CN103644265A - Engineering machine and planetary reduction mechanism thereof - Google Patents

Engineering machine and planetary reduction mechanism thereof Download PDF

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Publication number
CN103644265A
CN103644265A CN201310663986.6A CN201310663986A CN103644265A CN 103644265 A CN103644265 A CN 103644265A CN 201310663986 A CN201310663986 A CN 201310663986A CN 103644265 A CN103644265 A CN 103644265A
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Prior art keywords
gear
planetary
sun gear
gear ring
planet
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CN201310663986.6A
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Inventor
高一平
张世军
王少军
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Zoomlion Heavy Industry Science and Technology Co Ltd
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Zoomlion Heavy Industry Science and Technology Co Ltd
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Priority to CN201310663986.6A priority Critical patent/CN103644265A/en
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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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses an engineering machine and a planetary reduction mechanism thereof. The planetary reduction mechanism comprises a planetary transmission input shaft, a first planetary mechanism, a second planetary mechanism, a first brake, a second brake and a planetary transmission output shaft. The first planetary mechanism and the second planetary mechanism are composed of a sun gear, a planet gear, a gear ring and a planet carrier, wherein the planet transmission input shaft is used for driving the first sun gear and the second sun gear to synchronously rotate, the first brake and the second brake are used for selectively braking the first gear ring and the second gear ring respectively, the first planet carrier is connected with the second gear ring and synchronously rotates, and the second planet carrier is connected with the planet transmission output shaft. The planetary speed reducing mechanism has two different output transmission ratios, so that the use requirement of the engineering machinery on the variation range of the output speed can be met, and the power of the engine is utilized to a higher degree.

Description

Engineering machinery and planetary gear speed reducing mechanism thereof
Technical field
The present invention relates to engineering machinery field, particularly relate to a kind of planetary gear speed reducing mechanism and there is the engineering machinery of this planetary gear speed reducing mechanism.
Background technique
Object efficient in order to realize, low consumption work, moves fast when slow running while conventionally requiring the engineering machinery heavy duties such as hoist, rotary drilling rig, underloading, thereby motor and oil hydraulic pump can both be operated at full capacity.
Take rotary drilling rig as example, rotary drilling rig boring during work because load is large, now should reduce and revolve the output speed of digging drill bit, in order to avoid that motor is suppressed is flame-out; After drill bit is mentioned, rotate and get rid of in the process of mud, should have speed faster.Concerning hoist, when hoist is during at hoisting heavy, because load is heavier, now answer slow and steady; When the empty hook of hoist moves to certain specified position, suspension hook needs to arrive fast this specified position.
In order to realize heavy duty, go slowly, the object of underloading fastrunning, the most of hoisting speed reducer that adopts fluid motor-driven single speed ratio of engineering machinery.Because the reduction speed ratio of speed reducer is certain, therefore can only pass through to change rotating speed, the discharge capacity of oil hydraulic pump, and the discharge capacity of change motor regulates the output speed of engineering machinery.
Regulate by the way the excursion of the output speed obtaining more limited, can not meet the usage requirement of Part load and occasion, and the power of motor also can not be utilized completely.
Summary of the invention
The technical problem that the present invention mainly solves is to provide a kind of planetary gear speed reducing mechanism with Dual-speed-ratio.
For solving the problems of the technologies described above, the technological scheme that the present invention adopts is: a kind of planetary gear speed reducing mechanism is provided, it comprises Gear Planet Transmission input shaft, the first planetary mechanism, the second planetary mechanism, the first break, second brake and Gear Planet Transmission output shaft, the first planetary mechanism comprises the first sun gear, be arranged at the first sun gear around and with the first planetary gear set of the first sun gear outer gearing, with the first gear ring meshing in the first planetary gear set and be arranged at the first planet carrier in the first planetary gear set, the second planetary mechanism comprises the second sun gear, be arranged at the second sun gear around and with the second planetary gear set of the second sun gear outer gearing, with the second gear ring meshing in the second planetary gear set and be arranged at the second planet carrier in the second planetary gear set, wherein, the second sun gear is connected with the first sun gear, Gear Planet Transmission input shaft is connected with the first sun gear, and for driving the first sun gear and the second sun gear synchronously to rotate, the first break and second brake are used for selectivity respectively and brake the first gear ring and the second gear ring, the first planet carrier and the second gear ring connection and rotation of synchronizeing, the second planet carrier connects Gear Planet Transmission output shaft.
Wherein, when second brake is braked the second gear ring, and when the first break is not braked the first gear ring, it is motionless that the second gear ring and the first planet carrier keep, Gear Planet Transmission input shaft drives the first sun gear to rotate, and drive the first planetary gear set and the first gear ring to dally by the first sun gear, Gear Planet Transmission input shaft further drives the second sun gear to rotate, and drive the second planetary gear set and the second planet carrier to rotate by the second sun gear, and then drive Gear Planet Transmission output shaft to rotate with the first output reduction speed ratio.
Wherein, the first output reduction speed ratio is:
i 1 = 1 + Z 4 Z 3 ;
I 1be the first output reduction speed ratio, Z 4be the number of teeth of the second gear ring, Z 3it is the number of teeth of the second sun gear.
Wherein, when the first break is braked the first gear ring, and when second brake is not braked the second gear ring, it is motionless that the first gear ring keeps, Gear Planet Transmission input shaft drives the first sun gear to rotate, and drive the first planetary gear set to rotate by the first sun gear, first planet gear set drive the first planet carrier rotates, the second gear ring is synchronizeed and is rotated with the first planet carrier, Gear Planet Transmission input shaft further drives the second sun gear to rotate, and drive the second planetary gear set and the second planet carrier to rotate by the second sun gear and the second gear ring, and then drive Gear Planet Transmission output shaft to rotate with the second output reduction speed ratio.
Wherein, the second output reduction speed ratio is:
i 2 = 1 + Z 4 Z 3 1 + Z 1 · Z 4 Z 3 · ( Z 1 + Z 2 ) ;
I 2be the second output reduction speed ratio, Z 1be the number of teeth of the first sun gear, Z 2it is the number of teeth of the first gear ring.
Wherein, the first break and second brake are all Normally closed type hydraulic brakes, and comprise respectively the first oil hydraulic cylinder interface and the second oil hydraulic cylinder interface, when the first oil hydraulic cylinder interface input hydraulic pressure medium, the first break is removed the braking to the first gear ring, when the second oil hydraulic cylinder interface input hydraulic pressure medium, second brake is removed the braking to the second gear ring.
Wherein, the first break and second brake are all Normally closed type pneumatic braking devices, and comprise respectively the first cylinder interface and the second cylinder interface, when the first cylinder interface air inlet, the first break is removed the braking to the first gear ring, when the second cylinder interface air inlet, second brake is removed the braking to the second gear ring.
Wherein, planetary gear speed reducing mechanism further comprises the first spline mechanism, between Gear Planet Transmission input shaft and external connection power input shaft, by the first spline mechanism, is connected.
Wherein, planetary gear speed reducing mechanism further comprises the second spline mechanism, and Gear Planet Transmission output shaft is connected with external equipment by the second spline mechanism.
For solving the problems of the technologies described above, another technical solution used in the present invention is: a kind of engineering machinery is provided, and this project machinery comprises planetary gear speed reducing mechanism as above.
The invention has the beneficial effects as follows: the situation that is different from prior art, the first sun gear of planetary gear speed reducing mechanism the first planetary mechanism of the present invention and the second sun gear of the second planetary mechanism synchronously rotate, the first planet carrier of the first planetary mechanism and the second gear ring connection and rotation of synchronizeing, the second planet carrier of the second planetary mechanism connects Gear Planet Transmission output shaft, make planetary gear speed reducing mechanism when the first gear ring of the first planetary mechanism and the second gear ring of the second planetary mechanism are optionally braked, there are two different output transmission velocity ratios, therefore, during engineering machinery heavy duty, can select larger transmission velocity ratio with the slower speed of output, during underloading, can select less transmission velocity ratio to export speed faster, not only can meet the usage requirement of excursion of the output speed of engineering machinery, and the power of motor has also obtained the utilization of higher degree.
Accompanying drawing explanation
Fig. 1 is an embodiment's of planetary gear speed reducing mechanism of the present invention schematic diagram;
Fig. 2 is that planetary gear speed reducing mechanism of the present invention is applied to the schematic diagram in engineering machinery.
Embodiment
Refer to Fig. 1, one embodiment of the invention planetary gear speed reducing mechanism 100 comprises Gear Planet Transmission input shaft 11, the first planetary mechanism 12, the second planetary mechanism 13, the first break 14, second brake 15, Gear Planet Transmission output shaft 16, the first spline mechanism 17 and the second spline mechanism 18.
Gear Planet Transmission input shaft 11 is connected with external connection power input shaft by the first spline mechanism 17.
The first planetary mechanism 12 comprises the first sun gear 121, the first planetary gear set 122, the first gear ring 123 and the first planet carrier 124.The first sun gear 121 is arranged on Gear Planet Transmission input shaft 11 coaxial rotation with it.The first planetary gear set 122 be arranged at the first sun gear 121 surrounding and with the first sun gear 121 outer gearings.The first gear ring 123 and the interior engagement of the first planetary gear set 122.The first planet carrier 124 is arranged in the first planetary gear set 122 and is that the first planetary gear set 122 provides support rotating shaft.
The second planetary mechanism 13 comprises the second sun gear 131, the second planetary gear set 132, the second gear ring 133 and the second planet carrier 134.The second sun gear 131 be arranged on Gear Planet Transmission input shaft 11 and with Gear Planet Transmission input shaft 11 and the first sun gear 121 coaxial rotation.The second planetary gear set 132 be arranged at the second sun gear 131 surrounding and with the second sun gear 131 outer gearings.The second gear ring 133 and the interior engagement of the second planetary gear set 132.The second planet sets up 134 and is arranged in the second planetary gear set 132 and is that the second planetary gear set 132 provides support rotating shaft.
The first planet carrier 124 is fixedly attached on the second gear ring 133 and synchronizes and rotate with it.In the present embodiment, the second planet carrier 134 directly connects Gear Planet Transmission output shaft 16; In practical application, planetary gear speed reducing mechanism 100 of the present invention can also be made other distortion, such as the progression etc. that increases Gear Planet Transmission, makes the second planet carrier 134 indirectly connect Gear Planet Transmission output shaft 16.
The first break 14 and second brake 15 are braked the first gear ring 123 and the second gear ring 133 for selectivity respectively.In the present embodiment, the first break 14 and second brake 15 are all Normally closed type hydraulic brakes.The first break 14 comprises the first oil hydraulic cylinder interface 141, and second brake 15 comprises the second oil hydraulic cylinder interface 151.
During parking braking, the first oil hydraulic cylinder interface 141 and the second oil hydraulic cylinder interface 151 is input hydraulic pressure medium not all.
When the first oil hydraulic cylinder interface 141 input hydraulic pressure medium, the braking that the first break 14 is removed the first gear ring 123, the first gear ring 123 can rotate.Now, the braking that second brake 15 keeps the second gear ring 133, that is, the second gear ring 133 keeps motionless, and the first planet carrier 124 that is fixed to the second gear ring 133 also keeps motionless.Under this state, Gear Planet Transmission input shaft 11 drives the first sun gear 121 to rotate, and drive the first planetary gear set 122 and the first gear ring 123 to dally by the first sun gear 121, Gear Planet Transmission input shaft 11 further drives the second sun gear 131 to rotate, and drive the second planetary gear set 132 and the second planet carrier 134 to rotate by the second sun gear 131, and then drive Gear Planet Transmission output shaft 16 to rotate with the first output reduction speed ratio.
In simple terms, the input speed of Gear Planet Transmission input shaft 11 directly drives the second planet carrier 134 to obtain output speed through the second sun gear 131, that is, the first output reduction speed ratio is:
i 1 = 1 + Z 4 Z 3
In above-mentioned formula, i 1for described the first output reduction speed ratio, Z 4for the number of teeth of described the second gear ring 133, Z 3the number of teeth for described the second sun gear 131.
When the second oil hydraulic cylinder interface 151 input hydraulic pressure medium, the braking that second brake 15 is removed the second gear ring 133, the second gear ring 133 can rotate.Now, the braking that the first break 14 keeps the first gear ring 123, that is, the first gear ring 123 keeps motionless.Under this state, Gear Planet Transmission input shaft 11 drives the first sun gear 121 to rotate, and by the first sun gear 121, being driven that the first planetary gear set 122 are rotated, the first planetary gear set 122 drives the first planet carriers 124 to rotate, the second gear ring 133 is synchronizeed rotation with the first planet carrier 124; Gear Planet Transmission input shaft 11 further drives the second sun gear 131 to rotate, and drive the second planetary gear set 132 and the second planet carrier 134 to rotate by the second sun gear 131 and the second gear ring 133, and then drive Gear Planet Transmission output shaft 16 to rotate with the second output reduction speed ratio.
The second output reduction speed ratio computational process is as follows:
The first planetary mechanism 12 output reduction speed ratio are:
i 12 H 1 = n 1 - n H 1 n 2 - n H 1 = - Z 5 Z 1 × Z 2 Z 5 = - Z 2 Z 1 ①
Wherein,
Figure BDA0000433517650000061
represent the output reduction speed ratio of the first planetary mechanism 12, n 1represent the rotating speed of the first sun gear 121,
Figure BDA0000433517650000062
represent the rotating speed of the first planet carrier 124, n 2represent the rotating speed of the first gear ring 123, Z 5represent the number of teeth of a gear in the first planetary gear set 122, Z 1represent the number of teeth of the first sun gear 121, Z 2represent the number of teeth of the first gear ring 123.
The second planetary mechanism 13 output reduction speed ratio are:
i 34 H 2 = n 3 - n H 2 n 4 - n H 2 = - Z 6 Z 3 × Z 4 Z 6 = - Z 4 Z 3 ②
Wherein,
Figure BDA0000433517650000064
represent the output reduction speed ratio of the second planetary mechanism 13, n 3represent the rotating speed of the second sun gear 131, n 4represent the rotating speed of the second gear ring 133,
Figure BDA0000433517650000065
represent the rotating speed of the second planet carrier 134, Z 3represent the number of teeth of the second sun gear 131, Z 4represent the number of teeth of the second gear ring 133, Z 6represent the number of teeth of a gear in the second planetary gear set 132.
Formula 1. with formula 2. in, it is motionless that the first gear ring 123 keeps, i.e. n 2=0; The first planet carrier 124 is synchronizeed rotation with the second gear ring 133,
Figure BDA0000433517650000066
the first sun gear 121 and the second sun gear 131 are synchronizeed and are rotated with Gear Planet Transmission input shaft, i.e. n 1=n 3.
Simultaneous formula 1. with formula 2., can draw the second output reduction speed ratio i 2for:
i 2 = n 1 n H 2 = 1 + Z 4 Z 3 1 + Z 1 · Z 4 Z 3 · ( Z 1 + Z 2 )
In practical application, the first break 14 and second brake 15 can also be selected the pneumatic rot of Normally closed type simultaneously, and comprise respectively the first cylinder interface and the second cylinder interface.When the first cylinder interface air inlet, the braking that the first break 14 is removed the first gear ring 123; When the second cylinder interface air inlet, the braking that second brake 15 is removed the second gear ring 133.
See also Fig. 2, in practical application, planetary gear speed reducing mechanism 100 can also combine in engineering machinery such as being applied to rotary drilling rig, hoist with reducing gear 200.
Reducing gear 200 comprises deceleration input shaft 20, third planet mechanism 21, fourth planet mechanism 22, fifth line star mechanism 23 and deceleration shell 24.Now, Gear Planet Transmission output shaft 16 connects deceleration input shaft 20 by the second spline mechanism 18.
Third planet mechanism 21 comprises the 3rd sun gear 211, third planet gear train 212, the 3rd gear ring 213 and third planet frame 214.The 3rd sun gear 211 is arranged on deceleration input shaft 20 coaxial rotation with it.Third planet gear train 212 be arranged at the 3rd sun gear 211 surrounding and with the 3rd sun gear 211 outer gearings.The 3rd gear ring 213 and the interior engagement of third planet gear train 212.Third planet frame 214 is arranged on third planet gear train 212 and provides support rotating shaft for third planet gear train 212.
Fourth planet mechanism 22 comprises the 4th sun gear 221, fourth planet gear train 222, the 4th gear ring 223 and fourth planet frame 224.The 4th sun gear 221 is fixedly attached on third planet frame 214 and with it synchronizes and rotates.Fourth planet gear train 222 be arranged at the 4th sun gear 221 surrounding and with the 4th sun gear 221 outer gearings.The 4th gear ring 223 and the interior engagement of fourth planet gear train 222.Fourth planet frame 224 is arranged on fourth planet gear train 222 and provides support rotating shaft for fourth planet gear train 222.
Fifth line star mechanism 23 comprises the 5th sun gear 231, fifth line star gear train 232, the 5th gear ring 233 and fifth line star frame 234.The 5th sun gear 231 is fixedly attached on fourth planet frame 224 and with it synchronizes and rotates.Fifth line star gear train 232 be arranged at the 5th sun gear 231 surrounding and with the 5th sun gear 231 outer gearings.The 5th gear ring 233 and the 232 interior engagements of fifth line star gear train.Fifth line star frame 234 is fixed in the frame of engineering machinery and provides support rotating shaft for fifth line star gear train 232.
The 3rd gear ring 213, the 4th gear ring 223 and the 5th gear ring 233 are all fixedly installed on deceleration shell 24.The rotational velocity of deceleration shell 24 is the output speed of engineering machinery.
Be different from prior art, the first sun gear 121 of planetary gear speed reducing mechanism 100 first planetary mechanisms 12 of the present invention and the second sun gear 131 of the second planetary mechanism 13 synchronously rotate, the first planet carrier 124 of the first planetary mechanism 12 and the second gear ring 133 connections and rotation of synchronizeing, the second planet carrier 134 of the second planetary mechanism 13 connects Gear Planet Transmission output shaft 16, make planetary gear speed reducing mechanism 100 when the first gear ring 123 of the first planetary mechanism 12 and the second gear ring 133 of the second planetary mechanism 13 are optionally braked, there are two different output transmission velocity ratios, therefore, during engineering machinery heavy duty, can select larger transmission velocity ratio with the slower speed of output, during underloading, can select less transmission velocity ratio to export speed faster, not only can meet the usage requirement of excursion of the output speed of engineering machinery, and the power of motor has also obtained the utilization of higher degree.
The foregoing is only embodiments of the invention; not thereby limit the scope of the claims of the present invention; every equivalent structure or conversion of equivalent flow process that utilizes specification of the present invention and accompanying drawing content to do; or be directly or indirectly used in other relevant technical fields, be all in like manner included in scope of patent protection of the present invention.

Claims (10)

1. a planetary gear speed reducing mechanism (100), it is characterized in that, described planetary gear speed reducing mechanism (100) comprises Gear Planet Transmission input shaft (11), the first planetary mechanism (12), the second planetary mechanism (13), the first break (14), second brake (15) and Gear Planet Transmission output shaft (16), described the first planetary mechanism (12) comprises the first sun gear (121), be arranged at described the first sun gear (121) around and with first planetary gear set (122) of described the first sun gear (121) outer gearing, with described the first planetary gear set (122) in engagement the first gear ring (123) and be arranged at the first planet carrier (124) in described the first planetary gear set (122), described the second planetary mechanism (13) comprises the second sun gear (131), be arranged at described the second sun gear (131) around and with second planetary gear set (132) of described the second sun gear (131) outer gearing, with described the second planetary gear set (132) in engagement the second gear ring (133) and be arranged at the second planet carrier (124) in described the second planetary gear set (132), wherein, described the second sun gear (131) is connected with described the first sun gear (121), described Gear Planet Transmission input shaft (11) is connected with described the first sun gear (121), and for driving described the first sun gear (121) and described the second sun gear (131) synchronously to rotate, described the first break (14) and described second brake (15) are braked described the first gear ring (123) and described the second gear ring (133) for selectivity respectively, described the first planet carrier (124) and described the second gear ring (133) connection and the rotation of synchronizeing, described the second planet carrier (134) connects described Gear Planet Transmission output shaft (16).
2. planetary gear speed reducing mechanism according to claim 1 (100), it is characterized in that, when described second brake (15) is braked described the second gear ring (133), and when described the first break (14) is not braked described the first gear ring (123), described the second gear ring (133) and described the first planet carrier (124) keep motionless, described Gear Planet Transmission input shaft (11) drives described the first sun gear (121) to rotate, and drive described the first planetary gear set (122) and described the first gear ring (123) to dally by described the first sun gear (121), described Gear Planet Transmission input shaft (11) further drives described the second sun gear (131) to rotate, and drive described the second planetary gear set (132) and described the second planet carrier (134) to rotate by described the second sun gear (131), and then drive described Gear Planet Transmission output shaft (16) to rotate with the first output reduction speed ratio.
3. planetary gear speed reducing mechanism according to claim 2 (100), is characterized in that, described the first output reduction speed ratio is:
i 1 = 1 + Z 4 Z 3 ;
Wherein, i 1for described the first output reduction speed ratio, Z 4for the number of teeth of described the second gear ring (133), Z 3the number of teeth for described the second sun gear (131).
4. planetary gear speed reducing mechanism according to claim 3 (100), it is characterized in that, when described the first break (14) is braked described the first gear ring (123), and when described second brake (15) is not braked described the second gear ring (133), described the first gear ring (123) keeps motionless, described Gear Planet Transmission input shaft (11) drives described the first sun gear (121) to rotate, and drive described the first planetary gear set (122) to rotate by described the first sun gear (121), the first planetary gear set (122) drives described the first planet carrier (124) to rotate, described the second gear ring (133) is synchronizeed rotation with described the first planet carrier (124), described Gear Planet Transmission input shaft (11) further drives described the second sun gear (131) to rotate, and drive described the second planetary gear set (132) and described the second planet carrier (134) to rotate by described the second sun gear (131) and described the second gear ring (133), and then drive described Gear Planet Transmission output shaft (16) to rotate with the second output reduction speed ratio.
5. planetary gear speed reducing mechanism according to claim 4 (100), is characterized in that, described the second output reduction speed ratio is:
i 2 = 1 + Z 4 Z 3 1 + Z 1 · Z 4 Z 3 · ( Z 1 + Z 2 ) ;
Wherein, i 2for described the second output reduction speed ratio, Z 1for the number of teeth of described the first sun gear (121), Z 2the number of teeth for described the first gear ring (123).
6. planetary gear speed reducing mechanism according to claim 1 (100), it is characterized in that, described the first break (14) and described second brake (15) are all Normally closed type hydraulic brakes, and comprise respectively the first oil hydraulic cylinder interface (141) and the second oil hydraulic cylinder interface (151), when described the first oil hydraulic cylinder interface (141) input hydraulic pressure medium, described the first break (14) is removed the braking to described the first gear ring (123), when described the second oil hydraulic cylinder interface (151) input hydraulic pressure medium, described second brake (15) is removed the braking to described the second gear ring (133).
7. planetary gear speed reducing mechanism according to claim 1 (100), it is characterized in that, described the first break (14) and second brake (15) are all Normally closed type pneumatic braking devices, and comprise respectively the first cylinder interface and the second cylinder interface, when described the first cylinder interface air inlet, described the first break (14) is removed the braking to described the first gear ring (123), when described the second cylinder interface air inlet, described second brake (15) is removed the braking to described the second gear ring (133).
8. planetary gear speed reducing mechanism according to claim 1 (100), it is characterized in that, described planetary gear speed reducing mechanism (100) further comprises the first spline mechanism (17), between described Gear Planet Transmission input shaft (11) and external connection power input shaft, by described the first spline mechanism (17), is connected.
9. planetary gear speed reducing mechanism according to claim 1 (100), it is characterized in that, described planetary gear speed reducing mechanism (100) further comprises the second spline mechanism (18), and described Gear Planet Transmission output shaft (16) is connected with external equipment by described the second spline mechanism (18).
10. an engineering machinery, is characterized in that, described engineering machinery comprises the planetary gear speed reducing mechanism (100) as described in claim 1-9 item any one.
CN201310663986.6A 2013-12-09 2013-12-09 Engineering machine and planetary reduction mechanism thereof Pending CN103644265A (en)

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Cited By (4)

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Publication number Priority date Publication date Assignee Title
CN109159659A (en) * 2018-10-10 2019-01-08 广州市新域动力技术有限公司 Pure electric vehicle double speed dynamical system and its driving method
CN109538699A (en) * 2018-12-25 2019-03-29 德恩科电机（太仓）有限公司 A kind of double freedom planetary reduction box
CN110657200A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN110657202A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle

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