CN103016635A - Lifting speed reducer comprising planetary mechanism - Google Patents
Lifting speed reducer comprising planetary mechanism Download PDFInfo
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- CN103016635A CN103016635A CN2012105943135A CN201210594313A CN103016635A CN 103016635 A CN103016635 A CN 103016635A CN 2012105943135 A CN2012105943135 A CN 2012105943135A CN 201210594313 A CN201210594313 A CN 201210594313A CN 103016635 A CN103016635 A CN 103016635A
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- gear
- planetary mechanism
- speed reducer
- hoisting
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Abstract
The invention discloses a lifting speed reducer comprising a planetary mechanism. The lifting speed reducer comprises a first output shaft, a first motor shaft, a first transmission shaft, a second transmission shaft, a second motor shaft and a second output shaft, which are sequentially arranged, as well as first to ninth gears and the planetary mechanism, wherein the planetary mechanism comprises a gear ring, a planet gear, a sun gear and a tie bar; the gear ring comprises an inner gear ring and an outer gear ring; the first motor shaft directly drives the sun gear; the output end of the tie bar is connected with the second gear so as to enable the tie bar to rotate together with the second gear; the first to sixth gears are meshed with one another in sequence; and the outer gear ring and the seventh to ninth gears are meshed with one another in sequence. According to the invention, the number of intermediate wheels on the tie bar is greatly decreased; the line speed of all gears and the oil immersion depth are both reduced by half; churning loss is greatly reduced; and cooling apparatus can be omitted.
Description
Technical field
The present invention relates to the retarder of lifting mechanism, relate in particular to a kind of speed reducer used in hoisting that contains planetary mechanism.
Background technique
In the prior art, the speed reducer used in hoisting that contains planetary mechanism (normally planet bag) obtains more application in the jack up units such as hoist.
Be as depicted in figs. 1 and 2 the retarder that contains planetary mechanism of a kind of Germany design, this speed reducer used in hoisting that contains planetary mechanism comprises output shaft 11, motor shaft (or claiming the input motor shaft) 12, transmission shaft 13, motor shaft 14, transmission shaft 15 and output shaft 16.Be provided with the gear 21 that rotates synchronously with output shaft 11 at output shaft 11.Be provided with planetary mechanism 30 and gear 22 at motor shaft 12, the gear ring of planetary mechanism 30 has ring gear 20 and external toothing 27 simultaneously, and gear 22 is connected in the tie-rod of planetary mechanism 30, thereby rotates synchronously with tie-rod.Be provided with gear 23 and gear 28 at transmission shaft 13, wherein, gear 23 rotates synchronously with transmission shaft 13, and gear 28 is set on the transmission shaft 13 by bearing 31, thereby does not rotate synchronously with transmission shaft 13.Be provided with gear 24 and gear 29 at motor shaft 14, wherein, gear 29 rotates synchronously with motor shaft 14, and gear 24 is set on the motor shaft 14 by bearing 32, thereby does not rotate synchronously with motor shaft 14.On transmission shaft 15, then be provided with the gear 25 that rotates synchronously with transmission shaft 15.On output shaft 16, then be provided with the gear 26 that rotates synchronously with output shaft 16.
As depicted in figs. 1 and 2, gear 21, gear 22, gear 23, gear 24, gear 25 and gear 26 mesh successively, and the also successively engagement of external toothing 27, gear 28 and gear 29.
As depicted in figs. 1 and 2, the sun gear of the motor direct-drive planetary mechanism 30 that motor shaft 12 connects, and the motor that connects on the motor shaft 14 drives 27, two motions of external toothing synthetic output in planetary mechanism 30 by additional secondary breast wheel (gear 29 and gear 28) transmission.
The advantage of this structure is the asynchronous of the dual-motor start-up course that can automatic equalization motor shaft 12,14 connects.And when a motor broke down, another motor was still pressed normal duty work.But all there is heating problem in such speed reducer used in hoisting.This retarder calculates total efficiency 0.95 routinely, to the thermal power of this retarder of continuous operation check show poor few.But actual heating is serious, low many of total efficiency.This speed reducer used in hoisting that contains planetary mechanism of prior art, Main Problems are that the breast wheel on the tie-rod of planetary mechanism 30 (being gear 22) external diameter must be quite large owing to structural limitations, and its external diameter is about 1070mm.This makes the linear velocity V of whole row's breast wheel (elongated has 10 breast wheels, and short type has 6 breast wheels) too high, reaches V=20m/sec.And in order to guarantee that planetary mechanism can immersion oil, several larger breast wheel Immersion Depths excessive (allowing to be no more than 2 times of tooth depths is 45mm, but the maximum 280mm of actual breast wheel Immersion Depth, be allow more than 6 times).These will cause that the retarder churning loss increases, and generate heat under the aggravation continuous operation.In actual the use, increase by a cover sink, increase cost.
Summary of the invention
For problems of the prior art, the object of the present invention is to provide a kind of speed reducer used in hoisting that contains planetary mechanism, to solve the technical problem that speed reducer used in hoisting is too high owing to the breast wheel linear velocity and the excessive churning loss that is caused of Immersion Depth is large, the large needs of heating value increase sink that contains planetary mechanism of the prior art.
The present invention is achieved through the following technical solutions:
A kind of speed reducer used in hoisting that contains planetary mechanism, the described speed reducer used in hoisting that contains planetary mechanism comprise and setting gradually: the first output shaft is provided with the first gear that rotates with described the first output shaft synchronous; The first motor shaft is provided with on it: the second gear and planetary mechanism; The first transmission shaft is provided with on it: the 3rd gear that is sheathed on described the first transmission shaft by clutch shaft bearing; And the 7th gear that rotates synchronously with described the first transmission shaft; Second driving shaft is provided with on it: with synchronous the 4th gear that rotates of described second driving shaft; And the octadentate wheel of being located at described second driving shaft by the second bearing housing; The second motor shaft is provided with on it: the 5th gear of being located at the first transmission shaft by the 3rd bearing housing; And the 9th gear that rotates synchronously with described the second motor shaft; And second output shaft, be provided with on it: the 6th gear that rotates with described the second output shaft synchronous; Described planetary mechanism has gear ring, planet wheel, sun gear and tie-rod, described gear ring has ring gear and external toothing simultaneously, described the first motor shaft directly drives described sun gear, and the output terminal of described tie-rod is connected in described the second gear to rotate with described the second gear synchronous; Wherein, described the first gear, described the second gear, described the 3rd gear, described the 4th gear, described the 5th gear and described the 6th gear mesh successively; Described external toothing, described the 7th gear, described octadentate wheel and described the 9th gear mesh successively.
Beneficial effect of the present invention is, the speed reducer used in hoisting that contains planetary mechanism of the present invention, the centre distance of two motor shafts suitably increases, and forms 3 grades of breast wheel transmissions, so that breast wheel reduces much on the tie-rod, the linear velocity of each gear reduces half, and Immersion Depth reduces half, and churning loss greatly reduces, solved the existing heating problem of the speed reducer used in hoisting that contains planetary mechanism of prior art, do not need to install again radiator additional, reduced cost, can obtain good economic benefit.
Description of drawings
Fig. 1 is that the simplification master of the speed reducer used in hoisting that contains planetary mechanism of prior art looks schematic diagram;
Fig. 2 is the schematic top plan view of the speed reducer used in hoisting that contains planetary mechanism of prior art;
Fig. 3 is that the simplification master of the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention looks schematic diagram;
Fig. 4 be the embodiment of the invention the speed reducer used in hoisting that contains planetary mechanism schematic top plan view;
Fig. 5 be the embodiment of the invention the speed reducer used in hoisting that contains planetary mechanism overlook rough schematic view.
Embodiment
The exemplary embodiments that embodies feature ﹠ benefits of the present invention will be described in detail in the following description.Be understood that the present invention can have in different embodiments various variations, its neither departing from the scope of the present invention, and explanation wherein and accompanying drawing be when the usefulness that explain in itself, but not in order to limit the present invention.
The speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention can be used in the lifting mechanisms such as hoist.
Below specifically introduce the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, the present invention adopts the mode of double coaxial three grades of breast wheel transmissions.
As shown in Figure 3 and Figure 4, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention comprises output shaft 41, motor shaft 42, transmission shaft 43, transmission shaft 44, motor shaft 45 and the output shaft 46 that be arranged in parallel successively.
Be provided with the gear 51 that rotates synchronously with output shaft 41 at output shaft 41.Be provided with planetary mechanism 60 and gear 52 at motor shaft 42.Be provided with gear 53 and gear 57 at transmission shaft 43, wherein, gear 57 rotates synchronously with transmission shaft 43, and gear 53 is set on the transmission shaft 43 by bearing 72, thereby does not rotate synchronously with transmission shaft 43.Then be provided with gear 54 and gear 58 on transmission shaft 44, wherein, gear 54 rotates synchronously with transmission shaft 44, and gear 58 is set on the transmission shaft 44 by bearing 74, thereby does not rotate synchronously with transmission shaft 44.Then be provided with gear 55 and gear 59 on motor shaft 45, wherein, gear 59 rotates synchronously with motor shaft 45, and gear 55 is set on the motor shaft 45 by bearing 73, thereby does not rotate synchronously with motor shaft 45.On output shaft 46, then be provided with the gear 56 that rotates synchronously with output shaft 46.
As shown in Figure 3-Figure 5, planetary mechanism 60 comprises gear ring, sun gear 63, planet wheel 64 and tie-rod (or claiming planet carrier) 65, and gear ring has ring gear 62 and external toothing 61 simultaneously, and the output terminal of tie-rod 65 is connected in gear 52, therefore, the rotation of gear 52 is synchronous with tie-rod 65 all the time.The number of planet wheel 64 can be three, and the centre distance of planetary mechanism 60 (being the centre distance of sun gear and planet wheel) can be 192mm, and the external diameter of described external toothing is 850.27mm, and the external diameter of described sun gear is 168mm.
Wherein, the motor direct-drive sun gear 63 that motor shaft 42 connects, and the motor that connects on the motor shaft 45 drives 62, two motions of ring gear synthetic output in planetary mechanism 60 by additional three grades of breast wheels (gear 59, gear 58 and gear 57) transmission and by external toothing 61.
As shown in Figure 3 and Figure 4, gear 51, gear 52, gear 53, gear 54, gear 55 and gear 56 mesh successively, and the also successively engagement of external toothing 61, gear 57, gear 58 and gear 59.
As shown in Figure 3 and Figure 4, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, except gear 51 and gear 56, the external diameter of external toothing 61 is greater than the external diameter of other each gears, comprise the external diameter greater than gear 57 and described gear 59, the external diameter of gear 58 is slightly less than the external diameter of external toothing 61, and the external diameter of gear 52 is less than the internal diameter of ring gear 62.Therefore, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, its breast wheel Immersion Depth greatly reduces, the Immersion Depth of the speed reducer used in hoisting middle gear 22 that contains planetary mechanism as depicted in figs. 1 and 2 of prior art is 300mm, the Immersion Depth of gear 21 and gear 26 also has 200mm, the Immersion Depth of external toothing 27 is 149mm, the Immersion Depth of gear 28 also has 93mm, and in the embodiment of the invention, the Immersion Depth of maximum gear 51 is 136mm, and the Immersion Depth of the Immersion Depth of gear 56 and gear 51 is roughly the same.The Immersion Depth of external toothing 61 is 110mm, and the Immersion Depth of gear 58 is 110mm, therefore, the speed reducer used in hoisting that contains planetary mechanism of the present invention, its oil level 1 can be 300mm with the distance (being oil level flask joint distance) of medial axis 2, and in the prior art, its oil level 1 is 235mm with the distance of medial axis 2.In addition, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, two output shafts 41,46 spacing can reduce to 2930mm, therefore, 3080mm compared to existing technology, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, length direction can do shorter; At width direction, the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention does not increase width yet, so overall volume can be dwindled.Can be less except volume, because the external diameter of each gear reduces to some extent, so the gross weight of the speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention also can obviously alleviate, and can be reduced to the 70-80% of prior art.
The below introduces the calculating of the breast wheel number of teeth of the speed reducer used in hoisting that contains planetary mechanism of the present invention.
Can find out by schematic diagram of mechanism, the dual-motor input is arranged the synthetic tie-rod 65 of breast wheel (gear 57-gear 59) motion by the 1st and is rotated, and tie-rod 65 outputs are the 2nd row's breast wheel (gear 52-56) of drive bilateral output also.At first determine to need determine the gear parameter of planetary mechanism 60, carry out first the 1st row's breast wheel driven Design, do again the 2nd row's breast wheel driven Design after tie-rod 65 outputs of planetary mechanism 60.
The 1st row's breast wheel driven Design at first need meet the following conditions:
1) speed ratio need satisfy formula 1
Z wherein
1It is the number of teeth of the 1st row's breast wheel gear 59; z
4Be last gear number of teeth of the 1st row's breast wheel, the i.e. number of teeth of the external toothing 61 of gear ring; z
aBe planetary mechanism 60 central gears, the i.e. number of teeth of sun gear 63; z
bThe number of teeth for the ring gear 62 of planetary mechanism 60.
2) the 1st row's breast wheel module is larger 2 than planetary mechanism 60 modules, the requirement of so basic meeting geometric physical dimension.
3) 3 grades of breast wheel transmissions of the 1st row are determined near equal principle by centre distance at different levels, like this basic guarantee transmission equal strength at different levels.
4) to 3 grades of breast wheel transmissions, obtain ordering centre distance for a trial with reference to initial data by proposal plan, by formula the 2-formula 5 rough calculation gear numbers of teeth:
z
4=uz
1(formula 5)
Z wherein
2It is the number of teeth of the 1st row's breast wheel gear 58; z
3It is the number of teeth of the 1st row's breast wheel gear 57; a
1, a
2, a
3Being centre distance at different levels, also is gear 59 and the centre distance of centre distance, gear 58 and the gear 57 of gear 58 and the centre distance of gear 57 and external toothing 61; y
1, y
2, y
3Be centre distance Separating factors at different levels.M is modulus, and β is helix angle.
Can directly obtain z from following formula
1, z
2, z
3, z
4, calculate gear parameters at different levels behind the rounding that rounds up, if do not meet physical dimension, reset centre distance etc., recomputate, until rationally.But making software is done this calculating, automatically provides Reasonable Parameters.Wherein, z
1, z
2, z
3, z
4For example be 20,79,19,81.
Two, the 2nd row's breast wheel driven Design
The 2nd row's short side of breast wheel 1 grade (being gear 52-gear 51) is independent design, and long side 4 grades (being gear 52-gear 56) is the association design on short side group plinth.Short side selects tie-rod gear 52 numbers of teeth few to reduce the 2nd row's breast wheel linear velocity, 4 grades of centre distance a by the 1st row's breast wheel of long side as far as possible
3, a
2, a
1As 3 grades centre distance a before 4 grades of the long sides
1, a
2, a
3Design guarantees front 3 grades of centre distance and corresponding the equating of the 1st row's breast wheel.
After finishing the independent design of 1 grade of short side, obtain the number of teeth of the gear 52 that is connected with tie-rod 65, and with the number of teeth of the gearwheel (gear 51) of gear 52 engagements.The chopped-off head gear that long side is 4 grades is gear 52(number of teeth z
1), final-stage gear is that the gear 56(number of teeth is z
5) with the number of teeth identical (comprising modification coefficient) of gear 51, following calculating is to insert association design between 1 grade of two gear of short side and that 3 grades of centre distance restrictions are arranged.
4 grades of breast wheel transmissions have 3 breast wheels.If what provide is that head center is apart from a and front 2 grades of centre distance a
1, a
2, satisfy formula 6-formula 8:
Round up and calculate gear parameters at different levels behind the rounding, if do not meet physical dimension, reset centre distance etc., recomputate, until rationally.Also but making software is done this calculating, automatically provides Reasonable Parameters.Through above-mentioned calculating, in the present embodiment, the number of teeth of gear 51-gear 56 is respectively 78,40,51,38,51,78.
The speed reducer used in hoisting that contains planetary mechanism of the embodiment of the invention, two motor shafts 42,45 centre distance suitably is increased to 1530mm, and (motor shaft 12 in the prior art, 14 centre distance is 1110mm), form 3 grades of breast wheel transmissions, so that on the tie-rod breast wheel (especially gear 22, prior art is 1070mm, in the present embodiment less than 600mm) external diameter reduce a lot, the linear velocity of each gear reduces half, and (prior art is 21.6 meter per seconds, the present embodiment is 9.3 meter per seconds), Immersion Depth reduces half, churning loss greatly reduces, solved the existing heating problem of the speed reducer used in hoisting that contains planetary mechanism of prior art, do not need to install again radiator additional, reduced cost, can obtain good economic benefit.
Technological scheme of the present invention is disclosed as above by preferred embodiment.Those skilled in the art should recognize change and the retouching of doing in the situation that does not break away from the scope and spirit of the present invention that the appended claim of the present invention discloses, all belong within the protection domain of claim of the present invention.
Claims (10)
1. a speed reducer used in hoisting that contains planetary mechanism is characterized in that, the described speed reducer used in hoisting that contains planetary mechanism comprises and setting gradually:
The first output shaft is provided with the first gear that rotates with described the first output shaft synchronous;
The first motor shaft is provided with on it:
The second gear; And
Planetary mechanism;
The first transmission shaft is provided with on it:
Be sheathed on the 3rd gear of described the first transmission shaft by clutch shaft bearing; And
With synchronous the 7th gear that rotates of described the first transmission shaft;
Second driving shaft is provided with on it:
With synchronous the 4th gear that rotates of described second driving shaft; And
Be located at the octadentate wheel of described second driving shaft by the second bearing housing;
The second motor shaft is provided with on it:
Be located at the 5th gear of the first transmission shaft by the 3rd bearing housing; And
With synchronous the 9th gear that rotates of described the second motor shaft; And
The second output shaft is provided with on it:
The 6th gear with described the second output shaft synchronous rotation;
Described planetary mechanism has gear ring, planet wheel, sun gear and tie-rod, described gear ring has ring gear and external toothing simultaneously, described the first motor shaft directly drives described sun gear, and the output terminal of described tie-rod is connected in described the second gear to rotate with described the second gear synchronous;
Wherein, described the first gear, described the second gear, described the 3rd gear, described the 4th gear, described the 5th gear and described the 6th gear mesh successively; Described external toothing, described the 7th gear, described octadentate wheel and described the 9th gear mesh successively.
2. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 1, it is characterized in that, the external diameter of described external toothing is greater than the external diameter of described the 7th gear and described the 9th gear, and the external diameter of described octadentate wheel is greater than the external diameter of described the 7th gear and described the 9th gear.
3. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 2 is characterized in that, the external diameter of described external toothing is greater than the external diameter of described octadentate wheel, also greater than the external diameter of described the second to the 5th gear.
4. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 3 is characterized in that, the external diameter of described the second gear is less than the internal diameter of described ring gear.
5. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 1 is characterized in that, the centre distance between described the first output shaft and described the second output shaft is 2930mm, and the centre distance of described the first motor shaft and described the second motor shaft is 1530mm.
6. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 5, it is characterized in that, the centre distance of described the first transmission shaft and described second driving shaft is 505mm, the centre distance of described the first transmission shaft and described the first motor shaft is 515mm, and the centre distance of described second driving shaft and described the second motor shaft is 510mm.
7. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 6 is characterized in that, described the first gear is identical with the number of teeth of described the 6th gear.
8. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 7 is characterized in that, described the first gear to the number of teeth of described the 6th gear is respectively 78,40,51,38,51,78.
9. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 7 is characterized in that, the number of teeth of described the 7th gear to the nine gears is respectively 19,79,20, and the number of teeth of described external toothing is 81.
10. the speed reducer used in hoisting that contains planetary mechanism as claimed in claim 1 is characterized in that, the centre distance of described planetary mechanism 60 can be 192mm, and the external diameter of described external toothing is 850.27mm, and the external diameter of described sun gear is 168mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210594313.5A CN103016635B (en) | 2012-12-31 | 2012-12-31 | Lifting speed reducer comprising planetary mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210594313.5A CN103016635B (en) | 2012-12-31 | 2012-12-31 | Lifting speed reducer comprising planetary mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103016635A true CN103016635A (en) | 2013-04-03 |
| CN103016635B CN103016635B (en) | 2015-04-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210594313.5A Expired - Fee Related CN103016635B (en) | 2012-12-31 | 2012-12-31 | Lifting speed reducer comprising planetary mechanism |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2337425A1 (en) * | 1973-07-23 | 1975-02-06 | Stemmann Ohg A | Cable supply system from fixed point for mobile crane - includes storage drum powered by differential drive and using auxiliary drive to control angular speed |
| DE2533970A1 (en) * | 1975-07-30 | 1977-02-03 | Demag Ag | Travelling crane for ladle - uses twin crabs linked by synchronising shafts fitted with brakes |
| CN1651804A (en) * | 2004-02-04 | 2005-08-10 | 上海振华港口机械（集团）股份有限公司 | Differential gearbox of crane for 40 foot container |
| CN201517589U (en) * | 2009-10-26 | 2010-06-30 | 南京星能传动机械有限责任公司 | Crane differential planet gear case |
| CN201851601U (en) * | 2010-11-19 | 2011-06-01 | 太原重工股份有限公司 | Dual-planetary main hoist gearbox of ladle crane |
-
2012
- 2012-12-31 CN CN201210594313.5A patent/CN103016635B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2337425A1 (en) * | 1973-07-23 | 1975-02-06 | Stemmann Ohg A | Cable supply system from fixed point for mobile crane - includes storage drum powered by differential drive and using auxiliary drive to control angular speed |
| DE2533970A1 (en) * | 1975-07-30 | 1977-02-03 | Demag Ag | Travelling crane for ladle - uses twin crabs linked by synchronising shafts fitted with brakes |
| CN1651804A (en) * | 2004-02-04 | 2005-08-10 | 上海振华港口机械（集团）股份有限公司 | Differential gearbox of crane for 40 foot container |
| CN201517589U (en) * | 2009-10-26 | 2010-06-30 | 南京星能传动机械有限责任公司 | Crane differential planet gear case |
| CN201851601U (en) * | 2010-11-19 | 2011-06-01 | 太原重工股份有限公司 | Dual-planetary main hoist gearbox of ladle crane |
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| Publication number | Publication date |
|---|---|
| CN103016635B (en) | 2015-04-08 |
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Granted publication date: 20150408 Termination date: 20211231 |