CN100526684C - Hydraulic type gear wheel speed differientiator, and system and method for compensating output torque - Google Patents
Hydraulic type gear wheel speed differientiator, and system and method for compensating output torque Download PDFInfo
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- CN100526684C CN100526684C CNB2006100211050A CN200610021105A CN100526684C CN 100526684 C CN100526684 C CN 100526684C CN B2006100211050 A CNB2006100211050 A CN B2006100211050A CN 200610021105 A CN200610021105 A CN 200610021105A CN 100526684 C CN100526684 C CN 100526684C
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Abstract
The invention discloses a hydraulic gear differential mechanism, which contains shell, planetary gear, left half axis with gear, right half axis with gear, right and left hydraulic pump. The planetary gear fixed on the shell by its gear axis, which also meshing with left and right half axis. The stators of right and left hydraulic pump which connects with left and right half axis are fixed setting. Using hydraulic mechanism can fully make use of inherent braking pipe of vehicle system, beneficial to favorable to realize the integration of design and arrangement of whole vehicle. Because of stable action of hydraulic mechanism can improve the smooth property and adaptability. The product perform dynamic regulation to braking moment with control size of braking liquid flow by actuator, it has strong controllability.
Description
Technical field
The present invention relates to the compensating gear field.
Background technique
Existing inter-wheel differential is planetary a kind of deformation mechanism, generally speaking, the power of power engine (motor or motor etc.) is all imported via planet carrier, left and right half is connected in planet row's sun wheel shaft and gear ring axle, inherent characteristic according to planet row makes the rotating speed of input and output side that following relation be arranged:
2N
Input=N
A left side+ N
Right
Corresponding torque relation (not considering positive and negative) is:
T
Input: T
A left side: T
Right=2:1:1
When left and right wheel wheel speed is more or less the same, when promptly skidding without any single wheel, vehicle can be realized normal moment of torsion output, realizes the drive condition of expectation; But, in case single wheel skids, the load torque of its corresponding semiaxis descends, directly caused the output capability of opposite side semiaxis to descend, power can not be taken turns end maximization output preferably by road conditions, the driving force of vehicle just greatly reduces, and travelling of corresponding vehicle just produces decline by performance.The gross tractive effort maximum value that produce this moment on wheel can reach: F
Tmax=2F
Φ min+ T
f/ r
r, that is: maximum drawbar pull is 2 times the tractive force F that adheres to trundle
Φ minWith fricative power T in the differential mechanism
f/ r
rThis moment, the power performance of motor was not come out, cause the ability waste, so existing locking differential is to realize the relations of distribution of driving torque by increase by a cover friction mechanism between left and right half, locking between the wheel when realizing wheel left and right side wheel-slip, make the power of motor to take turns end output preferably, increase power character by adhering to situation.But there is following shortcoming in this friction mechanism that utilizes: the controlled locking that 1) can not realize differential mechanism; 2) sensitivity and locking efficient are low; 3) can not carry out dynamic adjustments, controllability is lower; 4) energy loss is big.
Summary of the invention
Technical problem to be solved by this invention is, overcomes the deficiencies in the prior art, and a kind of method that can carry out dynamic adjustments, strong, the adaptable compensating gear of controllability, system and output torque is compensated is provided.
The technical solution adopted for the present invention to solve the technical problems is: this hydraulic type gear wheel differential mechanism comprises differential mechanism shell, planetary pinion, have the left half axle of gear and have the right axle shaft of gear, this planetary pinion is fixed on this differential mechanism shell by its gear shaft, the gear of this left and right half all meshes with this planetary pinion, it is characterized in that: also comprise left and right oil hydraulic pump, the stator of this left and right oil hydraulic pump is for fixedly installing, and the rotor of this left and right oil hydraulic pump is connected with left and right half respectively.
The rotor of described left and right oil hydraulic pump all has the cavity that axially runs through, left and right half pass respectively left and right oil hydraulic pump cavity and with the chamber wall drive fit of cavity.
This hydraulic type gear wheel differential system comprises the differential mechanism shell, planetary pinion, left half axle with gear, right axle shaft with gear, left side oil hydraulic pump, right oil hydraulic pump and final controlling element, this planetary pinion is fixed on the differential mechanism shell by its gear shaft, this left side, the gear of right axle shaft all meshes with this planetary pinion, this left side, the stator of right oil hydraulic pump is for fixedly installing, this left side, the rotor of right oil hydraulic pump respectively with a left side, right axle shaft is connected, the import of this each oil hydraulic pump all is communicated with the brake fluid storage tank, its outlet is respectively by first, second pipeline is connected with wheel drag with oil back chamber, this final controlling element is connected with the output terminal of control unit and to first, the brake fluid flow of second pipeline distributes, and the input end of this control unit is connected with wheel speed sensors.
Described final controlling element is a three-way valve, and three interfaces of this three-way valve are communicated with hydraulic pressure delivery side of pump, oil back chamber and wheel drag respectively.Described oil back chamber is a high pressure accumulator.
This comprises the steps: the method that the output torque of hydraulic type gear wheel differential mechanism compensates
A) the brake fluid storage tank is communicated with the import of left and right oil hydraulic pump, and makes left and right oil hydraulic pump form the second brake fluid road with final controlling element and wheel drag respectively;
B) obtain the rotating speed of wheel and calculate the slip rate of this wheel;
C) control unit judges whether this slip rate is within the slip rate scope of setting, if this slip rate is in outside the slip rate scope of this setting, then control unit makes the second brake fluid liquid road conducting, high hydraulic brake fluid input wheel drag, wheel drag produce braking moment and the output torque of corresponding semiaxis are compensated.
Described step a) also comprises: the brake fluid storage tank is communicated with the import of left and right oil hydraulic pump, and make left and right oil hydraulic pump form the first brake fluid liquid road with final controlling element and oil back chamber respectively, described step c) also comprises: if be at this slip rate within the slip rate scope of setting, the then first brake fluid liquid road conducting, high hydraulic brake fluid input oil back chamber.
Described control unit is adjusted the flow of the high hydraulic brake fluid that is input to oil back chamber and wheel drag in real time by final controlling element according to the wheel slip size.
The invention has the beneficial effects as follows,, can make full use of the intrinsic braking line of Vehicular system, help realizing the integrated of car load design, layout owing to adopted hydraulic mechanism; Because so stable action of hydraulic mechanism is the whole smooth-going performance and the adaptability of this differential mechanism; By the flow size of final controlling element control brake liquid, can carry out dynamic adjustments to braking moment, controllability is strong.
Description of drawings
Fig. 1 is a structural representation of the present invention.
Fig. 2 is a sectional view of the present invention.
Fig. 3 is a brake fluid liquid of the present invention road schematic diagram.
Fig. 4 is a circuit block diagram of the present invention.
Fig. 5 is the FB(flow block) of an execution cycle of the present invention.
Embodiment
See also Fig. 1 to Fig. 5, hydraulic type gear wheel differential mechanism of the present invention is a kind of inter-wheel differential, it comprises planetary pinion 1, have the left half axle 5 of gear 51, have right axle shaft 4, left oil hydraulic pump 6 and the right oil hydraulic pump 3 of gear 41, this planetary pinion 1 is solidly set on the gear shaft 11, this gear shaft 11 is fixed on the differential mechanism shell 8, and this differential mechanism shell 8 is accepted the power that the power engine transmission comes.These left half axle 5 transmission left side wheel are rotated, its gear 51 and this planetary pinion 1 engagement.These right axle shaft 4 transmission right side wheels are rotated, its gear 41 and this planetary pinion 1 engagement.This left side oil hydraulic pump 6 comprises left hydraulic pump stator 60 and left cylinder block of hydraulic pumps 61, this left side hydraulic pump stator 60 fixedly installs (as being fixed on the vehicle body), this left side cylinder block of hydraulic pumps 61 has the cavity 611 that axially runs through, and this left half axle 5 is fixed with one by cooperating of gear spline with these cavity 611 chamber walls.This right side oil hydraulic pump 3 comprises right hydraulic pump stator 30 and right cylinder block of hydraulic pumps 31, this right side hydraulic pump stator 30 fixedly installs (as being fixed on the vehicle body), this right side cylinder block of hydraulic pumps 31 has the cavity 311 that axially runs through, and this right axle shaft 4 is fixed with one by cooperating of gear spline with these cavity 311 chamber walls.When differential mechanism shell 8 received the power input, planet pin 11 and planetary pinion 1 rotated synchronously, and then planetary pinion 1 is delivered to left and right half 5,4 respectively with power.
This left side, right oil hydraulic pump 6,3 import all is connected with brake fluid storage tank 7 by pipeline, its outlet is connected with final controlling element 8 by compensation braking line 11, this final controlling element 8 is a controlled three-way valve, the import of this controlled three-way valve is communicated with the oil hydraulic pump outlet by compensation conduit 11, an one outlet is communicated with oil back chamber 9 by conventional pipeline 13, its another outlet is communicated with wheel drag 10 by braking line 12, thereby can form first, the second brake fluid liquid road, this first brake fluid liquid road is: brake fluid storage tank → oil hydraulic pump → final controlling element → oil back chamber, this second brake fluid liquid road is: brake fluid storage tank → oil hydraulic pump → final controlling element → wheel drag.The high pressure accumulator 9 of this oil back chamber 9 as vehicle-mounted auxiliary system, this vehicle-mounted auxiliary system such as automatic anti-lock braking system (ABS), hydraulic power-assist steering system (HPS) or braking system with hydraulic assisting force (EHB).This wheel drag such as vehicle existing conventional break are as disc brake and hub type brake.This final controlling element is connected with control unit, and this control unit control final controlling element is realized the switching between first, second brake fluid liquid road and led to high pressure accumulator and the flow size of the brake fluid of wheel drag.In the present embodiment, the oil circuit of this brake fluid storage tank, high pressure accumulator and wheel drag all can be communicated with the existing oil circuit of vehicle, thereby can realize recycling.
When the differential of left and right wheel in normal range (NR), be that one-sided wheel is not when having slipping state, the high hydraulic brake fluid that the oil hydraulic pump rotation is produced can add to high pressure accumulator, this moment, the state and the common differential mechanism of this hydraulic type gear wheel differential mechanism were similar, the liquid road of this high hydraulic brake fluid is: brake fluid storage tank → oil hydraulic pump → compensation braking line → conventional pipeline → high pressure accumulator, and then carry out car load and distribute.This car load distribution is meant: since the difference of Vehicle Speed, the braking force of demand size variation constantly on front and rear wheel, and this differential system distributes the braking force of front and rear wheel according to the travelling state of current vehicle.
When one-sided wheel skids, by be serially connected in oil hydraulic pump on the semiaxis rotation, the high hydraulic brake fluid that produces is input to wheel drag by compensation braking line, final controlling element and braking line, thereby wheel is applied a braking moment by this wheel drag.According to the size of wheel-slip degree, adjust the flow size of leading to wheel drag mesohigh brake fluid in the final controlling element by control unit, produce the desired braking force square.When right side wheels is skidded, act on the torque T on the right axle shaft 4
4Be exactly ground provide adhere to moment T
The wheel end, wheel drag moment T
bResisting moment T with 4 generations of 3 pairs of these right axle shafts of right oil hydraulic pump
3Three's sum, that is:
T
4=T
The wheel end+ T
b+ T
3(a)
According to the theory of introducing previously, with reference to this structural element numbering, corresponding formulas is:
2N
8＝N
4+N
5； T
8∶T
4∶T
5＝2∶1∶1
Wherein, T8 is the moment of torsion of differential mechanism shell input, and T5 is the output torque of left half axle, and T4 is the output torque of right axle shaft.According to planet row inherent characteristic, by (a) formula as can be seen: along with right side wheels is skidded, though be transported to the torque T of right side wheels
The wheel endDiminish, but by adjusting the resisting moment T of oil hydraulic pump
3Torque T with wheel drag
bSize can be replenished by the output torque T4 to right axle shaft 4 in limited scope, thus the output torque T of the left half axle 5 that assurance is not skidded
5Still have suitable driving force, the power character to car load can compensate to some extent like this, strengthens the passing ability of vehicle.
Same, if left side wheel is skidded, system also can carry out so compensating movement.
The controlling method of this compensating gear comprises the steps: 1) wheel speed sensors that is positioned at the wheel place detects the tach signal of wheel and calculates the slip rate of wheel; 2) control unit judges whether this slip rate is in outside the slip rate scope of setting, if current slip rate is in outside the slip rate scope of setting, then judge this wheel-slip, control unit control final controlling element makes the second brake fluid liquid road conducting, high hydraulic brake fluid is delivered to wheel drag by final controlling element and braking line, and wheel drag produces braking moment and realizes compensation to the semiaxis output torque; If current slip rate is within the slip rate scope of setting, judge that then vehicle does not skid and is in the cruising state, the first brake fluid liquid road conducting, high hydraulic brake fluid is delivered to high pressure accumulator by final controlling element and conventional pipeline.In the present embodiment, can control the braking moment of wheel drag by the flow of adjusting final controlling element; When wheel-slip, first, second equal conducting in brake fluid liquid road, control the flow size of the brake fluid that flow into high pressure accumulator and wheel drag respectively by final controlling element, when wheel slip is big, the flow of brake fluid that then is assigned to wheel drag is bigger, when wheel slip hour, the flow of brake fluid that is assigned to wheel drag is less, certainly, when skidding, also can only make the second brake fluid liquid road conducting; This wheel speed sensors detects the rotating speed of wheel in real time and calculates slip rate, in case slip rate enters in the value range of permission, thinks that then vehicle is in the cruising state, and the second brake fluid liquid road disconnects, and wheel drag is not worked.
When the needs wheel drag is braked, test data accumulation (being slip rate that draws according to accumulation data and the corresponding relation that flows into the brake fluid flow of wheel drag) according to early stage, final controlling element outputs to braking line according to accumulation data according to initial flow, utilize the variation of the feedback of wheel slip being adjusted this flow then, make the slip rate of wheel be in allowed band.
Under identical semiaxis rotating speed, identical slip rate, the braking force that needs under the different road surfaces to compensate can be different, at this time can adopt variable displacement pump to come the fluctuation of compensation power is compensated, can ensure under the different conditions of adhering to, carry out power compensation and distribute.
Vehicle for the twin shaft driving, also can utilize the hydraulic type gear wheel differential mechanism of said structure, it need become left and right half the power intake of forward and backward axle, thereby realize the differential compensation between the forward and backward axle, for single front axle and rear axle, then can utilize hydraulic type gear wheel differential mechanism of the present invention to carry out left and right differential compensation then.
The present invention can make full use of the intrinsic braking line of Vehicular system owing to adopted hydraulic mechanism, helps realizing the integrated of car load design, layout.In addition, since stable action of hydraulic mechanism, the control technique maturation, and so the whole smooth-going performance of this mechanism is good, corresponding, adaptability also is better than traditional locking differential.
Above content be in conjunction with concrete preferred implementation to further describing that the present invention did, can not assert that concrete enforcement of the present invention is confined to these explanations.For the general technical staff of the technical field of the invention, without departing from the inventive concept of the premise, can also make some simple deduction or replace, all should be considered as belonging to the scope of patent protection that the present invention is determined by claims of being submitted to.
Claims (8)
1. hydraulic type gear wheel differential mechanism, comprise differential mechanism shell, planetary pinion, have the left half axle of gear and have the right axle shaft of gear, this planetary pinion is fixed on this differential mechanism shell by its gear shaft, the gear of this left and right half all meshes with this planetary pinion, it is characterized in that: also comprise left and right oil hydraulic pump, the stator of this left and right oil hydraulic pump is for fixedly installing, and the rotor of this left and right oil hydraulic pump is connected with left and right half respectively.
2. according to the described hydraulic type gear wheel differential mechanism of claim 1, it is characterized in that: the rotor of described left and right oil hydraulic pump all has the cavity that axially runs through, left and right half pass respectively left and right oil hydraulic pump cavity and with the chamber wall drive fit of cavity.
3. hydraulic type gear wheel differential system, comprise the differential mechanism shell, planetary pinion, have the left half axle of gear and have the right axle shaft of gear, this planetary pinion is fixed on the differential mechanism shell by its gear shaft, this left side, the gear of right axle shaft all meshes with this planetary pinion, it is characterized in that: also comprise a left side, right oil hydraulic pump and final controlling element, this left side, the stator of right oil hydraulic pump is for fixedly installing, this left side, the rotor of right oil hydraulic pump respectively with a left side, right axle shaft is connected, the import of this each oil hydraulic pump all is communicated with the brake fluid storage tank, its outlet is respectively by first, second pipeline is connected with wheel drag with oil back chamber, this final controlling element is connected with the output terminal of control unit and to first, the brake fluid flow of second pipeline distributes, and the input end of this control unit is connected with wheel speed sensors.
4. according to the described hydraulic type gear wheel differential system of claim 3, it is characterized in that: described final controlling element is a three-way valve, and three interfaces of this three-way valve are communicated with hydraulic pressure delivery side of pump, oil back chamber and wheel drag respectively.
5. according to the described hydraulic type gear wheel differential system of claim 4, it is characterized in that: described oil back chamber is a high pressure accumulator.
6. the method that the output torque of hydraulic type gear wheel differential mechanism is compensated is characterized in that: comprise the steps:
A) the brake fluid storage tank is communicated with the import of left and right oil hydraulic pump, and makes left and right oil hydraulic pump form the second brake fluid liquid road with final controlling element and wheel drag respectively;
B) obtain the rotating speed of wheel and calculate the slip rate of this wheel;
C) control unit judges whether this slip rate is within the slip rate scope of setting, if this slip rate is in outside the slip rate scope of this setting, then control unit makes the second brake fluid liquid road conducting, high hydraulic brake fluid input wheel drag, wheel drag produce braking moment and the output torque of corresponding semiaxis are compensated.
7. according to the described a kind of method that the output torque of compensating gear is compensated of claim 6, it is characterized in that: described step a) also comprises: the brake fluid storage tank is communicated with the import of left and right oil hydraulic pump, and make left and right oil hydraulic pump form the first brake fluid liquid road with final controlling element and oil back chamber respectively, described step c) also comprises: if be at this slip rate within the slip rate scope of setting, the then first brake fluid liquid road conducting, high hydraulic brake fluid input oil back chamber.
8. according to the described a kind of method that the output torque of compensating gear is compensated of claim 7, it is characterized in that: described control unit is adjusted the flow of the high hydraulic brake fluid that is input to oil back chamber and wheel drag in real time by final controlling element according to the wheel slip size.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100211050A CN100526684C (en) | 2006-05-31 | 2006-05-31 | Hydraulic type gear wheel speed differientiator, and system and method for compensating output torque |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006100211050A CN100526684C (en) | 2006-05-31 | 2006-05-31 | Hydraulic type gear wheel speed differientiator, and system and method for compensating output torque |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101082371A CN101082371A (en) | 2007-12-05 |
| CN100526684C true CN100526684C (en) | 2009-08-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100211050A Expired - Fee Related CN100526684C (en) | 2006-05-31 | 2006-05-31 | Hydraulic type gear wheel speed differientiator, and system and method for compensating output torque |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111022605A (en) * | 2019-12-24 | 2020-04-17 | 杨勇 | Controllable slip mechanical clutch |
| CN112963516A (en) * | 2021-02-25 | 2021-06-15 | 华域麦格纳电驱动系统有限公司 | Integrated differential assembly |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2039369U (en) * | 1988-08-24 | 1989-06-14 | 魏景丰 | Hydraulically-controlled differential planet gear |
| US5176589A (en) * | 1986-05-29 | 1993-01-05 | Slim Borgudd | Differential gear |
| CN1284607A (en) * | 2000-09-11 | 2001-02-21 | 孙会英 | Hydraulic double-blade pump and its motor |
| CN2456949Y (en) * | 2001-01-12 | 2001-10-31 | 韶关宏大齿轮有限公司 | Lock stop differential mechanism |
-
2006
- 2006-05-31 CN CNB2006100211050A patent/CN100526684C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5176589A (en) * | 1986-05-29 | 1993-01-05 | Slim Borgudd | Differential gear |
| CN2039369U (en) * | 1988-08-24 | 1989-06-14 | 魏景丰 | Hydraulically-controlled differential planet gear |
| CN1284607A (en) * | 2000-09-11 | 2001-02-21 | 孙会英 | Hydraulic double-blade pump and its motor |
| CN2456949Y (en) * | 2001-01-12 | 2001-10-31 | 韶关宏大齿轮有限公司 | Lock stop differential mechanism |
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|---|---|
| CN101082371A (en) | 2007-12-05 |
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