CN109099118B - Gearbox structure, bulldozer and control method - Google Patents
Gearbox structure, bulldozer and control method Download PDFInfo
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- CN109099118B CN109099118B CN201811074402.0A CN201811074402A CN109099118B CN 109099118 B CN109099118 B CN 109099118B CN 201811074402 A CN201811074402 A CN 201811074402A CN 109099118 B CN109099118 B CN 109099118B
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- gear
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- brake
- clutch
- bulldozer
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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
- F16H3/62—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
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/202—Mechanical transmission, e.g. clutches, gears
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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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three reverse speeds
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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
- 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
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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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
- 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
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a gearbox structure, a bulldozer and a control method, and relates to the technical field of bulldozers. The transmission structure comprises an input shaft, a support rod and an output shaft, wherein the support rod is rotatably sleeved on the input shaft; the reverse R gear brake and the forward F gear brake are direction control brakes; the reverse R gear clutch and the forward F gear clutch are direction control clutches; the first gear clutch, the second gear brake and the third gear brake are gear braking clutches. The bulldozer adopts the gearbox structure. The control method adopts the bulldozer. The gearbox structure disclosed by the invention can realize a plurality of forward gears and a plurality of backward gears, and the planet row is shared, so that the arrangement of the planet row is reduced, the arrangement of the whole gearbox structure is more compact, and the manufacturing cost is saved; the bulldozer is more reasonable in structural arrangement; the control method can effectively utilize the output power of the engine, can adapt to various working conditions, and has higher universality.
Description
Technical Field
The invention relates to the technical field of bulldozers, in particular to a gearbox structure, a bulldozer and a control method.
Background
In the prior art, a gearbox structure generally adopts a two-planet-row structure, and respectively controls a forward gear and a backward gear; in order to realize that the forward gear and the reverse gear are respectively provided with a plurality of gears, a clutch and a brake which can be matched with each other are also respectively arranged, and a plurality of planet row structures are used as transmission mechanisms.
The technical problem of the gearbox structure in the prior art is that in order to realize a forward gear with several gears, several planetary rows corresponding to the forward gear must be correspondingly arranged; in order to realize a reverse gear having several gears, several planetary rows corresponding to the reverse gear must be correspondingly provided. The forward gear and the backward gear can not share the planet row, so that the whole gearbox structure is more complex in arrangement, not compact enough and higher in manufacturing cost.
Disclosure of Invention
In view of the above problems, an object of the present invention is to provide a transmission structure capable of implementing multiple forward gears and multiple reverse gears, and the forward gears and the reverse gears share a planet row, so as to reduce the arrangement of the planet row, make the arrangement of the whole transmission structure more compact, occupy less space, reduce the volume of the transmission, and save the manufacturing cost.
The invention also aims to provide a bulldozer, which adopts the gearbox structure and is more reasonable in structural arrangement.
The invention further aims to provide a control method of the bulldozer, by adopting the bulldozer, the effective utilization of the output power of the engine is realized, the bulldozer can adapt to various working conditions, and the universality is higher.
The invention adopts the following technical scheme:
a transmission structure comprising:
the device comprises an input shaft, a support rod and an output shaft, wherein the support rod is rotatably sleeved on the input shaft;
the input shaft is connected with a first planet row, the first planet row is provided with a backward R gear brake and a forward F gear brake, and the backward R gear brake and the forward F gear brake are direction control brakes;
a backward R gear clutch and a forward F gear clutch are arranged between the support rod and the first planet row, and the backward R gear clutch and the forward F gear clutch are direction control clutches;
the output shaft is connected with a third planet row and a second planet row, one end of the third planet row is connected between a backward R-gear clutch and a forward F-gear clutch, the third planet row is provided with a III-gear brake, the second planet row is connected with the third planet row, the second planet row is provided with a II-gear brake, two ends of a connecting piece are respectively connected with the second planet row and the I-gear clutch, the connecting piece is sleeved on the output shaft through a bearing sleeve, and the I-gear clutch, the II-gear brake and the III-gear brake are gear braking clutches.
As a preferable aspect of the present invention, the first planetary row includes a first sun gear, a first planet gear, a first carrier, and a first planet ring gear, the first sun gear is connected to the input shaft, the first sun gear is engaged with the first planet gear, the first planet gear is engaged with a first planet ring, the first planet ring is connected to a forward F-range brake and a reverse R-range clutch, respectively, the first carrier is connected to a support rod, the support rod is connected to the forward F-range clutch, the first carrier is connected to the reverse R-range brake through a spline housing, and the reverse R-range brake brakes the first carrier through a spline housing.
As a preferable scheme of the invention, the spline housing and two sides of the supporting rod are supported by bearings.
As a preferred aspect of the present invention, the third planetary row includes a third sun gear, a third planet carrier, and a third planet ring gear, one end of the third planet carrier is connected to both the reverse R-range clutch and the forward F-range clutch, the third sun gear is connected to the output shaft, the third planet ring gear is connected to the iii-range brake, and the iii-range brake brakes the third planet ring gear.
As a preferable mode of the present invention, the second planetary row includes a second sun gear, a second planet carrier, a second planet gear, and a second planet ring gear, the second planet carrier is connected to the third planet ring gear, the second sun gear is connected to the output shaft, the second planet ring gear is connected to the second gear brake, and the second planet ring gear is braked by the second gear brake.
As a preferred scheme of the invention, the connecting piece is respectively connected with the second planet gear ring and the first-gear clutch, the first-gear clutch is connected with the output shaft, and the connecting piece is sleeved on the output shaft through the bearing.
As a preferable aspect of the present invention, the engagement of any one of the direction control clutches, any one of the shift position control clutches, and any one of the shift position brake clutches is controlled at the same time, and the shift positions of the transmission having different structures can be realized.
As a preferred scheme of the invention, a backward R gear brake, a forward F gear brake, a II gear brake and a III gear brake are wet multi-disc brakes; the reverse R gear clutch, the forward F gear clutch and the I gear clutch are wet multi-plate clutches.
A bulldozer comprises the gearbox structure, and further comprises:
one end of the input shaft is connected with the engine through a hydraulic torque converter, a speed measuring device is arranged on the input shaft, and a gear pressure sensor is arranged on the gearbox structure.
As a preferred scheme of the present invention, a speed measuring boss is disposed on one side of the output shaft, and a rotation speed sensor is disposed on the speed measuring boss and can sense the rotation speed of the input shaft.
A control method of a bulldozer adopts the bulldozer,
the rotating speed of the input shaft is provided with a set value;
when the rotating speed of the input shaft is greater than a set value and the bulldozer is not in a gear shifting state, the hydraulic torque converter is locked, and mechanical transmission is performed between the engine and the gearbox;
and when the rotating speed of the input shaft is less than a set value or the bulldozer is in a gear shifting state, the hydraulic torque converter is unlocked, and hydraulic transmission is realized between the engine and the gearbox through the hydraulic torque converter.
As a preferred scheme of the invention, the gear pressure of the gearbox is provided with a set value;
when the measured gear pressure of the gearbox is smaller than a set value of the gear pressure of the gearbox, the bulldozer is in a gear shifting state; and when the measured gear pressure of the gearbox is larger than the set value of the gear pressure of the gearbox, the bulldozer is not in a gear shifting state.
The invention has the beneficial effects that:
according to the gearbox structure, the first planet row is provided with the backward R gear brake and the forward F gear brake, and the backward R gear brake and the forward F gear brake are direction control brakes; the reverse R gear clutch is respectively connected with the first planet row and the forward F gear clutch, and the reverse R gear clutch and the forward F gear clutch are direction control clutches; the third planetary gear train is provided with a third gear brake, the second planetary gear train is provided with a second gear brake, the connecting piece is provided with a first gear clutch, the second gear brake and the third gear brake are gear braking clutches, so that the gearbox structure can realize three forward gears and three backward gears, the forward gears and the backward gears share the planetary gear train, the arrangement of the planetary gear train is reduced, the arrangement of the gearbox structure is more compact, the occupied space is small, the size of the gearbox is reduced, and the manufacturing cost is saved.
The bulldozer comprises the gearbox structure, one end of the input shaft is connected with the engine through the hydraulic torque converter, the input shaft is provided with the speed measuring device, the gearbox structure is provided with the gear pressure sensor, and the structure is more reasonable.
The bulldozer control method provided by the invention comprises the bulldozer, the rotating speed of the input shaft is provided with a set value, the hydraulic torque converter is controlled to be locked or unlocked by judging the relation between the rotating speed of the input shaft and the set value and judging whether the input shaft is in a gear shifting state, mechanical transmission or hydraulic transmission between the engine and the gearbox is realized, the output power of the engine is effectively utilized, the bulldozer can adapt to various working conditions, and the universality is higher.
Drawings
FIG. 1 is a schematic structural view of a transmission configuration provided by the present invention;
in the figure:
1. an input shaft; 2. a spline housing; 3. a reverse R gear brake;
4. a first planet row; 401. a first sun gear; 402. a first planet gear; 403. a first carrier; 404. a first planetary gear ring;
5. a forward F-gear brake; 6. a reverse R gear clutch; 7. a forward F-range clutch; 8. a support bar;
9. a third planet row; 901. a third sun gear; 902. a third planet gear; 903. a third carrier; 904. a third planetary gear ring;
10. a third gear brake;
11. a second planet row; 1101. a second sun gear; 1102. a second planet carrier; 1103. a second planet wheel; 1104. a second planetary gear ring;
12. a second gear brake; 13. a connecting member; 14. a first gear clutch; 15. an output shaft; 16. speed measuring boss.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures related to the present invention are shown in the drawings, not all of the structures.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Moreover, the placement on the left side and the placement on the right side are not intended to limit the specific locations, but merely to describe one arrangement.
Fig. 1 is a schematic structural diagram of a transmission structure provided by the present invention, and as shown in fig. 1, the transmission structure mainly includes: the transmission comprises an input shaft 1, a support rod 8 and an output shaft 15, wherein a reverse R gear brake 3 and a forward F gear brake 5 are direction control brakes, a reverse R gear clutch 6 and a forward F gear clutch 7 are direction control clutches, a first gear clutch 14, a second gear brake 12 and a third gear brake 10 are gear brake clutches, a first planet row 4 for connecting the direction control brakes and the direction control clutches, a third planet row 9 for connecting the direction control clutches and the third gear brake 10, and a second planet row 11 for connecting the second gear brake 12 and the third gear brake 10. The invention adopts two groups of directional control brakes, two groups of directional control clutches, three groups of gear braking clutches and three groups of planetary row structures, finally realizes the control of three forward gears and three reverse gears, and the forward gears and the reverse gears share the planetary rows, thus reducing the arrangement of the planetary rows, leading the arrangement of the whole gearbox structure to be more compact, occupying small space, reducing the volume of the gearbox and saving the manufacturing cost. Meanwhile, the engagement of any one of the direction control clutches, any one of the gear control clutches and any one of the gear brake clutches is controlled, so that different gears of the gearbox structure can be realized.
Specifically, as shown in fig. 1, the input shaft 1 is disposed through the entire transmission structure, the support rod 8 is rotatably sleeved on the input shaft 1, and the output shaft 15 is rotatably sleeved on the input shaft 1. Specifically, the support rod 8 is sleeved on the left side of the input shaft 1, and the output shaft 15 is sleeved on the right side of the input shaft 1. Because one end of the input shaft 1 is connected with the engine through the hydraulic torque converter, namely, the power provided by the engine is transmitted to the input shaft 1 through the hydraulic torque converter, and the input shaft 1 transmits the power to the output shaft 15 through the speed changing function of the gearbox structure. The input shaft 1 is connected with a first planet row 4, the first planet row 4 is provided with a reverse R gear brake 3 and a forward F gear brake 5, and a reverse R gear clutch 6 and a forward F gear clutch 7 are arranged between a support rod 8 and the first planet row 4; the output shaft 15 is connected with a third planet row 9 and a second planet row 11, one end of the third planet row 9 is connected between the reverse R-gear clutch 6 and the forward F-gear clutch 7, the third planet row 9 is provided with a III-gear brake 10, the second planet row 11 is connected with the third planet row 9, the second planet row 11 is provided with a II-gear brake 12, two ends of a connecting piece 13 are respectively connected with the second planet row 11 and the I-gear clutch 14, and the connecting piece 13 is sleeved on the output shaft 15.
Further, the first planetary row 4 includes a first sun gear 401, a first planet gear 402, a first carrier 403, and a first planet ring 404, the first sun gear 401 is connected to the input shaft 1, the first sun gear 401 is engaged with the first planet gear 402, the first planet gear 402 is engaged with the first planet ring 404, the first planet ring 404 is connected to the forward F-range brake 5 and the reverse R-range clutch 6, respectively, the first planet carrier 403 is connected to the support rod 8, the first planet carrier 403 is connected to the reverse R-range brake 3 through the spline housing 2, and the reverse R-range brake 3 brakes the first planet carrier 403 through the spline housing 2. Wherein, the spline housing 2 and the support rod 8 are supported on the input shaft by means of bearings.
Further, the third planetary row 9 includes a third sun gear 901, a third planetary gear 902, a third carrier 903, and a third planetary ring 904, one end of the third carrier 903 is connected to both the reverse R-range clutch 6 and the forward F-range clutch 7, the third sun gear 901 is connected to the output shaft 15, the third planetary ring 904 is connected to the iii-range brake 10, and the iii-range brake 10 brakes the third planetary ring 904.
Further, the second planetary row 11 includes a second sun gear 1101, a second planet carrier 1102, a second planet gear 1103 and a second planet ring gear 1104, the second planet carrier 1102 is connected with the third planet ring 904, the second sun gear 1101 is connected with the output shaft 15, the second planet ring gear 1104 is connected with the second gear brake 12, and the second planet ring gear 1104 is braked by the second gear brake 12.
Further, a first-gear clutch 14 is arranged between the connecting piece 13 and the output shaft 15, the connecting piece 13 is connected with the second planetary gear ring 1104 and the first-gear clutch 14 respectively, the first-gear clutch 14 is connected with the output shaft 15, and the connecting piece 13 is sleeved on the output shaft through a bearing.
Furthermore, the reverse R gear brake 3, the forward F gear brake 5, the II gear brake 12 and the III gear brake 10 are wet multi-plate brakes, and the wet multi-plate brakes have the characteristics of large braking torque, long service life, strong anti-fading capability, maintenance-free performance and the like. The reverse R gear clutch 6, the forward F gear clutch 7 and the I gear clutch 14 are wet multi-plate clutches which are good in heat dissipation and higher in reliability.
The gearbox structure provided by the invention can realize the control of three forward gears and three reverse gears, and specifically comprises a forward I gear, a forward II gear, a forward III gear, a reverse I gear, a reverse II gear and a reverse III gear, and the speed is faster and faster along with the increase of the gears, but the traction force which can be provided is smaller and smaller. Each gear corresponds to an actual working condition, and specifically comprises the following steps:
(1) advancing I gear
The I gear of marching forward is the operation gear of minimum speed, and the bull-dozer can provide maximum traction force, mainly used bulldozes, loosens the soil etc. and need the operating mode of great traction force, and for operation such as ordinary heavy load traction bulldozes, loosens the soil, its operating time accounts for more than 70% of total operating time about.
The working conditions of the gearbox structure are as follows:
the forward F-range brake 5 and the forward F-range clutch 7 are simultaneously closed, the reverse R-range brake 3 and the reverse R-range clutch 6 are separated, the forward F-range brake 5 brakes the first planetary gear ring 404, the forward F-range clutch 7 connects the support rod 8 and the third carrier 903 to rotate integrally, at this time, the input shaft 1 provides driving force to drive the first sun gear 401 to rotate, the first sun gear 401 drives the first carrier 403 through the first planetary gear 402, and further drives the support rod 8 to rotate, and the rotation is transmitted to the third carrier 903 of the third planetary row.
Meanwhile, the i-stage clutch 14 is closed, and the ii-stage brake 12 and the iii-stage brake 10 are both in a disengaged state, so that the power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901. The first-gear clutch 14 is closed, at this time, the connecting element 13 is rigidly connected with the output shaft 15 through the first-gear clutch 14, the second sun gear 1101, the second planet carrier 1102 and the second planet ring gear 1104 in the second planet row 11 integrally rotate at the same rotating speed, because the second sun gear 1101 and the third sun gear 901 are similarly fixed on the output shaft 15, and the second planet carrier 1102 and the third planet ring gear 904 are fixedly connected, therefore, the first-gear clutch 14, the third sun gear 901, the third planet carrier 903 and the third planet ring gear 904 which are closed at this time are integrally combined to integrally rotate at the same rotating speed, the transmission ratio is equal to 1, and the transmission realizes the forward first gear.
(2) Advance II gear
The forward II gear is an operation gear, and the bulldozer with the gear can provide a faster working speed and is generally suitable for medium and light load traction operation.
The power transmission of forward ii and forward i gears before the third carrier 903 is the same and will not be described further.
At the same time, the second brake 12 is closed, and the first clutch 14 and the third brake 10 are both disengaged, the second brake 12 brakes the second planetary gear ring 1104, and the coupling 13 connected to the second planetary gear ring 1104 is braked. The power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901; the third ring gear 904 transmits power to the second planetary gears 1103 and further to the second sun gear 1101 through the second carrier 1102. At this time, the first-speed clutch 14 is disengaged, the power of the coupling 13 cannot be directly transmitted to the output shaft 15 through the first-speed clutch 14, and the second sun gear 1101 is fixed to the output shaft 15 in the same manner as the third sun gear 901, so that the rotational speeds of the second sun gear 1101, the third sun gear 901, and the output shaft 15 are the same, but the gear ratio of the forward second speed is changed compared to the forward first speed, and therefore the rotational speed of the output shaft 15 of the forward second speed is greater than the rotational speed of the output shaft 15 of the forward first speed.
(3) Forward III gear
And when the bulldozer moves forward in a third gear, the bulldozer can provide a fast speed, and is generally suitable for light-load operation or no-load vehicle transfer working conditions.
The power transmission between forward III and forward I is the same before the third carrier 903 and will not be described further.
Meanwhile, the iii brake 10 is closed, and the i clutch 14 and the ii brake 12 are both in a disengaged state, the iii brake 10 brakes the third planetary gear 904, and the second carrier 1102 connected to the third planetary gear 904 is braked. The power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901.
At this time, the first-speed clutch 14 is disengaged, the power of the coupling 13 cannot be directly transmitted to the output shaft 15 through the first-speed clutch 14, and the second sun gear 1101 is fixed to the output shaft 15 in the same manner as the third sun gear 901, so that the rotational speeds of the second sun gear 1101, the third sun gear 901, and the output shaft 15 are the same, but the gear ratio of forward third speed is changed compared to forward second speed, and therefore the rotational speed of the output shaft 15 of forward third speed is greater than the rotational speed of the output shaft 15 of forward second speed.
The working conditions of the forward I gear, the forward II gear and the forward III gear are analyzed, and under the forward working condition, the transmission structure provided by the invention has the advantages that the forward F gear brake 5 and the forward F gear clutch 7 are closed, the reverse R gear brake 3 and the reverse R gear clutch 6 are separated, and the I gear clutch 14, the II gear brake 12 and the III gear brake 10 corresponding to the forward I gear, the forward II gear and the forward III gear respectively act to realize the forward gears with different speeds; and power is transmitted by the third planetary row 9 and the second planetary row 11.
Namely, under the forward working condition, three forward gears share the working state of one set of a forward F gear brake 5, a forward F gear clutch 7, a reverse R gear brake 3 and a reverse R gear clutch 6, and share two planetary row structures of a third planetary row 9 and a second planetary row 11.
(4) Back I gear
The bulldozer with the backing I gear is low in speed and is mainly used for backing when being limited by factors such as ground bump, narrow field, transfer distance and the like.
The working conditions of the gearbox structure are as follows:
the input shaft 1 provides a driving force to rotate the first sun gear 401, the reverse R-range brake 3 and the reverse R-range clutch 6 are simultaneously closed, and the forward F-range brake 5 and the forward F-range clutch 7 are disengaged. The backing R-range brake 3 brakes the spline housing 2, thereby braking the first carrier 403, and thereby braking the support rod 8. The power of the first sun gear 401 is transmitted to the first planetary gear 404 through the first planetary gears 402, the reverse R-range clutch 6 is closed, and the forward F-range clutch 7 is disengaged, so that the first planetary gear 404 can be connected to the third carrier 903 for unitary rotation through the reverse R-range clutch 6.
Meanwhile, the i-stage clutch 14 is closed, and the ii-stage brake 12 and the iii-stage brake 10 are both in a disengaged state, so that the power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901. The first-gear clutch 14 is closed, at this time, the connecting piece 13 is rigidly connected with the output shaft 15 through the first-gear clutch 14, the second sun gear 1101, the second planet carrier 1102 and the second planet ring gear 1104 in the second planet row 11 integrally rotate at the same rotating speed, because the second sun gear 1101 and the third sun gear 901 are similarly fixed on the output shaft 15, and the second planet carrier 1102 and the third planet ring gear 904 are fixedly connected, therefore, the first-gear clutch 14, the third sun gear 901, the third planet carrier 903 and the third planet ring gear 904 which are closed at this time are integrally combined to integrally rotate at the same rotating speed, the transmission ratio is equal to 1, and the gearbox realizes the backward first gear.
(5) Back II gear
The backward II gear is a reverse gear during operation, the bulldozer with the gear can provide a relatively fast reversing speed, the operation efficiency is improved, and the gear is used for reversing in most operation working conditions.
The reverse ii gear is the same as the reverse i gear in power transmission before the third carrier 903 and will not be described again.
At the same time, the second brake 12 is closed, and the first clutch 14 and the third brake 10 are both disengaged, the second brake 12 brakes the second planetary gear ring 1104, and the coupling 13 connected to the second planetary gear ring 1104 is braked. The power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901; the third ring gear 904 transmits power to the second planetary gears 1103 and further to the second sun gear 1101 through the second carrier 1102. At this time, the first-speed clutch 14 is disengaged, the power of the coupling 13 cannot be directly transmitted to the output shaft 15 through the first-speed clutch 14, and the second sun gear 1101 is fixed to the output shaft 15 in the same manner as the third sun gear 901, so that the rotational speeds of the second sun gear 1101, the third sun gear 901, and the output shaft 15 are the same, but the gear ratio of the reverse second speed is changed compared to the reverse first speed, and therefore the rotational speed of the output shaft 15 of the reverse second speed is greater than the rotational speed of the output shaft 15 of the reverse first speed.
(6) Backward III grade
The backward III gear is a fast reverse gear which provides the highest transfer speed of the bulldozer and is mainly used for fast transferring vehicles when the ground and the space meet the conditions.
The reverse iii gear is the same as the reverse i gear in power transmission before the third carrier 903 and will not be described again.
Meanwhile, the iii brake 10 is closed, and the i clutch 14 and the ii brake 12 are both in a disengaged state, the iii brake 10 brakes the third planetary gear 904, and the second carrier 1102 connected to the third planetary gear 904 is braked. The power transmitted from the third carrier 903 is transmitted to the output shaft 15 through the third planetary gear 902 and the third sun gear 901.
At this time, the i-stage clutch 14 is in the disengaged state, the power of the coupling 13 cannot be directly transmitted to the output shaft 15 through the i-stage clutch 14, and the second sun gear 1101 is fixed to the output shaft 15 in the same manner as the third sun gear 901, so that the rotational speeds of the second sun gear 1101, the third sun gear 901, and the output shaft 15 are the same, but the gear ratio of the reverse iii stage is changed compared to the reverse ii stage, and therefore the rotational speed of the reverse iii stage output shaft 15 is greater than the rotational speed of the reverse ii stage output shaft 15.
The working conditions of the reverse gear I, the reverse gear II and the reverse gear III are analyzed, and under the reverse working condition, the reverse R gear brake 3 and the reverse R gear clutch 6 are always closed, the forward F gear brake 5 and the forward F gear clutch 7 are always separated, and the forward gear I, the forward gear II and the forward gear III respectively correspond to the gear I clutch 14, the gear II brake 12 and the gear III brake 10 respectively to act so as to realize forward gears with different speeds; and the power transmission between the clutches of different gears is carried out by the third planetary row 9 and the second planetary row 11.
Namely, under the backward working condition, three backward gears share the working state of one set of forward F gear brake 5, forward F gear clutch 7, backward R gear brake 3 and backward R gear clutch 6, and share two planetary row structures of a third planetary row 9 and a second planetary row 11.
Comprehensively analyzing the forward gears and the reverse gears, the forward gears and the reverse gears share two planetary row structures of a third planetary row 9 and a second planetary row 11, and share a first gear clutch 14, a second gear brake 12 and a third gear brake 10. That is, the forward F-range brake 5, the forward F-range clutch 7, the reverse R-range brake 3, and the reverse R-range clutch 6 cooperate with the first planetary row 4 and the support bar 8 to form a forward/reverse function module, and the i-range clutch 14, the ii-range brake 12, and the iii-range brake 10 cooperate with the third planetary row 9 and the second planetary row 11 to form a gear module. The forward/backward function module and the gear module are matched to realize the control of three forward gears and three backward gears.
Further, as shown in tables 1 and 2, the data in table 1 are referred to, and the transmission ratio data of each gear in table 2 is obtained by calculating by using the transmission structure provided by the invention. From a combination of tables 1 and 2, it can be seen that the transmission architecture of the present invention provides three gear ratios for forward and reverse gears, respectively.
TABLE 1 gearbox Planet Row parameters under one embodiment
TABLE 2 Transmission ratios for each gear under the planetary row parameters of TABLE 1
The invention also provides a bulldozer, which preferably adopts the gearbox structure and is further provided with a speed measuring device in order to more effectively utilize the output power of the engine.
For the bulldozer of the electric control system, the gear shifting state can be judged, and whether the bulldozer is in the gear shifting state or not is judged without the gear pressure of a gearbox, so that the judgment is carried out only by a rotating speed sensor. For a bulldozer with a non-electric control system, such as a bulldozer with a mechanical control system, since the bulldozer cannot automatically judge the gear shifting state, it needs to judge whether the gear shifting state is in the gear shifting state through the gear pressure of the transmission, and the rotation speed of the output shaft of the torque converter (i.e., the rotation speed of the input shaft) is an index for determining whether the vehicle load is stable or not and whether the vehicle load is in the high-efficiency region of the output power of the engine.
The hydraulic torque converter is installed between engine and speed variator, and takes hydraulic oil as working medium to play the role of transmitting torque, changing speed and clutching. When the bulldozer is in a low-speed and loaded working state, such as working conditions of bulldozer operation and the like, a hydraulic torque converter is required to be connected between an engine and a transmission, and impact and vibration are eliminated through the action of the hydraulic torque converter, so that overload protection is provided. And when the bulldozer is in a working state with high speed and low load, such as the working condition that the bulldozer runs in an idle state, the hydraulic torque converter is not required to provide overload protection at the moment, and is locked to realize mechanical transmission.
During shifting of the bulldozer, the measured gear pressure of the transmission may suddenly decrease. Therefore, when the measured gear pressure of the gearbox is smaller than the set value of the gear pressure of the gearbox, the judgment can be made according to the gear pressure, the bulldozer is in a gear shifting state at the moment, and the hydraulic torque converter cannot be locked when the bulldozer shifts gears.
Specifically, the input shaft 1 penetrates through the whole gearbox structure, one end of the input shaft 1 is connected with an engine through a hydraulic torque converter, a speed measuring device is arranged on the input shaft 1, a gear pressure sensor is arranged on the gearbox structure, and the rotating speed of the input shaft 1 and the gear pressure of the gearbox respectively have set values. Further, a speed measuring boss 16 is arranged on one side of the output shaft 15, and a rotating speed sensor is arranged on the speed measuring boss 16 and can sense the rotating speed of the input shaft 1.
The invention also provides a control method of the bulldozer, which preferably adopts the bulldozer.
The rotating speed of the input shaft and the gear pressure of the gearbox are respectively set values.
When the rotating speed of the input shaft 1 is larger than the set value of the rotating speed of the input shaft 1 and the bulldozer is not in a gear shifting state, the hydraulic torque converter is locked, and mechanical transmission is performed between the engine and the gearbox. Namely, the hydraulic torque converter is locked to carry out mechanical transmission, two conditions need to be simultaneously met, the first condition is that the rotating speed of the input shaft 1 is greater than the set value of the rotating speed of the input shaft 1, and the bulldozer can be in a high-speed and low-load working state; the second condition is when the bulldozer is not in a shift state. Only if the two conditions are met simultaneously, the hydraulic torque converter is locked to perform mechanical transmission.
Specifically, if the bulldozer is a bulldozer with an electronic control system, whether the bulldozer is in a gear shifting state or not can be automatically judged; if the bulldozer is a bulldozer which is not an electronic control system, when the measured gear pressure of the gearbox is smaller than the set value of the gear pressure of the gearbox, the bulldozer at the moment can be judged to be in a gear shifting state.
When the rotating speed of the input shaft 1 is smaller than the set value of the rotating speed of the input shaft 1 or the bulldozer is in a gear shifting state, the hydraulic torque converter is unlocked, and hydraulic transmission is realized between the engine and the gearbox through the hydraulic torque converter. Namely, the hydraulic torque converter is unlocked to carry out hydraulic transmission, and any one of two conditions needs to be met, namely when the rotating speed of the input shaft 1 is less than the set value of the rotating speed of the input shaft 1, the bulldozer can be indicated to be in a low-speed and loaded working state, and the hydraulic torque converter is unlocked to carry out hydraulic transmission at the moment; or when the bulldozer is in a gear shifting state, the hydraulic torque converter cannot be locked and cannot perform mechanical transmission, so that the hydraulic torque converter needs to be unlocked to perform hydraulic transmission.
Specifically, if the bulldozer is a bulldozer with an electronic control system, whether the bulldozer is in a gear shifting state or not can be automatically judged; if the bulldozer is a bulldozer which is not an electronic control system, when the measured gear pressure of the gearbox is smaller than the set value of the gear pressure of the gearbox, the bulldozer at the moment can be judged to be in a gear shifting state. Meanwhile, when the measured gear pressure of the gearbox is smaller than a set value of the gear pressure of the gearbox, the fact that the bulldozer in the state at the moment possibly has a certain problem of a hydraulic torque converter is proved, and the hydraulic torque converter cannot be locked and cannot perform mechanical transmission at the moment, and needs to be unlocked to perform hydraulic transmission.
Therefore, the control method of the bulldozer provided by the invention realizes effective utilization of the output power of the engine through the unlocking and locking functions of the hydraulic torque converter, and the bulldozer can adapt to various working conditions and has higher universality.
It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments illustrated herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.
Claims (9)
1. A transmission structure, comprising:
the device comprises an input shaft (1), a support rod (8) which is rotatably sleeved on the input shaft (1) and an output shaft (15) which is rotatably sleeved on the input shaft (1);
the input shaft (1) is connected with a first planet row (4), the first planet row (4) is provided with a backward R gear brake (3) and a forward F gear brake (5), and the backward R gear brake (3) and the forward F gear brake (5) are direction control brakes;
a backward R gear clutch (6) and a forward F gear clutch (7) are arranged between the support rod (8) and the first planet row (4), and the backward R gear clutch (6) and the forward F gear clutch (7) are direction control clutches;
a third planet row (9) and a second planet row (11) are connected to the output shaft (15), one end of the third planet row (9) is connected between the reverse R-gear clutch (6) and the forward F-gear clutch (7), a III-gear brake (10) is arranged on the third planet row (9), the second planet row (11) is connected with the third planet row (9), a II-gear brake (12) is arranged on the second planet row (11), two ends of a connecting piece (13) are respectively connected to the second planet row (11) and the I-gear clutch (14), the connecting piece (13) is sleeved on the output shaft (15), and the I-gear clutch (14), the II-gear brake (12) and the III-gear brake (10) are gear braking clutches;
the first planet row (4) comprises a first sun gear (401), a first planet gear (402), a first planet carrier (403) and a first planet gear ring (404), the first planet gear ring (404) is respectively connected with the forward F gear brake (5) and the backward R gear clutch (6), the first planet carrier (403) is connected with the supporting rod (8), and the supporting rod (8) is connected with the forward F gear clutch (7); the first planet carrier (403) is connected with the backward R gear brake (3) through a spline housing (2), and the backward R gear brake (3) brakes the first planet carrier (403) through the spline housing (2);
the third planet row (9) comprises a third sun gear (901), a third planet gear (902), a third planet carrier (903) and a third planet gear ring (904), one end of the third planet carrier (903) is simultaneously connected with a reverse R gear clutch (6) and a forward F gear clutch (7), the third sun gear (901) is connected with an output shaft (15), the third planet gear ring (904) is connected with the III gear brake (10), and the III gear brake (10) brakes the third planet gear ring (904);
the second planet row (11) comprises a second sun gear (1101), a second planet carrier (1102), second planet gears (1103) and a second planet ring gear (1104), the second planet carrier (1102) is connected with the third planet ring gear (904), the second sun gear (1101) is connected with the output shaft (15), the second planet ring gear (1104) is connected with the II gear brake (12), and the II gear brake (12) brakes the second planet ring gear (1104);
the connecting piece (13) is respectively connected with the second planetary gear ring (1104) and the first-gear clutch (14), and the first-gear clutch (14) is connected with the output shaft (15).
2. A gearbox arrangement according to claim 1, characterised in that the first sun wheel (401) is connected to the input shaft (1), that the first sun wheel (401) meshes with a first planet wheel (402), and that the first planet wheel (402) meshes with the first planet ring (404).
3. Gearbox construction according to claim 2, characterised in that the spline housing (2) and the support bar (8) are supported on both sides by means of bearings.
4. A gearbox arrangement according to any one of claims 1-3, characterised in that simultaneous control of the engagement of any one of the directional control clutches, any one of the range control clutches and any one of the range brake clutches enables different gears of the gearbox arrangement.
5. A gearbox arrangement according to any one of claims 1-3, characterised in that the reverse R-range brake (3), the forward F-range brake (5), the ii-range brake (12) and the iii-range brake (10) are all wet multiplate brakes; the reverse R gear clutch (6), the forward F gear clutch (7) and the I gear clutch (14) are wet multi-plate clutches.
6. A bulldozer, characterized by comprising the transmission structure of any one of claims 1 to 5, and further comprising:
one end of the input shaft is connected with the engine through a hydraulic torque converter, a speed measuring device is arranged on the input shaft, and a gear pressure sensor is arranged on the gearbox structure.
7. Bulldozer according to claim 6, characterized in that a speed measuring boss (16) is arranged on one side of said output shaft (15), and a speed sensor is arranged on said speed measuring boss (16), said speed sensor being capable of sensing the speed of said input shaft (1).
8. A bulldozer control method, characterized in that the bulldozer according to any one of claims 6 to 7 is used,
the rotating speed of the input shaft is provided with a set value;
when the rotating speed of the input shaft is greater than a set value and the bulldozer is not in a gear shifting state, the hydraulic torque converter is locked, and mechanical transmission is performed between the engine and the gearbox;
and when the rotating speed of the input shaft is less than a set value or the bulldozer is in a gear shifting state, the hydraulic torque converter is unlocked, and hydraulic transmission is realized between the engine and the gearbox through the hydraulic torque converter.
9. The bulldozer control method according to claim 8,
the gear pressure of the gearbox is provided with a set value;
when the measured gear pressure of the gearbox is smaller than a set value of the gear pressure of the gearbox, the bulldozer is in a gear shifting state; and when the measured gear pressure of the gearbox is larger than the set value of the gear pressure of the gearbox, the bulldozer is in a non-gear shifting state.
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| CN201811074402.0A CN109099118B (en) | 2018-09-14 | 2018-09-14 | Gearbox structure, bulldozer and control method |
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| CN109099118B true CN109099118B (en) | 2021-04-23 |
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| CN114032984B (en) * | 2021-11-10 | 2023-04-18 | 山推工程机械股份有限公司 | Automatic gear shifting transmission system and gear shifting method |
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| KR20140143948A (en) * | 2013-06-10 | 2014-12-18 | 현대 파워텍 주식회사 | Automatic transmission for car |
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| CN106838154A (en) * | 2016-12-14 | 2017-06-13 | 山推工程机械股份有限公司 | A kind of manual transmission |
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| DE102016004373A1 (en) * | 2016-04-09 | 2017-10-12 | Daimler Ag | Drive device, in particular for an electric vehicle |
| CN207470708U (en) * | 2016-08-01 | 2018-06-08 | 福特环球技术公司 | Speed changer |
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| KR20140143948A (en) * | 2013-06-10 | 2014-12-18 | 현대 파워텍 주식회사 | Automatic transmission for car |
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| DE102016201855A1 (en) * | 2016-02-08 | 2017-08-10 | Zf Friedrichshafen Ag | Transmission for a motor vehicle, and powertrain for a motor vehicle |
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