CN208559007U - A kind of single planetary gear hybrid gearbox system - Google Patents
A kind of single planetary gear hybrid gearbox system Download PDFInfo
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- CN208559007U CN208559007U CN201821042932.2U CN201821042932U CN208559007U CN 208559007 U CN208559007 U CN 208559007U CN 201821042932 U CN201821042932 U CN 201821042932U CN 208559007 U CN208559007 U CN 208559007U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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Abstract
The utility model relates to a kind of single planetary gear hybrid gearbox systems, comprising: single planetary row: including three rotatable parts, i.e. outer gear ring, sun gear and the planetary gear engaged respectively with outer gear ring and sun gear, be connected with planet carrier on the planetary gear；Power source: including engine, first motor and the second motor respectively with single planetary row transmission connection, the first motor and the second motor are equipped with the power accumulator to charge with electricity consumption；Shift assembly: the single-phase clutch or brake of the transmission including shifting element and to locking engine and single planetary row；Output shaft: it is sequentially connected with single planetary row, which is provided with main reducing gear.Compared with prior art, the utility model has many advantages, such as that mechanical complexity is lower, control difficulty is low, multi-mode.
Description
Technical field
The utility model relates to electricity mixed power vehicle drive areas, more particularly, to a kind of single planetary gear hybrid power
Transmission system.
Background technique
Electromechanical mixing dynamic force vehicle is generally included using internal combustion engine and one or more motor/generators.Existing mixing
Power transmission scheme can substantially be divided into two major class: the mixed of one to two motors compositions is added on the basis of traditional speed change
The hybrid power scheme closing power scheme and specially being designed for hybrid power, wherein exclusively for the speed change of hybrid vehicle design
Device scheme mainly includes in series and parallel for the hybrid gearbox of main drive mode from the point of view of existing development trend
Scheme and the power dividing hybrid gearbox scheme based on planet row.With dynamic for the mixing of main drive mode in series and parallel
Power speed changer scheme is comparatively relatively simple for structure, and cost is relatively low for research and development, and the meshing efficiency between general gear is higher, but right
The regulating power of engine working point is limited, and the hybrid gearbox of power dividing is then according to planet row number and machinery
The difference of point number, includes single mode, and the power dividing hybrid gearbox of bimodulus and multimode, structure is more compact,
It is more flexibly effective to engine working point adjusting using the advantage of planet row power dividing, so as to improve fuel economy, but
With the increase of planet row number, speed changer structure is complex.So the existing dedicated hybrid transmission of two classes all exists respectively
From advantage and disadvantage, how to be effectively combined these two types of hybrid gearbox schemes, integrate respective advantage as in this patent
The maximum bright spot of described novel hybrid speed changer scheme.
Application No. is the Chinese utility model patent application of CN 201110405238, the mixing of variable proportion dynamic branch is dynamic
Power speed changer is engaged using single planet row and general gear, by different connection topological structures and combination, be may be implemented not
Same power dividing mode, but excessive torque-transmitting mechanisms have been used, the utilization rate of element is relatively low, the mode phase of realization
To limited.In addition, design scheme connection is complex, in turn result in cost increase, control difficulty increases
Utility model content
The purpose of this utility model is exactly to provide a kind of uniline star tooth to overcome the problems of the above-mentioned prior art
Take turns hybrid gearbox system.
The purpose of this utility model can be achieved through the following technical solutions:
A kind of single planetary gear hybrid gearbox system, comprising:
Single planetary row: it including three rotatable parts, i.e., outer gear ring, sun gear and is engaged respectively with outer gear ring and sun gear
Planetary gear, be connected with planet carrier on the planetary gear；
Power source: including engine, first motor and the second motor respectively with single planetary row transmission connection, described the
One motor and the second motor are equipped with the power accumulator to charge with electricity consumption, the engine, first motor and output
Axis is respectively corresponded with certain fixed speed ratio and is connect with three rotatable parts of single planetary row, and second motor is different
What the rotatable parts or output shaft selectively being connect with certain fixed speed ratio with engine under operating mode were connected turns
Dynamic component transmission connection；
Shift assembly: the single-phase clutch of the transmission including shifting element and to locking engine and single planetary row or
Brake；
Output shaft: it is sequentially connected with single planetary row, which is provided with main reducing gear.
The first motor is connect by one-way clutch or brake with outer gear ring, and the planet carrier passes sequentially through
First gear, third gear, the second shifting element, second driving shaft, second gear, the 5th gear and the 4th as output shaft
Transmission shaft driven connection, second motor passes sequentially through third transmission shaft and the 6th gear and second driving shaft transmission connects
It connects, the first motor passes through the center of first gear by the first transmission shaft and sun gear is sequentially connected.
It is connected with the revolving speed synchronization section of the first shifting element on first transmission shaft, is nibbled on the left of the first shifting element
It closes component to connect with first gear, right side meshing part and case of transmission are affixed.
It is connected with the revolving speed synchronization section of the first shifting element on first transmission shaft, is nibbled on the left of the first shifting element
Component is closed to connect with first gear.
The first motor is connect by one-way clutch or brake with planet carrier, and the outer gear ring passes sequentially through
Third gear, the second shifting element, second driving shaft, second gear, the 5th gear and the 4th transmission shaft as output shaft pass
Dynamic connection, second motor passes sequentially through third transmission shaft and the 6th gear and second driving shaft is sequentially connected, described
First motor passes through the center of first gear by the first transmission shaft and sun gear is sequentially connected.
It is connected with the revolving speed synchronization section of the first shifting element on first transmission shaft, is nibbled on the left of the first shifting element
It closes component to connect with planet carrier, right side meshing part and case of transmission are affixed.
It is connected with the revolving speed synchronization section of the first shifting element on first transmission shaft, is nibbled on the left of the first shifting element
Component is closed to connect with planet carrier.
The first motor passes sequentially through the 5th transmission shaft, eighth gear and the 7th gear and the first transmission shaft driven connects
It connects, the 7th gear and the first transmission shaft are affixed, and the eighth gear and the 5th transmission shaft are affixed, the 7th tooth
Wheel is connect with eighth gear internal messing.
The speed changer realizes different operating modes by different connection types, specifically includes:
Electric-only mode: it is individually energized by the second motor or is energized jointly by first motor and the second motor, and engine
It remains static；
Input power shunts hybrid mode: being energized jointly by engine, first motor and the second motor, this mode is suitable
The case where low speed (being lower than 50km/h) runs in for vehicle；
Parallel mode: individually being energized by engine or energized jointly by engine and first motor, the second motor, this mould
Formula is suitable for vehicle the case where high speed (being higher than 80km/h) operation；
Tandem mode: engine and wheel are full decoupled, individually energized by engine or by engine and first motor,
Second motor energizes jointly, this mode is suitable for vehicle the case where low speed runs and (is less than 80km/h)；
Parking charge mode: by engine as energizing, first motor or the second motor absorb the energy that engine generates
The case where amount, this mode is suitable for power accumulator electricity lower (less than 30%).
First shifting element and the second shifting element is synchronizer or dog tooth clutch, and is switched in different mode
In the process, including between electric-only mode, electric-only mode and input power shunt between hybrid mode, input power point
Flow between hybrid mode and parallel type hybrid dynamic mode, between electric-only mode and tandem mode and it is different and
Pattern switching is carried out between connection formula hybrid mode, the principal and subordinate end rotational speed difference of shifting element is actively adjusted using two motors,
Realize that the principal and subordinate end of shifting element switches without rotational speed difference.
Compared with prior art, the utility model has the advantage that
One, mechanical complexity is lower: novel hybrid speed changer scheme, transmission element described in the utility model
It is less by number, it only include single planetary gear group, the general gear of certain amount, two shifting elements, and two shift members
Part can be realized by synchronizer or dog tooth clutch.Under the entire each gear of hybrid gearbox or mode, pass
Dynamic route is relatively simple, and meshing efficiency is higher between gear, advantageously reduces hybrid gearbox machine-building and application cost,
Further reduce the volume and weight of speed changer.
Two, control difficulty is low: the novel hybrid speed changer scheme of the utility model, in all gear or mode
Under, it does not all need or only needs to operate a shifting element, in different mixed dynamic dynamic mode handoff procedures, mould
The principal and subordinate end rotational speed difference of formula switching front and back shifting element can realize that nature is synchronous, and there is no shift shock and power interruptions etc. to ask
Topic is compared with traditional laminated type clutch, and synchronizing speed is very fast, and ride comfort is preferable, and transmission control is reduced from structure
And the difficulty of switching.
Three, multi-mode: the utility model contains pure electric vehicle, power dividing hybrid power and parallel mixing and moves this three categories
Drive mode includes multiple subpatterns under each drive mode, and control model is more, and different modes can sufficiently meet difference
Drive duty requirements, engine working point can flexibly be adjusted, guarantee its work in the higher operating point of its efficiency,
The problem of so that system effectiveness is effectively ensured, and be not present the second energy conversion for being similar to series connection type hybrid power system.
Detailed description of the invention
Fig. 1 is the first embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 2 is second of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 3 is the third embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 4 is the 4th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 5 is the 5th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 6 is the 6th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 7 is the 7th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 8 is the 8th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Fig. 9 is the 9th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 10 is the tenth kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 11 is a kind of the tenth embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 12 is the 12nd kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 13 is the 13rd kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 14 is the 14th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 15 is the 15th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 16 is the 16th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 17 is the 17th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 18 is the 18th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 19 is the 19th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 20 is the 20th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 21 is a kind of the 20th embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 22 is the 22nd kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 23 is the 23rd kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 24 is the 24th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 25 is the 25th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 26 is the 26th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 27 is the 27th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 28 is the 28th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Figure 29 is the 29th kind of embodiment structure figure of novel hybrid speed changer provided by the utility model.
Description of symbols in figure:
1, engine, 2, first motor, the 3, second motor, 4, sun gear, 5, planetary gear, 6, outer gear ring, 7, planet carrier, 8,
First gear, the left side meshing part in the 9, first shifting element, the revolving speed synchronization section in the 10, first shifting element, 11,
Right side meshing part and the case of transmission connected with it in one shifting element, the 12, the 4th gear, the 13, the 6th gear, 14,
Revolving speed synchronization section in second shifting element, the left side meshing part in the 15, second shifting element, 16, third gear, 17,
Second gear, the 18, the 5th gear, the 19, first transmission shaft, 20, second driving shaft, 21, third transmission shaft, the 22, the 4th transmission
Axis, 23, common brake or one-way clutch, the 25, the 7th gear, 26, eighth gear, the 27, the 5th transmission shaft, 28 the 12nd teeth
Wheel, the 29, the tenth gear, the 30, the 11st gear, the 31, the 6th transmission shaft.
Specific embodiment
The characteristics of for above-mentioned novel mixed dynamic power transmission and advantage, will be carried out specifically by following specific embodiments
Bright and description.The utility model is described in detail in the following with reference to the drawings and specific embodiments.Obviously, described to be only
A part of preferred embodiment of the utility model, rather than whole embodiments.Man skilled in the art is easy to based on team
Utility model principle makes many changes, therefore the utility model is not secured to shown and described details, but is intended to
It include all changes and modification in Claims scope.
Embodiment 1:
As shown in figure 1 and table 1, Fig. 1 is a kind of reality of power dividing type hybrid gearbox provided by the utility model
Mode is applied, including
Single planetary row and 6 general gears: single planetary row include outer gear ring 6, sun gear 4 and respectively with outer gear ring 6 and
The planetary gear 5 and planet carrier 7 that sun gear 4 engages；6 general gears contain first gear 8, second gear 17, third gear
16, the 4th gear 12, the 5th gear 18 and the 6th gear 13, wherein single planetary row sun gear 4 and first gear 8 it is fixed respectively and
Empty set is on the first transmission shaft 19, second gear 17, and fixed and empty set second is driven respectively for the 4th gear 12 and third gear 16
On axis 20, the 6th gear 13 is fixed on third transmission shaft 21, and the 5th gear 18 is fixed on the 4th transmission shaft 22.Single planetary row
In planet carrier 7 and first gear 8 be connected directly by axis, first gear 8 and third gear 16 are intermeshed, the 4th gear 12
It is intermeshed with the 6th gear 13, second gear 17 and the intermeshing of the 5th gear 18, as level-one main reducing gear, the 4th transmission
Output end of the axis 22 as hybrid gearbox；Engine 1: it is directly connect with single planetary row outer gear ring 6.By commonly braking
Perhaps single clutch 23 is separately connected engine and case of transmission when common brake or single clutch 23 are in device
When lockup state, engine is locked up, and when common brake or single clutch 23 are in non-lockup state, engine can
With free movement；Left side meshing part 9 and first gear 8 in first shifting element are connected, the right side in the first shifting element
Meshing part 11 and case of transmission are connected, and by 10 side-to-side movement of revolving speed synchronization section in the first shifting element, can incite somebody to action
First gear 8 or case of transmission are connected on the first transmission shaft 19；15 He of left side meshing part in second shifting element
Third gear 16 is connected, and by the revolving speed synchronization section 14 in the second shifting element, third gear 16 can be bonded to second
On transmission shaft 20；First motor 2: it is connect with the first transmission shaft 19；Second motor 3: it is connect with third transmission shaft 21.
1 operating mode of table and its corresponding operating mode table
| Operating mode | One-way clutch | First shifting element | Second shifting element |
| Single motor pure electric vehicle drive mode | |||
| Bi-motor pure electric vehicle drives subpattern | In lockup state | 14,15 engagements | |
| Serial mixed power drive mode | In non-lockup state | 9,10 engagements | |
| Input power shunts hybrid mode | In non-lockup state | 14,15 engagements | |
| First parallel mixed dynamic dynamic mode | In non-lockup state | 10,11 engagements | 14,15 engagements |
| Second parallel mixed dynamic dynamic mode | In non-lockup state | 9,10 engagements | 14,15 engagements |
| Parking charge mode | In non-locking shape | 9,10 engagements |
In the present embodiment, novel hybrid gearbox can use different work under different driving cycles
Mode, as shown in table 1, comprising:
Electric-only mode: by the second motor energy supply 3 or by first motor 2 and the second energy supply jointly of motor 3.For single motor
Electric-only mode directly can drive vehicle by the second motor 3, operate without shifting element；For bi-motor pure electric vehicle mould
Formula needs to be closed 14 in the second shifting element and 15, and one-way clutch 23 will not be fallen by automatic locking, engine at this time
It drags, vehicle is driven by first motor 2 and the second motor 3 jointly, and the vehicle speed range driven is larger.
Input power shunts hybrid mode: by engine 1, first motor 2 and the second energy supply jointly of motor 3.At this time
One-way clutch 23 is in non-lockup state, and 14 and 15 closures in the second shifting element, first motor 2 is typically in power generation
State, the second motor 3 are in driving condition.
The mixed dynamic dynamic mode of tandem: by engine 1, first motor 2 and the second energy supply jointly of motor 3.At this time unidirectionally from
Clutch 23 is in non-lockup state, and 9 and 10 closures in the first shifting element, engine 1 and wheel are full decoupled.
First parallel mixed dynamic dynamic mode: by engine 1 and the second energy supply jointly of motor 3.One-way clutch 23 at this time
10 and 11 in non-lockup state, the first shifting element and the second 14 and 15 closures in shifting element, first motor
2 are locked up, and the second motor 3 carries out active adjusting to engine working point.
Second parallel mixed dynamic dynamic mode: by engine 1, first motor 2 and the second energy supply jointly of motor 3.It is single at this time
It is in non-lockup state to clutch 23,9 and 10 in the first shifting element and the second 14 and 15 closures in shifting element,
First motor 2 and the second motor 3 carry out active adjusting to engine working point.
For starting and low speed operational process:
In the higher situation of Vehicular battery SOC, when vehicle remains static, vehicle can be pure using single motor at this time
Electronic subpattern carries out pure electric vehicle starting, and vehicle pure motor driving is operated alone to certain speed by the second motor 3；Work as vehicle
When power demand is larger, when the subpattern of single motor pure electric vehicle cannot provide required power, or when using single motor pure electric vehicle
When modular system is relatively inefficient, it can be started to walk using the subpattern of bi-motor pure electric vehicle, and travel to certain speed, herein
For one-way clutch by 11 locking of engine 1 and case of transmission, engine 1 will not be dragged in the process.Certainly, if removed single
To clutch 23, then reduce by a shifting element, but only exist single motor pure electric vehicle subpattern at this time, or in the pure electricity of bi-motor
Engine 1 will be in dragging state in mover mode.
In the lower situation of Vehicular battery SOC, when vehicle remains static, vehicle can pass through two ways at this time
It starts to walk and is exercised in certain vehicle speed range to certain speed: first, input power shunts hybrid mode and starts to walk
And it travels to certain speed.In this mode, one-way clutch 23 is in lockup state, the output power of engine do not pass through
Single planetary row is shunted, and first motor 2 and the second motor 3 are respectively as generator or motor to 1 operating point of engine
It is adjusted, while guaranteeing higher starting dynamic property, improves the fuel consumption rate of engine；Second, tandem mixing is dynamic
Force mode is started to walk and is travelled to certain speed.In this mode, engine and wheel are full decoupled, and engine operation exists
Optimal working point drives vehicle start by the second motor 3.
For middle speed hybrid operational process:
When vehicle is started to walk by electric-only mode and is travelled after a certain period of time, when battery SOC is higher, vehicle can pass through list
Motor pure motor driving is then switched to bi-motor pure electric vehicle drive mode, guarantees vehicle in full speed range to certain speed
Pure motor driving.When SOC value of battery drops to certain level or system effectiveness is relatively low, vehicle can be pure by single motor
Electronic subpattern or bi-motor pure electric vehicle subpattern switch to input power and shunt hybrid mode.
For mixed at high speed power operational process:
When vehicle is started to walk by electric-only mode and is travelled after a certain period of time, when battery SOC is higher, vehicle can be by double
Motor pure electric vehicle drive mode.When SOC value of battery drops to certain level or system effectiveness is relatively low, vehicle can be by
Input power shunts hybrid mode and switches to parallel type hybrid dynamic mode, when avoiding high speed, input power shunt mode
The problem of causing efficiency to reduce due to power cycle.
For mode handover procedure:
The mixed dynamic dynamic mode of tandem is switched to for single motor electric-only mode: since first gear 8 does not transmit power,
Directly close 9 and 10 in the first shifting element.
Input power is switched to for the mixed dynamic dynamic mode of tandem and shunts mixed dynamic dynamic mode: needing to open the first shift
14 and 15 in the second shifting element are closed in 9 in element and 10.In the process, it changes first with first motor 2 first
9 and 10 unloadings in element are kept off, then it is opened, then guarantees the power of output end using the second motor 3, utilize the first electricity
14 and 15 rotational speed differences in 2 the second shifting element of active accommodation of machine are then shut off to certain level, complete the switching of mode.
Or do not open first in the first shifting element 9 and 10, close 14 in the second shifting element and 15 first, then
Opening 9 and 10 in the first shifting element.
Input power is switched to for single motor pure electric vehicle subpattern and shunts hybrid mode: firstly, closure second is changed
14 and 15 in element are kept off, since third gear 16 dallies, torque is not transmitted, can directly be closed the first shifting element.So
Afterwards, engine is started using first motor 2.After pulling engine 1 to certain revolving speed using first motor 2 at this time,
Engine 1 carries out oil spout igniting starting.Vehicle comfort is influenced to reduce the torque of engine start moment outburst, is needed at this time
It wants first motor to carry out of short duration power generation to be balanced the outburst torque of engine start moment, then vehicle enters input power
Shunt hybrid mode.
Or it is closed 9 in the first shifting element and 10 first, entire planetary gear rotates at the same speed at this time, utilizes the first electricity
After machine 2 pulls engine 1 to certain revolving speed, engine 1 carries out oil spout igniting starting.Then it separates in the first shifting element
9 and 10.But since the first shifting element is that synchronizer or dog tooth clutch at this time can not in the case where transmitting power
It is directly separated by the executing agency of shifting element, so to be carried out using first motor 2 to 9 and 10 in the first shifting element
Unloading, then again separates it.
Shunt hybrid mode for input power and switch to parallel mixed dynamic dynamic mode: input power shunts mixing
Dynamic mode is compared with parallel mixed dynamic dynamic mode, and a mechanical constraint is lacked on mechanical connection, is thus caused the 4th
It, can be by first motor 2 to engine speed or the shift that will be engaged in the case that 22 revolving speed of transmission shaft remains unchanged
Element principal and subordinate end rotational speed difference carries out active adjusting, while guaranteeing vehicle power output, will will fast and effeciently can connect
The shifting element principal and subordinate end rotational speed difference of conjunction is contracted to certain level, then corresponding synchronous by the engagement of shifting element executing agency
Device or dog tooth clutch.
Embodiment 2:
For second of embodiment of Fig. 2:
On the basis of first embodiment, reduce 11 in the first shifting element, reduce speed changer axial dimension at this time,
Realization is compared with function with the first embodiment, reduces the first parallel type hybrid dynamic mode, other modes are constant.
Embodiment 3:
For the third embodiment of Fig. 3:
On the basis of 3rd embodiment, remove the first shifting element, at this time reduce speed changer axial dimension, realize and
Function is compared with second of embodiment, reduces the second parallel type hybrid dynamic mode, other modes are constant.
Embodiment 4:
For the 4th kind of embodiment of Fig. 4:
On the basis of first embodiment, the second shifting element is removed, it is realized and function and the first embodiment at this time
It compares, reduces serial mixed power mode, other modes are constant.
Embodiment 5:
For the 5th kind of embodiment of Fig. 5:
On the basis of fourth embodiment, 11 in the first shifting element are removed, it is realized and function and first at this time
Kind embodiment is compared, and reduces the first parallel type hybrid dynamic mode, other modes are constant.
Embodiment 6:
For the 6th kind of embodiment of Fig. 6:
On the basis of fourth embodiment, 9 in the first shifting element are removed, it is realized and function and the first at this time
Embodiment is compared, and the second parallel type hybrid dynamic mode is reduced, other modes are constant.
Embodiment 7:
For the 7th kind of embodiment of Fig. 7:
On the basis of fourth embodiment, removal removes original 4th gear 12, at this time gear 16 and 13 directly in or
External toothing (is illustrated as external toothing), it is realized at this time is consistent with function and the 4th kind of embodiment.
Embodiment 8:
For the 8th kind of embodiment of Fig. 8:
On the basis of five embodiments, removal removes original 4th gear 12, at this time gear 16 and 13 directly in or
External toothing (is illustrated as external toothing), it is realized at this time is consistent with function and the 5th kind of embodiment.
Embodiment 9:
For the 9th kind of embodiment of Fig. 9:
On the basis of sixth embodiment, original 4th gear 12 of removal is completely removed, gear 16 and 13 is directly interior at this time
Or external toothing (being illustrated as external toothing), it is realized at this time is consistent with function and the 6th kind of embodiment.
Embodiment 10:
For the tenth kind of embodiment of Figure 10:
On the basis of the first embodiment, position and the connection relationship of first and second shifting element are changed.At this time
One, which changes left side meshing part 9 in part, connects case of transmission, and first changes right side meshing part 11 in part and the
The connection of one gear 8, the first revolving speed synchronization section 10 changed in part are connect with the planet carrier 7 in single planetary gear, are closed 9 Hes
10, can be by 7 locking of planet carrier in single planetary gear, being closed 10 and 11 can be by the planet carrier 7 and the in single planetary gear
One gear 8 links together；Right side meshing part 15 in second shifting element is connect with case of transmission, and second changes part
In revolving speed synchronization section 14 be consolidated on the first transmission shaft 19, closure 14 and 15 can be by the sun gear 4 in single planetary gear
Locking.The mode of realization is as shown in table 2.
2 operating mode of table and its corresponding operating mode table
| Operating mode | One-way clutch | First shifting element | Second shifting element |
| Single motor pure electric vehicle drive mode | |||
| Bi-motor pure electric vehicle drives subpattern | In lockup state | 10,11 engagements | |
| Serial mixed power drive mode | In non-lockup state | 9,10 engagements | |
| Input power shunts hybrid mode | In non-lockup state | 10,11 engagements | |
| First parallel mixed dynamic dynamic mode | In non-lockup state | 10,11 engagements | 14,15 engagements |
| Parking charge mode | In non-locking shape | 9,10 engagements |
Embodiment 11:
For a kind of the tenth embodiment of Figure 11:
On the basis of the tenth kind of embodiment, the second shifting element is removed, other connections remain unchanged, the mould realized at this time
Formula is compared with the tenth kind of embodiment, reduces the first parallel type hybrid dynamic mode, other modes remain unchanged.
Embodiment 12:
For the 12nd kind of embodiment of Figure 12:
On the basis of a kind of ten embodiments, removal removes original 4th gear 12, and gear 16 and 13 is directly interior at this time
Or external toothing (being illustrated as external toothing), it is realized at this time and function and a kind of the tenth embodiment are consistent.
Embodiment 13:
For the 13rd kind of embodiment of Figure 13:
On the basis of the first embodiment, change position and the connection type of the first shifting element, at this time the first shift
The left side meshing part 9 changed in part connects case of transmission, and the first right side meshing part 11 changed in part is consolidated in first
On transmission shaft 19, the first revolving speed synchronization section 10 changed in part is connect with the planet carrier 7 in single planetary gear, is closed 9 Hes
10, can by 7 locking of planet carrier in single planetary gear, be closed 10 and 11 at this time planetary gear as unitary rotation.It realizes
Mode is as shown in table 3.
3 operating mode of table and its corresponding operating mode table
| Operating mode | One-way clutch | First shifting element | Second shifting element |
| Single motor pure electric vehicle drive mode | |||
| Bi-motor pure electric vehicle drives subpattern | In lockup state | 14,15 engagements | |
| Serial mixed power drive mode 1 | In non-lockup state | 9,10 engagements | |
| Serial mixed power drive mode 2 | In non-lockup state | 10,11 engagements | |
| Input power shunts hybrid mode | In non-lockup state | 14,15 engagements | |
| First parallel mixed dynamic dynamic mode | In non-lockup state | 10,11 engagements | 14,15 engagements |
| Parking charge mode | In non-locking shape | 9,10 engagements |
Embodiment 14:
For the 14th kind of embodiment of Figure 14:
On the basis of the first embodiment, change the right side meshing part and revolving speed synchronization section of the first shifting element
Connection type, the first left side meshing part 9 changed in part connects the first transmission gear 8 and remains unchanged at this time, the first shift
The right side meshing part 11 changed in part is consolidated on the first transmission shaft 19, and first changes revolving speed synchronization section 10 and change in part
7 locking of planet carrier in single planetary gear can be closed 10 and 11 by fast device shell connection, closure 9 and 10, can be with locking row
Sun gear 4 in star gear.The mode of realization is compared with the first embodiment, reduces the second parallel type hybrid dynamic mode,
Remaining mode remains unchanged.
Embodiment 15:
For the 15th kind of embodiment of Figure 15:
On the basis of the first embodiment, increase the tenth gear 29, the 11st gear 30 and the 6th transmission shaft 31,
Engine 1 is connected with the 11st gear 30 at this time, and in the tenth gear 29 and the 11st gear 30 or external toothing (is illustrated as outer nibble
Close), the tenth gear 29 is consolidated on the 6th transmission shaft 31, and connects the gear ring 6 in planetary gear by the 6th transmission shaft 31,
One-way clutch or common brake 23 are between engine 1 and the 11st gear 30, can be with locking engine.The implementation
The mode and the first embodiment that example is realized are consistent.Certainly, this embodiment further includes above-mentioned all embodiments (embodiment 1-
Embodiment 14) by identical change, dynamic power transmission scheme mixed accordingly is obtained, details are not described herein.
For the 16th kind of embodiment of Figure 16:
On the basis of the 15th kind of embodiment, the position of original one-way clutch or common brake 23 is carried out
Change, one-way clutch or common brake 23 are on the 6th transmission shaft 31 at this time, are used for locking engine.
Embodiment 17:
For the 17th kind of embodiment of Figure 17:
On the basis of first embodiment, increase by the 7th gear 25, eighth gear 26 and the 5th transmission shaft 27 form the
Two kinds of embodiments.The 7th gear 25 is directly connected and the first transmission shaft 19 at this time.Eighth gear 26 is directly connected and the 5th transmission
Axis 27.7th gear 25 and eighth gear 26 are in internal messing state.5th transmission shaft 27 is directly connected with first motor 2.
The function that the embodiment is realized at this time is consistent with the first embodiment, and details are not described herein, but can effectively mention
The maximum speed of high first motor 2 limits, and realizes higher pure electric vehicle max. speed and the maximum of first motor 2 is effectively reduced
Torque-demand, to reduce the size of first motor 2.
Certainly, this embodiment further includes above-mentioned all embodiments (embodiment 1- embodiment 16) by identical change, is obtained
To corresponding mixed dynamic power transmission scheme, details are not described herein.
Embodiment 18:
For the 18th kind of embodiment of Figure 18:
Increase the position for changing the second motor 3 on the basis of a kind of embodiment, the second motor 3 is still passed with third at this time
Moving axis 21 connects, and the 6th gear 13 is consolidated on third transmission shaft 21, and third transmission shaft 21 is hollow shaft, is placed in the first transmission
On axis 19, the 6th gear 13 and the 9th gear 12 is outer or internal messing (being illustrated as external toothing), first motor 2 and the second motor 3
It is coaxially arranged.Its function of realizing and first embodiment are consistent, and details are not described herein.On further including in this certain embodiment
It states in embodiment, changes the second motor position using identical means and be formed by speed changer scheme.
Embodiment 19:
For the 19th kind of embodiment of Figure 19:
It is compared with first embodiment, firstly, the planet carrier 7 in engine 1 and single planetary gear is connected directly, removal first
Gear 8, left side meshing part 9 and planet carrier 7 in the first shifting element are connected directly.Outer gear ring in single planetary gear at this time
6 there are external gear pumps, and with 16 external toothing of third gear.The mode and the first embodiment complete one that the embodiment is realized
It causes, details are not described herein.
Embodiment 20:
For the 20th kind of embodiment of Figure 20:
On the basis of 19 embodiment, reduce 11 in the first shifting element, reduce speed changer axial dimension at this time,
Its realization is compared with function with the first embodiment, reduces the first parallel type hybrid dynamic mode, other modes are constant.
Embodiment 21:
For a kind of the 20th embodiment of Figure 21:
On the basis of the 20th kind of embodiment, change the connection type of meshing part on the left of the first shifting element, at this time
Left-hand side part in first shifting element is connected with the gear ring 6 in planetary gear, and closure 9 and 10, entire planetary gear is as one
Body rotation, the mode and embodiment 20 of realization are consistent.
Embodiment 22:
For the 22nd kind of embodiment of Figure 22:
On the basis of the 19th kind of embodiment, the second shifting element is removed, other connections remain unchanged.It realizes at this time
Mode is compared with the 19th kind of embodiment, reduces serial mixed power mode, other modes remain unchanged.
Embodiment 23:
For the 23rd kind of embodiment of Figure 23:
On the basis of the 19th kind of embodiment, removal removes original 4th gear 12, and gear 16 and 13 is directly interior at this time
Or external toothing (being illustrated as external toothing), it is realized at this time is consistent with function and the 22nd kind of embodiment.
Embodiment 24:
For the 24th kind of embodiment of Figure 24:
On the basis of the 19th kind of embodiment, change the connection type of the first shifting element, at this time the first shifting element
The left side meshing part 9 of kind connects case of transmission, and the right side meshing part in the first shifting element is consolidated in the first transmission shaft
On 19, the revolving speed synchronization section in the first shifting element is connected with the gear ring 6 in planetary gear, closure 9 and 10, can be with locking tooth
Circle 6 is closed 10 and 11 entire planetary gears as unitary rotation.The mode and the 19th kind of embodiment that the embodiment is realized are kept
Unanimously.
Embodiment 25:
For the 25th kind of embodiment of Figure 25:
On the basis of the 19th kind of embodiment, change the connection type of the first shifting element, at this time the first shifting element
The left side meshing part 9 of kind connects the gear ring 6 in planetary gear, and the right side meshing part in the first shifting element is consolidated in first
On transmission shaft 19, the revolving speed synchronization section in the first shifting element is connected with case of transmission.The embodiment realize mode and
19th kind of embodiment is consistent.
Embodiment 26:
For the 26th kind of embodiment of Figure 26:
On the basis of the 19th kind of embodiment, increase the 7th gear 25, eighth gear 26 and the 5th transmission shaft 27,
Form the 6th kind of embodiment.The 7th gear 25 is directly connected and the first transmission shaft 19 at this time.Eighth gear 26 is directly connected and the
Five transmission shafts 27.7th gear 25 and eighth gear 26 are in internal messing state.5th transmission shaft 27 is directly and 2 phase of first motor
Even.
The function that the embodiment is realized at this time is consistent with the first embodiment, and details are not described herein, but can effectively mention
The maximum speed of high first motor 2 limits, and realizes higher pure electric vehicle max. speed and the maximum of first motor 2 is effectively reduced
Torque-demand, to reduce the size of first motor 2.
Certainly, this embodiment further includes 19-embodiment of above-described embodiment 25 by identical change, is mixed accordingly
Dynamic power transmission scheme, details are not described herein.
Embodiment 27:
For the 27th kind of embodiment of Figure 27:
On the basis of the 19th kind of embodiment, increase by the 12nd gear 28,28 empty set of the 12nd gear is being started at this time
On machine output shaft, and it is connect with the gear ring of planetary gear kind 6.In addition, the 12nd gear 28 and gear 16 engage.Other connections
It remains unchanged.The mode and the 19th kind of embodiment that the embodiment is realized are consistent.
Certainly, this embodiment further includes 19-embodiment of above-described embodiment 25 by identical change, is mixed accordingly
Dynamic power transmission scheme, details are not described herein.
Embodiment 28:
For the 28th kind of embodiment of Figure 28:
On the basis of the 19th kind of embodiment, increase the tenth gear 29, the 11st gear 30 and the 6th transmission shaft 31,
Engine 1 is connected with the 11st gear 30 at this time, and in the tenth gear 29 and the 11st gear 30 or external toothing (is illustrated as outer nibble
Close), the tenth gear 29 is consolidated on the 6th transmission shaft 31, and connects the gear ring 6 in planetary gear by the 6th transmission shaft 31, single
It is between engine 1 and the 11st gear 30 to clutch or common brake 23, it can be with locking engine.The embodiment
The mode of realization and the 19th kind of embodiment are consistent.
Certainly, this embodiment further includes above-mentioned all embodiments (embodiment 19- embodiment 27) by identical change, is obtained
To corresponding mixed dynamic power transmission scheme, details are not described herein.
For the 29th kind of embodiment of Figure 29:
On the basis of the 28th kind of embodiment, by the position of original one-way clutch or common brake 23 into
Row change, one-way clutch or common brake 23 are on the 6th transmission shaft 31 at this time, are used for locking engine.
For this New Multi-mode hybrid gearbox, described a part for being only the utility model is preferably in fact
Apply example, rather than whole embodiments, therefore, all contents without departing from technical solutions of the utility model, according to the utility model
Technical spirit any simple modifications, equivalents, and modifications to the above embodiments, belong to the utility model technology
The protection scope of scheme.Including the speed ratio relationship benefit using general gear between the second motor 3 and single planetary gear planet carrier 7
It is realized with another planetary gear, the equivalent dual planetary gear of obtained function arranges speed changer scheme, or different real
Apply the efficient combination of example, perhaps by the external toothing formal argument of part of gear at internal messing form or engine 1 it
Increase torsion vibration absorber element afterwards, one-way clutch 23 is perhaps changed to ordinary clutch or changes the arrangement position of gear
It sets, perhaps change the position of gear arrangement or changes the position of shifting element by way of covering axis or will individually fix
In connected gear etc. of the gear as one of axis, but the hybrid gearbox of the consistent equal formation of essence connection.
Claims (8)
1. a kind of single planetary gear hybrid gearbox system characterized by comprising
Single planetary row: it including three rotatable parts, i.e., outer gear ring (6), sun gear (4) and is nibbled respectively with outer gear ring and sun gear
The planetary gear (5) of conjunction is connected with planet carrier (7) on the planetary gear (5)；
Power source: including engine (1), first motor (2) and the second motor (3) respectively with single planetary row transmission connection, institute
The first motor (2) and the second motor (3) stated are equipped with to the power accumulator that charges with electricity consumption, the engine (1),
First motor (2) and output shaft are respectively corresponded with certain fixed speed ratio to be connect with three rotatable parts of single planetary row, described
The second motor (3) under different working modes selectively with certain fixed speed ratio connect with engine (1) turn
The rotatable parts transmission connection that dynamic component or output shaft are connected；
Shift assembly: including shifting element and to the single-phase clutch of locking engine (1) and the transmission of single planetary row
(23) or brake；
Output shaft: it is sequentially connected with single planetary row, which is provided with main reducing gear.
2. a kind of single planetary gear hybrid gearbox system according to claim 1, which is characterized in that described
One motor (2) is connect by one-way clutch (23) or brake with outer gear ring (6), and the planet carrier (7) passes sequentially through the
One gear (8), third gear (16), the second shifting element, second driving shaft (20), second gear (17), the 5th gear (18)
With the 4th transmission shaft (22) transmission connection as output shaft, second motor (3) passes sequentially through third transmission shaft (21)
It is sequentially connected with the 6th gear (13) and second driving shaft (20), the first motor (2) is worn by the first transmission shaft (19)
The center and sun gear (4) for crossing first gear (8) are sequentially connected.
3. a kind of single planetary gear hybrid gearbox system according to claim 2, which is characterized in that described
The revolving speed synchronization section (10) of the first shifting element, meshing part on the left of the first shifting element are connected on one transmission shaft (19)
(9) it is connect with first gear (8), right side meshing part (11) and case of transmission are affixed.
4. a kind of single planetary gear hybrid gearbox system according to claim 2, which is characterized in that described
The revolving speed synchronization section (10) of the first shifting element, meshing part on the left of the first shifting element are connected on one transmission shaft (19)
(9) it is connect with first gear (8).
5. a kind of single planetary gear hybrid gearbox system according to claim 1, which is characterized in that described
One motor (2) is connect by one-way clutch (23) or brake with planet carrier (7), and the outer gear ring (6) passes sequentially through the
Three gears (16), the second shifting element, second driving shaft (20), second gear (17), the 5th gear (18) with as output shaft
The transmission connection of the 4th transmission shaft (22), second motor (3) passes sequentially through third transmission shaft (21) and the 6th gear
(13) it is sequentially connected with second driving shaft (20), the first motor (2) passes through first gear by the first transmission shaft (19)
(8) center and sun gear (4) is sequentially connected.
6. a kind of single planetary gear hybrid gearbox system according to claim 5, which is characterized in that described
The revolving speed synchronization section (10) of the first shifting element, meshing part on the left of the first shifting element are connected on one transmission shaft (19)
(9) it is connect with planet carrier (7), right side meshing part (11) and case of transmission are affixed.
7. a kind of single planetary gear hybrid gearbox system according to claim 5, which is characterized in that described
The revolving speed synchronization section (10) of the first shifting element, meshing part on the left of the first shifting element are connected on one transmission shaft (19)
(9) it is connect with planet carrier (7).
8. according to a kind of described in any item single planetary gear hybrid gearbox systems of claim 2-7, which is characterized in that
The first motor (2) passes sequentially through the 5th transmission shaft (27), eighth gear (26) and the 7th gear (25) and the first transmission
Axis (19) transmission connection, the 7th gear (25) and the first transmission shaft (19) are affixed, the eighth gear (26) and the
Five transmission shafts (27) are affixed, and the 7th gear (25) is connect with eighth gear (26) internal messing.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201821042932.2U CN208559007U (en) | 2018-07-03 | 2018-07-03 | A kind of single planetary gear hybrid gearbox system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201821042932.2U CN208559007U (en) | 2018-07-03 | 2018-07-03 | A kind of single planetary gear hybrid gearbox system |
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| CN208559007U true CN208559007U (en) | 2019-03-01 |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108725177A (en) * | 2018-07-03 | 2018-11-02 | 陈海军 | A kind of single planetary gear hybrid gearbox system |
| CN111516480A (en) * | 2020-02-24 | 2020-08-11 | 绿传(北京)汽车科技股份有限公司 | Two-gear power coupling transmission device, hybrid vehicle and operation method of hybrid vehicle |
| CN112046267A (en) * | 2020-07-27 | 2020-12-08 | 西安交通大学 | Input split-flow type two-gear transmission system for hybrid electric vehicle and vehicle |
| CN113002287A (en) * | 2021-03-01 | 2021-06-22 | 凯博易控车辆科技(苏州)股份有限公司 | Single-planet-row hybrid driving system and control method thereof |
| CN113232501A (en) * | 2021-05-12 | 2021-08-10 | 东风汽车集团股份有限公司 | Hybrid power driving system |
| CN114228473A (en) * | 2021-11-16 | 2022-03-25 | 东风汽车集团股份有限公司 | Hybrid four-gear transmission, hybrid driving system and hybrid vehicle |
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2018
- 2018-07-03 CN CN201821042932.2U patent/CN208559007U/en active Active
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108725177A (en) * | 2018-07-03 | 2018-11-02 | 陈海军 | A kind of single planetary gear hybrid gearbox system |
| CN111516480A (en) * | 2020-02-24 | 2020-08-11 | 绿传(北京)汽车科技股份有限公司 | Two-gear power coupling transmission device, hybrid vehicle and operation method of hybrid vehicle |
| CN112046267A (en) * | 2020-07-27 | 2020-12-08 | 西安交通大学 | Input split-flow type two-gear transmission system for hybrid electric vehicle and vehicle |
| CN112046267B (en) * | 2020-07-27 | 2022-04-01 | 西安交通大学 | Input split-flow type two-gear transmission system for hybrid electric vehicle and vehicle |
| CN113002287A (en) * | 2021-03-01 | 2021-06-22 | 凯博易控车辆科技(苏州)股份有限公司 | Single-planet-row hybrid driving system and control method thereof |
| CN113232501A (en) * | 2021-05-12 | 2021-08-10 | 东风汽车集团股份有限公司 | Hybrid power driving system |
| CN113232501B (en) * | 2021-05-12 | 2022-12-27 | 东风汽车集团股份有限公司 | Hybrid power driving system |
| CN114228473A (en) * | 2021-11-16 | 2022-03-25 | 东风汽车集团股份有限公司 | Hybrid four-gear transmission, hybrid driving system and hybrid vehicle |
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