CN105819333A - Speed reduction unit for traveling crane and cart - Google Patents
Speed reduction unit for traveling crane and cart Download PDFInfo
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- CN105819333A CN105819333A CN201610374135.3A CN201610374135A CN105819333A CN 105819333 A CN105819333 A CN 105819333A CN 201610374135 A CN201610374135 A CN 201610374135A CN 105819333 A CN105819333 A CN 105819333A
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- teeth
- transmission
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C9/00—Travelling gear incorporated in or fitted to trolleys or cranes
- B66C9/14—Trolley or crane travel drives
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Gears, Cams (AREA)
- Retarders (AREA)
Abstract
The invention relates to a speed reduction unit for a traveling crane and a cart. The speed reduction unit comprises a plurality of speed reducers and frequency converters. Each speed reducer is a second-level transmission mechanism and mainly comprises a high-speed shaft, a first gear set, an intermediate shaft, a second gear set and an output shaft, wherein first-level transmission is formed through cooperation of the first gear set, the high-speed shaft and the intermediate shaft, second-level transmission is formed through cooperation of the second gear set, the intermediate shaft and the output shaft, and the second-level transmission mechanism has a transmission effect of a national standard third-level speed reducer. According to the speed reduction unit for the traveling crane and the cart, the second-level transmission speed reducers are adopted, the structure is simple, and the speed reduction unit is not prone to damage under the high-load work condition; and the manufacturing cost is reduced, the transmission efficiency is higher, and production is stabilized.
Description
Technical field
The present invention relates to a kind of travelling crane truck deceleration unit, particularly relate to a kind of on the premise of installation site and installation dimension are constant, the Transform Type design of reductor, increase reductor bearing capacity and shock loading.
Background technology
Reductor is that iron and steel domain heat treatment produces one of visual plant, and in view of the particularity of heat treatment production process, the use of driving becomes the core that main line produces, and uses operating rate to become focus.For 24 round-the-clock operatings of reductor twenty four hours, frequently open, brake and workload is very big, often result in that gear shaft is disconnected, the phenomenon such as gear tooth breakage and off-axis, seriously constrain production security.Meanwhile too increase equipment and spare part cost.Heat treatment yield was the most soaring the most in recent years, further increases reductor and opens frequently, brakes number of times, increase the impact of gear shaft, gear, causing the fatigue load of profile of tooth serious wear and axle to increase, breaking down so easilying lead to reductor.4 reductors used the most on the same stage, if there being a damage, stop production replacing not in time, and the driving load of other 3 reductors certainly will be caused to increase, and causes car body entirety to reverse and gnaw rail phenomenon, serious caused vehicle body frame deformation.Simultaneously when traveling crane weight runs, due to the deformation of crossbeam, gnaw rail phenomenon all the more substantially, gnaw rail phenomenon and cause load impacting when driving resistance and gnaw rail of driving drivewheel, reductor off-axis, broken teeth phenomenon certainly will be caused to occur.If high-speed cruising, more aggravate the generation of this kind of phenomenon.
Summary of the invention
The technical problem to be solved is to provide a kind of deceleration unit improved for above-mentioned prior art, does not damages, increases the service life, reduce cost, steady production under the operating mode ensureing heavy-duty service.
The present invention solves the technical scheme that the problems referred to above are used: a kind of travelling crane truck deceleration unit, including some reductors and converter, described reductor is secondary drive mechanism, mainly include high speed shaft, gear train one, jackshaft, gear train two and output shaft, gear train one coordinates with high speed shaft and jackshaft to constitute first order transmission respectively, and gear train two coordinates with jackshaft and output shaft to constitute second level transmission respectively；
Secondary drive mechanism has the transmission effect of three grades of reductors of GB, and the design parameter of secondary drive mechanism is as follows:
The first order: gear shaft minimum diameter 50mm；
Modulus 4mm；
The number of teeth 17/73；
Helical angle 9 degree；
Tooth justifies 80.344/305.36mm surely；
The second level: gear shaft minimum diameter 90mm；
Modulus 5.5mm；
The number of teeth 16/74；
Helical angle 10 degree；
Tooth justifies 105.28/426.335mm surely；
Head center is away from a=185+255=440mm；
Overall ratio I=19.85.
Single travelling crane truck travelling mechanism includes four reductors and two converters, two corresponding converters of reductor.
Following principle is followed in designing and developing of above-mentioned secondary transmission reductor:
The parameter of electric machine；30kw980rpm；Travelling crane truck travelling mechanism uses four mechanisms to drive, and 2 converters use one drag two form, 2 converter debugging scopes 0---1000rpm.
Working condition and original use three grades of transmission speed reducer bikini installation forms and location dimension constant at the scene, and on the premise of overall ratio is basically unchanged, three grades of driven Designs of reductor of national standard it is modified as non-national standard speed ratio secondary transmission reductor.
One, after reductor remodeling, cabinet design length is constant by former reductor centre-to-centre spacing, and length direction volume increases to maximum space size；Cabinet design height is constant by former reductor installed height mark, and short transverse volume extends downward maximum space size；
Slow speed turbine stage gear wheel directly affects the size of reductor, reduces slow speed turbine stage gear ratio, i.e. reduces slow speed turbine stage gear wheel and contains its size of casing；Increase the gear ratio of high speed level, i.e. increase the size of high speed level gear wheel, reduce and the difference in size of slow speed turbine stage gear wheel.One, design meets and is basically unchanged in reductor installation form and location dimension and overall ratio, increases the mentality of designing of casing；Its two, gears the most at different levels simultaneously bath lubrication.
Two, after reductor remodeling, the gear shaft number of teeth and the individual gears number of teeth and modulus determine
Before remodeling, flimsy three grades of transmission speed reducer speed ratios and centre-to-centre spacing are for design parameter foundation, it then follows gear ratio determines that the number of teeth, centre-to-centre spacing and the number of teeth determine the principle Method of Spreading Design of modulus.
(1) with the front fragile reductor speed ratio used of remodeling for design parameter foundation, it then follows gear ratio determines the number of teeth.
Three grades of transmissions of fragile reductor for using before remodeling change secondary transmission into, require that Transmission Ratio Control meets the design of secondary transmission GB while ± 5% as far as possible and requires that Transmission Ratio Control is ± 4% three grades of transmission GB designs.But due to the maximum body structure size designed according to in-site installation, the gear ratio distribution gear number of teeth it is unsatisfactory for the non-national standard reductor Transmission Ratio Control of the design of GB secondary transmission, i.e. design forming secondary transmission 4.24%.If, gear ratio GB 20, double reduction, carry out gear ratio distribution according to the condition that tooth contact intensity is equal, design gear ratio is 19.957.
In order to make gear drive compact, calculate the number of teeth selecting the little gear of high speed level, close to the minimum number of teeth (with the number of teeth of fragile three grades of transmission speed reducer little gears of high speed level as minimum number of teeth) allowed, it is ensured that do not occur root to cut and (fracture tooth root bending-fatigue strength criterion for hardened face gear transmission tooth root flexural fatigue) the reference design that the number of teeth is the number of teeth, its design rule: gear ratio, equal to number of gear teeth inverse ratio, it is integer that the number of teeth is chosen.
(2) with the front fragile reductor centre-to-centre spacing used of remodeling for design parameter foundation, it then follows centre-to-centre spacing and the number of teeth determine the principle Method of Spreading Design of modulus.
Utilize (1) design secondary transmission reductor number of teeth, keep that three grades of drive centre distancc are constant changes secondary transmission reductor into.Modulus is directly proportional to centre-to-centre spacing, with the number of teeth and being inversely proportional to；When three grades of drive centre distancc are constant, secondary transmission design modulus increases, and the number of teeth reduces；
Module choose when being design of gears, according to Strength co-mputation, check and to determine.The check of modulus intensity is to apply mechanically design formula according to the number of teeth set with modulus, job specification, lubrication consideration etc. to check, depend on manufacturing reason because modulus is arranged, will not remove to produce the gear of a variety of modulus, modulus kind more multi-processing cost is the highest, checking so listing various combination during design, which meets which condition i.e. uses.
Three, the defect that the fragile three grades of transmission speed reducers used before remodeling exist high speed shaft and jackshaft torsion fractures；Design increases high speed shaft, jackshaft diameter, strengthens torsional strength accordingly.
Axle is one of major part of composition reductor, itself requires there are enough strength and stiffness, sufficiently accurate size and higher surface roughness, high hardness is also had with the journal surface at bearing fit, thus material selection should have a higher comprehensive mechanical performance, and bigger impact load can be often born in work.
(1) torsion of fragile three grades of transmission speed reducer high speed shafts and jackshaft fractures, and mainly torsional strenght causes not.By torsional strenght (section factor and cross sectional shape determine) constraints, calculate the transmission moment of axle, the force of periphery of gear, the radial force of gear, the axial force of gear, the material (yield strength converts) of chosen axis, determine the minimum diameter of axle.Here design is that the maximum gauge according to three grades of transmission speed reducer high speed shafts and jackshaft is as secondary transmission reductor high speed shaft and the minimum diameter of jackshaft.
(2) geometry constraint conditions such as the support of axle upper bearing (metal), gear installation position and parts on shaft location, processing request and different part assembling modes are pressed, and on gear shaft, installation bearing is simultaneously by radial force and axial force from amechanical angle, determines structure design and physical dimension and the bearing designation of axle.
(3) according to physical dimension and job requirement, selecting physical constraint, check whether to meet corresponding physical constraint, if being unsatisfactory for, needing countershaft physical dimension to make necessity amendment, until meeting requirement.
(4) after transmission shaft structure size is selected, force analysis, it is starting point from overcoming axial force and radial force, determines the physical dimension of auxiliary component.
Compared with existing three grades of transmission speed reducers, it is an advantage of the current invention that:
1), secondary transmission higher than three grades of transmission efficiencies, for same type reductor, progression reduces transmission efficiency and increases.If secondary transmission efficiency is 98%, then three grades of transmission efficiencies are 96.04%=98% × 98%.
2), modulus increases, high speed shaft diameter increases, jackshaft diameter increases, and strengthens torsional strength accordingly, and its equipment dependability is high.
3), structure design advantages of simple, it is simple to assembly or disassembly.
4), the raising of bearing capacity, gear shock stiffness increase.
5), maintainability strong, interchange level is high, and at a high speed and slow-speed shaft uses double speed to go out, not installed type of belt drive by reductor is affected, for 24 reductors of scene installation, Parts Inventory 2.
6), under specific application target, intensity, rigidity and stability requirement are met.
7), the part stock that the interchangeability such as gear, gear shaft, axle are big, Supply period shortened are reduced.
8), shorten the reductor complete machine production cycle, reduce stock.
9), the size of part, specification simplify unified, greatly reduce number of parts in series.
10), remodeling secondary transmission reductor use after, machine life improve more than 4 times.
Accompanying drawing explanation
Fig. 1 is the structure of these existing three grades of transmission speed reducers；
Fig. 2 is the structure of secondary transmission reductor in the embodiment of the present invention；
In Fig. 1,1.1 high speed shafts, 1.2 gear I, 1.3 jackshaft one, 1.4 gear II, 1.5 jackshaft two, 1.6 gear III, 1.7 output shafts.
Detailed description of the invention
Below in conjunction with accompanying drawing embodiment, the present invention is described in further detail.
As shown in Figure 2, reductor in the present embodiment is secondary drive mechanism, mainly include high speed shaft 1, gear train 1, jackshaft 3, gear train 24 and output shaft 5, gear train 1 coordinates to constitute first order transmission respectively with high speed shaft 1 and jackshaft 3, and gear train 24 coordinates to constitute second level transmission with jackshaft 3 and output shaft 5 respectively.
Above-mentioned reductor parameter；30kw980rpm；Travelling crane truck travelling mechanism uses four mechanisms to drive, and 2 converters use one drag two form, 2 converter debugging scopes 0---1000rpm.
Secondary drive mechanism has the transmission effect of three grades of reductors of GB, and the design parameter of secondary drive mechanism is as follows:
The first order: gear shaft minimum diameter 50mm；
Modulus 4mm；
The number of teeth 17/73；
Helical angle 9 degree；
Tooth justifies 80.344/305.36mm surely；
The second level: gear shaft minimum diameter 90mm；
Modulus 5.5mm；
The number of teeth 16/74；
Helical angle 10 degree；
Tooth justifies 105.28/426.335mm surely；
Head center is away from a=185+255=440mm；
Overall ratio I=19.85；
The method for designing of secondary drive mechanism is as follows:
Power of motor 30Kw, rotating speed 980rpm, centre-to-centre spacing 440mm
One, input shaft design
(1), material selection: 20CrMnTi material coefficient A=98 107, dangerouse cross-section suitably increases 4 5% according to keyway；
(2), the minimum diameter of axle is chosen:
d≥A=33.705mm
This diameter of axle of three grades of reductors is 35m, also meets design requirement；But after onsite application, it is critical section herein, occurs repeatedly rupturing；
Consider and take: input gear axle minimum diameter takes 50mm；
Two, distribution gear ratio
Tentatively distributing gear ratio, gear ratio distribution should be reasonable, meets the work characteristics of transmission, and makes compact conformation, and dimensional structure is uniformly reasonable, will not interfere with between driving parts.Arrange by expansion, consider lubrication and radiating condition, for making two-stage gear wheel diameter similar, as far as possible close to three grades of reductor speed ratios of GB, if different from three grades of transmission speed ratios, should select the scope of converter adjustable speed, the basic speed of service keeping three grades of reductors of GB, contrast GB developed curve obtains: gear ratio I=4.294 × 4.625；
Three, tooth Shape Design
Helical gear is chosen by GB design
(1), choice of material 20CrMnTi takes its strength grade by MQ level quality: yield strength 835MPa, tensile strength 1080MPa；
(2), using the parameter of three grades of reductors of GB as the basic data of transformation 2-level reducer design parameter, combine the on-the-spot frequent statistical analysis a little that repeatedly breaks down, determine centre-to-centre spacing and modulus,
Utilize empirical equation m=(0.007 0.03) a
Wherein: m modulus；A centre-to-centre spacing
Determine the one-level of secondary transmission reductor, two grades of moduluses and centre-to-centre spacing respectively, and ensure 440mm head center away from constant,
There is tooth root phenomenon of rupture when being 3 in second level modulus according to on-the-spot three grades of reductors of GB；
When designing two grades, first order modulus takes m1=4；A is determined in conjunction with at the beginning of above-mentioned empirical equation1=185
Second level modulus takes m1=5.5；A is determined in conjunction with at the beginning of above-mentioned empirical equation1=255
0.021 that coefficient is in 0.007～0.03 is taken in calculating；
Calculating is taken modulus and is preferred series modulus；
Head center is away from 440=185+255；
(3), in view of the stationarity of transmission, in conjunction with the parameter of three grades of reductors of GB, Preliminary design helical angle φ=9 degree；
(4) number of teeth and gear ratio, are determined
Follow number of teeth selection principle: arbitrary tooth is shaped with a minimum number of teeth, for preventing the generation root when gear hobbing from cutting, as far as possible more than minimum number of teeth 17 during selection:
Z1=2aCOSφ/m(i+1)
Z2=Z1i
Wherein: Z1And Z2It it is the number of teeth of one pair of which gear；
A be a pair gear centre away from；
I is the speed ratio Z of a pair gear2/Z1；
Obtain: Z2=73.65 take Z2=73
I1=Z2/Z1=73/17=4.29
If keeping being basically unchanged with three grades of transmission overall ratios 19.57 of GB, then I2=Z3/Z4=19.57/4.29=4.56
For ensureing that 2-level reducer can reach the speed of service of three grades of reductors of GB, and controlling adjustable speed in frequency conversion motor speed adjustable range, overall ratio is adjusted to 19.82, and helical angle φ=10 degree meet secondary gear and distribute,
In like manner two grades draw: Z3=16Z4=74
(5), essence seeks helical angle φ: COS φ=m (Z1+Z2) meet requirement after 2a；
(6) gear compound graduation circular diameter, is determined
Normal module=transverse module × COS φ
Reference diameter=transverse module × number of teeth=(normal module/COS φ) × number of teeth.
The travelling crane truck deceleration unit of said structure uses secondary transmission reductor, simple in construction, under high load capacity operating mode, is hardly damaged, and manufacturing cost is reduced, and transmission efficiency is higher, stabilizes production.
In addition to the implementation, present invention additionally comprises the technical scheme that other embodiments, all employing equivalents or equivalence substitute mode are formed, all should fall within the scope of the hereto appended claims.
Claims (2)
1. a travelling crane truck deceleration unit, including some reductors and converter, it is characterized in that: described reductor is secondary drive mechanism, mainly include high speed shaft, gear train one, jackshaft, gear train two and output shaft, gear train one coordinates with high speed shaft and jackshaft to constitute first order transmission respectively, and gear train two coordinates with jackshaft and output shaft to constitute second level transmission respectively；
Secondary drive mechanism has the transmission effect of three grades of reductors of GB, and the design parameter of secondary drive mechanism is as follows:
The first order: gear shaft minimum diameter 50mm；
Modulus 4mm；
The number of teeth 17/73；
Helical angle 9 degree；
Tooth justifies 80.344/305.36mm surely；
The second level: gear shaft minimum diameter 90mm；
Modulus 5.5mm；
The number of teeth 16/74；
Helical angle 10 degree；
Tooth justifies 105.28/426.335mm surely；
Head center is away from a=185+255=440mm；
Overall ratio I=19.85；
The method for designing of secondary drive mechanism is as follows:
Power of motor 30Kw, rotating speed 980rpm, centre-to-centre spacing 440mm
One, input shaft design
(1), material selection: 20CrMnTi material coefficient A=98 107, dangerouse cross-section suitably increases 4 5% according to keyway；
(2), the minimum diameter of axle is chosen:
d≥A=33.705mm
This diameter of axle of three grades of reductors is 35m, also meets design requirement；But after onsite application, it is critical section herein, occurs repeatedly rupturing；
Consider and take: input gear axle minimum diameter takes 50mm；
Two, distribution gear ratio
Tentatively distributing gear ratio, gear ratio distribution should be reasonable, meets the work characteristics of transmission, and makes compact conformation, and dimensional structure is uniformly reasonable, will not interfere with between driving parts；Arrange by expansion, consider lubrication and radiating condition, for making two-stage gear wheel diameter similar, as far as possible close to three grades of reductor speed ratios of GB, if different from three grades of transmission speed ratios, should select the scope of converter adjustable speed, the basic speed of service keeping three grades of reductors of GB, contrast GB developed curve obtains: gear ratio I=4.294 × 4.625；
Three, tooth Shape Design
Helical gear is chosen by GB design
(1), choice of material 20CrMnTi takes its strength grade by MQ level quality: yield strength 835MPa, tensile strength 1080MPa；
(2), using the parameter of three grades of reductors of GB as the basic data of transformation 2-level reducer design parameter, combine the on-the-spot frequent statistical analysis a little that repeatedly breaks down, determine centre-to-centre spacing and modulus,
Utilize empirical equation m=(0.007 0.03) a
Wherein: m modulus；A centre-to-centre spacing
Determine the one-level of secondary transmission reductor, two grades of moduluses and centre-to-centre spacing respectively, and ensure 440mm head center away from constant,
There is tooth root phenomenon of rupture when being 3 in second level modulus according to on-the-spot three grades of reductors of GB；
When designing two grades, first order modulus takes m1=4；A is determined in conjunction with at the beginning of above-mentioned empirical equation1=185
Second level modulus takes m1=5.5；A is determined in conjunction with at the beginning of above-mentioned empirical equation1=255
0.021 that coefficient is in 0.007～0.03 is taken in calculating；
Calculating is taken modulus and is preferred series modulus；
Head center is away from 440=185+255；
(3), in view of the stationarity of transmission, in conjunction with the parameter of three grades of reductors of GB, Preliminary design helical angle φ=9 degree；
(4) number of teeth and gear ratio, are determined
Follow number of teeth selection principle: arbitrary tooth is shaped with a minimum number of teeth, for preventing the generation root when gear hobbing from cutting, as far as possible more than minimum number of teeth 17 during selection:
Z1=2aCOSφ/m(i+1)
Z2=Z1i
Wherein: Z1And Z2It it is the number of teeth of one pair of which gear；
A be a pair gear centre away from；
I is the speed ratio Z of a pair gear2/Z1；
Obtain: Z2=73.65 take Z2=73
I1=Z2/Z1=73/17=4.29
If keeping being basically unchanged with three grades of transmission overall ratios 19.57 of GB, then I2=Z3/Z4=19.57/4.29=4.56
For ensureing that 2-level reducer can reach the speed of service of three grades of reductors of GB, and controlling adjustable speed in frequency conversion motor speed adjustable range, overall ratio is adjusted to 19.82, and helical angle φ=10 degree meet secondary gear and distribute,
In like manner two grades draw: Z3=16Z4=74
(5), essence seeks helical angle φ: COS φ=m (Z1+Z2) meet requirement after 2a；
(6) gear compound graduation circular diameter, is determined
Normal module=transverse module × COS φ
Reference diameter=transverse module × number of teeth=(normal module/COS φ) × number of teeth.
Travelling crane truck deceleration unit the most according to claim 1, it is characterised in that: single travelling crane truck travelling mechanism includes four reductors and two converters, two corresponding converters of reductor.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610374135.3A CN105819333B (en) | 2016-05-31 | 2016-05-31 | A kind of travelling crane truck deceleration unit |
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| CN201610374135.3A CN105819333B (en) | 2016-05-31 | 2016-05-31 | A kind of travelling crane truck deceleration unit |
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| CN105819333B CN105819333B (en) | 2018-05-04 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114671344A (en) * | 2022-05-27 | 2022-06-28 | 河南东起机械有限公司 | Crane power assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5547044A (en) * | 1994-01-19 | 1996-08-20 | Mitsubishi Denki Kabushiki Kaisha | Elevator hoist apparatus and manufacturing method therefor |
| CN2937653Y (en) * | 2006-08-03 | 2007-08-22 | 宁波东力传动设备股份有限公司 | Clearance operating reducer |
| KR20150004131A (en) * | 2013-07-02 | 2015-01-12 | 현대위아 주식회사 | Hook for crane |
| CN104455223A (en) * | 2014-12-05 | 2015-03-25 | 成都合瑞辰科技有限公司 | Novel speed reduction device for railway station electric sweeper |
| CN204237450U (en) * | 2014-11-28 | 2015-04-01 | 孙庆成 | Hoisting crane translation driving device |
| CN204664306U (en) * | 2015-04-16 | 2015-09-23 | 凤阳县鼎盛矿山设备有限公司 | Vertical shaft type Two Grade Column Gear Reducer |
| CN204778406U (en) * | 2015-05-27 | 2015-11-18 | 武汉钢铁(集团)公司 | Controlling means that rectifies is taken turns in walking |
-
2016
- 2016-05-31 CN CN201610374135.3A patent/CN105819333B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5547044A (en) * | 1994-01-19 | 1996-08-20 | Mitsubishi Denki Kabushiki Kaisha | Elevator hoist apparatus and manufacturing method therefor |
| CN2937653Y (en) * | 2006-08-03 | 2007-08-22 | 宁波东力传动设备股份有限公司 | Clearance operating reducer |
| KR20150004131A (en) * | 2013-07-02 | 2015-01-12 | 현대위아 주식회사 | Hook for crane |
| CN204237450U (en) * | 2014-11-28 | 2015-04-01 | 孙庆成 | Hoisting crane translation driving device |
| CN104455223A (en) * | 2014-12-05 | 2015-03-25 | 成都合瑞辰科技有限公司 | Novel speed reduction device for railway station electric sweeper |
| CN204664306U (en) * | 2015-04-16 | 2015-09-23 | 凤阳县鼎盛矿山设备有限公司 | Vertical shaft type Two Grade Column Gear Reducer |
| CN204778406U (en) * | 2015-05-27 | 2015-11-18 | 武汉钢铁(集团)公司 | Controlling means that rectifies is taken turns in walking |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114671344A (en) * | 2022-05-27 | 2022-06-28 | 河南东起机械有限公司 | Crane power assembly |
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| CN105819333B (en) | 2018-05-04 |
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