CN204921903U - Adopt mechanical hydraulic hybrid infinitely variable device of secondary component - Google Patents
Adopt mechanical hydraulic hybrid infinitely variable device of secondary component Download PDFInfo
- Publication number
- CN204921903U CN204921903U CN201520695320.3U CN201520695320U CN204921903U CN 204921903 U CN204921903 U CN 204921903U CN 201520695320 U CN201520695320 U CN 201520695320U CN 204921903 U CN204921903 U CN 204921903U
- Authority
- CN
- China
- Prior art keywords
- valve
- secondary component
- gear
- outlet
- planet row
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Abstract
The utility model discloses an adopt mechanical hydraulic hybrid infinitely variable device of secondary component, including device input shaft, hydraulic drive branch road, device output shaft, box, first planet row, second planet row, the ring gear that is arranged in arranging first planet and the second planet ring gear in arranging plays braking action's stopper and is used for control the transmission system of stopper. The utility model discloses a slewing range is great to can satisfy the requirement of medium -and -large -sized engineering machinery to transmission system.
Description
Technical field
The utility model belongs to machinery and hydraulic transmission and control technical field, relates to a kind of mechanical-hydraulic mixing stepless speed changes devices adopting secondary component.
Background technique
Hydraulic transmission has that quality is light, volume is little, specific power is large, and easily realize stepless speed regulation and the advantage such as controls automatically, but there is the deficiencys such as transmission efficiency is low simultaneously, especially in high speed and low speed rotation operating mode, transmission efficiency this deficiency low is more outstanding.Gear mechanism transmission have transmit motion accurately and reliably, constant, the compact structure of instantaneous transmission ratio, the large and transmission efficiency advantages of higher of comparatively big speed ratio, transmitted power can be realized, but not easily realize automatic speed changing, more cannot realize stepless change.Medium-and-large-sized engineering machinery is when operation, and transmission system often needs to transmit relatively high power, and requirement can carry out high efficiency speed and torque conversion according to working condition and load change to power source.Single use mechanical transmission or hydraulic transmission are all difficult to perfection and meet the requirement of medium-and-large-sized engineering machinery to transmission system.
For solving the problem, novel mechanical hydraulic hybrid transmission device becomes one of research direction.This type of hybrid transmission combines the advantage of machinery and hydraulic pressure two kinds of kinds of drive, mainly contain two kinds of structural types at present: one is that mechanical transmission branch road is connected with hydraulic transmission branch road, between the output terminal and traveller (or equipment) of oil hydraulic motor or hydraulic type speed change mechanism, mechanical type speed change gear is set, realize the stepless change of segmentation, expand the slewing range of transmission system, improve transmission efficiency, another kind is mechanical transmission branch road and hydraulic transmission branch circuit parallel connection, i.e. so-called power dividing transmission, engine output is divided into machinery and hydraulic pressure two strands " poower flow ", poower flow through mechanical transmission branch road can keep high efficiency transmission, utilize the controllability of hydraulic power stream simultaneously, these two strands of poower flow are made to realize the step-less adjustment of total output speed/moment of torsion when again converging, the advantage of mechanically operated high efficiency and hydraulic transmission stepless speed regulation combines by above-mentioned mixed drive, both there is stepless speed regulation performance, there is again greater efficiency and the speed change gear compared with wide speed regulating range.Wherein in two branch circuit parallel connection schemes, hydraulic transmission branch road generally only needs transmitting portions power, all the other power are born by the mechanical transmission branch road with higher transmission efficiency, substantially increase the efficiency of transmission system, stepless speed regulation performance in a big way can be obtained again, the usage requirement of medium-and-large-sized load working truck can be met, to lifting overall operation performance, energy-saving and cost-reducing significant.
In current existing mechanical-hydraulic mixed drive scheme, hydraulic transmission branch road many employings volume speed-modulating loop, can be divided into variable displacement pump-fixed displacement motor, metering pump-variable displacement motor and variable displacement pump-variable displacement motor three types.In theory, these three kinds of volume speed-modulating loops all can be used for mechanical-hydraulic hybrid transmission, but according to above-mentioned loop as hydraulic branch, the transmission of poower flow is unidirectional all the time, total output speed of hybrid transmission, be only " increase " speed of hydraulic transmission branch road on the basis of mechanical transmission branch road output speed, it is limited in one's ability that slewing range expands.
Model utility content
The purpose of this utility model is the shortcoming overcoming above-mentioned prior art, provides a kind of mechanical-hydraulic mixing stepless speed changes devices adopting secondary component, and the slewing range of this device is comparatively large, and can meet the requirement of medium-and-large-sized engineering machinery to transmission system.
For achieving the above object, the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component described in the utility model comprise device input shaft, hydraulic transmission branch road, device output shaft, casing, first planet row, the second planet row, for playing the break of braking action and the transmission system for controlling described break to the gear ring in first planet row and the gear ring in the second planet row;
First secondary component and the second secondary component are connected in series, the output shaft of the first secondary component is connected with device input shaft, the sun gear of first planet row is connected with device input shaft, the planet carrier of first planet row is connected with device output shaft, the sun gear of the second planet row is connected with the output shaft of the second secondary component, the planet carrier of the second planet row is fixed on casing, the gear ring of first planet row is connected with the gear ring of the second planet row, and the output shaft of hydraulic transmission branch road is connected with the swash plate of the swash plate of the first secondary component and the second secondary component.
Described transmission system comprises fuel tank, the first gear pump, accumulator, solenoid directional control valve and one-way throttle valve, the oil outlet of fuel tank is connected with the entrance of accumulator through the first gear pump, and the outlet of accumulator is connected with the filler opening of break through solenoid directional control valve and one-way throttle valve successively.
Described transmission system also comprises the first filter and the first relief valve, and the first gear delivery side of pump is divided into two-way, and wherein road first relief valve is connected with the return opening of fuel tank, and another road first filter is connected with the import of accumulator.
Described hydraulic transmission branch road comprises the second gear pump, first throttle valve second throttle, first electric proportional valve, second electric proportional valve, first swash plate performs oil hydraulic cylinder and the second swash plate performs oil hydraulic cylinder, fuel tank is divided into two-way after the second gear pump, wherein a road is connected through the filler opening of first throttle valve with the first electric proportional valve, another road is connected through the filler opening of second throttle with the second electric proportional valve, the filler opening that oil outlet and first swash plate of the first electric proportional valve perform oil hydraulic cylinder is connected, the piston rod that first swash plate performs oil hydraulic cylinder is connected with the swash plate of the first secondary component, the filler opening that oil outlet and second swash plate of the second electric proportional valve perform oil hydraulic cylinder is connected, the piston rod that second swash plate performs oil hydraulic cylinder is connected with the swash plate of the second secondary component.
Also comprise the second filter, the oil outlet of fuel tank is connected with the filler opening of the first gear pump and the filler opening of the second gear pump through the second filter.
Described hydraulic transmission branch road also comprises pressure shut-off valve, the 3rd throttle valve, the first one-way valve, the second one-way valve, the second relief valve, the 3rd relief valve, the 4th relief valve and flushing valve;
First actuator port of the first secondary component and the first filler opening of pressure shut-off valve, the outlet of the first one-way valve, the import of the second relief valve, first import of flushing valve and the first actuator port of the second secondary component are connected, second actuator port of the first secondary component and the second filler opening of pressure shut-off valve, the outlet of the second one-way valve, the import of the 3rd relief valve, second import of flushing valve and the second actuator port of the second secondary component are connected, second gear delivery side of pump is connected with the import of the 3rd throttle valve, the import of the 4th relief valve and the import of the first one-way valve, the import of the second one-way valve, the outlet of the second relief valve, outlet and the second gear delivery side of pump of the 3rd relief valve are connected, outlet and the outlet of flushing valve of the 4th relief valve are connected with the import of fuel tank.
The import of fuel tank is connected with the outlet of the 4th relief valve and the outlet of flushing valve through cooler.
The entrance of fuel tank is connected with the outlet of the 4th relief valve and the outlet of flushing valve through cooler.
The output shaft of described first secondary component is provided with the first gear, and device input shaft is provided with the second gear be meshed with described first gear;
The output shaft of described second secondary component is provided with the 3rd gear, and the sun gear of the second planet row is provided with the 4th gear be meshed with described 3rd gear.
The utility model has following beneficial effect:
The mechanical-hydraulic mixing stepless speed changes devices of employing secondary component described in the utility model operationally, arranged by first planet and the second planet row as mechanical transmission branch road, and using the first secondary component and the second secondary component composition volume speed-modulating loop as oil hydraulic circuit, the transmission being carried out pure mechanical transmission and mechanical-hydraulic mixed drive by break is switched, realize the mixed drive of machinery and hydraulic pressure two kinds of modes, improve the scope of speed change, and meet the requirement of medium-and-large-sized engineering machinery to transmission system.In addition, first secondary component and the second secondary component both can be used as oil hydraulic motor and had used, can be used as again oil hydraulic pump to use, during work, by regulating swash plate direction and angle, first secondary component and the second secondary component can work in the four-quadrant of rotating speed-moment of torsion coordinate plane, realize the mutual conversion of mechanical energy and hydraulic energy, volume speed-modulating loop is utilized not only to possess the advantage of variable displacement pump-variable displacement motor speed control system completely, and pass through the working condition of change first secondary component and the second secondary component, realize pump-motor and motor-pump two kinds of oil hydraulic circuits, during work, power can be obtained and return mechanism input shaft from device output shaft, the transmission of poower flow becomes bi-directional, the speed of hydraulic transmission branch road can not only be increased on the basis of mechanical transmission branch road output speed, also can deduct the speed of hydraulic transmission branch road, the utility model is not only made to have higher transmission efficiency, and expand slewing range further, realize the double of slewing range.
Accompanying drawing explanation
Fig. 1 is structural representation of the present utility model;
Fig. 2 is the structural representation of transmission system and hydraulic transmission branch road in the utility model.
Wherein, 1 is casing, 2 is the second gear, 3 is the first gear, 4 is the first secondary component, 5 is break, 6 is the second secondary component, 7 is the 3rd gear, 8 is the 4th gear, 9 is first planet row, 10 is the second planet row, 11 is cooler, 12 is one-way throttle valve, 13 is solenoid directional control valve, 14 is accumulator, 151 is the first relief valve, 152 is the second relief valve, 153 is the 3rd relief valve, 154 is the 4th relief valve, 16 is the first filter, 17 is the first gear pump, 18 is the second gear pump, 19 is the second filter, 201 is the first electric proportional valve, 202 is the second electric proportional valve, 211 is that the first swash plate performs oil hydraulic cylinder, 212 is that the second swash plate performs oil hydraulic cylinder, 221 is first throttle valve, 222 is second throttle, 223 is the 3rd throttle valve, 23 is flushing valve, 24 is pressure shut-off valve, 251 is the first one-way valve, 252 is the second one-way valve.
Embodiment
Below in conjunction with accompanying drawing, the utility model is described in further detail:
With reference to figure 1, the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component described in the utility model comprise device input shaft, hydraulic transmission branch road, device output shaft, casing 1, first planet row the 9, second planet row 10, first planet row the 9, second planet row 10, for playing the break 5 of braking action and the transmission system for controlling described break 5 to the gear ring in first planet row 9 and the gear ring in the second planet row 10, first secondary component 4 and the second secondary component 6 are connected in series, the output shaft of the first secondary component 4 is connected with device input shaft, the sun gear of first planet row 9 is connected with device input shaft, the planet carrier of first planet row 9 is connected with device output shaft, the sun gear of the second planet row 10 is connected with the output shaft of the second secondary component 6, the planet carrier of the second planet row 10 is fixed on casing 1, the gear ring of first planet row 9 is connected with the gear ring of the second planet row 10, the output shaft of hydraulic transmission branch road is connected with the swash plate of the swash plate of the first secondary component 4 and the second secondary component 6.
It should be noted that, described transmission system comprises fuel tank, the first gear pump 17, accumulator 14, solenoid directional control valve 13 and one-way throttle valve 12, the oil outlet of fuel tank is connected with the entrance of accumulator 14 through the first gear pump 17, and the outlet of accumulator 14 is connected with the filler opening of break 5 through solenoid directional control valve 13 and one-way throttle valve 12 successively.Described transmission system also comprises the first filter 16 and the first relief valve 151, the outlet of the first gear pump 17 is divided into two-way, wherein road first relief valve 151 is connected with the return opening of fuel tank, and another road first filter 16 is connected with the import of accumulator 14.
Described hydraulic transmission branch road comprises the second gear pump 18, first throttle valve 221, second throttle 222, first electric proportional valve 201, second electric proportional valve 202, first swash plate performs oil hydraulic cylinder 211 and the second swash plate performs oil hydraulic cylinder 212, fuel tank is divided into two-way after the second gear pump 18, wherein a road is connected through the filler opening of first throttle valve 221 with the first electric proportional valve 201, another road is connected through the filler opening of second throttle 222 with the second electric proportional valve 202, the filler opening that oil outlet and first swash plate of the first electric proportional valve 201 perform oil hydraulic cylinder 211 is connected, the piston rod that first swash plate performs oil hydraulic cylinder 211 is connected with the swash plate of the first secondary component 4, the filler opening that oil outlet and second swash plate of the second electric proportional valve 202 perform oil hydraulic cylinder 212 is connected, the piston rod that second swash plate performs oil hydraulic cylinder 212 is connected with the swash plate of the second secondary component 6.In addition, the utility model also comprises the second filter 19, and the oil outlet of fuel tank is connected with the filler opening of the first gear pump 17 and the filler opening of the second gear pump 18 through the second filter 19.
Described hydraulic transmission branch road also comprises pressure shut-off valve 24, the 3rd throttle valve 223, first one-way valve 251, second one-way valve 252, second relief valve 152, the 3rd relief valve 153, the 4th relief valve 154 and flushing valve 23, first actuator port of the first secondary component 4 and the first filler opening of pressure shut-off valve 24, the outlet of the first one-way valve 251, the import of the second relief valve 152, first import of flushing valve 23 and the first actuator port of the second secondary component 6 are connected, second actuator port of the first secondary component 4 and the second filler opening of pressure shut-off valve 24, the outlet of the second one-way valve 252, the import of the 3rd relief valve 153, second import of flushing valve 23 and the second actuator port of the second secondary component 6 are connected, the outlet of the second gear pump 18 is connected with the import of the 3rd throttle valve 223, the import of the 4th relief valve 154 and the import of the first one-way valve 251, the import of the second one-way valve 252, the outlet of the second relief valve 152, the outlet of the 3rd relief valve 153 and the outlet of the second gear pump 18 are connected, outlet and the outlet of flushing valve 23 of the 4th relief valve 154 are connected with the import of fuel tank.
The entrance of fuel tank is connected with the outlet of the 4th relief valve 154 and the outlet of flushing valve 23 through cooler 11, and the output shaft of the first secondary component 4 is provided with the first gear 3, and device input shaft is provided with the second gear 2 be meshed with described first gear 3; The sun gear that the output shaft of described second secondary component 6 is provided with the 3rd gear 7, second planet row 10 is provided with the 4th gear 8 be meshed with described 3rd gear 7.
Device input shaft rotating speed divides two-way, wherein a road is hydraulic transmission branch road, by the adjustment of the first secondary component 4 and the second secondary component 6 discharge capacity, rotating speed is delivered to the sun gear of the second planet row 10, another road is mechanical transmission branch road, input speed is directly delivered to the sun gear of first planet row 9, then rotating speed is delivered to the planet carrier of first planet row 9, i.e. device output shaft; The gear ring that gear ring and the first planet of the second planet row 10 arrange 9 is connected, the rotating speed of sun gear in second planet row 10 is delivered to the gear ring of first planet row 9, utilize the relation between planet row three component, the rotating speed of two branch road transmission converges at the planet carrier of first planet row 9, obtains final output speed.
Wherein, the relation between planet row three component is as follows:
n
s+kn
r-(1+k)n
c＝0(1)
M
s:M
r:M
c＝1:k:-(1+k)(2)
Wherein, n
s, n
rand n
cbe respectively the rotating speed of planet row sun gear, gear ring and planet carrier; M
s, M
rand M
cbe respectively the moment of torsion of planet row sun gear, gear ring and planet carrier; K is planet row special parameter.
Connect between all-in-one-piece gear ring and casing 1 first planet row 9 and the second planet row 10 and break 5 is set, realize the switching between mixing stepless speed changes devices operating mode by the opening and closing of regulating brake 5.
During break 5 locking, the gear ring of first planet row 9 and the second planet row 10 is fixed on casing 1, first secondary component 4 and the second secondary component 6 are in zero delivery, second planet row 10 is in free state, the sun gear rotating speed of the second planet row 10 cannot be delivered to the gear ring of first planet row 9, therefore the rotating speed of hydraulic transmission branch road transmission can not act on the planet carrier of first planet row 9, now speed change gear is in pure mechanical transmission operating mode.
When break 5 is opened, the gear ring of first planet row 9 and the second planet row 10 is unrestricted, the relation between planet row three component is utilized the rotating speed of hydraulic transmission branch road to be delivered to the planet carrier of first planet row 9, the rotating speed of hydraulic transmission branch road and mechanical transmission branch road converges, obtain final output speed after superposition, now speed change gear is in machinery and hydraulic hybrid transmission condition; Regulate the discharge capacity of the first secondary component 4 and the second secondary component 6 in hydraulic transmission branch road, thus change the size and Orientation of hydraulic transmission branch road output speed, thus realize the control to device output shaft rotating speed, mixed drive can be divided into speedup and two kinds of operating modes of slowing down.
If n
iand n
obe respectively the rotating speed of device input shaft and the rotating speed of device output shaft; n
sa, n
raand n
cabe respectively the rotating speed of the sun gear of first planet row 9, gear ring and planet carrier; k
aand k
bbe respectively first planet row 9 and and the special parameter of the second planet row 10; η
v4and η
v6be respectively the volumetric efficiency of the first secondary component 4 and the second secondary component 6; q
4and q
6be respectively the discharge capacity of the first secondary component 4 and the second secondary component 6; n
2, n
3, n
6and n
7be respectively the rotating speed of the second gear 2, first gear 3, the 3rd gear 7 and the 4th gear 8; z
2, z
3, z
6and z
7be respectively the number of teeth of the second gear 2, first gear 3, the 3rd gear 7 and the 4th gear 8; The input output velocity relationship (velocity ratio) of the utility model under three kinds of operating modes is as follows:
1) pure mechanical transmission operating mode
As shown in Figure 1, the resultant gear ratio i of speed change gear is device output speed n
owith input speed n
iratio, namely
i is compared in the fixed axis gear auxiliary driving of the first gear 3 and the second gear 2 and the 3rd gear 7 and the 4th gear 8 composition
1and i
2be respectively
under this operating mode, n
i=n
sa, n
o=n
ca, n
ra=0, the resultant gear ratio of speed change gear is
In vehicle operation, when pure mechanical transmission can meet job requirements, pure mechanical transmission operating mode should be used, to obtain higher transmission efficiency as far as possible.
2) mixed drive speedup operating mode
Mixed drive speedup operating mode can increase output speed on pure mechanically operated basis.As shown in Figure 1, under this operating mode, sun gear and the gear ring of first planet row 9 turn to identical (n
ra>0), planet carrier and the casing 1 of the second planet row 10 are fixed, then n
cb=0, the gear ring connection one of first planet row 9 and the second planet row 10, therefore turn to identical and be just, the planet carrier of the second planet row 10 fixes (n
cb=0), now the sun gear of the second planet row 10 turns to as negative (n
sb<0), the resultant gear ratio i of speed change gear is
Speedup operating mode can meet the fair speed requirement needed for the operating modes such as transition.
3) mixed drive decelerating mode
When pure mechanical transmission operating mode can not meet the load request of vehicle operation, or when vehicle needs to export lower stable operating speed, adopt mixed drive decelerating mode can play the effect of deceleration (increasing is turned round), reach job requirements.In addition, during vehicle start, adopt this operating mode can obtain starting performance comparatively stably, as shown in Figure 1, under decelerating mode, sun gear and the gear ring of first planet row 9 turn to (n on the contrary
ra<0), planet carrier and the casing 1 of the second planet row 10 are fixed, then n
cb=0, from planet row three component rotation speed relation, now the sun gear of the second planet row 10 turns to as just (n
sb>0), the resultant gear ratio i of speed change gear is
Mechanical-hydraulic mixing stepless speed changes devices adopts hydraulic control system, mainly completes the control to the first secondary component 4, second secondary component 6 and break 5.Wherein, the hydraulic control loop of the first secondary component 4 and the second secondary component 6 is made up of two electric proportional valves, two swash plate execution oil hydraulic cylinders, pressure shut-off valve 24, three throttle valve, two one-way valves, three relief valves, flushing valve 23 and coolers 11; The hydraulic control loop of break 5 is made up of solenoid directional control valve 13, one-way throttle valve 12, accumulator 14, two oil purifiers and relief valve.
The first electric proportional valve 201 and the first electric proportional valve 202 is adopted to realize to the control of the first secondary component 4 and the second secondary component 6, by giving the first electric proportional valve 201 and the second electric proportional valve 202 input control signal respectively, thus control the piston rod position of the first swash plate execution oil hydraulic cylinder 211 and the piston rod position of the second swash plate execution oil hydraulic cylinder 212, thus the control realized the first secondary component 4 and the second secondary component 6, thus the velocity ratio needed for obtaining, for the first electric proportional valve 201 in Fig. 2, move to right at electrical signal effect lower valve core, first swash plate performs on the right side of oil hydraulic cylinder 211 oil-filled, left side draining, hydraulic cylinder piston rod moves to left, the swash plate of the first secondary component 4 turns clockwise, if move to left at electrical signal effect lower valve core, then the left side of the first swash plate execution oil hydraulic cylinder 211 is oil-filled, right side draining, hydraulic cylinder piston rod moves to right, the swash plate of the first secondary component 4 is rotated counterclockwise, first electric proportional valve 201 and the second electric proportional valve 202 are under the control of different electrical signals, and adjustable first secondary component 4 and the second secondary component 6 obtain different swash plate angle, and then obtain target discharge capacity.As shown in Figure 1, for forward when exceeding meta clockwise with the swash plate of secondary component, when the first secondary component 4 swash plate direction is just, the swash plate direction of the second secondary component 6 is for time negative, first secondary component 4-second secondary component 6 is in pump-motor operating conditions, and hybrid transmission is in speedup operating mode; Otherwise when the first secondary component 44 swash plate direction is negative, the swash plate direction of the second secondary component 6 is timing, and the first secondary component 4-second secondary component 6 is in motor-pump condition, and hybrid transmission is in decelerating mode.
The utility model adopts solenoid directional control valve 13 as the control unit of break 5 opening and closing, under control signal effect, when the right position of solenoid directional control valve 13 is connected, hydraulic system starts the execution oil hydraulic cylinder of break 5 oil-filled, under the promotion of the execution hydraulic cylinder piston rod of break 5, break 5 rotating plate and driven plate engage, and hydraulic branch participates in speed superposition; When the left position of solenoid directional control valve 13 is connected, the quick draining of execution oil hydraulic cylinder of break 5, the rotating plate of break 5 is separated with driven plate, and hydraulic branch does not participate in speed superposition.
Claims (8)
1. one kind adopts the mechanical-hydraulic mixing stepless speed changes devices of secondary component, it is characterized in that, comprise device input shaft, hydraulic transmission branch road, device output shaft, casing (1), first planet row (9), the second planet row (10), for playing the break (5) of braking action and the transmission system for controlling described break (5) to the gear ring in first planet row (9) and gear ring in the second planet row (10);
First secondary component (4) and the second secondary component (6) are connected in series, the output shaft of the first secondary component (4) is connected with device input shaft, the sun gear of first planet row (9) is connected with device input shaft, the planet carrier of first planet row (9) is connected with device output shaft, the sun gear of the second planet row (10) is connected with the output shaft of the second secondary component (6), the planet carrier of the second planet row (10) is fixed on casing (1), the gear ring of first planet row (9) is connected with the gear ring of the second planet row (10), the output shaft of hydraulic transmission branch road is connected with the swash plate of the swash plate of the first secondary component (4) and the second secondary component (6).
2. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 1, it is characterized in that, described transmission system comprises fuel tank, the first gear pump (17), accumulator (14), solenoid directional control valve (13) and one-way throttle valve (12), the oil outlet of fuel tank is connected through the entrance of the first gear pump (17) with accumulator (14), and the outlet of accumulator (14) is connected with the filler opening of break (5) through solenoid directional control valve (13) and one-way throttle valve (12) successively.
3. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 2, it is characterized in that, described transmission system also comprises the first filter (16) and the first relief valve (151), the outlet of the first gear pump (17) is divided into two-way, wherein a road first relief valve (151) is connected with the return opening of fuel tank, and another road first filter (16) is connected with the import of accumulator (14).
4. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 3, it is characterized in that, described hydraulic transmission branch road comprises the second gear pump (18), first throttle valve (221), second throttle (222), first electric proportional valve (201), second electric proportional valve (202), first swash plate performs oil hydraulic cylinder (211) and the second swash plate performs oil hydraulic cylinder (212), fuel tank is divided into two-way after the second gear pump (18), wherein a road is connected through the filler opening of first throttle valve (221) with the first electric proportional valve (201), another road is connected through the filler opening of second throttle (222) with the second electric proportional valve (202), the filler opening that oil outlet and first swash plate of the first electric proportional valve (201) perform oil hydraulic cylinder (211) is connected, the piston rod that first swash plate performs oil hydraulic cylinder (211) is connected with the swash plate of the first secondary component (4), the filler opening that oil outlet and second swash plate of the second electric proportional valve (202) perform oil hydraulic cylinder (212) is connected, the piston rod that second swash plate performs oil hydraulic cylinder (212) is connected with the swash plate of the second secondary component (6).
5. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 4, it is characterized in that, also comprise the second filter (19), the oil outlet of fuel tank is connected with the filler opening of the first gear pump (17) and the filler opening of the second gear pump (18) through the second filter (19).
6. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 5, it is characterized in that, described hydraulic transmission branch road also comprises pressure shut-off valve (24), the 3rd throttle valve (223), the first one-way valve (251), the second one-way valve (252), the second relief valve (152), the 3rd relief valve (153), the 4th relief valve (154) and flushing valve (23);
First actuator port of the first secondary component (4) and the first filler opening of pressure shut-off valve (24), the outlet of the first one-way valve (251), the import of the second relief valve (152), first import of flushing valve (23) and the first actuator port of the second secondary component (6) are connected, second actuator port of the first secondary component (4) and the second filler opening of pressure shut-off valve (24), the outlet of the second one-way valve (252), the import of the 3rd relief valve (153), second import of flushing valve (23) and the second actuator port of the second secondary component (6) are connected, the outlet of the second gear pump (18) is connected with the import of the 3rd throttle valve (223), the import of the 4th relief valve (154) and the import of the first one-way valve (251), the import of the second one-way valve (252), the outlet of the second relief valve (152), the outlet of the 3rd relief valve (153) and the outlet of the second gear pump (18) are connected, the outlet of the 4th relief valve (154) and the outlet of flushing valve (23) are connected with the import of fuel tank.
7. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 6, it is characterized in that, the import of fuel tank is connected with the outlet of the 4th relief valve (154) and the outlet of flushing valve (23) through cooler (11).
8. the mechanical-hydraulic mixing stepless speed changes devices of employing secondary component according to claim 1, it is characterized in that, the output shaft of described first secondary component (4) is provided with the first gear (3), and device input shaft is provided with the second gear (2) be meshed with described first gear (3);
The output shaft of described second secondary component (6) is provided with the 3rd gear (7), and the sun gear of the second planet row (10) is provided with the 4th gear (8) be meshed with described 3rd gear (7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520695320.3U CN204921903U (en) | 2015-09-09 | 2015-09-09 | Adopt mechanical hydraulic hybrid infinitely variable device of secondary component |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520695320.3U CN204921903U (en) | 2015-09-09 | 2015-09-09 | Adopt mechanical hydraulic hybrid infinitely variable device of secondary component |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204921903U true CN204921903U (en) | 2015-12-30 |
Family
ID=54971032
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520695320.3U Expired - Fee Related CN204921903U (en) | 2015-09-09 | 2015-09-09 | Adopt mechanical hydraulic hybrid infinitely variable device of secondary component |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204921903U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105090427A (en) * | 2015-09-09 | 2015-11-25 | 长安大学 | Mechanical-hydraulic hybrid stepless speed change device with secondary elements |
-
2015
- 2015-09-09 CN CN201520695320.3U patent/CN204921903U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105090427A (en) * | 2015-09-09 | 2015-11-25 | 长安大学 | Mechanical-hydraulic hybrid stepless speed change device with secondary elements |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105090427A (en) | Mechanical-hydraulic hybrid stepless speed change device with secondary elements | |
| CN103223849B (en) | A kind of parallel-connection type hybrid power driver for vehicle | |
| CN103591247B (en) | Geometric ratio four-part form hydraulic machinery compound continuously variable transmittion | |
| CN103213487B (en) | Based on the drive device for hybrid vehicle of voltage transformer, Hydraulic Pump and multi-joint motor | |
| CN107143540B (en) | Digital load sensing hydraulic control system and method | |
| CN105263733A (en) | A power system for a working machine | |
| CN108591144B (en) | Hydraulic system of motor-driven double-dosing pump double-accumulator distributed direct-drive excavator | |
| CN103062140A (en) | Hydraulic device on basis of confluence control mode | |
| CN112483623B (en) | Mechanical hydraulic composite multi-mode driving system | |
| CN111946794B (en) | Power split type mechanical-hydraulic compound transmission system with automatic adjusting function | |
| CN101788052B (en) | Motor driven CVT (continuously variable transmission) electro-hydraulic control system | |
| CN107859723B (en) | A kind of multi-mode hydraulic machinery stepless speed change device | |
| CN204921903U (en) | Adopt mechanical hydraulic hybrid infinitely variable device of secondary component | |
| CN103419630A (en) | Vehicular self-drive hydraulic control system with function of inertial energy accumulation | |
| CN113006190B (en) | Control device of closed type traveling system of wheel type excavator | |
| CN105015316B (en) | Possesses the hydraulic hybrid power transmission system of self adaptation commutation function | |
| CN104442340A (en) | Composite double-planet-row type hydraulically-driven hybrid power system | |
| CN106246859A (en) | A kind of buncher of composite hydraulic torque converter | |
| CN103171429A (en) | Hybrid power vehicle driving device based on variable pump and quantitative multi-joint motor | |
| CN204398866U (en) | High-power all-hydraulic liquid nitrogen pump actuating device and direct-combustion type liquid nitrogen pump truck | |
| CN207018464U (en) | A kind of machine liquid composite transmission based on Stress control | |
| CN101215841B (en) | Hydraulic grader transmission gear | |
| CN1600672A (en) | Speed adjustable cable hoist driven through pressure-fluid | |
| CN202944560U (en) | Hydraulic system for controlling float-garbage ship to travel | |
| CN106402063B (en) | Travelling control valve group, hydraulic closed running gear and aerial working platform vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151230 Termination date: 20160909 |