CN101566200B - Pneumatic and hydraulic liquid power retarder controller - Google Patents
Pneumatic and hydraulic liquid power retarder controller Download PDFInfo
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- CN101566200B CN101566200B CN2009100433492A CN200910043349A CN101566200B CN 101566200 B CN101566200 B CN 101566200B CN 2009100433492 A CN2009100433492 A CN 2009100433492A CN 200910043349 A CN200910043349 A CN 200910043349A CN 101566200 B CN101566200 B CN 101566200B
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- way valve
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- retarder
- electromagnetic switch
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Abstract
The invention discloses a pneumatic and hydraulic liquid power retarder controller, comprising a pneumatic-hydraulic convertor consisting of a converter pneumatic cylinder, a converter pneumatic piston and a converter hydraulic piston, wherein a left air cavity of the pneumatic-hydraulic convertor is connected with a left electromagnetic switching valve, an inlet of which is connected with an airsource; a right air cavity of the pneumatic-hydraulic convertor is connected with a right electromagnetic switching valve, an inlet of which is connected with an air source, and an ECU is connected between the working position of the left electromagnetic switching valve and the working position of the right electromagnetic switching valve; a left oil cavity of the pneumatic-hydraulic convertor isconnected with a transmission oil pool through a left oil pool one-way valve and connected with a working oil pool of a hydraulic retarder through a right retarder one-way valve; a right oil cavity ofthe pneumatic-hydraulic convertor is connected with the converter oil pool through a right oil pool one-way valve; a bypass one-way valve is connected between the front end of the right oil pool one-way valve and the rear end of the right retarder one-way valve; and a hydraulic retarder driving gear is arranged on the pump wheel shaft of the hydraulic retarder, a turbine of the hydraulic retarderis fixed on the housing and an oil outlet thereof is connected with a heat exchanger. The invention has the beneficial effects as follows: 1. the existing air sources of the vehicles can accomplish the transportation of medium to save the special intermediate and high pressure hydraulic pumps; 2. the electromagnetic switching valves are used instead of the conventional electro-hydraulic proportional valves to assist the achievement of automatic control of computer; and 3. simple structure and low cost are provided.
Description
Technical field
The present invention relates to a kind of automobile-used hydrodynamic retarder control gear, especially have only source of the gas and do not have the hydrodynamic retarder control gear of hydraulic power automobile.
Background technique
During the vehicle descending, often need to use Service Brake continuously or frequently, cause brake drum and braking plate heavy wear, even cause brake drum be full of cracks, braking plate scaling loss, the working life of not only having reduced Service Brake because of heating, increase operating cost, also threatened traffic safety when serious.Retarder being installed can being made the steady deceleration of the bigger vehicle of quality and not consume braking system, is the effective way that addresses the above problem, and especially medium-and-large-sized vehicle substantially all is equipped with this complemental brake system.At present, Chang Yong retarder can be divided into two kinds on structural type: electromagnetic retarder and hydrodynamic retarder.Wherein hydrodynamic retarder is to increase a hydraulic couplers in speed changer case shell rear end, and Coupler is made up of pump impeller and turbine, and wherein pump impeller rotates synchronously by gear and transmission output shaft, and turbine then is installed on the speed changer case shell, can not arbitrarily rotate.When not needing to brake, ECU sends instruction, stops working medium (hydraulic oil) to enter the active chamber of hydrodynamic retarder, and therefore aneroid mechanical resistance Buddhist nun between pump impeller and the turbine does not have retarding torque yet; When needs are braked, ECU sends instruction, the working medium of some and pressure is pressed into the active chamber of hydrodynamic retarder, there is hydraulic damping between pump impeller and the turbine, the kinetic energy of automobile is transformed into heat energy in hydrodynamic retarder, with heat energy dissipation, pump impeller is bad student's opposing torque under the effect of hydraulic damping, thereby plays the braking purpose by special-purpose heat exchanger for heated hydraulic oil.Hydraulic speed buffer structure compactness, braking moment are big, have significant advantage with respect to electromagnetic retarder, begin extensive use on high-grade commercial car.The braking effect of hydrodynamic retarder depends on the pressure and the quantity of working medium in the active chamber, obviously need control gear, at present, the control gear of known hydrodynamic retarder working medium, all be to adopt intermediate and high pressure hydraulic pumps to finish medium transport, infeed the pressure and the quantity of active chamber by electric-hydraulic proportion valve regulation working medium.For some the vehicle of intermediate and high pressure hydraulic pumps is arranged, make full use of resource, has original advantage, yet do not have intermediate and high pressure hydraulic pumps for some but the vehicle of mesohigh source of the gas is arranged, must install an intermediate and high pressure hydraulic pumps additional, not only increased cost, and because spatial constraints is not easy layout.
Summary of the invention
When hydrodynamic retarder being installed, must install the problem of intermediate and high pressure hydraulic pumps additional, the invention provides a kind of Pneumatic and hydraulic liquid power retarder controller in order to solve the vehicle that has only source of the gas.
The objective of the invention is to realize in the following way: a kind of Pneumatic and hydraulic liquid power retarder controller, comprise an air pressure-liquid pressure transducer, described air pressure-liquid pressure transducer is made up of three parts: transducer pneumatic linear actuator, transducer pneumatic piston and transducer hydraulic piston, this air pressure-liquid pressure transducer left side air cavity links to each other with left electromagnetic switch valve, and left electromagnetic switch valve import connects source of the gas; The right air cavity of air pressure-liquid pressure transducer links to each other with right electromagnetic switch valve, right electromagnetic switch valve import connection source of the gas, the working position of left electromagnetic switch valve and with the working position of right electromagnetic switch valve between be connected ECU; Air pressure-liquid pressure transducer left side oil pocket links to each other with the speed changer oil sump by left oil sump one-way valve, links to each other by right retarder one-way valve hydrodynamic retarder working oil chamber; The right oil pocket of air pressure-liquid pressure transducer links to each other with the speed changer oil sump by right oil sump one-way valve, connection one bypass one-way valve between the rear end of the front end of right oil sump one-way valve and right retarder one-way valve; The hydrodynamic retarder actuation gear is arranged on the Pump wheel shaft of hydrodynamic retarder, and the turbine of hydrodynamic retarder is fixed on the shell, and the hydrodynamic retarder oil outlet connects heat exchanger.
Left side electromagnetic switch valve, right electromagnetic switch valve, air pressure-liquid pressure transducer and left oil sump one-way valve, right oil sump one-way valve, retarder one-way valve, the serial of bypass one-way valve are provided with, and are hydraulic pipe line therebetween.
The present invention utilizes the air pressure-hydraulic pressure conversion equipment of a special use, infeed the working medium of determining pressure and quantity to the hydrodynamic retarder active chamber, this air pressure-hydraulic pressure conversion equipment is made up of two electromagnetic switch valves and a reciprocating movement oil cylinder, can work automatically by electronic control.The invention has the beneficial effects as follows: 1, can directly utilize the existing source of the gas of vehicle to finish medium transport, save special-purpose intermediate and high pressure hydraulic pumps; 2, utilize electromagnetic switch valve rather than traditional electro-hydraulic proportional valve, more help realizing computer controlled automatic; 3, simple in structure, with low cost.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is the present invention and speed changer annexation figure;
Among the figure, 1. transmission output shaft, 2. output shaft gear, 3. coupling, 4. transmission shaft, 5. hydrodynamic retarder actuation gear, 6. hydrodynamic retarder shell, 7. hydrodynamic retarder pump impeller, 8. hydrodynamic retarder turbine, 9. heat exchanger, 10. retarder one-way valve, 11. the bypass one-way valve, 12. right oil sump one-way valves, 13. left oil sump one-way valves, 14. the transducer hydraulic piston, 15. transducer pneumatic pistons, 16. transducer pneumatic linear actuators, 17. right electromagnetic switch valve, 18. left electromagnetic switch valves, 19. hydrodynamic retarders.
Embodiment
As shown in Figure 1, a kind of Pneumatic and hydraulic liquid power retarder controller, comprise an air pressure-liquid pressure transducer, described air pressure-liquid pressure transducer is made up of three parts: transducer pneumatic linear actuator 16, transducer pneumatic piston 15 and transducer hydraulic piston 14, this air pressure-liquid pressure transducer left side air cavity links to each other with left electromagnetic switch valve 18, and left electromagnetic switch valve 18 imports connect source of the gas; The right air cavity of air pressure-liquid pressure transducer links to each other with right electromagnetic switch valve 17, right electromagnetic switch valve 17 imports connection source of the gas, the working position of left electromagnetic switch valve 18 and with the working position of right electromagnetic switch valve 17 between be connected ECU; Air pressure-liquid pressure transducer left side oil pocket links to each other with the speed changer oil sump by left oil sump one-way valve 13, links to each other with hydrodynamic retarder 19 working oil chambers by right retarder one-way valve 10; The right oil pocket of air pressure-liquid pressure transducer links to each other with the speed changer oil sump by right oil sump one-way valve 12, connection one bypass one-way valve 11 between the rear end of the front end of right oil sump one-way valve 12 and right retarder one-way valve 10; On the axle of hydrodynamic retarder pump impeller 7 hydrodynamic retarder actuation gear 5 is arranged, hydrodynamic retarder actuation gear 5 and 2 engagements of transmission output shaft gear, hydrodynamic retarder turbine 8 is fixed on the shell 6, and hydrodynamic retarder 19 oil outlets connect heat exchanger 9; Left side electromagnetic switch valve 18, right electromagnetic switch valve 17, air pressure one liquid pressure transducer and left oil sump one-way valve 13, right oil sump one-way valve 12, right retarder one-way valve 10, the 11 serial settings of bypass one-way valve are hydraulic pipe line therebetween.
As shown in Figure 2, the present invention utilizes the working medium of the lubricant oil of speed changer oil sump for hydrodynamic retarder 19, and special-purpose air pressure-hydraulic pressure conversion equipment is made up of three parts: transducer pneumatic linear actuator 16, transducer pneumatic piston 15, transducer hydraulic piston 14.Wherein, transducer pneumatic linear actuator 16 is fixed with car body, can not voluntary activity; Transducer pneumatic piston 15 is made of one with hydraulic cylinder body, drives the hydraulic cylinder body axially reciprocating under the effect of air pressure; Transducer hydraulic piston 14 is fixed with car body, can not voltuntary movement.Like this, when hydraulic cylinder body moved back and forth under the atmospheric pressure effect, the volume in hydraulic piston 14 both sides sealing chambeies took place to change relatively, and it is big that the volume of a side becomes, and the volume of opposite side diminishes.At this moment, the airtight cavity volume of a side that volume diminishes will be confessed the hydraulic oil of certain pressure and quantity, and this hydraulic oil infeeds the hydrodynamic retarder active chamber by follow-up one-way valve Path selection, cause hydrodynamic retarder to produce retarding torque; The airtight cavity volume of a side that volume diminishes will be under vacuum action, with the hydraulic oil suction of speed changer oil sump.Cooperate the gas that infeeds certain pressure to transducer both sides air chamber by right electromagnetic switch valve 17 and left electromagnetic switch valve 18, make air pressure-liquid pressure transducer pneumatic piston move back and forth incessantly, ceaselessly infeed the hydraulic oil of certain pressure and quantity to hydrodynamic retarder 19 active chambers.
When not needing to brake slowly, ECU sends the right electromagnetic switch valve 17 of command control and left electromagnetic switch valve 18 all works in " position, a left side ", air pressure-liquid pressure transducer both sides air chamber did not all have pressed gas and infeeded this moment, air pressure-liquid pressure transducer pneumatic piston 15 (transducer hydraulic cylinder body) does not move, there is not hydraulic oil to infeed hydrodynamic retarder 19 active chambers, owing to there is not working medium, hydrodynamic retarder pump impeller 7 just opposing torque can not occur, therefore there is not opposing torque on the transmission output shaft gear 2, therefore there is not retarding torque on the engine output shaft 1 yet, there is not retarding torque to pass to transmission shaft 4, normal vehicle operation by coupling 3 yet.When needs are braked, ECU is according to the position of brake petal, send the working position of right electromagnetic switch valve 17 of command control and left electromagnetic switch valve 18, right electromagnetic switch valve 17 works in " position, a left side ", and left electromagnetic switch valve 18 works in " right position ", obviously pressurized gas infeed the air chamber in air pressure-liquid pressure transducer left side by left electromagnetic switch valve 18, air pressure-liquid pressure transducer pneumatic piston 15 drives air pressure-liquid pressure transducer hydraulic cylinder body and moves axially to the right, because hydraulic piston 14 can not move axially, the volume of the airtight cavity volume of hydraulic pressure in left side diminishes, the hydraulic fluid pressure of this cavity volume rises, the left oil sump one-way valve 13 that links to each other with this cavity volume is in closing state under the effect of pressure, and retarder one-way valve 10 is opened, and hydraulic oil flows into hydrodynamic retarder 19 active chambers as the fluid power working medium; It is big that the volume of the airtight cavity volume of hydraulic pressure on right side becomes, the hydraulic fluid pressure of this cavity volume descends, form vacuum, the bypass one-way valve 11 that links to each other with this cavity volume is in closing state under the effect of pressure, and right oil sump one-way valve 12 is opened, and the lubricant oil of speed changer oil sump enters this cavity volume under the effect of gravity and negative pressure.After transducer pneumatic piston 15 moves to right limit position, ECU sends the working position of right electromagnetic switch valve 17 of command control and left electromagnetic switch valve 18, right electromagnetic switch valve 17 works in " right position ", and left electromagnetic switch valve 18 works in " position, a left side ", obviously pressurized gas infeed the air chamber on air pressure-liquid pressure transducer right side by right electromagnetic switch valve 17, air pressure-liquid pressure transducer pneumatic piston 15 drives the transducer hydraulic cylinder body and moves axially left, because hydraulic piston 14 can not move axially, the volume of the airtight cavity volume of hydraulic pressure on right side diminishes, the hydraulic fluid pressure of this cavity volume rises, the right oil sump one-way valve 12 that links to each other with this cavity volume is in closing state under the effect of pressure, and bypass one-way valve 11 is opened, and hydraulic oil flows into hydrodynamic retarder 19 active chambers as the fluid power working medium; It is big that the volume of the airtight cavity volume of hydraulic pressure in left side becomes, the hydraulic fluid pressure of this cavity volume descends, form vacuum, the retarder one-way valve 10 that links to each other with this cavity volume is in closing state under the effect of pressure, and left oil sump one-way valve 13 is opened, and the lubricant oil of speed changer oil sump enters this cavity volume under the effect of gravity and negative pressure.Like this, hydraulic oil as working medium moves back and forth the active chamber that constantly infeeds hydrodynamic retarder 19 in the process at air pressure-liquid pressure transducer, because working medium is arranged, opposing torque appears in hydrodynamic retarder pump impeller 7, also occur opposing torque on the transmission output shaft gear 2, occur certain retarding torque on the engine output shaft 1, this retarding torque passes to transmission shaft 4 by coupling 3, ransaxle acts on the wheel after this retarding torque is amplified, and vehicle operation is in braking state.And the PWM dutycycle of passing through right electromagnetic switch valve 17 of control and left electromagnetic switch valve 18 driving voltages gets final product the pressure and the quantity of Control work medium, makes things convenient for the size of control brake power.The hydrodynamic retarder control gear that device provided by the invention can replace traditional Intermediate High Pressure oil hydraulic pump and electro-hydraulic proportional valve to combine fully, technical realization is easy, and is simple in structure, with low cost.
Claims (2)
1. Pneumatic pressure formula hydrodynamic retarder control gear, it is characterized in that: comprise an air pressure-liquid pressure transducer, described air pressure-liquid pressure transducer is made up of three parts: transducer pneumatic linear actuator [16], transducer pneumatic piston [15] and transducer hydraulic piston [14], this air pressure-liquid pressure transducer left side air cavity links to each other with left electromagnetic switch valve [18], and left electromagnetic switch valve [18] import connects source of the gas; The right air cavity of air pressure-liquid pressure transducer links to each other with right electromagnetic switch valve [17], right electromagnetic switch valve [17] import connection source of the gas, the working position of left electromagnetic switch valve [18] and with the working position of right electromagnetic switch valve [17] between be connected ECU; Air pressure-liquid pressure transducer left side oil pocket links to each other with the speed changer oil sump by left oil sump one-way valve [13], links to each other with hydrodynamic retarder [19] working oil chamber by right retarder one-way valve [10]; The right oil pocket of air pressure-liquid pressure transducer links to each other with the speed changer oil sump by right oil sump one-way valve [12], connection one bypass one-way valve [11] between the rear end of the front end of right oil sump one-way valve [12] and right retarder one-way valve [10]; Hydrodynamic retarder actuation gear [5] is arranged on the Pump wheel shaft of hydrodynamic retarder [19], and the turbine of hydrodynamic retarder [19] is fixed on the shell, and hydrodynamic retarder [19] oil outlet connects heat exchanger [9].
2. Pneumatic pressure formula hydrodynamic retarder control gear according to claim 1, it is characterized in that: when left electromagnetic switch valve [18] at working position, right electromagnetic switch valve [17] during not at working position, air pressure-liquid pressure transducer and right oil sump one-way valve [12], right retarder one-way valve [10] serial setting; When right electromagnetic switch valve [17] at working position, left electromagnetic switch valve [18] during not at working position, air pressure-liquid pressure transducer and left oil sump one-way valve [13], bypass one-way valve [11] serial setting are hydraulic pipe line therebetween.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100433492A CN101566200B (en) | 2009-05-11 | 2009-05-11 | Pneumatic and hydraulic liquid power retarder controller |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100433492A CN101566200B (en) | 2009-05-11 | 2009-05-11 | Pneumatic and hydraulic liquid power retarder controller |
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| Publication Number | Publication Date |
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| CN101566200A CN101566200A (en) | 2009-10-28 |
| CN101566200B true CN101566200B (en) | 2011-12-14 |
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| CN2009100433492A Expired - Fee Related CN101566200B (en) | 2009-05-11 | 2009-05-11 | Pneumatic and hydraulic liquid power retarder controller |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI615293B (en) * | 2014-12-02 | 2018-02-21 | 郭美菁 | Hydraulic cylinder-type retarding device |
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| CN102937234A (en) * | 2012-10-29 | 2013-02-20 | 陕西法士特齿轮有限责任公司 | Pressure valve used for idle lubrication of hydrodynamic machine |
| CN103615520B (en) * | 2013-12-13 | 2016-06-22 | 宁波华盛汽车部件有限公司 | The connecting device of Retarder and reduction box |
| CN104875733A (en) * | 2014-02-28 | 2015-09-02 | 林会明 | Hydraulic retarder control system and control method |
| CN104455170B (en) * | 2014-11-28 | 2017-06-30 | 宁波华盛汽车部件有限公司 | Grease chamber housing oil drainage structure |
| CN105715618B (en) * | 2014-12-02 | 2017-12-05 | 郭美菁 | Hydraulic jack retarding device |
| CN104709257B (en) * | 2015-03-31 | 2017-09-29 | 武汉理工大学 | A kind of Retarder of low windage loss |
| DE102016224716B4 (en) * | 2016-12-12 | 2024-03-14 | Zf Friedrichshafen Ag | Engine brake request by a retarder |
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| DE102017214602A1 (en) * | 2017-08-22 | 2019-02-28 | Robert Bosch Gmbh | Control device and method for operating a vehicle deceleration device of a vehicle |
| SE541312C2 (en) * | 2017-10-13 | 2019-06-25 | Scania Cv Ab | Retarder Device, Powertrain, Vehicle, and Method of operating a Retarder Device |
| CN108775502B (en) * | 2018-06-20 | 2023-08-08 | 陕西法士特齿轮有限责任公司 | Idle self-lubricating system and method for hydraulic retarder |
| CN113119931B (en) * | 2019-12-30 | 2022-05-24 | 北汽福田汽车股份有限公司 | Slow-speed auxiliary braking system and vehicle |
| CN113246938B (en) * | 2021-07-05 | 2021-11-09 | 陕西法士特齿轮有限责任公司 | Retarder braking torque pressure control system and method |
| CN113738793B (en) * | 2021-09-09 | 2022-02-22 | 北京裕峻汽车技术研究院有限公司 | Braking system and control method of hydraulic retarder |
| CN114738400B (en) * | 2022-03-12 | 2023-06-30 | 富奥汽车零部件股份有限公司 | Hydraulic retarder oil circuit control system |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10302505A1 (en) * | 2003-01-23 | 2004-09-02 | Zf Friedrichshafen Ag | Hydraulic system for triggering, controlling and filling up a hydrodynamic retarder uses a hydraulic ratio of transmission with a continuous link to a retarder space to vary retarder filling time |
| CN1791525A (en) * | 2003-09-15 | 2006-06-21 | 福伊特涡轮机两合公司 | Automotive drive comprising a water-based retarder |
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| DE102006030791A1 (en) * | 2006-06-30 | 2008-01-03 | Zf Friedrichshafen Ag | Hydrodynamic retarder |
Cited By (1)
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| TWI615293B (en) * | 2014-12-02 | 2018-02-21 | 郭美菁 | Hydraulic cylinder-type retarding device |
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| CN101566200A (en) | 2009-10-28 |
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