EP0492141B1 - Dispositif d'entraînement - Google Patents
Dispositif d'entraînement Download PDFInfo
- Publication number
- EP0492141B1 EP0492141B1 EP91119938A EP91119938A EP0492141B1 EP 0492141 B1 EP0492141 B1 EP 0492141B1 EP 91119938 A EP91119938 A EP 91119938A EP 91119938 A EP91119938 A EP 91119938A EP 0492141 B1 EP0492141 B1 EP 0492141B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- internal combustion
- coolant
- combustion engine
- speed
- fan
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/167—Controlling of coolant flow the coolant being liquid by thermostatic control by adjusting the pre-set temperature according to engine parameters, e.g. engine load, engine speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P5/12—Pump-driving arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/02—Controlling of coolant flow the coolant being cooling-air
- F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
- F01P7/046—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using mechanical drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/06—Retarder
Definitions
- the invention relates to a drive device according to the preamble of patent claim 1.
- a generic drive device is known from WO 85/02 227, in which the fan is driven via the outer central wheel of the planetary gear.
- the fan speed can be changed continuously with respect to a specific engine speed. This makes it possible when there are high cooling water temperatures, e.g. at low engine speed and high engine load to increase the fan speed and thus the cooling capacity.
- the invention has for its object to develop a generic drive device such that a further improvement in the cooling performance can be achieved in a simple and space-saving manner in particular.
- the moment at which the inner central wheel is supported by the braking device on the housing of the planetary gear can be increased to the maximum, so that a maximum cooling capacity is immediately available via the now increased speed of the outer central wheel Available.
- installation space is saved in that both the fan itself is fastened to the outer central wheel and the drive of the coolant pump takes place from this outer central wheel.
- FIG. 1 shows an internal combustion engine driving a vehicle, which is coupled to an additional braking device designed as a retarder 2.
- the activation or deactivation of the additional braking device 2 is carried out in a known manner by filling or emptying the flow circuit of the retarder 2, the braking power being able to be regulated by correspondingly changing or adapting the degree of filling.
- the thermal energy generated during braking operation is released to the coolant liquid of the internal combustion engine 1 via a heat exchanger 3.
- the retarder 2 is therefore connected to the coolant circuit 4 of the internal combustion engine 1.
- the coolant heated by the retarder 2 and by the internal combustion engine 1 itself is cooled by a cooler 5 lying in the airstream.
- the coolant is conveyed via the coolant pump 10.
- the internal combustion engine 1 there is also a device 8 driven by the crankshaft 7 thereof for driving two structural units which influence the heat dissipation from the coolant.
- These units are, on the one hand, a fan 9 arranged behind the cooler 5, and the coolant pump 10, which is driven via the V-belt 11 by the pulley 12 (see FIG. 2).
- the device 8 consists of a planetary gear, the planet gear carrier 13 is driven by the crankshaft 7 of the internal combustion engine 1.
- the fan 9 and the pulley 12 for driving the coolant pump 10 are on the outer Central wheel 14 of the planetary gear rotatably mounted.
- the inner central wheel 15 is supported by a further flow brake (retarder) 16 on the housing 19 of the internal combustion engine 1, the rotor 17 of the flow brake 16 being firmly connected to the inner central wheel 15 and the stator 18 being firmly connected to the machine housing 19.
- the size of the torque, which can now be supported on the housing 19 via the flow brake 16, depends on the amount of oil in the flow circuit of the retarder 16. The greater this is, the greater the torque that can be supported. However, the greater the torque that can be supported, the lower the speed of the inner central wheel 15.
- the degree of filling of the flow circuit of the retarder 16 can be changed as desired.
- the oil required for the retarder 16 is taken from the lubricating oil circuit of the internal combustion engine 1.
- the inner central wheel 15 since it is braked only slightly, can rotate at a relatively high speed or on the radius r i at a relatively high peripheral speed (arrow 22).
- the outer Central wheel 14 (radius r a ) and thus the fan 9 and the pulley 12 for driving the coolant pump 10 only rotate at a low speed (arrow 23).
- the fan 9 and the coolant pump 10 are therefore also operated at an increased speed (regardless of whether braking operation is present or not) when the coolant temperature T KM is above a critical value T KMg critical for the internal combustion engine.
- the retarder 16 and the additional braking device are controlled via an electronic control unit 27 (see FIG. 1) which, via the sensor 28 and the measured value line 29, receives a signal corresponding to the current deflection ⁇ of the brake pedal 26 which can be actuated by a driver, Via the sensor 30 and the measured value line 31, a signal corresponding to the temperature T R of the operating fluid of the additional brake device 2 and a signal corresponding to the current temperature T KM of the coolant of the internal combustion engine 1 is supplied via the sensor 32 and the measured value line 33.
- control unit 27 Based on these input variables, the control unit 27 generates a manipulated value signal for actuating the retarder 16, or for actuating an actuating device provided on the retarder 16 and not shown in the drawing for the sake of clarity for changing the oil quantity in the flow circuit between the rotor 17 and the stator 18 ( Control line 34).
- the electronic control unit 27 naturally also actuates the auxiliary brake device 2 corresponding to the deflection ⁇ of the brake pedal to set the required braking power (control line 35). This is also done by appropriately filling or emptying the flow circuit of the retarder 2.
- the current value for the deflection ⁇ of the brake pedal 26 and the current value for the temperature T KM of the coolant of the internal combustion engine 1 are first adopted in the input block 37.
- a check is carried out to determine whether the coolant temperature T KM lies above a predetermined limit value T KMg . If this is the case, the flow brake 16 is actuated via the output block 39 according to the diagram B in FIG. 2, ie the outer central wheel 14 and thus the fan 9 and the pulley 12 for driving the coolant pump 10 run at an increased speed, as a result of which the heat dissipation from the coolant is increased.
- the additional brake device (retarder 2) is also controlled via this output block 39 in accordance with the deflection ⁇ of the brake pedal 26.
- the control then branches back to point 46 to re-enter ⁇ and T KM .
- the flow brake 16 is therefore controlled according to the diagram A in FIG. 2, ie the flow circuit of the retarder 16 is also emptied, so that only a small moment can be supported on the motor housing 19.
- the outer central wheel 14 and thus also the fan 9 and the pulley 12 for driving the coolant pump 10 rotate at a relatively low speed (normal speed).
- a branch is then made to point 55 or point 46 to re-enter ⁇ and T KM .
- the auxiliary braking device 2 is actuated via the output block 42 in such a way that its flow circuit is filled in accordance with the predetermined deflection ⁇ of the brake pedal 26.
- the vehicle is braked to the corresponding extent desired by the driver, which of course leads to the operating fluid of the auxiliary brake device 2 being heated.
- This heat energy is released via the heat exchanger 3 to the coolant of the internal combustion engine 1.
- the coolant is heated up more.
- the heating of the coolant of the internal combustion engine 1 is, however, greatly delayed in relation to the heating of the operating fluid of the auxiliary brake device 2.
- the invention provides for the speed of the fan 9 and the coolant pump 10 to be increased via the output block 42, i.e. immediately after it has been determined that braking operation is present increase.
- the flow brake 16 is accordingly controlled according to the diagram B in FIG. 2, namely its flow circuit is filled, so that a greater moment can be supported on the machine housing 19. The result of this is an increased output speed of the outer central wheel 14 and thus also an increased speed of the fan 9 and the coolant pump 10.
- the measures for increased heat dissipation from the coolant of the internal combustion engine 1 are activated at an early stage to activate a thermal one Overloading the additional braking device 2 is excluded.
- the current temperature T R of the retarder 2 or that of it is taken over Operating fluid and the current deflection ⁇ of the brake pedal 26.
- branch block 44 it is checked whether braking operation is still present ( ⁇ > 0 °?) Or not. If this is the case, control branches to point 45 for re-entering the current values of T R and ⁇ . This happens until the query in branch block 44 shows that there is no longer any braking operation.
- T R the values of T R detected via the input block 43 are stored in a memory. If there is no longer any braking operation, the output block 53 first causes the flow circuit of the retarder 2 to be emptied, ie the auxiliary braking device 2 is inactive so that its operating fluid is no longer heated. Then, in block 47, the previously stored values for T R become an average T R (mean temperature T R determined during the previous braking phase). This mean T R based on the amount of operating fluid present in the flow circuit of the retarder 2 is essentially a measure of the energy converted from kinetic to heat during the past braking phase, that is to say for the braking power output.
- a characteristic diagram 49 now becomes a function of the mean value T R a time period t s is read out, which has to elapse after the determination that there is no longer any braking operation (branching block 44) until fan 9 and coolant pump 10 can run again at their normal speed (activation of flow brake 16 according to diagram A in FIG. 2) .
- a timer is started in block 50.
- a query is made as to whether the time period t s has already passed. If not, a return is made to point 52 for a new query.
- the flow brake 16 is activated via the output block 54 according to the diagram A in FIG. 2, ie the speed of the fan 9 and the coolant pump 10 is reduced back to normal. With this measure, the temperature T R of the retarder 2 is reduced as quickly as possible after a braking phase. Then there is a branch to point 55 or point 46 for re-entering ⁇ and T KM .
- the invention is not limited to the fact that for the output the outer central wheel, for driving the planet carrier and the inner central wheel of the planetary gear is provided for support via the flow brake, another suitable constellation is also conceivable. Instead of using a flow brake, the change in the supporting torque can also be controlled using another braking device, such as a friction brake or an eddy current brake.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Of Braking Force In Braking Systems (AREA)
- Braking Arrangements (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
Claims (2)
- Dispositif d'entraînement d'un ventilateur refroidissant un fluide de refroidissement d'un moteur à combustion interne propulsant un véhicule, comprenant un mécanisme épicycloïdal dont le porte-satellites est entraîné par le vilebrequin du moteur à combustion interne, dont la roue planétaire prend appui sur un carter par l'intermédiaire d'un dispositif de freinage, le couple d'appui pouvant être modifié au besoin au moyen du dispositif de freinage, et dont la couronne extérieure est solidaire du ventilateur en rotation,
caractérisé
en ce que la couronne (14) assure en supplément l'entraînement d'une pompe à fluide de refroidissement (12), intercalée dans le circuit de fluide de refroidissement du moteur à combustion interne. - Dispositif d'entraînement selon la revendication 1,
caractérisé
en ce qu'une poulie à courroie (12) servant pour l'entraînement de la pompe (10) à fluide de refroidissement est montée solidaire en rotation sur la couronne (14).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4041158A DE4041158C1 (fr) | 1990-12-21 | 1990-12-21 | |
DE4041158 | 1990-12-21 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0492141A2 EP0492141A2 (fr) | 1992-07-01 |
EP0492141A3 EP0492141A3 (en) | 1992-09-23 |
EP0492141B1 true EP0492141B1 (fr) | 1994-01-26 |
Family
ID=6421014
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91119938A Expired - Lifetime EP0492141B1 (fr) | 1990-12-21 | 1991-11-23 | Dispositif d'entraînement |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0492141B1 (fr) |
DE (2) | DE4041158C1 (fr) |
ES (1) | ES2051065T3 (fr) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19502326A1 (de) * | 1995-01-26 | 1996-08-01 | Bayerische Motoren Werke Ag | Brennkraftmaschine mit einer Vorrichtung zur Belastung einer Abtriebswelle |
US5782715A (en) * | 1996-08-29 | 1998-07-21 | Eaton Corporation | Dual ratio viscous fan drive |
DE19939726A1 (de) * | 1999-08-21 | 2001-03-22 | Voith Turbo Kg | Baugruppe für eine Brennkraftmaschine |
JP2005207357A (ja) * | 2004-01-26 | 2005-08-04 | Honda Motor Co Ltd | エンジンの可変容量流体ポンプ |
DE102004043304A1 (de) * | 2004-09-08 | 2006-03-30 | Voith Turbo Gmbh & Co. Kg | Bremsvorrichtung |
DE102004057123B4 (de) * | 2004-11-26 | 2014-11-27 | Zf Friedrichshafen Ag | Verfahren zur Erhöhung der Bremsleistung eines Retarders |
EP2096276A1 (fr) * | 2008-02-28 | 2009-09-02 | Behr GmbH & Co. KG | Procédé de contrôle d'un système de suralimentation de moteur, système de contrôle, produit de programme informatique, support de stockage et système de suralimentation de moteur |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3502056A (en) * | 1968-03-26 | 1970-03-24 | James W Dillard | R.p.m. multiplier for automobile fan |
FR2499192B1 (fr) * | 1981-01-30 | 1985-06-28 | Borg Warner | Systeme d'entrainement d'accessoires automobiles |
DE3338417C1 (de) * | 1983-10-22 | 1985-04-18 | Daimler-Benz Ag, 7000 Stuttgart | Planetenraeder-Hilfsgetriebe fuer ein Kraftfahrzeug |
DE3440428A1 (de) * | 1983-11-17 | 1985-05-30 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Temperaturgesteuerter luefterantrieb fuer maschinen grosser leistung |
DE3700037C2 (de) * | 1987-01-02 | 1995-12-21 | Voith Turbo Kg | Kühlanlage für die gemeinsame Kühlflüssigkeit der Antriebsmaschine sowie eines Retarders eines Fahrzeuges |
DE3821367A1 (de) * | 1988-06-24 | 1989-06-01 | Daimler Benz Ag | Antriebsvorrichtung fuer mindestens ein an einer brennkraftmaschine angeordnetes nebenaggregat |
-
1990
- 1990-12-21 DE DE4041158A patent/DE4041158C1/de not_active Expired - Fee Related
-
1991
- 1991-11-23 ES ES91119938T patent/ES2051065T3/es not_active Expired - Lifetime
- 1991-11-23 EP EP91119938A patent/EP0492141B1/fr not_active Expired - Lifetime
- 1991-11-23 DE DE91119938T patent/DE59100953D1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE4041158C1 (fr) | 1992-08-20 |
EP0492141A3 (en) | 1992-09-23 |
ES2051065T3 (es) | 1994-06-01 |
DE59100953D1 (de) | 1994-03-10 |
EP0492141A2 (fr) | 1992-07-01 |
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