CN104089000A - Slip difference equivalent method and system for hydraulic automatic transmission - Google Patents
Slip difference equivalent method and system for hydraulic automatic transmission Download PDFInfo
- Publication number
- CN104089000A CN104089000A CN201410309307.XA CN201410309307A CN104089000A CN 104089000 A CN104089000 A CN 104089000A CN 201410309307 A CN201410309307 A CN 201410309307A CN 104089000 A CN104089000 A CN 104089000A
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- China
- Prior art keywords
- planet
- equivalent
- rotating speed
- slippage
- inertia
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H61/0437—Smoothing ratio shift by using electrical signals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/04—Smoothing ratio shift
- F16H2061/0462—Smoothing ratio shift by controlling slip rate during gear shift transition
Abstract
The invention provides a slip difference equivalent method and system for a hydraulic automatic transmission. According to the equivalent method and system, firstly engine equivalent rotation inertia and input shaft equivalent rotation inertia are obtained, then according to an obtained clutch slip difference conversion coefficient, the engine equivalent rotation inertia and the input shaft equivalent rotation inertia, clutch slip difference is finally equivalent to an input shaft of an automobile, so that the hydraulic automatic transmission can conduct smooth gear shift through equivalent slip difference.
Description
Technical field
The application relates to automobile technical field, more particularly, relates to a kind of slippage equivalent method and system of hydraulic automatic speed variator.
Background technique
The essential advantage of hydraulic automatic speed variator is that it makes the shift process of vehicle more smooth-going, even allows the shift process of the imperceptible vehicle of occupant.Level and smooth shift process is due to the good control to hydraulic automatic speed variator clutch to a great extent, clutch is for connecting or two of separated hydraulic automatic speed variators planet row rotating component independently, to realize two switchings between different drive ratios, it is shift process, therefore, the shift process of hydraulic automatic speed variator is the process of cut-off clutch and engaging clutch co-ordination.If it is too fast that engaging clutch engages, can cause a plurality of clutch transmission torques and cause that automatic transmission crosses constraint and impact; And cut-off clutch separation is too fast, can cause automatic transmission transmission of power to be interrupted.
Gearshift work by slip control hydraulic automatic speed variator can effectively improve shift quality.And how by clutch slip equivalence, to input shaft, to be the basis of realizing slip control.
Summary of the invention
In view of this, the application provides a kind of slippage equivalent method and system of hydraulic automatic speed variator, for the clutch slip equivalence of hydraulic automatic speed variator is arrived to input shaft, so that hydraulic automatic speed variator can smoothly be shifted gears with equivalent slippage.
To achieve these goals, the existing scheme proposing is as follows:
A slippage equivalent method for hydraulic automatic speed variator, comprises the steps:
Obtain motor equivalent moment of inertia and input shaft equivalent moment of inertia;
Calculate the clutch slip conversion coefficient of hydraulic automatic speed variator;
According to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalent moment of inertia, the input shaft by clutch slip equivalence to automobile.
Preferably, the slippage conversion coefficient of the clutch of described calculating hydraulic automatic speed variator, comprising:
According to the drive connection of constant mesh gear, determine the single planetary row speed diagram of single planet row;
Many planet rows speed diagram while determining a plurality of planet row cooperating according to described single planetary row calculating chart;
Rotating speed point while determining not skidding on each longitudinal axis of described many planet rows calculating chart, the point using it as fixed rotating speed; Rotating speed point while determining skidding on each longitudinal axis of described many planet rows speed diagram, using it as slip rotating speed point;
According to described fixed rotating speed point and described slip rotating speed point, calculate described clutch slip conversion coefficient.
Preferably, described planet row comprises sun gear, planet wheel and wheel rim.
Preferably, described a plurality of planet row is two planet rows.
Preferably, described hydraulic automatic speed variator comprises eight gears.
A slippage equivalent system for hydraulic automatic speed variator, comprising:
Acquisition module, is configured to for obtaining motor equivalent moment of inertia and input shaft equivalent moment of inertia;
The first computing module, is configured to for calculating the clutch slip conversion coefficient of hydraulic automatic speed variator;
The second computing module, is configured to, for according to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalent moment of inertia, clutch slip equivalence be arrived to the input shaft of automobile.
Preferably, described the first computing module comprises:
The first computing unit, is configured to for determine the single planetary row speed diagram of single planet row according to the drive connection of constant mesh gear;
The second computing unit, is configured to the many planet rows speed diagram when determining a plurality of planet row cooperating according to described single planetary row calculating chart;
The 3rd computing unit, is configured to the rotating speed point when determining not skidding on each longitudinal axis of described many planet rows speed diagram, the point using it as fixed rotating speed; Rotating speed point while determining skidding on each longitudinal axis of described many planet rows calculating chart, using it as slip rotating speed point;
The 4th computing unit, is configured to, for according to described fixed rotating speed point and described slip rotating speed point, calculate described clutch slip conversion coefficient.
Preferably, described planet row comprises sun gear, planet wheel and wheel rim.
Preferably, described a plurality of planet row is two planet rows.
Preferably, described hydraulic automatic speed variator comprises eight gears.
From technique scheme, can find out, the application provides a kind of slippage equivalent method and system of hydraulic automatic speed variator, first this equivalent method and system obtain motor equivalent moment of inertia and input shaft equivalent moment of inertia, then according to the clutch slip conversion coefficient, motor equivalent moment of inertia and the input shaft equivalent moment of inertia that calculate, final realization arrived the input shaft of automobile by clutch slip equivalence, thereby can make hydraulic automatic speed variator carry out smooth-going gearshift with equivalent slippage.
Accompanying drawing explanation
In order to be illustrated more clearly in the embodiment of the present application or technological scheme of the prior art, to the accompanying drawing of required use in embodiment or description of the Prior Art be briefly described below, apparently, accompanying drawing in the following describes is only some embodiments of the application, for those of ordinary skills, do not paying under the prerequisite of creative work, can also obtain according to these accompanying drawings other accompanying drawing.
The flow chart of the slippage equivalent method of a kind of hydraulic automatic speed variator that Fig. 1 provides for the embodiment of the present application;
A kind of car load power transmission system schematic diagram that Fig. 2 provides for the embodiment of the present application;
A kind of constant mesh gear that Fig. 3 provides for the embodiment of the present application and the speed diagram of common planet row;
Fig. 4 is that eight grades of hydraulic automatic speed variators are at the planet arrangement mechanism sketch of 1 gear;
Fig. 5 is the planet row speed diagram of eight grades of hydraulic automatic speed variator planet arrangement mechanisms;
Fig. 6 is the planet row speed diagram of eight grades of hydraulic automatic speed variator planet arrangement mechanisms;
The structural drawing of the slippage equivalent system of a kind of hydraulic automatic speed variator that Fig. 7 provides for another embodiment of the application.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present application, the technological scheme in the embodiment of the present application is clearly and completely described, obviously, described embodiment is only the application's part embodiment, rather than whole embodiments.Embodiment based in the application, those of ordinary skills are not making the every other embodiment who obtains under creative work prerequisite, all belong to the scope of the application's protection.
Embodiment one
The flow chart of the slippage equivalent method of a kind of hydraulic automatic speed variator that Fig. 1 provides for the embodiment of the present application.
The slippage equivalent method of the hydraulic automatic speed variator that as shown in Figure 1, the present embodiment provides comprises the steps:
S101: obtain motor equivalent moment of inertia and input shaft equivalent moment of inertia.
S102: the clutch slip conversion coefficient that calculates hydraulic automatic speed variator.
The conversion coefficient that is equivalent to basic clutch position equivalence migration with slippage and torque can calculate according to planet row speed diagram method.
S103: the input shaft by clutch slip equivalence to automobile.
According to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalent moment of inertia, the input shaft by clutch slip equivalence to automobile.
As shown in Figure 2, through the equivalent conversion of clutch position, the Clutch Control of hydraulic automatic speed variator can be converted to the problem that double clutch is controlled.I in Fig. 2
e, I
vbe respectively the equivalent moment of inertia of motor and car load load, C
l, C
hbe respectively in shift process the clutch engaging at low gear and high gear, i
l, i
hbe respectively the velocity ratio of low gear and high gear in shift process, λ
cL, λ
cHbe respectively C
l, C
hslippage conversion coefficient by original position equivalence to input shaft position.
From technique scheme, can find out, the present embodiment provides a kind of slippage equivalent method of hydraulic automatic speed variator, first this equivalent method obtains motor equivalent moment of inertia and input shaft equivalent moment of inertia, then according to the clutch slip conversion coefficient, motor equivalent moment of inertia and the input shaft equivalent moment of inertia that calculate, final realization arrived the input shaft of automobile by clutch slip equivalence, thereby can make hydraulic automatic speed variator carry out smooth-going gearshift with equivalent slippage.
The detailed process according to planet row speed diagram method calculating clutch slip conversion coefficient in the present embodiment is as follows:
First according to the drive connection of constant mesh gear, determine the single planetary row speed diagram of single planet row.
Each constant mesh gear is comprised of two primary elements: driving gear and driven gear.Each planet row is comprised of three primary elements: sun gear, planet carrier and gear ring.The gear ratio of definition gear ring and sun gear is final ratio, defines the internal tooth number of teeth for negative simultaneously, and the external tooth number of teeth just.
For constant mesh gear, defining its final ratio is the opposite number of the gear ratio of Partner gear and drive end gear:
In formula:
Z
1, z
2---the number of teeth of driven gear and driving gear
For simple planet row structure, define the gear ratio that its final ratio is gear ring and sun gear:
In formula:
Z
r, z
s---the number of teeth of gear ring and sun gear
As shown in Fig. 3 (a), for its speed diagram of constant mesh gear, comprise that two represent that respectively the longitudinal axis (Gear1 and Gear2) of main quilt moved end gear rotational speed and the longitudinal axis that remains 0 rotating speed form.Stipulate that the distance between 0 axle and Gear2 axle is 1 reference units, the distance between 0 axle and Gear1 axle is i
0individual reference units; By straight line that on 0 axle, 0rpm is ordered and the intersection point rotating speed of Gear1 axle and Gear2 axle, all meet the velocity ratio relation between Gear1 and Gear2 arbitrarily like this, equally after determining the rotating speed of Gear1, take that this puts as starting point the 0rpm point by 0 axle are to Gear2 axle line, the intersection point of itself and Gear2 axle must be the rotating speed of Gear2.
In like manner, as shown in Fig. 3 (b), for its tachometer nomogram of the simple planet row structure in figure, comprise the longitudinal axis that represents respectively sun gear (Sun Gear), planet carrier (Carrier) and gear ring (Ring Gear).Distance between regulation planet carrier and the gear ring longitudinal axis is 1 reference units, and the distance between sun gear and planet carrier is i
0individual reference units; Three intersection point rotating speeds of any like this straight line by these three longitudinal axis and its formation all meet the velocity ratio relation of planet row, same after the rotating speed point of known any two longitudinal axis, connect these two known rotating speed points and extend to the 3rd longitudinal axis, the intersection point of extension must be the rotating speed of the 3rd rotating element.
Secondly, single file star speed diagram is converted to the inner constant mesh gear of 8 grades of hydraulic automatic speed variators and planet row speed diagram.
For the automatic transmission that comprises two or more planet rows, because the joint of clutch can be by the axle that is connected to of two independent rotation part rigidity of different planet rows.Therefore the speed diagram relation forming separately except each planet row, also can link together to share the mode of the longitudinal axis by the joint of clutch between two planet rows.Fig. 4 be eight gear hydraulic automatic speed variators at the planet arrangement mechanism sketch of 1 gear, 1 when gear clutch B1, C1, tri-clutches of C4 engage.Fig. 5 is the planet row speed diagrams of eight speed automatic transmissions when 1 gear, and the longitudinal axis represents the rotating speed size of each rotating component, and each planet arrangement mechanism or ordinary gear vice mechanism are in independent plane.The engagement of clutch or be rigidly connected makes by sharing the mode of the longitudinal axis, to intersect between different mechanism's planes.R1, P1, S1 represent respectively gear ring, planet carrier and the sun gear of planet row SP1, and R3, P3, S3 represent respectively gear ring, planet carrier and the sun gear of planet row SP3, and G5, G8, G6 and G10 represent respectively gear 5,8,6 and 10, i
01, i
03, i
g5_8, i
g6_10be respectively the velocity ratio of planet row SP1, planet row SP3, gear pair G5/G8, gear pair G6/G10.
Finally according to a plurality of planet row speed diagrams, calculate eight grades of hydraulic automatic speed variator clutch equivalence slip ratios.
For the automatic transmission structure compressing completely in the state respective clutch of not shifting gears, in its planetary structure speed diagram, on all longitudinal axis, there is and only has a rotating speed point.But for clutch, due to malcompression, skid and produce the situation of slippage, will inevitably cause on the corresponding longitudinal axis, occurring two rotating speed points in speed diagram.
C4 skids and occurs two rotating speed point n by causing on the shared axle of S1 and G6 as shown in Figure 6
s1and n '
s1, the difference between these two rotating speed points is the slippage n ' of C4 drive end and Partner
s.And take respectively these two rotating speed points as starting point according to the rule of planet row speed diagram to other speed shaft line, and the difference of two rotating speed intersection points that finally form on automatic transmission input shaft is the equivalent slippage n of clutch C4
s.N ' shown in Fig. 6
sfor the slippage of clutch C4, n
sslippage for input shaft position equivalence clutch.According to similar triangle theory, the slippery difference n ' of any one clutch
sall can be multiplied by the slippage n that corresponding scaling factor λ is equivalent to input shaft position equivalence clutch
s:
n'
s＝λ·n
s
n′
s＝n
p-n
N
n
s＝n
E-n
o2i
g
In formula: λ---the slippage equivalent coefficient of clutch;
N
p---clutch drive end rotating speed;
N
n---clutch Partner rotating speed;
N
e---engine speed;
N
o---output shaft rotating speed;
I
g---the velocity ratio of current shift.
From Fig. 6, can calculate the slippage conversion coefficient λ when slippage of clutch C4 is transformed into equivalent clutch slip during 1 gear
c4:
Same method can obtain the slippage conversion coefficient of all clutches under all gears.
Embodiment two
Fig. 7 provides a kind of structural drawing of slippage equivalent system of hydraulic automatic speed variator for another embodiment of the application.
The slippage equivalent system of the hydraulic automatic speed variator that as shown in Figure 7, the present embodiment provides comprises that acquisition module 10, the first computing module 20 and the second computing module 30, the first computing modules 20 are connected with acquisition module 10, the second computing module 30 respectively.
Acquisition module 10 is for obtaining motor equivalent moment of inertia and input shaft equivalence conversion inertia;
The first computing module 20 is for calculating the clutch slip conversion coefficient of hydraulic automatic speed variator;
The second computing module 30, for according to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalence conversion inertia, arrives clutch slip equivalence the input shaft of automobile.
Wherein the first computing module 20 comprises the first computing unit 21, the second computing unit 22, the 3rd computing unit 23 and the 4th computing unit 24.
The first computing unit 21 is for determining the single planetary row calculating chart of single planet row according to the drive connection of constant mesh gear; The many planet row calculating chart of the second computing unit 22 when determining a plurality of planet row cooperating according to described single planetary row calculating chart; The rotating speed point of the 3rd computing unit 23 when determining not skidding on each longitudinal axis of described many planet rows calculating chart, the point using it as fixed rotating speed; Rotating speed point while determining skidding on each longitudinal axis of described many planet rows calculating chart, using it as slip rotating speed point; The 4th computing unit 24, for according to described fixed rotating speed point and described slip rotating speed point, calculates described clutch slip conversion coefficient.
Planet row comprises sun gear, planet wheel and wheel rim.Planet row is generally two planet rows.Hydraulic automatic speed variator in the present embodiment comprises eight gears.
Finally, also it should be noted that, in this article, relational terms such as the first and second grades is only used for an entity or operation to separate with another entity or control panel, and not necessarily requires or imply and between these entities or operation, have the relation of any this reality or sequentially.And, term " comprises ", " comprising " or its any other variant are intended to contain comprising of nonexcludability, thereby the process, method, article or the equipment that make to comprise a series of key elements not only comprise those key elements, but also comprise other key elements of clearly not listing, or be also included as the intrinsic key element of this process, method, article or equipment.The in the situation that of more restrictions not, the key element being limited by statement " comprising ... ", and be not precluded within process, method, article or the equipment that comprises described key element and also have other identical element.
In this specification, each embodiment adopts the mode of going forward one by one to describe, and each embodiment stresses is the difference with other embodiments, between each embodiment identical similar part mutually referring to.
Above-mentioned explanation to the disclosed embodiments, makes professional and technical personnel in the field can realize or use the application.To these embodiments' multiple modification, will be apparent for those skilled in the art, General Principle as defined herein can be in the situation that do not depart from the application's spirit or scope, realization in other embodiments.Therefore, the application will can not be restricted to these embodiments shown in this article, but will meet the widest scope consistent with principle disclosed herein and features of novelty.
Claims (10)
1. a slippage equivalent method for hydraulic automatic speed variator, is characterized in that, comprises the steps:
Obtain motor equivalent moment of inertia and input shaft equivalent moment of inertia;
Calculate the clutch slip conversion coefficient of hydraulic automatic speed variator;
According to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalent moment of inertia, the input shaft by clutch slip equivalence to automobile.
2. slippage equivalent method as claimed in claim 1, is characterized in that, the slippage conversion coefficient of the clutch of described calculating hydraulic automatic speed variator, comprising:
According to the drive connection of constant mesh gear, determine the single planetary row speed diagram of single planet row;
Many planet rows speed diagram while determining a plurality of planet row cooperating according to described single planetary row calculating chart;
Rotating speed point while determining not skidding on each longitudinal axis of described many planet rows calculating chart, the point using it as fixed rotating speed; Rotating speed point while determining skidding on each longitudinal axis of described many planet rows speed diagram, using it as slip rotating speed point;
According to described fixed rotating speed point and described slip rotating speed point, calculate described clutch slip conversion coefficient.
3. slippage equivalent method as claimed in claim 2, is characterized in that, described planet row comprises sun gear, planet wheel and wheel rim.
4. slippage equivalent method as claimed in claim 2, is characterized in that, described a plurality of planet rows are two planet rows.
5. slippage equivalent method as claimed in claim 2, is characterized in that, described hydraulic automatic speed variator comprises eight gears.
6. a slippage equivalent system for hydraulic automatic speed variator, is characterized in that, comprising:
Acquisition module, is configured to for obtaining motor equivalent moment of inertia and input shaft equivalent moment of inertia;
The first computing module, is configured to for calculating the clutch slip conversion coefficient of hydraulic automatic speed variator;
The second computing module, is configured to, for according to described clutch slip conversion coefficient, described motor equivalent moment of inertia and input shaft equivalence conversion inertia, clutch slip equivalence be arrived to the input shaft of automobile.
7. slippage equivalent system as claimed in claim 6, is characterized in that, described the first computing module comprises:
The first computing unit, is configured to for determine the single planetary row speed diagram of single planet row according to the drive connection of constant mesh gear;
The second computing unit, is configured to the many planet rows speed diagram when determining a plurality of planet row cooperating according to described single planetary row calculating chart;
The 3rd computing unit, is configured to the rotating speed point when determining not skidding on each longitudinal axis of described many planet rows speed diagram, the point using it as fixed rotating speed; Rotating speed point while determining skidding on each longitudinal axis of described many planet rows calculating chart, using it as slip rotating speed point;
The 4th computing unit, is configured to, for according to described fixed rotating speed point and described slip rotating speed point, calculate described clutch slip conversion coefficient.
8. slippage equivalent system as claimed in claim 7, is characterized in that, described planet row comprises sun gear, planet wheel and wheel rim.
9. slippage equivalent system as claimed in claim 7, is characterized in that, described a plurality of planet rows are two planet rows.
10. slippage equivalent system as claimed in claim 7, is characterized in that, described hydraulic automatic speed variator comprises eight gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410309307.XA CN104089000A (en) | 2014-07-01 | 2014-07-01 | Slip difference equivalent method and system for hydraulic automatic transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410309307.XA CN104089000A (en) | 2014-07-01 | 2014-07-01 | Slip difference equivalent method and system for hydraulic automatic transmission |
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| CN104089000A true CN104089000A (en) | 2014-10-08 |
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| CN201410309307.XA Pending CN104089000A (en) | 2014-07-01 | 2014-07-01 | Slip difference equivalent method and system for hydraulic automatic transmission |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106438760A (en) * | 2016-10-08 | 2017-02-22 | 盛瑞传动股份有限公司 | Method for controlling lockup clutch of hydraulic torque converter under sudden accelerator stepping-on condition |
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Cited By (2)
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| CN106438760A (en) * | 2016-10-08 | 2017-02-22 | 盛瑞传动股份有限公司 | Method for controlling lockup clutch of hydraulic torque converter under sudden accelerator stepping-on condition |
| CN106438760B (en) * | 2016-10-08 | 2019-03-29 | 盛瑞传动股份有限公司 | A kind of converter lockout clutch control method under urgency open out operating condition |
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