CN103362833A - Cantilever type motor rotor for direct connection centrifugal compressor and direct connection centrifugal compressor - Google Patents
Cantilever type motor rotor for direct connection centrifugal compressor and direct connection centrifugal compressor Download PDFInfo
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- CN103362833A CN103362833A CN2012101050210A CN201210105021A CN103362833A CN 103362833 A CN103362833 A CN 103362833A CN 2012101050210 A CN2012101050210 A CN 2012101050210A CN 201210105021 A CN201210105021 A CN 201210105021A CN 103362833 A CN103362833 A CN 103362833A
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Abstract
The invention discloses a cantilever type motor rotor for a direct connection centrifugal compressor. An impeller mounting part, a front bearing mounting part, a rotor iron core mounting part and a rear bearing mounting part are formed on the rotor sequentially in an axial direction, wherein a rotor iron core is mounted on the rotor iron core mounting part; the external diameter of the rotor iron core is D, and the length of the rotor iron core is L3; and a range of a ratio D/L3 of the external diameter of the rotor iron core to the axial length of the rotor iron core is 0.25-0.35. The invention further discloses the direct connection centrifugal compressor provided with the motor rotor structure. According to the centrifugal compressor, a motor is adopted to drive an impeller to rotate directly; a speed-increasing gearbox is removed; the centrifugal compressor has the advantages of high rated efficiency, small size, light weight and high energy efficiency; a rotating shaft structure is optimized; and the compressor can keep lower vibration at a high rotating speed.
Description
Technical field
The present invention relates to the compressor for 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 adopts fixed frequently AC motor or frequency-conversion alternating current motor usually, by overdrive gear rotating speed is brought up to design speed, and impeller is rotated the incoming flow air work, thereby improves gas pressure.The compressor arrangement of this routine has the following disadvantages: (1) has increased the mechanical loss of compressor owing to the intermediate gear speedup box, thereby increases the compressor power consumption, affects unit performance; (2) existence of gear-box increases the form structure of compressor greatly, so that casing seems is huge, heavy, cost also increases thereupon; (3) because the rotating speed of centrifugal compressor is very high, and gear up process noise is very large, therefore the noise of conventional centrifuge is commonly about 93 decibels, so that it needs additionally to increase soundproof measures in engineering is used, 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, because compressor impeller and motor share a rotating shaft, 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 having 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 be balanced, and this has further aggravated again the vibration of compressor.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, as adopt 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 obtains 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 by compressor drum, reduces compressor in the vibration of high rotating speed operating conditions.
In order to realize above-mentioned purpose of the present invention, the technological scheme that adopts is: a kind of direct connection centrifugal compressor cantilever type rotor, described rotor vertically in turn 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 external diameter of rotor iron core is D, 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.
Preferred embodiment as technique scheme, described rotor also is provided with the auxiliary 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 auxiliary thrust disc and main thrust dish, is set to radially-twin shaft axial thrust bearing structure.
As the preferred embodiment of technique scheme, radially described-twin shaft axial thrust bearing is hydrodynamic sliding bearing.
As the preferred embodiment of technique scheme, described rear bearing is set to the radial-axial thrust bearing, thereby forms axially two thrust bearing structures of compressor drum.
As the preferred embodiment of technique scheme, the arm length that is positioned at the rotor of impeller assembly department one end is L1, and the forward and backward bearing of rotor centre of support 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, 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 auxiliary 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 auxiliary 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.
As the preferred embodiment of technique scheme, between described the first impeller and described the second impeller, be provided with the tonifying Qi cavity, described tonifying Qi cavity is communicated with refrigerant channel between described the first impeller and described the second impeller.
The present invention also further relates to a kind of straight connection type centrifugal compressor, and it has each described rotor such as claim 1-12, and described compressor has one or more levels impeller.
As the preferred embodiment of technique scheme, described multi-stage impeller is arranged on the cantilever end of rotor in the same way in turn.
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, described motor is the DC frequency-changing synchronous machine, and its power is between 150kw to 800kw.
Compressor of the present invention utilizes the motor direct-drive vane rotary, 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 not being 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 compacter.
(2) owing to having adopted the rotor structure that can suppress to vibrate, greatly optimized the vibration performance of compressor, 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 one capacity controlling gears, 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-the first impeller, 18-the 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:
Figure 1 shows that the structural representation of two stage centrifugal compressor, centrifugal compressor mainly is comprised of casing 3, housing 1, the first impeller 17, the second impeller 18, motor 9 and positioning device, and wherein, casing 3 is casting structure, is used for the most of component of fixing 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 fixed energies controlling mechanism 2 and steering flow direction is connected with casing 3, and housing 1 forms the sealing chamber with intakeport and relief opening with casing 3.
Be provided with the first impeller 17 and the second impeller 18, the first impellers 17 are arranged on the intakeport side enclosed cavity is indoor, the second impeller 18 adjacent the first impellers 17 arrange, the first impeller 17 be connected 18 in impeller and connect by rigidity lining 16.The first impeller 17 is unshrouded impeller, at impeller arranged outside wheel cap 12, forms accurate closed flow to cooperate impeller, and gas is carried out compressed action.The first impeller 17 exit flows guide to 18 imports of the second impeller by bend 13, return channel 14.Return channel 14 at the second impeller 18 front ends processes middle air supply passage 15, and joins by the economizer of the flange on the casing 3 and unit, when compressor operating, by 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 it is indoor that its rotor 8 stretches into enclosed cavity from the axis hole on the casing 3.The first impeller 17 and the second impeller 18 hot chargings are on rotor 8, and lock by 11 pairs of the first impellers 17 of locking nut, locking nut 11 hand of spirals and vane rotary opposite direction, make impeller when High Rotation Speed, nut is more fastening, guarantees the stability of motor 9 direct impeller High Rotation Speeds.In the present embodiment, impeller is 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 the 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 being 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 produces in the gear-driven situation.Forward and backward bearing all wraps the radial-axial thrust bearing that possesses simultaneously radial support and axial thrust function.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-the twin shaft axial thrust bearing usually is positioned near impeller one end, also can adopt two thrust bearing structures, namely the radial-axial thrust bearing is all adopted at rotor 8 two ends.Because the present embodiment gearless speedup structure, be the axial force that balance vane rotary better brings, the two ends of rotating shaft respectively arrange a radial-axial thrust bearing, and namely two selection structures make structure more reliable.
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 stably requirement of rotor operation, integral structure characteristic to rotor distributes as follows: L:850mm～1650mm, D: φ 100mm～φ 400mm, L1:245～285mm, L4:600～750mm, each dimension scale relation is 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 auxiliary 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, and wherein: d4 is 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 overall length, L1 is cantilever segment length, L2 is motor fore bearing assembly department width, L3 is rotor core length, and L4 is bearings centre distance, and D is the rotor iron core external diameter, d1 is the auxiliary thrust disc external diameter of rotor, d2 is motor fore bearing root diameter, and d3 is rotor main thrust dish external diameter, and d4 is motor rear bearing assembly department diameter;
The effect of each section is as follows:
Cantilever segment L1: for guaranteeing that the firsts and seconds impeller shaft is to the design of installation dimension and optimization impeller channel.If the undersized meeting of L1 causes impeller shaft to reduce to installation dimension, affect impeller channel and overall construction design, make impeller performance not reach designing requirement, if L1 is oversize, with increasing the length of cantilever segment, increase the amount of deflection of cantilever segment, and then affect the stability of rotor operation.
Motor fore bearing assembly department width L2: be used for guaranteeing the bearing capacity of bearing, too small, bearing capacity descends and do not reach requirement, and is excessive, can cause rotor length to lengthen, and affects operation stability.
Rotor core length L3: mutually optimize 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: determine two bearings in epitrochanterian support scope, this scope can affect 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 because turning the excessive centrifugal force that causes under the high rotating speed of iron core external diameter to the impact of iron core, because the rotor iron core external diameter is larger, suffered centrifugal force is just larger, critical speed of rotation can be affected, and then affects the smooth operation of rotor.
Auxiliary thrust disc outside diameter d 1: guarantee that on the one hand impeller passes through to connect the required area of transmitting torque without key, restricts the generation that cantilever segment perturbs on the other hand.When cantilever segment perturbed, the oil film kinetic pressure by non axial thrust direction restricted the generation that cantilever segment perturbs, and brought bearing and axle journal edge abrasion after avoiding the amount of deflection of axle to surpass limit value, thereby reached the purpose that improves the rotor rigidity.
In addition, cantilever segment L1: for guaranteeing that the firsts and seconds impeller shaft is to the design of installation dimension and optimization impeller channel.If the undersized meeting of L1 causes impeller shaft to reduce to installation dimension, affect impeller channel and overall construction design, make impeller performance not reach designing requirement, if L1 is oversize, with increasing the length of cantilever segment, increase the amount of deflection of cantilever segment, and then affect the stability of rotor operation.
Motor fore bearing assembly department width L2: be used for guaranteeing the bearing capacity of bearing, too small, bearing capacity descends and do not reach requirement, and is excessive, can cause rotor length to lengthen, and affects operation stability.
Rotor core length L3: mutually optimize 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: determine two bearings in epitrochanterian support scope, this scope can affect 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 because turning the excessive centrifugal force that causes under the high rotating speed of iron core external diameter to the impact of iron core, because the rotor iron core external diameter is larger, suffered centrifugal force is just larger, critical speed of rotation can be affected, and then affects the smooth operation of rotor.
Auxiliary thrust disc outside diameter d 1: guarantee that on the one hand impeller passes through to connect the required area of transmitting torque without key, restricts the generation that cantilever segment perturbs on the other hand.When cantilever segment perturbed, the oil film kinetic pressure by non axial thrust direction restricted the generation that cantilever segment perturbs, and brought bearing and axle journal edge abrasion after avoiding the amount of deflection of axle to surpass limit value, thereby reached the purpose that improves the rotor rigidity.
The capacity controlling gear 2 that is used for the adjusting gas flow size is installed in the intakeport side of sealing chamber, and is assemblied on the housing 1 by fastening piece.Capacity controlling gear 2 mainly is comprised of a plurality of blades 4 and vane drive mechanism, and 4 rotations change flow area thereby vane drive mechanism is according to the load drive vane.When the air-conditioning system load reduces, reduce first the rotating speed of motor 9, when motor 9 rotating speeds reach liminal value, reduce again blade 4 apertures of capacity controlling gear 2, reduce the flow that enters sealing chamber intakeport; When the air-conditioning system load increases, first the blade 4 of capacity controlling gear 2 is opened to maximum, increased the incoming flow gas flow that enters described sealing chamber intakeport, when the incoming flow gas flow transfers to maximum, improve again the rotating speed of motor 9 by frequency variator.Make like this blade 4 apertures of capacity controlling gear 2 remain on a larger aperture, reduce owing to the too small restriction loss that brings of blade 4 apertures, improve the comprehensive part load performance of compressor.
The structure of the rotor of the present embodiment as shown in Figure 2, rotor comprises rotor 8, impeller and rotor iron core 804, the left end of rotor 8 has impeller assembly department 801, the first impeller 17, lining 16 and the second impeller 18 are installed on the impeller assembly department 801, the left end of the first impeller 17 contacts with locking nut 11, the right-hand member of the second impeller 18 contacts with step 802 on being formed on rotor 8, by the effect of locking nut 11 with step 802, the first impeller 17 and the second impeller 18 are 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 for installing radially-the fore bearing assembly department 805 of twin shaft axial thrust bearing 7 and be used for installing the rear bearing assembly department 806 of radial-axial thrust bearing 10.
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 that determines the compressor resonant frequency, if the optimal design by rotor structure, make the resonant frequency of compressor away from its frequency of okperation, can guarantee that then compressor keeps lower level of vibration when running up.By analyzing, the impeller assembly department of rotor 8 and rotor iron core assembly department 803 places are the key positions that determine the 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 larger 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 diameter D that selects rotor iron core 804 and the ratio D/L3 of length L 3 are as main Optimal Parameters.
Based on the said structure parameter, compressor with the described structure of the present embodiment is tested, used structural parameter D/L3 to be respectively 0.19 in the test, 0.31,0.77 rotor, according to GB GB/T18430.1-2007 maximum load water temperature, compressor is respectively 6000,7000,9000,10500, move under the rotating speed of 12000rpm, by vibroscope test compression machine sucking pipe, outlet pipe, the motor front support leg, the motor rear supporting leg, the Vibration Condition at place in before the motor and in behind the motor, outcome record is in table 1, table 2, in the table 3, wherein table 1 is that D/L3 is 0.19 test result, 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), vibration begins to strengthen when rotating speed is 9000rpm, larger 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), Vibration Condition is that 0.77 rotor is good than adopting D/L3 obviously, maximum vibration is 0.026mm, be 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 illustrate; When to adopt D/L3 be 0.31 rotor (referring to table 2), vibrate larger place and be in motor leg and suction, outlet pipe place, but numerical value be much smaller with respect to GB specified value 0.03mm, illustrates 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 namely the ratio of the D outer diameter of the rotor iron core of the present embodiment rotor and length L 3 gets 0.31.
Be specific embodiments of the invention only below, do not limit protection scope of the present invention with this; Not violating any replacement and the improvement of doing on the basis of the present invention, all belong to protection scope of the present invention.
Claims (14)
1. direct connection centrifugal compressor cantilever type rotor, described rotor vertically in turn 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 external diameter of rotor iron core is D, 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.
2. rotor according to claim 1, it is characterized in that: described rotor also is provided with the auxiliary 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 auxiliary thrust disc and main thrust dish, is set to radially-twin shaft axial thrust bearing structure.
3. rotor according to claim 2, it is characterized in that: radially described-twin shaft axial thrust bearing is hydrodynamic sliding bearing.
4. rotor according to claim 3, it is characterized in that: described 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, it is characterized in that: the arm length that is positioned at the rotor of impeller assembly department one end is L1, and the forward and backward bearing of rotor centre of support is apart from being L4, and wherein the ratio range of L1/L4 is 0.3～0.4.
6. rotor according to claim 5, it is characterized in that: the total length of rotor is L, wherein the ratio range of L3/L is 0.35～0.55.
7. rotor according to claim 3, it is characterized in that: fore bearing assembly department diameter is d2, and auxiliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 1.6～1.9.
8. rotor according to claim 7, it is characterized in that: fore bearing assembly department width is L2, wherein the ratio range of the width-diameter ratio L2/d2 of fore bearing is 1.5～1.8.
9. rotor according to claim 3, it 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.
10. rotor according to claim 3, it is characterized in that: fore bearing assembly department diameter is d2, and auxiliary thrust disc external diameter is d1, and wherein the ratio range of d1/d2 is 0.9～1.1.
11. rotor according to claim 10 is characterized in that: rear bearing assembly department diameter is d4, and wherein the ratio range of d4/d2 is 1.6～1.9.
12. a straight connection type centrifugal compressor, it has each described rotor such as claim 1-11, and described compressor has one or more levels impeller.
13. straight connection type centrifugal compressor according to claim 12 is characterized in that: described multi-stage impeller is arranged on the cantilever end of rotor in the same way in turn.
14. according to claim 12 or 13 described straight connection type centrifugal compressors, it is characterized in that: the rotating speed of described rotor is more than 6000 rev/mins, preferably more than 7000 rev/mins, described motor is the DC frequency-changing synchronous machine, and its power is between 150kw to 800kw.
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| CN105226900A (en) * | 2015-10-20 | 2016-01-06 | 上海电气集团上海电机厂有限公司 | A kind of petroleum pipeline variable-frequency control asynchronous motor rotor structure |
| KR20180130860A (en) * | 2017-05-30 | 2018-12-10 | 엘지전자 주식회사 | motor assembly |
| CN110296089A (en) * | 2018-03-23 | 2019-10-01 | Jcbe日本合同会社 | Turbo-compressor and the refrigerator for using the turbo-compressor |
| CN110391718A (en) * | 2017-11-24 | 2019-10-29 | 惠州市卓能电机技术有限公司 | Rotor |
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| CN110296089A (en) * | 2018-03-23 | 2019-10-01 | Jcbe日本合同会社 | Turbo-compressor and the refrigerator for using the turbo-compressor |
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| CN103362833B (en) | 2016-06-08 |
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