CN103693101B - A kind of vehicle speed variation hydraulic steering gear - Google Patents
A kind of vehicle speed variation hydraulic steering gear Download PDFInfo
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- CN103693101B CN103693101B CN201310711674.8A CN201310711674A CN103693101B CN 103693101 B CN103693101 B CN 103693101B CN 201310711674 A CN201310711674 A CN 201310711674A CN 103693101 B CN103693101 B CN 103693101B
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Abstract
The invention discloses a kind of vehicle speed variation hydraulic steering gear, between rotary valve and measure motor, embed a change-speed box, this change-speed box is internal gear deceleration transmission and direct-drive two kinds of speed ratios, the valve pocket of rotary valve and motor rotor constant velocity rotation during direct-drive, when internal gear deceleration transmission, the valve pocket of rotary valve realizes decelerated movement relative to motor rotor, and thus in identical steering wheel angle situation, measure motor can realize flow and increases by speed ratio.This structure is simple, and cost is low, adapts to the multiple steering reduction ratio requirement of vehicle, improves handling maneuver performance.
Description
Technical field
The present invention relates to engineering truck all hydraulic pressure steering-gear field, particularly relate to a kind of vehicle speed variation hydraulic steering gear.
Background technology
Be illustrated in figure 1 typical engineering truck hydrostatic steering system, form primarily of following elements: oil pump 1, hydraulic steering gear 2, bearing circle transmission shaft 3, bearing circle 4, steering cylinder 5, safety valve 6, check valve 7, fuel tank 8.
Be illustrated in figure 2 the basic structure of hydraulic steering gear 2, comprise rotary valve 101, measure motor 102, universal driving shaft 15, dividing plate 16; Wherein rotary valve 101 forms primarily of valve body 11, spool 12, valve pocket 13, finger 14, measure motor 102 forms primarily of rotor 18, stator 19, rotor 18 endoporus has tooth, connect with universal driving shaft 15 one end, finger 14 connects with the other end of universal driving shaft 15, finger 14 coordinates with valve pocket 13, has certain rotational displacement amount between finger 14 and spool 12, links when being just combined with finger 14 after spool 12 turns of certain angles.
Principle of work is: during Vehicular turn, steering wheel rotation 4 rotates θ angle, spool 12 is driven to rotate by bearing circle transmission shaft 3, open the valve port between spool 12 and valve pocket 13, the oil of oil pump 1 enters measure motor 102 drive rotor 18 rotary rowed oil pump capacity q by rotary valve 101, rotor 18 drives universal driving shaft 15 by the internal spline of self simultaneously, finger 14, valve pocket 13 rotates θ corner at equidirectional, valve port between spool 12 and valve pocket 13 gets back to closed condition, the oil mass q discharged and steering wheel angle θ is proportional, the oil mass q discharged promotes steering cylinder 5 makes vehicle produce deflection angle α.In steering procedure, the corner displacement θ of the bearing circle 4 and steering angular displacement α of vehicle is proportional, and that is, the transmitting ratio (ratio of steering wheel angle and steered wheel corner) of Vehicular turn is substantially constant.
But for some vehicle, such as loader, many employings chevron pointing mode of operation during operation, shovel dress material and discharging need once and again quick steering operation, therefore less steering gear ratio is wished, only need the less corner of steering wheel rotation namely to obtain larger machine deflection angle, be conducive to reducing tired driver, improve operating efficiency.And when running at high speed on highway, wish again larger steering gear ratio, make vehicle have good steering stability.Turning to of current loader only has a transmitting ratio, can not meet two kinds of demands, and steering wheel angle scope is generally ± 2.5 ~ 3 circles, and steer ability during operation is poor, and the labour intensity of driver is large.
Summary of the invention
The object of the invention is to overcome above-mentioned the deficiencies in the prior art, a kind of vehicle speed variation hydraulic steering gear is provided; With the handling maneuver performance that speed change turns to type of drive to solve vehicle to have had under different operating conditions, have that structure is simple, cost is low, improve steer ability.
The present invention is achieved through the following technical solutions:
A kind of vehicle speed variation hydraulic steering gear, includes rotary valve 101, measure motor 102, universal driving shaft 15, dividing plate 16; Described rotary valve 101 comprises valve body 11, spool 12, valve pocket 13, finger 14, in the circuferential spacing of valve pocket 13 between spool 12 and valve body 11, finger 14 with valve pocket 13 for pin connects, mutually be rotationally connected between finger 14 and spool 12 (there is between them certain rotational displacement amount), be combined with finger 14 when spool 12 rotates and link;
Described measure motor 102 comprises rotor 17, stator 18, and rotor 17 is rotation and revolution in stator 18, and the endoporus of rotor 17 has tooth;
There is tooth one end of described universal driving shaft 15, has this end of tooth to connect with the tooth of rotor 17 endoporus of measure motor 102 and forms splined;
Described dividing plate 16 is between rotary valve 101 and measure motor 102;
Described vehicle speed variation hydraulic steering gear also comprises a change-speed box 103, and described change-speed box 103 comprises input shaft 27, output shaft 20, coupler 28; Change-speed box 103 is between rotary valve 101 and dividing plate 16, and the input shaft 27 of change-speed box 103 is connected with the other end of universal driving shaft 15 by coupler 28, and the output shaft 20 of change-speed box 103 connects with the finger 14 of rotary valve 101; Described coupler 28 is gimbal coupling;
Described change-speed box 103 also comprises spline housing 21, housing 22, shifting gear 23, engaging sleeve 24, internally toothed annulus 25, bolster 26, sun wheel 29, transition gear 30, gearshift internal tooth casing 31, shift fork 32, handle supporting 33, handle 34;
The inner of described output shaft 20 is engaged with spline housing 21, and outer end connects with the finger 14 of rotary valve 101;
Described spline housing 21 is enclosed within by splined on output shaft 20, and output shaft 20 moves vertically, and one end cylindrical of described spline housing 21 is provided with groove, and this groove coordinates with shift fork 32, and other end cylindrical and the shifting gear 23 of spline housing 21 are consolidated;
Described internally toothed annulus 25 and gearshift internal tooth casing 31 consolidation are integrated, and internally toothed annulus 25 engages with transition gear 30, and the gearshift internal tooth casing 31 of opposite side engages with the external tooth engage a gear of shifting gear 23;
Described bolster 26 is fixed on change-speed box 103 housing 22, and transition gear 30 is contained on bolster 26;
Described input shaft 27 side connects with sun wheel 29, and opposite side connects with coupler 28;
Described sun wheel 29 and engaging sleeve 24 consolidation are integrated, and sun wheel 29 engages with transition gear 30, and the engaging sleeve 24 of sun wheel 29 side can engage with shifting gear 23 engage a gear;
Described handle supporting 33 is fixed on housing 22, and handle supporting 33 is porose;
Groove on described spline housing 21 cylindrical and shift fork 32 matching relationship are that described shift fork 32 one end has arc fork to embed in the groove of spline housing 21 one end, and the other end is that cylindrical shroud is enclosed within the axle of handle 34 one end.
Described handle 34 is arranged in the hole of handle supporting 33 in a rotating manner, and is connected by axis hole with shift fork 32.
Relative to prior art, tool of the present invention has the following advantages and beneficial effect:
(1) between rotary valve and measure motor, embed a change-speed box, this change-speed box is internal gear deceleration transmission and direct-drive two kinds of speed ratios, the valve pocket of rotary valve and motor rotor constant velocity rotation during direct-drive, when internal gear deceleration transmission, the valve pocket of rotary valve realizes decelerated movement relative to motor rotor, and thus in identical steering wheel angle situation, measure motor can realize flow and increases by speed ratio.This structure is simple, and cost is low, adapts to the multiple steering reduction ratio requirement of vehicle, improves handling maneuver performance.
(2) many transmitting ratios handling maneuver is selected, and is suitable for different job requirements.
(3) because change-speed box is by fluid motor-driven, therefore on the steering force of bearing circle without impact.
Accompanying drawing explanation
Fig. 1 is all hydraulic pressure steering-gear schematic diagram.
Fig. 2 is existing hydraulic steering gear structural representation.
Fig. 3 is vehicle speed variation hydraulic steering gear structural representation of the present invention.
Detailed description of the invention
Below in conjunction with specific embodiment, the present invention is more specifically described in detail.
Embodiment
As shown in Figure 3.Vehicle speed variation hydraulic steering gear of the present invention, includes rotary valve 101, measure motor 102, universal driving shaft 15, dividing plate 16;
Described rotary valve 101 comprises valve body 11, spool 12, valve pocket 13, finger 14, in the circuferential spacing of valve pocket 13 between spool 12 and valve body 11, finger 14 with valve pocket 13 for pin connects, mutually be rotationally connected between finger 14 and spool 12 (there is between them certain rotational displacement amount), be combined with finger 14 when spool 12 rotates and link;
Described measure motor 102 comprises rotor 17, stator 18, and rotor 17 is rotation and revolution in stator 18, and the endoporus of rotor 17 has tooth;
There is tooth one end of described universal driving shaft 15, has this end of tooth to connect with the tooth of rotor 17 endoporus of measure motor 102 and forms splined;
Described dividing plate 16 is between rotary valve 101 and measure motor 102;
Described vehicle speed variation hydraulic steering gear also comprises a change-speed box 103, and described change-speed box 103 comprises input shaft 27, output shaft 20, coupler 28; Change-speed box 103 is between rotary valve 101 and dividing plate 16, and the input shaft 27 of change-speed box 103 is connected with the other end of universal driving shaft 15 by coupler 28, and the output shaft 20 of change-speed box 103 connects with the finger 14 of rotary valve 101;
Described change-speed box 103 also comprises spline housing 21, housing 22, shifting gear 23, engaging sleeve 24, internally toothed annulus 25, bolster 26, sun wheel 29, transition gear 30, gearshift internal tooth casing 31, shift fork 32, handle supporting 33, handle 34;
The inner of described output shaft 20 is engaged with spline housing 21, and outer end connects with the finger 14 of rotary valve 101;
Described spline housing 21 is enclosed within by splined on output shaft 20, and output shaft 20 moves vertically, and one end cylindrical of described spline housing 21 is provided with groove, and this groove coordinates with shift fork 32, and other end cylindrical and the shifting gear 23 of spline housing 21 are consolidated;
Described internally toothed annulus 25 and gearshift internal tooth casing 31 consolidation are integrated, and internally toothed annulus 25 engages with transition gear 30, and the gearshift internal tooth casing 31 of opposite side engages with the external tooth engage a gear of shifting gear 23;
Described bolster 26 is fixed on change-speed box 103 housing 22, and transition gear 30 is contained on bolster 26;
Described input shaft 27 side connects with sun wheel 29, and opposite side connects with coupler 28;
Described sun wheel 29 and engaging sleeve 24 consolidation are integrated, and sun wheel 29 engages with transition gear 30, and the engaging sleeve 24 of sun wheel 29 side can engage with shifting gear 23 engage a gear;
Described handle supporting 33 is fixed on housing 22, and handle supporting 33 is porose;
Groove on described spline housing 21 cylindrical and shift fork 32 matching relationship are that described shift fork 32 one end has arc fork to embed in the groove of spline housing 21 one end, and the other end is that cylindrical shroud is enclosed within the axle of handle 34 one end.
Described handle 34 is arranged in the hole of handle supporting 33 in a rotating manner, and is connected by axis hole with shift fork 32.
Described coupler 28 is gimbal coupling.
Principle of work of the present invention is as follows:
(composition graphs 1 as shown in Figure 3, 2), when low speed ratio (ratio at finger direction dish corner and Vehicular turn angle) turns to, twisting handle 34, stir spline housing 21 and shifting gear 23 by shift fork 32 to move axially shifting gear 23 is engaged with gearshift internal tooth casing 31, steering wheel rotation 4 turns of θ angles, the spool 12 of rotary valve 101 is driven to rotate by bearing circle transmission shaft 3, relative angular displacement is produced between spool 12 and valve pocket 13, valve port is opened, oil pump 1 fuel feeding enters measure motor 102 by the valve port opened between the spool 12 of rotary valve 101 and valve pocket 13, drive rotor 17 rotates, the oil that measure motor 102 is discharged enters again the valve port of rotary valve 101 through having opened between spool 12 and valve pocket 13 and enters steering cylinder 5 and drive Vehicular turn, the oil in another chamber of steering cylinder 5 gets back to fuel tank 8 through rotary valve 101, rotor 17 time rotational of measure motor 102 is by universal driving shaft 15, coupler 28 drives the input shaft 27 of change-speed box 103 and sun wheel 29 to rotate, sun wheel 29 engages with transition gear 30, transition gear 30 engages with internally toothed annulus 25 again, thus internally toothed annulus 25 realizes decelerated movement, by shifting gear 23 driver output axle 20, finger 14, valve pocket 13 realizes underdrive, until valve pocket 13 also rotates θ, valve port is closed, in this course, ratio=the sun wheel 29 of the angular transposition of bearing circle 4 and the angular transposition of rotor 17 and the ratio of the number of teeth of internally toothed annulus 25, if this ratio is λ, then: compared with existing hydraulic steering gear, under rotating same steering wheel angle situation, the flow that measure motor 102 exports increases λ doubly.
When turning to than (ratio at finger direction dish corner and Vehicular turn angle) at a high speed, twisting handle 34, stir spline housing 21 and shifting gear 23 by shift fork 32 to move axially shifting gear 23 is engaged with engaging sleeve 24, steering wheel rotation 4 turns of θ angles, the spool 12 of rotary valve 101 is driven to rotate by bearing circle transmission shaft 3, relative angular displacement is produced between spool 12 and valve pocket 13, valve port is opened, oil pump 1 fuel feeding enters measure motor 102 by the valve port opened between the spool 12 of rotary valve 101 and valve pocket 13, drive rotor 17 rotates, the oil that measure motor 102 is discharged enters again the valve port of rotary valve 101 through having opened between spool 12 and valve pocket 13 and enters steering cylinder 5 and drive Vehicular turn, the oil in another chamber of steering cylinder 5 gets back to fuel tank 8 through rotary valve 101, rotor 17 time rotational of measure motor 102 is by universal driving shaft 15, coupler 28 drives the input shaft 27 of change-speed box 103 and sun wheel 29 to rotate, sun wheel 29 drives engaging sleeve 24, output shaft 20, finger 14, valve pocket 13 rotates, until valve pocket 13 rotates θ, valve port is closed, in this course, the angular transposition of bearing circle 4 is identical with the angular transposition of rotor 17, identical with existing hydraulic steering gear.
Just the fluid-link steering function of two kinds of speed is achieved as mentioned above, simultaneously because variable speed drive (VSD) is by fluid motor-driven, so steering force is not affected.
Above-described embodiment is the present invention's preferably embodiment; but embodiments of the present invention are not limited by the examples; other are any do not deviate from Spirit Essence of the present invention and principle under do change, modification, substitute, combine, simplify; all should be the substitute mode of equivalence, be included within protection scope of the present invention.
Claims (5)
1. a vehicle speed variation hydraulic steering gear, includes rotary valve, measure motor, universal driving shaft, dividing plate;
Described rotary valve comprises valve body, spool, valve pocket, finger, and in the circuferential spacing of valve pocket between spool and valve body, finger and valve pocket are that pin connects, and are mutually rotationally connected between finger and spool, be combined link when valve core rotation with finger;
Described measure motor comprises rotor, stator, and rotor is rotation and revolution in stator, and the endoporus of rotor has tooth;
There is tooth one end of described universal driving shaft, has this end of tooth to connect with the tooth of the rotor inner hole of measure motor and forms splined;
Described dividing plate is between rotary valve and measure motor;
It is characterized in that:
Described vehicle speed variation hydraulic steering gear also comprises a change-speed box, and described change-speed box comprises input shaft, output shaft, coupler; Change-speed box is between rotary valve and dividing plate, and the input shaft of change-speed box is connected with the other end of universal driving shaft by coupler, and the output shaft of change-speed box connects with the finger of rotary valve.
2. vehicle speed variation hydraulic steering gear according to claim 1, is characterized in that: described change-speed box also comprises spline housing, housing, shifting gear, engaging sleeve, internally toothed annulus, bolster, sun wheel, transition gear, gearshift internal tooth casing, shift fork, handle supporting, handle;
The inner of described output shaft is engaged with spline housing, and outer end connects with the finger of rotary valve;
Described spline housing is enclosed within by splined on output shaft, and output shaft moves vertically, and one end cylindrical of described spline housing is provided with groove, and this groove coordinates with shift fork, and the other end cylindrical of spline housing and shifting gear are consolidated;
Described internally toothed annulus and gearshift internal tooth casing consolidation are integrated, and internally toothed annulus engages with transition gear, and the gearshift internal tooth casing of opposite side engages with the external tooth engage a gear of shifting gear;
Described bolster is fixed on case of transmission, and transition gear is contained on bolster;
Described input shaft side connects with sun wheel, and opposite side connects with coupler;
Described sun wheel and engaging sleeve consolidation are integrated, and sun wheel engages with transition gear, and the engaging sleeve of sun wheel side can engage with shifting gear engage a gear;
Described handle supporting is fixed on housing, and handle supporting is porose.
3. vehicle speed variation hydraulic steering gear according to claim 2, it is characterized in that: the groove on described spline housing cylindrical and shift fork matching relationship are, described shift fork one end has arc fork to embed in the groove of spline housing one end, and the other end is that cylindrical shroud is enclosed within the axle of handle one end.
4. vehicle speed variation hydraulic steering gear according to claim 2, is characterized in that: described handle is arranged in the hole of handle supporting in a rotating manner, and is connected by axis hole with shift fork.
5. vehicle speed variation hydraulic steering gear according to claim 2, is characterized in that: described coupler is gimbal coupling.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310711674.8A CN103693101B (en) | 2013-12-20 | 2013-12-20 | A kind of vehicle speed variation hydraulic steering gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310711674.8A CN103693101B (en) | 2013-12-20 | 2013-12-20 | A kind of vehicle speed variation hydraulic steering gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103693101A CN103693101A (en) | 2014-04-02 |
| CN103693101B true CN103693101B (en) | 2016-04-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310711674.8A Expired - Fee Related CN103693101B (en) | 2013-12-20 | 2013-12-20 | A kind of vehicle speed variation hydraulic steering gear |
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| Country | Link |
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| CN (1) | CN103693101B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105405348B (en) * | 2015-12-11 | 2018-05-15 | 广东交通职业技术学院 | A kind of fully hydraulic servo steering teaching bench |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3339660A (en) * | 1964-09-14 | 1967-09-05 | Budzich Tadeusz | Hydrostatic mechanism |
| US4140199A (en) * | 1974-10-05 | 1979-02-20 | Coles Cranes Limited | Mobile crane |
| CN1824562A (en) * | 2006-03-27 | 2006-08-30 | 镇江液压件厂有限责任公司 | Geluote energy saving high efficiency hydraulic deflector |
| CN2913122Y (en) * | 2006-05-08 | 2007-06-20 | 宁波中意液压马达有限公司 | Combined valve type cycloidal hydraulic steering gear |
| CN203637935U (en) * | 2013-12-20 | 2014-06-11 | 华南理工大学 | Speed-changing hydraulic steering gear for vehicle |
-
2013
- 2013-12-20 CN CN201310711674.8A patent/CN103693101B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3339660A (en) * | 1964-09-14 | 1967-09-05 | Budzich Tadeusz | Hydrostatic mechanism |
| US4140199A (en) * | 1974-10-05 | 1979-02-20 | Coles Cranes Limited | Mobile crane |
| CN1824562A (en) * | 2006-03-27 | 2006-08-30 | 镇江液压件厂有限责任公司 | Geluote energy saving high efficiency hydraulic deflector |
| CN2913122Y (en) * | 2006-05-08 | 2007-06-20 | 宁波中意液压马达有限公司 | Combined valve type cycloidal hydraulic steering gear |
| CN203637935U (en) * | 2013-12-20 | 2014-06-11 | 华南理工大学 | Speed-changing hydraulic steering gear for vehicle |
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| CN103693101A (en) | 2014-04-02 |
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Granted publication date: 20160413 Termination date: 20211220 |
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