U.S. patent application number 17/050427 was filed with the patent office on 2021-08-12 for hydro-mechanical hybrid transmission device and control method thereof.
This patent application is currently assigned to JIANGSU UNIVERSITY. The applicant listed for this patent is JIANGSU UNIVERSITY. Invention is credited to Yingfeng CAI, Long CHEN, Jiangyi HAN, Longhui LAI, Dehua SHI, Xiaodong SUN, Xiang TIAN, Changgao XIA, Chaochun YUAN, Zhen ZHU.
Application Number | 20210245597 17/050427 |
Document ID | / |
Family ID | 1000005735954 |
Filed Date | 2021-08-12 |
United States Patent
Application |
20210245597 |
Kind Code |
A1 |
ZHU; Zhen ; et al. |
August 12, 2021 |
HYDRO-MECHANICAL HYBRID TRANSMISSION DEVICE AND CONTROL METHOD
THEREOF
Abstract
A hydro-mechanical hybrid transmission device and a control
method thereof, including an input shaft, a split mechanism, a
hydraulic transmission assembly, a mechanical transmission
assembly, a convergence mechanism, and an output shaft, wherein the
input shaft is connected, through the split mechanism, to the
hydraulic transmission assembly and the mechanical transmission
assembly, wherein the hydraulic transmission assembly and the
mechanical transmission assembly are connected in parallel, and the
hydraulic transmission assembly and the mechanical transmission
assembly are each connected to the output shaft through the
convergence mechanism. In the hydro-mechanical hybrid transmission
device, planetary gear structures are combined with
engagement/disengagement of brakes and clutches, to implement
switching of power split and convergence structural forms.
Inventors: |
ZHU; Zhen; (Zhenjiang,
CN) ; CAI; Yingfeng; (Zhenjiang, CN) ; CHEN;
Long; (Zhenjiang, CN) ; XIA; Changgao;
(Zhenjiang, CN) ; HAN; Jiangyi; (Zhenjiang,
CN) ; TIAN; Xiang; (Zhenjiang, CN) ; SUN;
Xiaodong; (Zhenjiang, CN) ; LAI; Longhui;
(Zhenjiang, CN) ; SHI; Dehua; (Zhenjiang, CN)
; YUAN; Chaochun; (Zhenjiang, CN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
JIANGSU UNIVERSITY |
Zhenjiang |
|
CN |
|
|
Assignee: |
JIANGSU UNIVERSITY
Zhenjiang
CN
|
Family ID: |
1000005735954 |
Appl. No.: |
17/050427 |
Filed: |
December 4, 2019 |
PCT Filed: |
December 4, 2019 |
PCT NO: |
PCT/CN2019/122860 |
371 Date: |
October 23, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16H 37/10 20130101;
B60K 6/365 20130101; F16H 47/04 20130101 |
International
Class: |
B60K 6/365 20060101
B60K006/365; F16H 47/04 20060101 F16H047/04 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 6, 2019 |
CN |
201911076475.8 |
Claims
1. A hydro-mechanical hybrid transmission device, comprising an
input shaft, a split mechanism, a hydraulic transmission assembly,
a mechanical transmission assembly, a convergence mechanism, and an
output shaft, wherein the input shaft is connected, through the
split mechanism, to the hydraulic transmission assembly and the
mechanical transmission assembly wherein the hydraulic transmission
assembly and the mechanical transmission assembly are connected in
parallel, and the hydraulic transmission assembly and the
mechanical transmission assembly are each connected to the output
shaft through the convergence mechanism; the split mechanism
comprises a clutch C.sub.3, a split mechanism sun gear, a split
mechanism planet carrier, a split mechanism ring gear, and a brake
B.sub.1, wherein the clutch C.sub.3 is connected to the split
mechanism sun gear and the split mechanism planet carrier, the
brake B.sub.1 is connected to the split mechanism ring gear, the
input shaft is connected to the split mechanism sun gear, the split
mechanism is connected to the hydraulic transmission assembly
through the split mechanism ring gear, and the split mechanism is
connected to the mechanical transmission assembly through the split
mechanism sun gear and the split mechanism planet carrier; the
convergence mechanism comprises a brake B.sub.6, a convergence
mechanism ring gear, a convergence mechanism planet carrier, a
convergence mechanism sun gear, and a clutch C.sub.7, wherein the
brake B.sub.6 is connected to the convergence mechanism ring gear,
the clutch C.sub.7 is connected to the convergence mechanism planet
carrier and the convergence mechanism sun gear, the convergence
mechanism is connected to the hydraulic transmission assembly
through the convergence mechanism ring gear, the convergence
mechanism is connected to the mechanical transmission assembly
through the convergence mechanism sun gear, and the convergence
mechanism is connected to the output shaft through the convergence
mechanism planet carrier and the convergence mechanism sun gear;
the hydraulic transmission assembly comprises a hydraulic
transmission input clutch C.sub.1, a hydraulic transmission input
gear pair, a unidirectional variable pump, a hydraulic pipe, a
unidirectional quantitative motor, a reverse gear pair, a hydraulic
transmission output gear pair, and a hydraulic transmission output
clutch C.sub.2, wherein the unidirectional variable pump is
connected to the split mechanism through the hydraulic transmission
input gear pair, the hydraulic transmission input clutch C.sub.1 is
arranged between the hydraulic transmission input gear pair and the
unidirectional variable pump, the unidirectional variable pump is
connected to the unidirectional quantitative motor through the
hydraulic pipe, the unidirectional quantitative motor is connected
to the convergence mechanism sequentially through the hydraulic
transmission output gear pair and the reverse gear pair, and the
hydraulic transmission output clutch C.sub.2 is arranged between
the unidirectional quantitative motor and the hydraulic
transmission output gear pair.
2. The hydro-mechanical hybrid transmission device according to
claim 1, wherein the mechanical transmission assembly comprises a
front-set sun gear, a front-set planet carrier, a front-set ring
gear, a rear-set sun gear, a rear-set planet carrier, a rear-set
ring gear, a clutch C.sub.4, a clutch C.sub.5, a clutch C.sub.6, a
brake B.sub.2, a brake B.sub.3, a brake B.sub.4, a brake B.sub.5, a
one-way clutch F.sub.1, a one-way clutch F.sub.2, and a one-way
clutch F.sub.3; wherein the front-set sun gear is connected to the
split mechanism through the clutch C.sub.5 and the clutch C.sub.6,
wherein the clutch C.sub.5 and the clutch C.sub.6 are connected in
parallel, the one-way clutch F.sub.1 is arranged between the clutch
C.sub.5 and the front-set sun gear, and the one-way clutch F.sub.2
is arranged between the clutch C.sub.6 and the front-set sun gear,
the one-way clutch F.sub.1 and the one-way clutch F.sub.2 have
opposite power conduction directions, and the front-set sun gear is
also connected to the brake B.sub.3; the front-set planet carrier
is connected to the split mechanism through the clutch C.sub.4, the
brake B.sub.2 is arranged between the front-set planet carrier and
the clutch C.sub.4, and the front-set planet carrier is fixedly
connected to the rear-set ring gear; the front-set ring gear is
connected to the rear-set planet carrier and the convergence
mechanism; the rear-set sun gear is connected to the brake B.sub.4
and the brake B.sub.5, wherein the brake B.sub.4 and the brake
B.sub.5 are connected in parallel, the one-way clutch F.sub.3 is
arranged between the rear-set sun gear and the brake B.sub.5, and a
brake direction of the one-way clutch F.sub.3 is a rotation
direction of the rear-set sun gear and the rotation direction of
the rear-set sun gear is opposite to a rotation direction of the
split mechanism planet carrier; the rear-set planet carrier is
connected to the front-set ring gear and the convergence mechanism;
the rear-set ring gear is connected to the front-set planet carrier
and the split mechanism, and the brake B.sub.2 and the clutch
C.sub.4 in parallel connection are arranged between the rear-set
ring gear and the split mechanism.
3. A control method of the hydro-mechanical hybrid transmission
device according to claim 2, wherein three types of transmission in
a forward direction, comprising a forward pure hydraulic
transmission, a forward hydro-mechanical hybrid transmission, and a
forward pure mechanical transmission, and three types of
transmission in a reverse direction, comprising a reverse pure
hydraulic transmission, a reverse hydro-mechanical hybrid
transmission, and a reverse pure mechanical transmission, are
implemented through a combination and an engagement/disengagement
of the brakes and the clutches; wherein in the forward pure
hydraulic transmission, the brake B.sub.2, the hydraulic
transmission input clutch C.sub.1, the hydraulic transmission
output clutch C.sub.2, the clutch C.sub.4, and the clutch C.sub.7
are engaged, while other brakes and clutches are disengaged; when
the brake B.sub.2 and the clutch C.sub.4 are engaged, the split
mechanism planet carrier is locked, the split mechanism sun gear
and the split mechanism ring gear rotate in opposite directions,
and power passes through the input shaft, the split mechanism, the
hydraulic transmission assembly, and the convergence mechanism and
the power is output from the output shaft; when the clutch C.sub.7
is engaged, the convergence mechanism planet carrier and the
convergence mechanism sun gear of the convergence mechanism are
interlocked, an entire convergence mechanism rotates, and by an
action of the reverse gear pair, the input shaft and the output
shaft rotate in a same direction; in the forward pure mechanical
transmission, the brake B.sub.1 and the brake B.sub.6 are engaged,
while the brake B.sub.2, the brake B.sub.4, the hydraulic
transmission input clutch C.sub.1, the hydraulic transmission
output clutch C.sub.2, the clutch C.sub.3, and the clutch C.sub.7
are disengaged; the power passes through the input shaft, the split
mechanism, the mechanical transmission assembly, and the
convergence mechanism and the power is output from the output
shaft; when the brake B.sub.1 is engaged, the split mechanism ring
gear is locked, and the split mechanism sun gear and the split
mechanism planet carrier transmit the power as gear transmission
mechanisms; when the brake B.sub.6 is engaged, the convergence
mechanism ring gear is locked, and power passes through the
convergence mechanism sun gear and the convergence mechanism planet
carrier to the output shaft; in the forward hydro-mechanical hybrid
transmission, the hydraulic transmission input clutch C.sub.1, the
hydraulic transmission output clutch C.sub.2, and the clutch
C.sub.7 are engaged, while the brake B.sub.1, the brake B.sub.3,
the brake B.sub.5, the brake B.sub.6, the clutch C.sub.3, and the
one-way clutch F.sub.3 are disengaged; the power passes through the
input shaft to the split mechanism, transmitted by the split
mechanism to the hydraulic transmission assembly and the mechanical
transmission assembly respectively, then converged by the
convergence mechanism, and output from the output shaft; when the
clutch C.sub.3 is disengaged, the split mechanism planet carrier
transmits a first part of the power from the input shaft to the
mechanical transmission assembly, and the split mechanism ring gear
transmits a second part of the power from the input shaft to the
hydraulic transmission assembly; when the clutch C.sub.7 is
engaged, the power in the mechanical transmission assembly passes
through the convergence mechanism sun gear and the convergence
mechanism planet carrier and is transmitted to the output shaft,
the power in the hydraulic transmission assembly passes through the
convergence mechanism ring gear and the convergence mechanism
planet carrier and is transmitted to the output shaft, and the
convergence mechanism planet carrier rotates in the same direction
as the input shaft within a set displacement ratio range; in the
reverse pure hydraulic transmission, the hydraulic transmission
input clutch C.sub.1, the hydraulic transmission output clutch
C.sub.2, the clutch C.sub.3, and the clutch C.sub.7 are engaged,
while the other brakes and clutches are disengaged; when the clutch
C.sub.3 is engaged, the split mechanism sun gear and the split
mechanism planet carrier are interlocked, an entire split mechanism
rotates, and the power passes through the input shaft, the split
mechanism, the hydraulic transmission assembly, and the convergence
mechanism and the power is output from the output shaft; when the
clutch C.sub.7 is engaged, the convergence mechanism planet carrier
and the convergence mechanism sun gear of the convergence mechanism
are interlocked, the entire convergence mechanism rotates, and the
input shaft and the output shaft rotate in the opposite directions;
in the reverse pure mechanical transmission, the brake B.sub.1, the
brake B.sub.2, the brake B.sub.6, the clutch C.sub.6, and the
one-way clutch F.sub.2 are engaged, while the other brakes and
clutches are disengaged; when the brake B.sub.1 is engaged, the
split mechanism ring gear is locked, and the power passes through
the split mechanism sun gear and the split mechanism planet carrier
and the power is transmitted to the mechanical transmission
assembly; when the clutch C.sub.6 and the one-way clutch F.sub.2
are engaged, the power in the mechanical transmission assembly
sequentially passes through the clutch C.sub.6, the one-way clutch
F.sub.2, the front-set sun gear, and the front-set ring gear, and
is then transmitted to the convergence mechanism sun gear; when the
brake B.sub.6 is engaged, the convergence mechanism ring gear is
locked, and the power passes through the convergence mechanism sun
gear and the convergence mechanism planet carrier to the output
shaft; in the reverse hydro-mechanical hybrid transmission, the
hydraulic transmission input clutch C.sub.1, the hydraulic
transmission output clutch C.sub.2, and the clutch C.sub.3 are
engaged, while the brake B.sub.1, the brake B.sub.3, the brake
B.sub.5, the brake B.sub.6, the clutch C.sub.7, and the one-way
clutch F.sub.3 are disengaged; the power passes through the input
shaft to the split mechanism, transmitted by the split mechanism to
the hydraulic transmission assembly and the mechanical transmission
assembly respectively, then converged by the convergence mechanism,
and output from the output shaft; when the clutch C.sub.3 is
engaged, the split mechanism planet carrier transmits the first
part of the power from the input shaft to the mechanical
transmission assembly, and the split mechanism ring gear transmits
the second part of the power from the input shaft to the hydraulic
transmission assembly; when the clutch C.sub.7 is disengaged, the
power in the mechanical transmission assembly passes through the
convergence mechanism sun gear and the convergence mechanism planet
carrier and is transmitted to the output shaft, the power in the
hydraulic transmission assembly passes through the convergence
mechanism ring gear and the convergence mechanism planet carrier
and is transmitted to the output shaft, and the convergence
mechanism planet carrier rotates in a direction opposite to the
input shaft within the set displacement ratio range.
4. The control method of the hydro-mechanical hybrid transmission
device according to claim 3, wherein the forward pure mechanical
transmission comprises a first mechanical gear, a second mechanical
gear, a third mechanical gear, and a fourth mechanical gear,
specifically implemented as follows: in the first mechanical gear,
the brake B.sub.5, the one-way clutch F.sub.3, the clutch C.sub.6,
and the one-way clutch F.sub.2 are engaged, while the brake
B.sub.3, the clutch C.sub.4, the clutch C.sub.5, and the one-way
clutch F.sub.1 are disengaged; the power sequentially passes
through the clutch C.sub.6, the one-way clutch F.sub.2, and the
front-set sun gear to the front-set planet carrier, and the power
is split at the front-set planet carrier into the front-set ring
gear and the rear-set ring gear respectively; the power in the
rear-set ring gear passes through the rear-set planet carrier and
the power is converged with the power in the front-set ring gear,
and the power is then transmitted to the convergence mechanism;
when the brake B.sub.5 and the one-way clutch F.sub.3 are engaged,
the rear-set sun gear is locked; in the second mechanical gear, the
brake B.sub.5, the one-way clutch F.sub.3, and the clutch C.sub.4
are engaged, while the brake B.sub.3, the clutch C.sub.5, the
clutch C.sub.6, the one-way clutch F.sub.1, and the one-way clutch
F.sub.2 are disengaged; the power sequentially passes through the
clutch C.sub.4, the rear-set ring gear, and the rear-set planet
carrier, and the power is then transmitted to the convergence
mechanism; when the brake B.sub.5 and the one-way clutch F.sub.3
are engaged, the rear-set sun gear is locked; in the third
mechanical gear, the brake B.sub.5, the clutch C.sub.4, the clutch
C.sub.5, the one-way clutch F.sub.1, and the one-way clutch F.sub.3
are engaged, while the brake B.sub.3, the clutch C.sub.6, and the
one-way clutch F.sub.2 are disengaged; the power sequentially
passes through the clutch C.sub.4, the front-set planet carrier,
and the front-set ring gear, and the power is then transmitted to
the convergence mechanism; since the clutch C.sub.5 and the one-way
clutch F.sub.1 are engaged, the front-set sun gear is prevented
from an overspeed rotation and the front-set sun gear rotates at a
speed consistent with the front-set planet carrier, enabling an
entire front planetary gear set mechanism to rotate; in the fourth
mechanical gear, the brake B.sub.3 and the clutch C.sub.4 are
engaged, while the brake B.sub.5, the clutch C.sub.5, the clutch
C.sub.6, the one-way clutch F.sub.1, the one-way clutch F.sub.2,
and the one-way clutch F.sub.3 are disengaged; the power
sequentially passes through the clutch C.sub.4, the front-set
planet carrier, and the front-set ring gear, and the power is then
transmitted to the convergence mechanism.
5. The control method of the hydro-mechanical hybrid transmission
device according to claim 3, wherein the forward hydro-mechanical
hybrid transmission comprises a first forward hybrid transmission
gear, a second forward hybrid transmission gear, a third forward
hybrid transmission gear, and a fourth forward hybrid transmission
gear, specifically implemented as follows: in the first forward
hybrid gear, the brake B.sub.4, the clutch C.sub.6, and the one-way
clutch F.sub.2 are engaged, while the brake B.sub.2, the clutch
C.sub.4, the clutch C.sub.5, and the one-way clutch F.sub.1 are
disengaged; the power in the mechanical transmission assembly
sequentially passes through the clutch C.sub.6, the one-way clutch
F.sub.2, and the front-set sun gear to the front-set planet
carrier, and the power is split at the front-set planet carrier
into the front-set ring gear and the rear-set ring gear
respectively; the power in the rear-set ring gear passes through
the rear-set planet carrier and the power is converged with the
power in the front-set ring gear, and the power is then transmitted
to the convergence mechanism; when the brake B.sub.4 is engaged,
the rear-set sun gear is locked; in the second forward hybrid gear,
the brake B.sub.4 and the clutch C.sub.4 are engaged, while the
brake B.sub.2, the clutch C.sub.5, the clutch C.sub.6, the one-way
clutch F.sub.1, and the one-way clutch F.sub.2 are disengaged; the
power in the mechanical transmission assembly sequentially passes
through the clutch C.sub.4, the rear-set ring gear, and the
rear-set planet carrier, and the power is then transmitted to the
convergence mechanism; in the third forward hybrid gear, the clutch
C.sub.4, the clutch C.sub.5, and the one-way clutch F.sub.1 are
engaged, while the brake B.sub.2, the brake B.sub.4, the clutch
C.sub.6, and the one-way clutch F.sub.2 are disengaged; the power
in the mechanical transmission assembly sequentially passes through
the clutch C.sub.4, the front-set planet carrier, and the front-set
ring gear, and the power is then transmitted to the convergence
mechanism; since the clutch C.sub.5 and the one-way clutch F.sub.1
are engaged, the front-set sun gear is prevented from an overspeed
rotation and rotates at a speed consistent with the front-set
planet carrier, enabling an entire front planetary gear set
mechanism to rotate; in the fourth forward hybrid gear, the brake
B.sub.2, the clutch C.sub.6, and the one-way clutch F.sub.2 are
engaged, while the brake B.sub.4, the clutch C.sub.4, the clutch
C.sub.5, and the one-way clutch F.sub.1 are disengaged; the power
in the mechanical transmission assembly sequentially passes through
the clutch C.sub.6, the one-way clutch F.sub.2, the front-set sun
gear, and the front-set ring gear, and the power is then
transmitted to the convergence mechanism.
6. The control method of the hydro-mechanical hybrid transmission
device according to claim 3, wherein the reverse hydro-mechanical
hybrid transmission comprises a first reverse hybrid transmission
gear, a second reverse hybrid transmission gear, a third reverse
hybrid transmission gear, and a fourth reverse hybrid transmission
gear, specifically implemented as follows: in the first reverse
hybrid gear, the brake B.sub.4, the clutch C.sub.6, and the one-way
clutch F.sub.2 are engaged, while the brake B.sub.2, the clutch
C.sub.4, the clutch C.sub.5, and the one-way clutch F.sub.1 are
disengaged; the power in the mechanical transmission assembly
sequentially passes through the clutch C.sub.6, the one-way clutch
F.sub.2, and the front-set sun gear to the front-set planet
carrier, and the power is split at the front-set planet carrier
into the front-set ring gear and the rear-set ring gear
respectively; the power in the rear-set ring gear passes through
the rear-set planet carrier and the power is converged with the
power in the front-set ring gear, and the power is then transmitted
to the convergence mechanism; when the brake B.sub.4 is engaged,
the rear-set sun gear is locked; in the second reverse hybrid gear,
the brake B.sub.4 and the clutch C.sub.4 are engaged, while the
brake B.sub.2, the clutch C.sub.5, the clutch C.sub.6, the one-way
clutch F.sub.1, and the one-way clutch F.sub.2 are disengaged; the
power in the mechanical transmission assembly sequentially passes
through the clutch C.sub.4, the rear-set ring gear, and the
rear-set planet carrier, and the power is then transmitted to the
convergence mechanism; in the third reverse hybrid gear, the clutch
C.sub.4, the clutch C.sub.5, and the one-way clutch F.sub.1 are
engaged, while the brake B.sub.2, the brake B.sub.4, the clutch
C.sub.6, and the one-way clutch F.sub.2 are disengaged; the power
in the mechanical transmission assembly sequentially passes through
the clutch C.sub.4, the front-set planet carrier, and the front-set
ring gear, and the power is then transmitted to the convergence
mechanism; since the clutch C.sub.5 and the one-way clutch F.sub.1
are engaged, the front-set sun gear is prevented from an overspeed
rotation and rotates at a speed consistent with the front-set
planet carrier, enabling an entire front planetary gear set
mechanism to rotate; in the fourth reverse hybrid gear, the brake
B.sub.2, the clutch C.sub.6, and the one-way clutch F.sub.2 are
engaged, while the brake B.sub.4, the clutch C.sub.4, the clutch
C.sub.5, and the one-way clutch F.sub.1 are disengaged; the power
in the mechanical transmission assembly sequentially passes through
the clutch C.sub.6, the one-way clutch F.sub.2, the front-set sun
gear, and the front-set ring gear, and the power is then
transmitted to the convergence mechanism.
7. The control method of the hydro-mechanical hybrid transmission
device according to claim 5, wherein an online rolling optimization
control is implemented by adopting a vehicle predictive control
based on a time domain in combination with a dynamic programming;
in a prediction region q, a state transition equation of the
vehicle predictive control in a hybrid transmission is:
x(k+1)=.mu.[x(k),u(k)]; wherein .mu. is a time-discrete system
function, x(k+1) is a state variable related to k+1, x(k) is a
state variable related to k, and u(k) is a control variable related
to k; in the prediction region q, an objective function of
minimizing a fuel consumption of a hydro-mechanical hybrid
transmission system is: J 1 = min .times. t = t .function. ( k ) t
= t .function. ( k + q ) .times. v k .function. ( x k , u k )
.times. .DELTA. .times. t ; ##EQU00018## wherein J.sub.1 is an
objective function of a fuel economy when a linear predictive
control system is adopted, v.sub.k is a stage indicator of the
k.sup.th stage, x.sub.k is a state variable of the k.sup.th stage,
u.sub.k is a control variable of the k.sup.th stage, .DELTA.t is a
time interval, t(k) is a time point of the k.sup.th stage, and
t(k+q) is a time point of the (k+q).sup.th stage; in a control
region p, a sensing device is adopted for measurement; and in the
prediction region q, a GPS/GIS system is adopted for a prediction;
a nonlinear predictive control is adopted to control state
variables of the hydro-mechanical hybrid transmission system
enabling both a power split and a convergence in each power range,
constrain control variables, and estimate future states; the
objective function of minimizing the fuel consumption of the hybrid
transmission system is: J 2 = min .times. t = t .function. ( k ) t
= t .function. ( k + q ) .times. L .function. [ x .function. ( t )
, u .function. ( t ) ] ; ##EQU00019## wherein J.sub.2 is the
objective function of the fuel economy when a nonlinear predictive
control system is adopted, and L is an instantaneous fuel
consumption function at a time point t.
8. (canceled)
9. (canceled)
10. (canceled)
Description
CROSS REFERENCE TO THE RELATED APPLICATIONS
[0001] This application is the national stage entry of
International Application No. PCT/CN2019/122860, filed on Dec. 4,
2019, which is based upon and claims priority to Chinese Patent
Application No. 201911076475.8, filed on Nov. 6, 2019, the entire
contents of which are incorporated herein by reference.
TECHNICAL FIELD
[0002] The present invention relates to a transmission device and a
control method thereof, and in particular, to a hydro-mechanical
hybrid transmission device enabling both power split and
convergence in each power range and a control method thereof.
BACKGROUND
[0003] High-power engineering vehicles work in harsh environments
and bear variable loads, raising a high requirement on the
adaptability of the variable-speed transmission system. Hence, the
variable-speed transmission device needs to operate at different
rotation speeds and torques to adapt to different working
conditions in a timely manner, thereby ensuring the power
performance and fuel economy of running vehicles. Hydraulic
transmission enables flexible startup, hydro-mechanical
transmission enables stepless speed regulation, and mechanical
transmission enables efficient speed variation, which can meet the
requirements of working conditions for startup, operation, and
transfer respectively. At present, hybrid transmission devices that
integrate hydraulic, hydro-mechanical, and mechanical transmission
modes are rare, let alone hybrid transmission devices enabling both
power split and convergence.
[0004] Two conventional hydro-mechanical transmission modes are:
(1) a power-split transmission mode of using planetary gears as
split mechanisms and ordinary gears as convergence mechanisms; (2)
a power-convergence transmission mode using ordinary gears as split
mechanisms and planetary gears as convergence mechanisms.
Currently, hydro-mechanical transmission is designed based on the
idea of sacrificing the transmission efficiency and speed
regulation range of secondary working areas for efficient
transmission in major working areas, and it is difficult for the
conventional design to take into account the transmission
requirements of various working conditions including direction
change and mode switching.
[0005] When implementing forward transmission and reverse
transmission, the conventional transmission device has limited
power split and convergence structural forms and can hardly enable
both, which is not conducive to the optimization of structural
parameters and may easily cause circulating power, thereby reducing
the transmission efficiency. Multi-mode transmission devices
generally have a few gears to choose from in each mode, and cannot
meet the requirements of complex working conditions.
[0006] The overall design of mechanical-electrical-hydraulic
integration not only involves the performance of the transmission
device, but also involves the matching of engine-transmission
device-travel device, and then develops to the integration of
man-machine-environment. As for the transmission device, the
control of rotation speed and torque focuses on the adjustment of
the transmission ratio; as for engine-transmission device-travel
device, it involves the selection of transmission mode and the
shift of gears in the transmission mode, as well as adaptive
optimization control of the energy management system and so on; as
for the integration of man-machine-environment, it involves the
online optimal control problem of a bounded region.
SUMMARY
[0007] Objective of the invention: The objective of the present
invention is to provide a hydro-mechanical hybrid transmission
device and a control method thereof to solve the above problems.
The present invention implements forward transmission and reverse
transmission by using power split and convergence combined
structural forms, which is conducive to the optimization of
structural parameters and improves the system efficiency.
[0008] Technical solution: A hydro-mechanical hybrid transmission
device includes an input shaft, a split mechanism, a hydraulic
transmission assembly, a mechanical transmission assembly, a
convergence mechanism, and an output shaft, wherein the input shaft
is connected, through the split mechanism, to the hydraulic
transmission assembly and the mechanical transmission assembly that
are connected in parallel, and the hydraulic transmission assembly
and the mechanical transmission assembly are each connected to the
output shaft through the convergence mechanism; the split mechanism
includes a clutch C.sub.3, a split mechanism sun gear, a split
mechanism planet carrier, a split mechanism ring gear, and a brake
B.sub.1, the clutch C.sub.3 is connected to the split mechanism sun
gear and the split mechanism planet carrier, the brake B.sub.1 is
connected to the split mechanism ring gear, the input shaft is
connected to the split mechanism sun gear, the split mechanism is
connected to the hydraulic transmission assembly through the split
mechanism ring gear, and the split mechanism is connected to the
mechanical transmission assembly through the split mechanism sun
gear and the split mechanism planet carrier;
[0009] the convergence mechanism includes a brake B.sub.6, a
convergence mechanism ring gear, a convergence mechanism planet
carrier, a convergence mechanism sun gear, and a clutch C.sub.7,
the brake B.sub.6 is connected to the convergence mechanism ring
gear, the clutch C.sub.7 is connected to the convergence mechanism
planet carrier and the convergence mechanism sun gear, the
convergence mechanism is connected to the hydraulic transmission
assembly through the convergence mechanism ring gear, the
convergence mechanism is connected to the mechanical transmission
assembly through the convergence mechanism sun gear, and the
convergence mechanism is connected to the output shaft through the
convergence mechanism planet carrier and the convergence mechanism
sun gear.
[0010] In the present invention, planetary gear structures are
combined with engagement/disengagement of brakes and clutches, to
implement switching of power split and convergence structural
forms. Therefore, during forward transmission and reverse
transmission, power split and convergence structural forms are
diversified and both can be enabled, which is conducive to the
optimization of structural parameters and prevents circulating
power, thereby improving the transmission efficiency. Multi-mode
transmission devices are provided with various gears to choose
from, and can meet the requirements of complex working
conditions.
[0011] Preferably, to ensure the reliability of the hydraulic
transmission assembly, the hydraulic transmission assembly includes
a hydraulic transmission input clutch C.sub.1, a hydraulic
transmission input gear pair, a unidirectional variable pump, a
hydraulic pipe, a unidirectional quantitative motor, a reverse gear
pair, a hydraulic transmission output gear pair, and a hydraulic
transmission output clutch C.sub.2, the unidirectional variable
pump is connected to the split mechanism through the hydraulic
transmission input gear pair, the hydraulic transmission input
clutch C.sub.1 is arranged between the hydraulic transmission input
gear pair and the unidirectional variable pump, the unidirectional
variable pump is connected to the unidirectional quantitative motor
through the hydraulic pipe, the unidirectional quantitative motor
is connected to the convergence mechanism sequentially through the
hydraulic transmission output gear pair and the reverse gear pair,
and the hydraulic transmission output clutch C.sub.2 is arranged
between the unidirectional quantitative motor and the hydraulic
transmission output gear pair.
[0012] Preferably, to ensure the reliability of mechanical
transmission, the mechanical transmission assembly includes a
front-set sun gear, a front-set planet carrier, a front-set ring
gear, a rear-set sun gear, a rear-set planet carrier, a rear-set
ring gear, a clutch C.sub.4, a clutch C.sub.5, a clutch C.sub.6, a
brake B.sub.2, a brake B.sub.3, a brake B.sub.4, a brake B.sub.5, a
one-way clutch F.sub.1, a one-way clutch F.sub.2, and a one-way
clutch F.sub.3;
[0013] the front-set sun gear is connected to the split mechanism
through the clutch C.sub.5 and the clutch C.sub.6 that are
connected in parallel, the one-way clutch F.sub.1 is arranged
between the clutch C.sub.5 and the front-set sun gear, and the
one-way clutch F.sub.2 is arranged between the clutch C.sub.6 and
the front-set sun gear, the one-way clutch F.sub.1 and the one-way
clutch F.sub.2 have opposite power conduction directions, and the
front-set sun gear is also connected to the brake B.sub.3;
[0014] the front-set planet carrier is connected to the split
mechanism through the clutch C.sub.4, the brake B.sub.2 is arranged
between the front-set planet carrier and the clutch C.sub.4, and
the front-set planet carrier is fixedly connected to the rear-set
ring gear;
[0015] the front-set ring gear is connected to the rear-set planet
carrier and the convergence mechanism;
[0016] the rear-set sun gear is connected to the brake B.sub.4 and
the brake B.sub.5 that are connected in parallel, the one-way
clutch F.sub.3 is arranged between the rear-set sun gear and the
brake B.sub.5, and the brake direction of the one-way clutch
F.sub.3 is the rotation direction of the rear-set sun gear and is
opposite to the rotation direction of the split mechanism planet
carrier;
[0017] the rear-set planet carrier is connected to the front-set
ring gear and the convergence mechanism;
[0018] the rear-set ring gear is connected to the front-set planet
carrier and the split mechanism, and the brake B.sub.2 and the
clutch C.sub.4 in parallel connection are arranged between the
rear-set ring gear and the split mechanism.
[0019] Preferably, to ensure that multiple gears are available for
selection, three types of transmission in two directions, namely,
pure hydraulic transmission, hydro-mechanical hybrid transmission,
and pure mechanical transmission in forward transmission as well as
pure hydraulic transmission, hydro-mechanical hybrid transmission,
and pure mechanical transmission in reverse transmission are
implemented through combination and engagement/disengagement of the
brakes and the clutches.
[0020] Three types of forward transmission are as follows:
[0021] in forward pure hydraulic transmission, the brake B.sub.2,
the hydraulic transmission input clutch C.sub.1, the hydraulic
transmission output clutch C.sub.2, the clutch C.sub.4, and the
clutch C.sub.7 are engaged, while the other brakes and clutches are
disengaged; when the brake B.sub.2 and the clutch C.sub.4 are
engaged, the split mechanism planet carrier is locked, the split
mechanism sun gear and the split mechanism ring gear rotate in
opposite directions, and power passes through the input shaft, the
split mechanism, the hydraulic transmission assembly, and the
convergence mechanism and is output from the output shaft; when the
clutch C.sub.7 is engaged, the convergence mechanism planet carrier
and the convergence mechanism sun gear of the convergence mechanism
are interlocked, the entire convergence mechanism rotates, and by
the action of the reverse gear pair, the input shaft and the output
shaft rotate in the same direction;
[0022] in forward pure mechanical transmission, the brake B.sub.1
and the brake B.sub.6 are engaged, while the brake B.sub.2, the
brake B.sub.4, the hydraulic transmission input clutch C.sub.1, the
hydraulic transmission output clutch C.sub.2, the clutch C.sub.3,
and the clutch C.sub.7 are disengaged; power passes through the
input shaft, the split mechanism, the mechanical transmission
assembly, and the convergence mechanism and is output from the
output shaft; when the brake B.sub.1 is engaged, the split
mechanism ring gear is locked, and the split mechanism sun gear and
the split mechanism planet carrier transmit power as gear
transmission mechanisms; when the brake B.sub.6 is engaged, the
convergence mechanism ring gear is locked, and power passes through
the convergence mechanism sun gear and the convergence mechanism
planet carrier to the output shaft;
[0023] in forward hydro-mechanical hybrid transmission, the
hydraulic transmission input clutch C.sub.1, the hydraulic
transmission output clutch C.sub.2, and the clutch C.sub.7 are
engaged, while the brake B.sub.1, the brake B.sub.3, the brake
B.sub.5, the brake B.sub.6, the clutch C.sub.3, and the one-way
clutch F.sub.3 are disengaged; power passes through the input shaft
to the split mechanism, transmitted by the split mechanism to the
hydraulic transmission assembly and the mechanical transmission
assembly respectively, then converged by the convergence mechanism,
and output from the output shaft; when the clutch C.sub.3 is
disengaged, the split mechanism planet carrier transmits a part of
the power from the input shaft to the mechanical transmission
assembly, and the split mechanism ring gear transmits the other
part of the power from the input shaft to the hydraulic
transmission assembly; when the clutch C.sub.7 is engaged, the
power in the mechanical transmission assembly passes through the
convergence mechanism sun gear and the convergence mechanism planet
carrier and is transmitted to the output shaft, the power in the
hydraulic transmission assembly passes through the convergence
mechanism ring gear and the convergence mechanism planet carrier
and is transmitted to the output shaft, and the convergence
mechanism planet carrier rotates in the same direction as the input
shaft within a set displacement ratio range.
[0024] Three types of reverse transmission are as follows:
[0025] in reverse pure hydraulic transmission, the hydraulic
transmission input clutch C.sub.1, the hydraulic transmission
output clutch C.sub.2, the clutch C.sub.3, and the clutch C.sub.7
are engaged, while the other brakes and clutches are disengaged;
when the clutch C.sub.3 is engaged, the split mechanism sun gear
and the split mechanism planet carrier are interlocked, the entire
split mechanism rotates, and power passes through the input shaft,
the split mechanism, the hydraulic transmission assembly, and the
convergence mechanism and is output from the output shaft; when the
clutch C.sub.7 is engaged, the convergence mechanism planet carrier
and the convergence mechanism sun gear of the convergence mechanism
are interlocked, the entire convergence mechanism rotates, and the
input shaft and the output shaft rotate in opposite directions;
[0026] in reverse pure mechanical transmission, the brake B.sub.1,
the brake B.sub.2, the brake B.sub.6, the clutch C.sub.6, and the
one-way clutch F.sub.2 are engaged, while the other brakes and
clutches are disengaged; when the brake B.sub.1 is engaged, the
split mechanism ring gear is locked, and power passes through the
split mechanism sun gear and the split mechanism planet carrier and
is transmitted to the mechanical transmission assembly; when the
clutch C.sub.6 and the one-way clutch F.sub.2 are engaged, the
power in the mechanical transmission assembly sequentially passes
through the clutch C.sub.6, the one-way clutch F.sub.2, the
front-set sun gear, and the front-set ring gear, and is then
transmitted to the convergence mechanism sun gear; when the brake
B.sub.6 is engaged, the convergence mechanism ring gear is locked,
and power passes through the convergence mechanism sun gear and the
convergence mechanism planet carrier to the output shaft;
[0027] in reverse hydro-mechanical hybrid transmission, the
hydraulic transmission input clutch C.sub.1, the hydraulic
transmission output clutch C.sub.2, and the clutch C.sub.3 are
engaged, while the brake B.sub.1, the brake B.sub.3, the brake
B.sub.5, the brake B.sub.6, the clutch C.sub.7, and the one-way
clutch F.sub.3 are disengaged; power passes through the input shaft
to the split mechanism, transmitted by the split mechanism to the
hydraulic transmission assembly and the mechanical transmission
assembly respectively, then converged by the convergence mechanism,
and output from the output shaft; when the clutch C.sub.3 is
engaged, the split mechanism planet carrier transmits a part of the
power from the input shaft to the mechanical transmission assembly,
and the split mechanism ring gear transmits the other part of the
power from the input shaft to the hydraulic transmission assembly;
when the clutch C.sub.7 is disengaged, the power in the mechanical
transmission assembly passes through the convergence mechanism sun
gear and the convergence mechanism planet carrier and is
transmitted to the output shaft, the power in the hydraulic
transmission assembly passes through the convergence mechanism ring
gear and the convergence mechanism planet carrier and is
transmitted to the output shaft, and the convergence mechanism
planet carrier rotates in a direction opposite to the input shaft
within a set displacement ratio range.
[0028] Preferably, to further ensure that forward mechanical
transmission gears are available for selection, the forward pure
mechanical transmission includes mechanical gear-1, mechanical
gear-2, mechanical gear-3, and mechanical gear-4, specifically
implemented as follows:
[0029] in mechanical gear-1, the brake B.sub.5, the one-way clutch
F.sub.3, the clutch C.sub.6, and the one-way clutch F.sub.2 are
engaged, while the brake B.sub.3, the clutch C.sub.4, the clutch
C.sub.5, and the one-way clutch F.sub.1 are disengaged; power
sequentially passes through the clutch C.sub.6, the one-way clutch
F.sub.2, and the front-set sun gear to the front-set planet
carrier, and is split at the front-set planet carrier into the
front-set ring gear and the rear-set ring gear respectively; the
power in the rear-set ring gear passes through the rear-set planet
carrier and is converged with the power in the front-set ring gear,
and the power is then transmitted to the convergence mechanism;
when the brake B.sub.5 and the one-way clutch F.sub.3 are engaged,
the rear-set sun gear is locked;
[0030] in mechanical gear-2, the brake B.sub.5, the one-way clutch
F.sub.3, and the clutch C.sub.4 are engaged, while the brake
B.sub.3, the clutch C.sub.5, the clutch C.sub.6, the one-way clutch
F.sub.1, and the one-way clutch F.sub.2 are disengaged; power
sequentially passes through the clutch C.sub.4, the rear-set ring
gear, and the rear-set planet carrier, and is then transmitted to
the convergence mechanism; when the brake B.sub.5 and the one-way
clutch F.sub.3 are engaged, the rear-set sun gear is locked;
[0031] in mechanical gear-3, the brake B.sub.5, the clutch C.sub.4,
the clutch C.sub.5, the one-way clutch F.sub.1, and the one-way
clutch F.sub.3 are engaged, while the brake B.sub.3, the clutch
C.sub.6, and the one-way clutch F.sub.2 are disengaged; power
sequentially passes through the clutch C.sub.4, the front-set
planet carrier, and the front-set ring gear, and is then
transmitted to the convergence mechanism; since the clutch C.sub.5
and the one-way clutch F.sub.1 are engaged, the front-set sun gear
is prevented from overspeed rotation and rotates at a speed
consistent with the front-set planet carrier, enabling the entire
front planetary gear set mechanism to rotate;
[0032] in mechanical gear-4, the brake B.sub.3 and the clutch
C.sub.4 are engaged, while the brake B.sub.5, the clutch C.sub.5,
the clutch C.sub.6, the one-way clutch F.sub.1, the one-way clutch
F.sub.2, and the one-way clutch F.sub.3 are disengaged; power
sequentially passes through the clutch C.sub.4, the front-set
planet carrier, and the front-set ring gear, and is then
transmitted to the convergence mechanism.
[0033] Preferably, to increase forward hybrid transmission gears,
the forward hydro-mechanical hybrid transmission includes hybrid
transmission gear-1, hybrid transmission gear-2, hybrid
transmission gear-3, and hybrid transmission gear-4, specifically
implemented as follows:
[0034] in forward hybrid gear-1, the brake B.sub.4, the clutch
C.sub.6, and the one-way clutch F.sub.2 are engaged, while the
brake B.sub.2, the clutch C.sub.4, the clutch C.sub.5, and the
one-way clutch F.sub.1 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.6, the one-way clutch F.sub.2, and the front-set sun gear to
the front-set planet carrier, and is split at the front-set planet
carrier into the front-set ring gear and the rear-set ring gear
respectively; the power in the rear-set ring gear passes through
the rear-set planet carrier and is converged with the power in the
front-set ring gear, and the power is then transmitted to the
convergence mechanism; when the brake B.sub.4 is engaged, the
rear-set sun gear is locked;
[0035] in forward hybrid gear-2, the brake B.sub.4 and the clutch
C.sub.4 are engaged, while the brake B.sub.2, the clutch C.sub.5,
the clutch C.sub.6, the one-way clutch F.sub.1, and the one-way
clutch F.sub.2 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.4, the rear-set ring gear, and the rear-set planet carrier,
and is then transmitted to the convergence mechanism;
[0036] in forward hybrid gear-3, the clutch C.sub.4, the clutch
C.sub.5, and the one-way clutch F.sub.1 are engaged, while the
brake B.sub.2, the brake B.sub.4, the clutch C.sub.6, and the
one-way clutch F.sub.2 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.4, the front-set planet carrier, and the front-set ring gear,
and is then transmitted to the convergence mechanism; since the
clutch C.sub.5 and the one-way clutch F.sub.1 are engaged, the
front-set sun gear is prevented from overspeed rotation and rotates
at a speed consistent with the front-set planet carrier, enabling
the entire front planetary gear set mechanism to rotate;
[0037] in forward hybrid gear-4, the brake B.sub.2, the clutch
C.sub.6, and the one-way clutch F.sub.2 are engaged, while the
brake B.sub.4, the clutch C.sub.4, the clutch C.sub.5, and the
one-way clutch F.sub.1 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.6, the one-way clutch F.sub.2, the front-set sun gear, and
the front-set ring gear, and is then transmitted to the convergence
mechanism.
[0038] Preferably, to increase reverse hybrid transmission gears,
the reverse hydro-mechanical hybrid transmission includes hybrid
transmission gear-1, hybrid transmission gear-2, hybrid
transmission gear-3, and hybrid transmission gear-4, specifically
implemented as follows:
[0039] in reverse hybrid gear-1, the brake B.sub.4, the clutch
C.sub.6, and the one-way clutch F.sub.2 are engaged, while the
brake B.sub.2, the clutch C.sub.4, the clutch C.sub.5, and the
one-way clutch F.sub.1 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.6, the one-way clutch F.sub.2, and the front-set sun gear to
the front-set planet carrier, and is split at the front-set planet
carrier into the front-set ring gear and the rear-set ring gear
respectively; the power in the rear-set ring gear passes through
the rear-set planet carrier and is converged with the power in the
front-set ring gear, and the power is then transmitted to the
convergence mechanism; when the brake B.sub.4 is engaged, the
rear-set sun gear is locked;
[0040] in reverse hybrid gear-2, the brake B.sub.4 and the clutch
C.sub.4 are engaged, while the brake B.sub.2, the clutch C.sub.5,
the clutch C.sub.6, the one-way clutch F.sub.1, and the one-way
clutch F.sub.2 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.4, the rear-set ring gear, and the rear-set planet carrier,
and is then transmitted to the convergence mechanism;
[0041] in reverse hybrid gear-3, the clutch C.sub.4, the clutch
C.sub.5, and the one-way clutch F.sub.1 are engaged, while the
brake B.sub.2, the brake B.sub.4, the clutch C.sub.6, and the
one-way clutch F.sub.2 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.4, the front-set planet carrier, and the front-set ring gear,
and is then transmitted to the convergence mechanism; since the
clutch C.sub.5 and the one-way clutch F.sub.1 are engaged, the
front-set sun gear is prevented from overspeed rotation and rotates
at a speed consistent with the front-set planet carrier, enabling
the entire front planetary gear set mechanism to rotate;
[0042] in reverse hybrid gear-4, the brake B.sub.2, the clutch
C.sub.6, and the one-way clutch F.sub.2 are engaged, while the
brake B.sub.4, the clutch C.sub.4, the clutch C.sub.5, and the
one-way clutch F.sub.1 are disengaged; the power in the mechanical
transmission assembly sequentially passes through the clutch
C.sub.6, the one-way clutch F.sub.2, the front-set sun gear, and
the front-set ring gear, and is then transmitted to the convergence
mechanism.
[0043] Through model predictive control of the transmission system,
the problem of globally optimal dynamic programming of fuel economy
is transformed into the local optimization control problem in a
prediction region, and the future vehicle operation status in the
prediction region is continuously updated through rolling
optimization, to obtain optimization results and realize real-time
application of predictive control in the hydro-mechanical hybrid
transmission system. Vehicle predictive control based on time
domain is online rolling optimization control within the framework
of model predictive control and implemented in combination with
dynamic programming.
[0044] In a prediction region q, the state transition equation of
vehicle predictive control in hybrid transmission is:
x(k+1)=.mu.[x(k),u(k)]
[0045] wherein .mu. is a time-discrete system function, x(k+1) is a
state variable related to k+1, x(k) is a state variable related to
k, and u(k) is a control variable related to k.
[0046] In the prediction region q, an objective function of
minimizing the fuel consumption of the hybrid transmission system
is:
[0047] wherein J.sub.1 is an objective function of fuel economy
when a linear predictive control system is adopted, v.sub.k is a
stage indicator of the k.sup.th stage, x.sub.k is a state variable
of the k.sup.th stage, u.sub.k is a control variable of the
k.sup.th stage, .DELTA.t is a time interval, t(k) is a time point
of the k.sup.th stage, and t(k+q) is a time point of the
(k+q).sup.th stage.
[0048] In a control region p, a sensing device is generally adopted
for measurement; and in the prediction region q, a GPS/GIS system
is generally adopted for prediction. Prediction relies on the
selection of an appropriate prediction window length for data
collection as well as a high cost-performance ratio of the
predictive control system.
[0049] A nonlinear predictive control system is adopted to control
dynamic characteristics and state variables of the hybrid
transmission system, constrain control variables, estimate future
states, and solve the online optimal control problem of a bounded
region.
[0050] In this case, the objective function of minimizing the fuel
consumption of the hybrid transmission system is:
J 2 = min .times. t = t .function. ( k ) t = t .function. ( k + q )
.times. L .function. [ x .function. ( t ) , u .function. ( t ) ]
##EQU00001##
[0051] wherein J.sub.2 is an objective function of fuel economy
when a nonlinear predictive control system is adopted, L is an
instantaneous fuel consumption function at a time point t, x(t) is
a state variable at a time point t, and u(t) is a control variable
at a time point t.
[0052] Beneficial effects: In the present invention, planetary gear
structures are combined with engagement/disengagement of brakes and
clutches, to implement switching of power split and convergence
structural forms. Therefore, during forward transmission and
reverse transmission, power split and convergence structural forms
are diversified and both can be enabled, which is conducive to the
optimization of structural parameters and prevents circulating
power, thereby improving the transmission efficiency. Multi-mode
transmission devices are provided with various gears to choose
from, and can meet the requirements of complex working conditions.
In each mechanical transmission gear, the one-way clutch may
overrun and disables engine braking. In particular circumstances,
the mechanical transmission system in the hydro-mechanical
transmission mode can be directly used to replace the mechanical
system in the mechanical transmission mode, to enable engine
braking or improve the service life of the gear-shift components.
The replacement of a two-way variable pump and a two-way
quantitative motor with the unidirectional variable pump and the
unidirectional quantitative motor largely reduces the production
and maintenance costs.
BRIEF DESCRIPTION OF THE DRAWINGS
[0053] FIG. 1 is a schematic structural diagram of the present
invention;
[0054] FIG. 2 is a table showing engagement/disengagement states of
gear-shift components in the present invention;
[0055] FIG. 3 is a schematic diagram showing the power flow in a
forward pure hydraulic gear in the present invention;
[0056] FIG. 4 is a schematic diagram showing the power flow in a
reverse pure hydraulic gear in the present invention;
[0057] FIG. 5 is a schematic diagram showing the power flow in
forward hydro-mechanical hybrid transmission gear-1 in the present
invention;
[0058] FIG. 6 is a schematic diagram showing the power flow in
forward hydro-mechanical hybrid transmission gear-2 in the present
invention;
[0059] FIG. 7 is a schematic diagram showing the power flow in
forward hydro-mechanical hybrid transmission gear-3 in the present
invention;
[0060] FIG. 8 is a schematic diagram showing the power flow in
forward hydro-mechanical hybrid transmission gear-4 in the present
invention;
[0061] FIG. 9 is a schematic diagram showing the power flow in
reverse hydro-mechanical hybrid transmission gear-1 in the present
invention;
[0062] FIG. 10 is a schematic diagram showing the power flow in
reverse hydro-mechanical hybrid transmission gear-2 in the present
invention;
[0063] FIG. 11 is a schematic diagram showing the power flow in
reverse hydro-mechanical hybrid transmission gear-3 in the present
invention;
[0064] FIG. 12 is a schematic diagram showing the power flow in
reverse hydro-mechanical hybrid transmission gear-4 in the present
invention;
[0065] FIG. 13 is a schematic diagram showing the power flow in
forward mechanical gear-1 in the present invention;
[0066] FIG. 14 is a schematic diagram showing the power flow in
forward mechanical gear-2 in the present invention;
[0067] FIG. 15 is a schematic diagram showing the power flow in
forward mechanical gear-3 in the present invention;
[0068] FIG. 16 is a schematic diagram showing the power flow in
forward mechanical gear-4 in the present invention;
[0069] FIG. 17 is a schematic diagram showing the power flow in a
reverse pure mechanical transmission gear in the present
invention;
[0070] FIG. 18 is a diagram showing the principle of vehicle
predictive control; and
[0071] FIG. 19 is a diagram showing the principle of dynamic
coordinated control of a hybrid transmission system in a
man-machine interaction environment.
DETAILED DESCRIPTION OF THE EMBODIMENTS
[0072] The present invention is further described below with
reference to the accompanying drawings.
[0073] As shown in FIG. 1, a hydro-mechanical hybrid transmission
device includes an input shaft 1, a split mechanism 2, a hydraulic
transmission assembly 3, a mechanical transmission assembly 4, a
convergence mechanism 5, and an output shaft 6. The input shaft 1
is connected, through the split mechanism 2, to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
that are connected in parallel. The hydraulic transmission assembly
3 and the mechanical transmission assembly 4 are each connected to
the output shaft 6 through the convergence mechanism 5. The split
mechanism 2 includes a clutch C.sub.3 21, a split mechanism sun
gear 22, a split mechanism planet carrier 23, a split mechanism
ring gear 24, and a brake B.sub.1 25. The clutch C.sub.3 21 is
connected to the split mechanism sun gear 22 and the split
mechanism planet carrier 23. The brake B.sub.1 25 is connected to
the split mechanism ring gear 24. The input shaft 1 is connected to
the split mechanism sun gear 22. The split mechanism 2 is connected
to the hydraulic transmission assembly 3 through the split
mechanism ring gear 24. The split mechanism 2 is connected to the
mechanical transmission assembly 4 through the split mechanism sun
gear 22 and the split mechanism planet carrier 23.
[0074] The convergence mechanism 5 includes a brake B.sub.6 51, a
convergence mechanism ring gear 52, a convergence mechanism planet
carrier 53, a convergence mechanism sun gear 54, and a clutch
C.sub.7 55. The brake B.sub.6 51 is connected to the convergence
mechanism ring gear 52. The clutch C.sub.7 55 is connected to the
convergence mechanism planet carrier 53 and the convergence
mechanism sun gear 54. The convergence mechanism 5 is connected to
the hydraulic transmission assembly 3 through the convergence
mechanism ring gear 52. The convergence mechanism 5 is connected to
the mechanical transmission assembly 4 through the convergence
mechanism sun gear 54. The convergence mechanism 5 is connected to
the output shaft 6 through the convergence mechanism planet carrier
53 and the convergence mechanism sun gear 54.
[0075] The hydraulic transmission assembly 3 includes a hydraulic
transmission input clutch C.sub.1 31, a hydraulic transmission
input gear pair 32, a unidirectional variable pump 33, a hydraulic
pipe 34, a unidirectional quantitative motor 35, a reverse gear
pair 36, a hydraulic transmission output gear pair 37, and a
hydraulic transmission output clutch C.sub.2 38. The unidirectional
variable pump 33 is connected to the split mechanism 2 through the
hydraulic transmission input gear pair 32. The hydraulic
transmission input clutch C.sub.1 31 is arranged between the
hydraulic transmission input gear pair 32 and the unidirectional
variable pump 33. The unidirectional variable pump 33 is connected
to the unidirectional quantitative motor 35 through the hydraulic
pipe 34. The unidirectional quantitative motor 35 is connected to
the convergence mechanism 5 sequentially through the hydraulic
transmission output gear pair 37 and the reverse gear pair 36. The
hydraulic transmission output clutch C.sub.2 38 is arranged between
the unidirectional quantitative motor 35 and the hydraulic
transmission output gear pair 37.
[0076] The mechanical transmission assembly 4 includes a front-set
sun gear 41, a front-set planet carrier 42, a front-set ring gear
43, a rear-set sun gear 44, a rear-set planet carrier 45, a
rear-set ring gear 46, a clutch C.sub.4 47, a clutch C.sub.5 48, a
clutch C.sub.6 49, a brake B.sub.2 410, a brake B.sub.3 411, a
brake B.sub.4 412, a brake B.sub.5 413, a one-way clutch F.sub.1
414, a one-way clutch F.sub.2 415, and a one-way clutch F.sub.3
416.
[0077] The front-set sun gear 41 is connected to the split
mechanism 2 through the clutch C.sub.5 48 and the clutch C.sub.6 49
that are connected in parallel. The one-way clutch F.sub.1 414 is
arranged between the clutch C.sub.5 48 and the front-set sun gear
41, and the one-way clutch F.sub.2 415 is arranged between the
clutch C.sub.6 49 and the front-set sun gear 41. The one-way clutch
F.sub.1 414 and the one-way clutch F.sub.2 415 have opposite power
conduction directions. The front-set sun gear 41 is also connected
to the brake B.sub.3 411.
[0078] The front-set planet carrier 42 is connected to the split
mechanism 2 through the clutch C.sub.4 47. The brake B.sub.2 410 is
arranged between the front-set planet carrier 42 and the clutch
C.sub.4 47. The front-set planet carrier 42 is fixedly connected to
the rear-set ring gear 46.
[0079] The front-set ring gear 43 is connected to the rear-set
planet carrier 45 and the convergence mechanism 5.
[0080] The rear-set sun gear 44 is connected to the brake B.sub.4
412 and the brake B.sub.5 413 that are connected in parallel. The
one-way clutch F.sub.3 416 is arranged between the rear-set sun
gear 44 and the brake B.sub.5 413. The brake direction of the
one-way clutch F.sub.3 416 is the rotation direction of the
rear-set sun gear 44 and is opposite to the rotation direction of
the split mechanism planet carrier 23.
[0081] The rear-set planet carrier 45 is connected to the front-set
ring gear 43 and the convergence mechanism 5.
[0082] The rear-set ring gear 46 is connected to the front-set
planet carrier 42 and the split mechanism 2. The brake B.sub.2 410
and the clutch C.sub.4 47 in parallel connection are arranged
between the rear-set ring gear 46 and the split mechanism 2.
[0083] As shown in FIG. 2 and FIG. 3, in forward pure hydraulic
transmission, the brake B.sub.2 410, the hydraulic transmission
input clutch C.sub.1 31, the hydraulic transmission output clutch
C.sub.2 38, the clutch C.sub.4 47, and the clutch C.sub.7 55 are
engaged, while the other brakes and clutches are disengaged. When
the brake B.sub.2 410 and the clutch C.sub.4 47 are engaged, the
split mechanism planet carrier 23 is locked to become a reverse
gear, and power passes through the input shaft 1, the split
mechanism 2, the hydraulic transmission assembly 3, and the
convergence mechanism 5 and is output from the output shaft 6. When
the clutch C.sub.7 55 is engaged, the convergence mechanism planet
carrier 53 and the convergence mechanism sun gear 54 of the
convergence mechanism 5 are interlocked, the entire convergence
mechanism 5 rotates, and by the action of the reverse gear pair 36,
the input shaft 1 and the output shaft 6 rotate in the same
direction.
[0084] The rotation speeds of the input shaft 1 and the output
shaft 6 are in the following relationship:
n o = e k 1 .times. i 1 .times. i 2 .times. i 3 .times. n I
##EQU00002##
[0085] wherein n.sub.0 is the rotation speed of the output shaft 6,
n.sub.1 is the rotation speed of the input shaft 1, e is a ratio of
the displacement of the variable pump 33 to the displacement of the
quantitative motor 35, i.sub.1, i.sub.2, and i.sub.3 are
respectively transmission ratios of gears, and k.sub.1 is a split
mechanism characteristic parameter,
if .times. .times. k 1 = 2 .times. .times. and .times. .times. i 1
.times. i 2 .times. i 3 = 1 , n o = e 2 .times. n I ; ##EQU00003##
when .times. .times. e .di-elect cons. [ 0 , 1 ] , n 0 .di-elect
cons. [ 0 , 1 2 ] .times. n I . ##EQU00003.2##
[0086] As shown in FIG. 2 and FIG. 4, in reverse pure hydraulic
transmission, the hydraulic transmission input clutch C.sub.1 31,
the hydraulic transmission output clutch C.sub.2 38, the clutch
C.sub.3 21, and the clutch C.sub.7 55 are engaged, while the other
brakes and clutches are disengaged. When the clutch C.sub.3 21 is
engaged, the split mechanism sun gear 22 and the split mechanism
planet carrier 23 are interlocked, the entire split mechanism 2
rotates, and power passes through the input shaft 1, the split
mechanism 2, the hydraulic transmission assembly 3, and the
convergence mechanism 5 and is output from the output shaft 6. When
the clutch C.sub.7 55 is engaged, the convergence mechanism planet
carrier 53 and the convergence mechanism sun gear 54 of the
convergence mechanism 5 are interlocked, and the input shaft 1 and
the output shaft 6 rotate in opposite directions.
[0087] The rotation speeds of the input shaft 1 and the output
shaft 6 are in the following relationship:
n o = - e i 1 .times. i 2 .times. i 3 .times. n I ;
##EQU00004##
[0088] when e.di-elect cons.[0, 1], n.sub.0.di-elect cons.[-1,
0]n.sub.1.
[0089] As shown in FIG. 2 and FIG. 5, in forward hydro-mechanical
hybrid transmission gear-1, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.7 55 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.3 21, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
disengaged, the split mechanism planet carrier 23 transmits a part
of the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is engaged, the
power in the mechanical transmission assembly 4 passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in the same
direction as the input shaft 1 within a set displacement ratio
range.
[0090] The brake B.sub.4 412, the clutch C.sub.6 49, and the
one-way clutch F.sub.2 415 are engaged, while the brake B.sub.2
410, the clutch C.sub.4 47, the clutch C.sub.5 48, and the one-way
clutch F.sub.1 414 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.6 49, the one-way clutch F.sub.2 415, and the front-set sun
gear 41 to the front-set planet carrier 42, and is split at the
front-set planet carrier 42 into the front-set ring gear 43 and the
rear-set ring gear 46 respectively. The power in the rear-set ring
gear 46 passes through the rear-set planet carrier 45 and is
converged with the power in the front-set ring gear 43, and the
power is then transmitted to the convergence mechanism 5. When the
brake B.sub.4 412 is engaged, the rear-set sun gear 44 is
locked.
[0091] As shown in FIG. 2 and FIG. 6, in forward hydro-mechanical
hybrid transmission gear-2, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.7 55 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.3 21, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
disengaged, the split mechanism planet carrier 23 transmits a part
of the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is engaged, the
power in the mechanical transmission assembly 4 passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in the same
direction as the input shaft 1 within a set displacement ratio
range.
[0092] The brake B.sub.4 412 and the clutch C.sub.4 47 are engaged,
while the brake B.sub.2 410, the clutch C.sub.5 48, the clutch
C.sub.6 49, the one-way clutch F.sub.1 414, and the one-way clutch
F.sub.2 415 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.4 47, the rear-set ring gear 46, and the rear-set planet
carrier 45, and is then transmitted to the convergence mechanism
5.
[0093] As shown in FIG. 2 and FIG. 7, in forward hydro-mechanical
hybrid transmission gear-3, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.7 55 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.3 21, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
disengaged, the split mechanism planet carrier 23 transmits a part
of the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is engaged, the
power in the mechanical transmission assembly 4 passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in the same
direction as the input shaft 1 within a set displacement ratio
range.
[0094] The clutch C.sub.4 47, the clutch C.sub.5 48, and the
one-way clutch F.sub.1 414 are engaged, while the brake B.sub.2
410, the brake B.sub.4 412, the clutch C.sub.6 49, and the one-way
clutch F.sub.2 415 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.4 47, the front-set planet carrier 42, and the front-set ring
gear 43, and is then transmitted to the convergence mechanism 5.
Since the clutch C.sub.5 48 and the one-way clutch F.sub.1 414 are
engaged, the front-set sun gear 41 is prevented from overspeed
rotation and rotates at a speed consistent with the front-set
planet carrier 42, enabling the entire front planetary gear set
mechanism to rotate.
[0095] As shown in FIG. 2 and FIG. 8, in forward hydro-mechanical
hybrid transmission gear-4, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.7 55 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.3 21, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
disengaged, the split mechanism planet carrier 23 transmits a part
of the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is engaged, the
power in the mechanical transmission assembly 4 passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in the same
direction as the input shaft 1 within a set displacement ratio
range.
[0096] The brake B.sub.2 410, the clutch C.sub.6 49, and the
one-way clutch F.sub.2 415 are engaged, while the brake B.sub.4
412, the clutch C.sub.4 47, the clutch C.sub.5 48, and the one-way
clutch F.sub.1 414 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.6 49, the one-way clutch F.sub.2 415, the front-set sun gear
41, and the front-set ring gear 43, and is then transmitted to the
convergence mechanism 5.
[0097] The forward hydro-mechanical hybrid transmission includes
four hydro-mechanical transmission split gears, and the rotation
speeds of the input shaft 1 and the output shaft 6 are in the
following relationship:
n 0 = n I ( k 1 + 1 ) .times. i m + k 1 .times. i 1 .times. i 2
.times. i 3 e ##EQU00005## if .times. .times. k 1 = 2 .times.
.times. and .times. .times. i 1 .times. i 2 .times. i 3 = 1 , n 0 =
n I 3 .times. i m + 2 e , ##EQU00005.2##
[0098] wherein i.sub.m is a transmission ratio of the mechanical
transmission assembly, i.sub.m1=2.92 is a transmission ratio of the
mechanical transmission assembly in mechanical gear-1,
i.sub.m2=1.57 is a transmission ratio of the mechanical
transmission assembly in mechanical gear-2, i.sub.m3=1.00 is a
transmission ratio of the mechanical transmission assembly in
mechanical gear-3, and i.sub.m4=-2.38 is a transmission ratio of
the mechanical transmission assembly in mechanical gear-4.
[0099] In hydro-mechanical transmission split gear-1,
i.sub.m1=2.92, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = n I 8.76 + 2 e ##EQU00006##
[0100] when e.di-elect cons.[0,1], n.sub.0.di-elect
cons.[0,0.093]n.sub.1.
[0101] In hydro-mechanical transmission split gear-2,
i.sub.m2=1.57, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = n I 4.71 + 2 e ##EQU00007##
[0102] when e.di-elect cons.[0,1], n.sub.0.di-elect
cons.[0,0.149]n.sub.1.
[0103] In hydro-mechanical transmission split gear-3,
i.sub.m3=1.00, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = n I 3.00 + 2 e ##EQU00008##
[0104] when e.di-elect cons.[0,1], n.sub.0.di-elect
cons.[0,0.200]n.sub.1.
[0105] In hydro-mechanical transmission split gear-4,
i.sub.m4=-2.38, and the rotation speeds of the input shaft 1 and
the output shaft 6 are in the following relationship:
n 0 = n I - 7.14 + 2 e ##EQU00009##
[0106] when e.di-elect cons.[0,0.25], n.sub.0.di-elect
cons.[0,1.163]n.sub.1.
[0107] As shown in FIG. 2 and FIG. 9, in reverse hydro-mechanical
hybrid transmission gear-1, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.3 21 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.7 55, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
engaged, the split mechanism planet carrier 23 transmits a part of
the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is disengaged,
the power in the mechanical transmission assembly 4 passes through
the convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in a direction
opposite to the input shaft 1 within a set displacement ratio
range.
[0108] The brake B.sub.4 412, the clutch C.sub.6 49, and the
one-way clutch F.sub.2 415 are engaged, while the brake B.sub.2
410, the clutch C.sub.4 47, the clutch C.sub.5 48, and the one-way
clutch F.sub.1 414 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.6 49, the one-way clutch F.sub.2 415, and the front-set sun
gear 41 to the front-set planet carrier 42, and is split at the
front-set planet carrier 42 into the front-set ring gear 43 and the
rear-set ring gear 46 respectively. The power in the rear-set ring
gear 46 passes through the rear-set planet carrier 45 and is
converged with the power in the front-set ring gear 43, and the
power is then transmitted to the convergence mechanism 5. When the
brake B.sub.4 412 is engaged, the rear-set sun gear 44 is
locked.
[0109] As shown in FIG. 2 and FIG. 10, in reverse hydro-mechanical
hybrid transmission gear-2, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.3 21 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.7 55, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
engaged, the split mechanism planet carrier 23 transmits a part of
the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is disengaged,
the power in the mechanical transmission assembly 4 passes through
the convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in a direction
opposite to the input shaft 1 within a set displacement ratio
range.
[0110] The brake B.sub.4 412 and the clutch C.sub.4 47 are engaged,
while the brake B.sub.2 410, the clutch C.sub.5 48, the clutch
C.sub.6 49, the one-way clutch F.sub.1 414, and the one-way clutch
F.sub.2 415 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.4 47, the rear-set ring gear 46, and the rear-set planet
carrier 45, and is then transmitted to the convergence mechanism
5.
[0111] As shown in FIG. 2 and FIG. 11, in reverse hydro-mechanical
hybrid transmission gear-3, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.3 21 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.7 55, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
engaged, the split mechanism planet carrier 23 transmits a part of
the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is disengaged,
the power in the mechanical transmission assembly 4 passes through
the convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in a direction
opposite to the input shaft 1 within a set displacement ratio
range.
[0112] The clutch C.sub.4 47, the clutch C.sub.5 48, and the
one-way clutch F.sub.1 414 are engaged, while the brake B.sub.2
410, the brake B.sub.4 412, the clutch C.sub.6 49, and the one-way
clutch F.sub.2 415 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.4 47, the front-set planet carrier 42, and the front-set ring
gear 43, and is then transmitted to the convergence mechanism 5.
Since the clutch C.sub.5 48 and the one-way clutch F.sub.1 414 are
engaged, the front-set sun gear 41 is prevented from overspeed
rotation and rotates at a speed consistent with the front-set
planet carrier 42, enabling the entire front planetary gear set
mechanism to rotate.
[0113] As shown in FIG. 2 and FIG. 12, in reverse hydro-mechanical
hybrid transmission gear-4, the hydraulic transmission input clutch
C.sub.1 31, the hydraulic transmission output clutch C.sub.2 38,
and the clutch C.sub.3 21 are engaged, while the brake B.sub.1 25,
the brake B.sub.3 411, the brake B.sub.5 413, the brake B.sub.6 51,
the clutch C.sub.7 55, and the one-way clutch F.sub.3 416 are
disengaged. Power passes through the input shaft 1 to the split
mechanism 2, transmitted by the split mechanism 2 to the hydraulic
transmission assembly 3 and the mechanical transmission assembly 4
respectively, then converged by the convergence mechanism 5, and
output from the output shaft 6. When the clutch C.sub.3 21 is
engaged, the split mechanism planet carrier 23 transmits a part of
the power from the input shaft 1 to the mechanical transmission
assembly 4, and the split mechanism ring gear 24 transmits the
other part of the power from the input shaft 1 to the hydraulic
transmission assembly 3. When the clutch C.sub.7 55 is disengaged,
the power in the mechanical transmission assembly 4 passes through
the convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, the
power in the hydraulic transmission assembly 3 passes through the
convergence mechanism ring gear 52 and the convergence mechanism
planet carrier 53 and is transmitted to the output shaft 6, and the
convergence mechanism planet carrier 53 rotates in a direction
opposite to the input shaft 1 within a set displacement ratio
range.
[0114] The brake B.sub.2 410, the clutch C.sub.6 49, and the
one-way clutch F.sub.2 415 are engaged, while the brake B.sub.4
412, the clutch C.sub.4 47, the clutch C.sub.5 48, and the one-way
clutch F.sub.1 414 are disengaged. The power in the mechanical
transmission assembly 4 sequentially passes through the clutch
C.sub.6 49, the one-way clutch F.sub.2 415, the front-set sun gear
41, and the front-set ring gear 43, and is then transmitted to the
convergence mechanism 5.
[0115] The reverse hydro-mechanical hybrid transmission includes
four hydro-mechanical transmission convergence gears, and the
rotation speeds of the input shaft 1 and the output shaft 6 are in
the following relationship:
n 0 = 1 i m - k 2 .times. e i 1 .times. i 2 .times. i 3 k 2 + 1
.times. n I ##EQU00010##
[0116] wherein k.sub.2 is a convergence mechanism characteristic
parameter,
[0117] if k.sub.2=2 and i.sub.1i.sub.2i.sub.3=1,
n 0 = 1 i m - 2 .times. e 3 .times. n I . ##EQU00011##
[0118] In hydro-mechanical transmission convergence gear-1,
i.sub.m1=2.92, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = 0 . 3 .times. 4 .times. 2 - 2 .times. e 3 .times. n I
##EQU00012##
[0119] when e.di-elect cons.[0, 171,1], n.sub.0.di-elect cons.[-0,
553,0]n.sub.1.
[0120] In hydro-mechanical transmission convergence gear-2,
i.sub.m2=1.57, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = 0 . 6 .times. 3 .times. 7 - 2 .times. e 3 .times. n I
##EQU00013##
[0121] when e.di-elect cons.[0, 3185,1], n.sub.0.di-elect cons.[-0,
454,0]n.sub.1.
[0122] In hydro-mechanical transmission convergence gear-3,
i.sub.m3=1.00, and the rotation speeds of the input shaft 1 and the
output shaft 6 are in the following relationship:
n 0 = 1 - 2 .times. e 3 .times. n I ##EQU00014##
[0123] when e.di-elect cons.[0, 5,1], n.sub.0.di-elect cons.[-0,
333,0]n.sub.1.
[0124] In hydro-mechanical transmission convergence gear-4,
i.sub.m4=-2.38, and the rotation speeds of the input shaft 1 and
the output shaft 6 are in the following relationship:
n 0 = - 0 . 4 .times. 2 .times. 0 - 2 .times. e 3 .times. n I
##EQU00015##
[0125] when e.di-elect cons.[0,1], n.sub.0.di-elect cons.[-0.807,
-0.140]n.sub.1.
[0126] As shown in FIG. 2 and FIG. 13, in forward pure mechanical
transmission gear-1, the brake B.sub.1 25 and the brake B.sub.6 51
are engaged, while the brake B.sub.2 410, the brake B.sub.4 412,
the hydraulic transmission input clutch C.sub.1 31, the hydraulic
transmission output clutch C.sub.2 38, the clutch C.sub.3 21, and
the clutch C.sub.7 55 are disengaged. Power passes through the
input shaft 1, the split mechanism 2, the mechanical transmission
assembly 4, and the convergence mechanism 5 and is output from the
output shaft 6. When the brake B.sub.1 25 is engaged, the split
mechanism ring gear 24 is locked, and the entire split mechanism 2
rotates. When the brake B.sub.6 51 is engaged, the convergence
mechanism ring gear 52 is locked, and power passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 to the output shaft 6.
[0127] The brake B.sub.5 413, the one-way clutch F.sub.3 416, the
clutch C.sub.6 49, and the one-way clutch F.sub.2 415 are engaged,
while the brake B.sub.3 411, the clutch C.sub.4 47, the clutch
C.sub.5 48, and the one-way clutch F.sub.1 414 are disengaged.
Power sequentially passes through the clutch C.sub.6 49, the
one-way clutch F.sub.2 415, and the front-set sun gear 41 to the
front-set planet carrier 42, and is split at the front-set planet
carrier 42 into the front-set ring gear 43 and the rear-set ring
gear 46 respectively. The power in the rear-set ring gear 46 passes
through the rear-set planet carrier 45 and is converged with the
power in the front-set ring gear 43, and the power is then
transmitted to the convergence mechanism 5. When the brake B.sub.5
413 and the one-way clutch F.sub.3 416 are engaged, the rear-set
sun gear 44 is locked.
[0128] As shown in FIG. 2 and FIG. 14, in forward pure mechanical
transmission gear-2, the brake B.sub.1 25 and the brake B.sub.6 51
are engaged, while the brake B.sub.2 410, the brake B.sub.4 412,
the hydraulic transmission input clutch C.sub.1 31, the hydraulic
transmission output clutch C.sub.2 38, the clutch C.sub.3 21, and
the clutch C.sub.7 55 are disengaged. Power passes through the
input shaft 1, the split mechanism 2, the mechanical transmission
assembly 4, and the convergence mechanism 5 and is output from the
output shaft 6. When the brake B.sub.1 25 is engaged, the split
mechanism ring gear 24 is locked, and the entire split mechanism 2
rotates. When the brake B.sub.6 51 is engaged, the convergence
mechanism ring gear 52 is locked, and power passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 to the output shaft 6.
[0129] The brake B.sub.5 413, the one-way clutch F.sub.3 416, and
the clutch C.sub.4 47 are engaged, while the brake B.sub.3 411, the
clutch C.sub.5 48, the clutch C.sub.6 49, the one-way clutch
F.sub.1 414, and the one-way clutch F.sub.2 415 are disengaged.
Power sequentially passes through the clutch C.sub.4 47, the
rear-set ring gear 46, and the rear-set planet carrier 45, and is
then transmitted to the convergence mechanism 5. When the brake
B.sub.5 413 and the one-way clutch F.sub.3 416 are engaged, the
rear-set sun gear 44 is locked.
[0130] As shown in FIG. 2 and FIG. 15, in forward pure mechanical
transmission gear-3, the brake B.sub.1 25 and the brake B.sub.6 51
are engaged, while the brake B.sub.2 410, the brake B.sub.4 412,
the hydraulic transmission input clutch C.sub.1 31, the hydraulic
transmission output clutch C.sub.2 38, the clutch C.sub.3 21, and
the clutch C.sub.7 55 are disengaged. Power passes through the
input shaft 1, the split mechanism 2, the mechanical transmission
assembly 4, and the convergence mechanism 5 and is output from the
output shaft 6. When the brake B.sub.1 25 is engaged, the split
mechanism ring gear 24 is locked, and the entire split mechanism 2
rotates. When the brake B.sub.6 51 is engaged, the convergence
mechanism ring gear 52 is locked, and power passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 to the output shaft 6.
[0131] The brake B.sub.5 413, the clutch C.sub.4 47, the clutch
C.sub.5 48, the one-way clutch F.sub.1 414, and the one-way clutch
F.sub.3 416 are engaged, while the brake B.sub.3 411, the clutch
C.sub.6 49, and the one-way clutch F.sub.2 415 are disengaged.
Power sequentially passes through the clutch C.sub.4 47, the
front-set planet carrier 42, and the front-set ring gear 43, and is
then transmitted to the convergence mechanism 5. Since the clutch
C.sub.5 48 and the one-way clutch F.sub.1 414 are engaged, the
front-set sun gear 41 is prevented from overspeed rotation and
rotates at a speed consistent with the front-set planet carrier 42,
enabling the entire front planetary gear set mechanism to
rotate.
[0132] As shown in FIG. 2 and FIG. 16, in forward pure mechanical
transmission gear-4, the brake B.sub.1 25 and the brake B.sub.6 51
are engaged, while the brake B.sub.2 410, the brake B.sub.4 412,
the hydraulic transmission input clutch C.sub.1 31, the hydraulic
transmission output clutch C.sub.2 38, the clutch C.sub.3 21, and
the clutch C.sub.7 55 are disengaged. Power passes through the
input shaft 1, the split mechanism 2, the mechanical transmission
assembly 4, and the convergence mechanism 5 and is output from the
output shaft 6. When the brake B.sub.1 25 is engaged, the split
mechanism ring gear 24 is locked, and the entire split mechanism 2
rotates. When the brake B.sub.6 51 is engaged, the convergence
mechanism ring gear 52 is locked, and power passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 to the output shaft 6.
[0133] The brake B.sub.3 411 and the clutch C.sub.4 47 are engaged,
while the brake B.sub.5 413, the clutch C.sub.5 48, the clutch
C.sub.6 49, the one-way clutch F.sub.1 414, the one-way clutch
F.sub.2 415, and the one-way clutch F.sub.3 416 are disengaged.
Power sequentially passes through the clutch C.sub.4 47, the
front-set planet carrier 42, and the front-set ring gear 43, and is
then transmitted to the convergence mechanism 5.
[0134] As shown in FIG. 2 and FIG. 17, in reverse pure mechanical
transmission, the brake B.sub.1 25, the brake B.sub.2 410, the
brake B.sub.6 51, the clutch C.sub.6 49, and the one-way clutch
F.sub.2 415 are engaged, while the other brakes and clutches are
disengaged. When the brake B.sub.1 25 is engaged, the split
mechanism ring gear 24 is locked, and power passes through the
split mechanism sun gear 22 and the split mechanism planet carrier
23 and is transmitted to the mechanical transmission assembly 4.
When the clutch C.sub.6 49 and the one-way clutch F.sub.2 415 are
engaged, the power in the mechanical transmission assembly 4
sequentially passes through the clutch C.sub.6 49, the one-way
clutch F.sub.2 415, the front-set sun gear 41, and the front-set
ring gear 43, and is then transmitted to the convergence mechanism
sun gear 54. When the brake B.sub.6 51 is engaged, the convergence
mechanism ring gear 52 is locked, and power passes through the
convergence mechanism sun gear 54 and the convergence mechanism
planet carrier 53 to the output shaft 6.
[0135] In pure mechanical transmission, the rotation speeds of the
input shaft 1 and the output shaft 6 are in the following
relationship:
[0136] in mechanical gear-1, n.sub.0=0.342n.sub.1;
[0137] in mechanical gear-2, n.sub.0=0.637n.sub.1;
[0138] in mechanical gear-3, n.sub.0=n.sub.1;
[0139] in mechanical gear-4, n.sub.0=1.429n.sub.1;
[0140] in mechanical reverse gear, n.sub.0=-0.420n.sub.1.
[0141] Through model predictive control of the transmission system,
the problem of globally optimal dynamic programming of fuel economy
is transformed into the local optimization control problem in a
prediction region, and the future vehicle operation status in the
prediction region is continuously updated through rolling
optimization, to obtain optimization results and realize real-time
application of predictive control in the hydro-mechanical hybrid
transmission system. Vehicle predictive control based on time
domain is online rolling optimization control within the framework
of model predictive control and implemented in combination with
dynamic programming, and the principle thereof is shown in FIG.
18(a).
[0142] In a prediction region q, the state transition equation of
vehicle predictive control in hybrid transmission is:
x(k+1)=.mu.[x(k),u(k)]
[0143] wherein .mu. is a time-discrete system function, x(k+1) is a
state variable related to k+1, x(k) is a state variable related to
k, and u(k) is a control variable related to k.
[0144] In the prediction region q, an objective function of
minimizing the fuel consumption of the hybrid transmission system
is:
J 1 = min .times. t = t .function. ( k ) t = t .function. ( k + q )
.times. v k .function. ( x k , u k ) .times. .DELTA. .times. t
##EQU00016##
[0145] wherein J.sub.1 is an objective function of fuel economy
when a linear predictive control system is adopted, v.sub.k is a
stage indicator of the k.sup.th stage, x.sub.k is a state variable
of the k.sup.th stage, u.sub.k is a control variable of the
k.sup.th stage, .DELTA.t is a time interval, t(k) is a time point
of the k.sup.th stage, and t(k+q) is a time point of the
(k+q).sup.th stage.
[0146] In a control region p, a sensing device is generally adopted
for measurement; and in the prediction region q, a GPS/GIS system
is generally adopted for prediction. Prediction relies on the
selection of an appropriate prediction window length for data
collection as well as a high cost-performance ratio of the
predictive control system.
[0147] The structures of the predictive control systems are shown
in FIG. 18(b). The vehicle dynamics model of the hybrid
transmission system is of a typical nonlinear system, and needs to
satisfy various constraints. The linear predictive control system
can hardly describe the practical dynamics model of a vehicle
system. Therefore, the nonlinear predictive control system is
adopted to control dynamic characteristics and state variables of
the hybrid transmission system, constrain control variables,
estimate future states, and solve the online optimal control
problem of a bounded region.
[0148] In this case, the objective function of minimizing the fuel
consumption of the hybrid transmission system is:
J 2 = min .times. t = t .function. ( k ) t = t .function. ( k + q )
.times. L .function. [ x .function. ( t ) , u .function. ( t ) ]
##EQU00017##
[0149] wherein J.sub.2 is an objective function of fuel economy
when a nonlinear predictive control system is adopted, L is an
instantaneous fuel consumption function at a time point t, x(t) is
a state variable at a time point t, and u(t) is a control variable
at a time point t.
* * * * *