.
15. according to claim 13 or 14 described straight connection type centrifugal compressors; It is characterized in that: the rotating speed of said rotor is more than 6000 rev/mins; Preferably more than 7000 rev/mins, said motor is the DC frequency-changing synchronous machine, and its power is between 150kw to 800kw.
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| CN2012201513260U CN202510384U (en) | 2012-04-02 | 2012-04-02 | Cantilever type motor rotor for direct connection centrifugal compressors and direct connection centrifugal compressor |
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| CN2012201513260U CN202510384U (en) | 2012-04-02 | 2012-04-02 | Cantilever type motor rotor for direct connection centrifugal compressors and direct connection centrifugal compressor |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362850A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | Cantilever type motor rotor for direct connection centrifugal compressor and direct connection centrifugal compressor |
| CN108431426A (en) * | 2015-06-12 | 2018-08-21 | 创科（澳门离岸商业服务）有限公司 | Tube-axial fan air blower |
| CN110094352A (en) * | 2019-06-19 | 2019-08-06 | 湖南联诚轨道装备有限公司 | A kind of high-speed fan shafting structure and its assemble method |
| CN110173443A (en) * | 2019-04-18 | 2019-08-27 | 西安热工研究院有限公司 | The overcritical working medium semi-open type centrifugal compressed device and method of micro volume flow |
-
2012
- 2012-04-02 CN CN2012201513260U patent/CN202510384U/en not_active Withdrawn - After Issue
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103362850A (en) * | 2012-04-02 | 2013-10-23 | 珠海格力电器股份有限公司 | Cantilever type motor rotor for direct connection centrifugal compressor and direct connection centrifugal compressor |
| CN103362850B (en) * | 2012-04-02 | 2015-11-25 | 珠海格力电器股份有限公司 | Direct connection centrifugal compressor cantilever type motor rotor and straight connection type centrifugal compressor |
| CN108431426A (en) * | 2015-06-12 | 2018-08-21 | 创科（澳门离岸商业服务）有限公司 | Tube-axial fan air blower |
| CN108431426B (en) * | 2015-06-12 | 2021-06-18 | 创科（澳门离岸商业服务）有限公司 | Axial flow fan blower |
| CN110173443A (en) * | 2019-04-18 | 2019-08-27 | 西安热工研究院有限公司 | The overcritical working medium semi-open type centrifugal compressed device and method of micro volume flow |
| CN110094352A (en) * | 2019-06-19 | 2019-08-06 | 湖南联诚轨道装备有限公司 | A kind of high-speed fan shafting structure and its assemble method |
| CN110094352B (en) * | 2019-06-19 | 2023-08-29 | 湖南联诚轨道装备有限公司 | High-speed fan shafting structure and assembling method thereof |
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