EP0142713A2 - Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails - Google Patents

Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails Download PDF

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Publication number
EP0142713A2
EP0142713A2 EP84112506A EP84112506A EP0142713A2 EP 0142713 A2 EP0142713 A2 EP 0142713A2 EP 84112506 A EP84112506 A EP 84112506A EP 84112506 A EP84112506 A EP 84112506A EP 0142713 A2 EP0142713 A2 EP 0142713A2
Authority
EP
European Patent Office
Prior art keywords
control
valve
fan drive
drive according
pressure
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.)
Granted
Application number
EP84112506A
Other languages
German (de)
English (en)
Other versions
EP0142713B1 (fr
EP0142713A3 (en
Inventor
Franz Ing. Pigisch (Grad.)
Thomas Klaucke
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Priority to AT84112506T priority Critical patent/ATE36375T1/de
Publication of EP0142713A2 publication Critical patent/EP0142713A2/fr
Publication of EP0142713A3 publication Critical patent/EP0142713A3/de
Application granted granted Critical
Publication of EP0142713B1 publication Critical patent/EP0142713B1/fr
Expired legal-status Critical Current

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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
    • F01P7/02—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
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives

Definitions

  • the invention relates to a fan drive, in particular for cooling systems of rail vehicles of the type specified in the preamble of claim 1.
  • Such a fan drive is the subject of the German patent application P 32 22 851.
  • a sensitive regulation of the fan drive is achieved, in particular through integration of parts and a small number of hydraulic connecting lines, a very simple and reliable construction the fan drive is guaranteed.
  • this adjustable fan drive can be used universally for various arrangements of hydrostatically driven fan wheels.
  • control valve of the fan drive consists of simple parts that are inexpensive to manufacture and easy to assemble and that an extremely small installation space is required due to the arrangement of the pilot valve within the control piston.
  • the control valve enables control that responds quickly to small setpoint changes.
  • the fan drive according to the invention is suitable for various hydrostatic drives, in particular also for fans of electric traction motors. With the regulated fan drive and the sensitive control, it is avoided that the fan is operated unnecessarily or at an unnecessarily high speed, which leads to considerable energy savings.
  • control spring is supported on the insert with its end remote from the control piston. In this way, there is no separate fastening of the insert, which is held on a wall part of the electromechanical actuator due to the spring preload.
  • the control valve controlling the bypass is expediently designed as a seat valve, the one acted upon by a supply pressure
  • the area of the control piston is equal to the area acted upon by the control pressure. This design ensures an extremely short overall length.
  • the control valve controlling the bypass is designed as a slide valve, the surfaces acted upon by the supply pressure and the control pressure likewise being the same. In order to create this area ratio in the slide valve, it is advantageous that the central bore extends over the entire axial length of the control piston and the insert protrudes through this bore.
  • Another important advantage of the invention is that a leak oil line can be dispensed with.
  • the surfaces of the control piston acted upon by a back pressure in the opening or closing direction of the control valve are compensated. Since the pressure medium does not have to escape from the pilot valve into a leakage oil line, but can easily be led into the return line, the control valve is particularly suitable for gear motors or other drives that do not require a leakage oil line, or for the series connection of drives.
  • a control magnet or a stepper motor can be provided as the electromechanical actuator.
  • the use of a stepper motor has the advantage that electrical energy is only required for the change of position.
  • this essentially consists of a valve cone, a valve seat and a valve cone loading spring, and the tip of the valve cone interacts with a ball through which the valve cone can be lifted off the valve seat.
  • the spring force of the spring loading the valve cone of the pilot valve can be adjusted.
  • an adjustment screw can be used for adjustment or a support element that can be inserted in a sliding manner and can be fixed in any position. The latter has the advantage that the force of the spring can be measured when the pilot valve is installed, so that subsequent adjustment is not necessary.
  • control chamber is connected to a feed line of the motor via a first throttle and to the pilot valve via a second throttle.
  • the control piston and the pilot valve can be arranged in a connecting plate of the hydraulic motor. So that in the event of a fault in the electrical system, the fan motor is operated regardless of the cooling water temperature in any case, it is advantageous that the pilot valve assumes its closed position when the electronic circuit or the electromechanical actuator is de-energized.
  • FIG 1 shows a cooler 1 with water boxes 2 and 3, to which an axial fan 4 is assigned.
  • the axial fan 4 is located on a shaft 5 of a hydraulic motor 6, for example a gear motor, which is connected to a supply line 7 carrying high pressure and to a return line 8 carrying a back pressure of a hydraulic circuit.
  • a spring-loaded check valve 13 is connected in a bypass line 11, 12.
  • the connection with chokes 34 and 46 and the operation of the check valve 13 will be explained in detail later with reference to FIGS. 2 to 4.
  • a pilot valve 14 is provided which is actuated by an electromechanical actuator 15.
  • the valves 13 and 14 are connected to the return line 8.
  • the electromechanical actuator 15 is via a control line 16 at the output terminal men of an electronic controller 17 switched.
  • a temperature sensor 19 arranged in the water tank 8 of the cooler 1 is connected to input terminals of the controller 17 via control lines 18.
  • the temperature sensor 19 has a low electrical resistance, so that a high input signal is input to the electronic controller 17.
  • Characterized the pilot valve 14 is brought into its open position, whereby the pressure forces acting on the check valve 13 are influenced such that the resulting pressure force in the opening direction of the valve overcomes the force of the control spring and thus switches the bypass line 11, 12 through.
  • the fan motor 6 is bridged by the bypass line 11, 12, so that the pressure medium flow in the feed line 7 does not act on the fan motor 6 or only to a very small extent.
  • the resistance characteristic of the changes Tem p eraturfactlers 19, resulting in a change in the input of the electronic controller 17 has the consequence. Accordingly, the output signal of the electronic controller 17 also changes, which has an influence on the electromechanical actuator 15. As a result, the pilot valve 14 is set to a smaller passage cross section. This position of the pilot valve 14 affects the pressure conditions at the valve closing member of the check valve 13 so that the passage cross section of the valve 13 is also reduced. Due to the now lower pressure medium flow in the bypass line 11, 12, the proportion of the pressure medium flow acting on the fan motor 6 increases, as a result of which the fan motor 6 drives the axial fan 4 at a corresponding speed.
  • the input signal on the electronic real 17 is so low due to the large resistance value of the temperature sensor 19 that the output signal of the controller brings the electromechanical actuator 15 into an end position by which the pilot valve 14 is completely closed .
  • the same pressure builds up on both sides of the valve closing member of the check valve 13 (in the closing direction with a time delay), so that the check valve 13 is closed. Since the bypass line 11, 12 is now shut off, the fan motor 6 is acted upon by the entire pressure medium flow and the axial fan 4 is operated at maximum speed.
  • the axial fan 4 would be assigned to an electric machine.
  • the temperature sensor 19 is then integrated into the motor winding, the respective temperature of the winding as the input variable of the electronic controller 17 determining the position of the pilot valve 14 and thus the fan speed.
  • FIG. 2 shows a connecting plate 20 of a hydraulic motor 21.
  • the connection plate 2o has a bore 22, to which a bore 23 carrying a high pressure HD and a back pressure RD carrying a bore 24 are arranged at right angles, but at an axial distance.
  • the connection of the flow line carrying the high pressure HD is designated 22 a and the connection of the return line carrying the back pressure RD is designated 24 a.
  • a step 25 is provided in the bore 22 between the bore 23 and the bore 24, the inner radius of which serves as the valve seat 26 of the check valve.
  • the control piston 27 has a stepped central bore 29 a, 29 b, wherein the section 29 a is part of the control chamber 28.
  • the radial area delimiting the control chamber 28 is equal to the area of the control piston 27 acted upon by the high pressure HD.
  • an insert piece 3o is pressure-tight g e-guided, ie the control piston 27 is displaceably mounted on the outer surface of the insert piece (3o).
  • the insert 3o has at its end facing away from the control piston 27 a radial collar 31 on which one end of a control spring 32 is supported, the other end of which lies on the gradation of the bore 29a, 29b and thus the control piston 27 against the Valve seat 26 loaded.
  • an axial bore 33 lying outside the bore section 29 b is provided with a throttle 34, through which the part of the bore 22 located in front of the check valve is connected to the control chamber 28.
  • the insert 3o has a central, multiply stepped bore 36 which extends over the entire length of the insert 3o.
  • the right end of the bore 36 in FIG. 2 is provided with a thread 37 into which a hollow screw 38 is turned.
  • a spring 39 is supported on the hollow screw 38 and loads a valve cone 41 against a valve seat 42.
  • the valve cone 41 and valve seat 42 form the essential elements of the pilot valve 14.
  • the tip of the valve cone 41 is supported on a ball 43, which is located on the right side in the bore 36 and in turn interacts with a tappet 44 of a control magnet 45 .
  • the electronic controller 17 is structurally combined with the control magnet 52.
  • the portion of the bore 36 in which the ball 43 is located, and the bore portion 29 a, which is part of the control chamber 28, are connected to one another via a throttle 4G.
  • This throttle 46 has the task of preventing the two spring-supported elements (control piston 27 and valve cone 41) from swinging open.
  • the limited by the insert 27 space of the bore portion 29 b forms a pressure outlet chamber 47 which is connected by a radial bore 48 with the bore 24 carrying the back pressure RD.
  • the control piston 27 is moved in the opening direction of the bypass from this pressure is applied. Due to the throttle bore 34, a corresponding back pressure builds up in the control chamber 28, which corresponds to the pressure prevailing on the right-hand side of the control piston 27. Due to the same pressures and the same pressurized surfaces, the resulting force is the control spring 32, which keeps the control piston 27 in contact with the valve seat 26 and thus the bypass.
  • the hydraulic motor 21 is then acted upon by the entire pressure medium flow and the fan at its maximum speed. operated. On the basis of a corresponding signal from the temperature sensor in the cooling water, the coil of the control magnet 45 is excited and the valve cone 41 is lifted off the valve seat 42 by the ball 43.
  • FIG. 3 shows the arrangement of the check valve 13 and the pilot valve 14 in a housing 50 , which can be structurally combined with a hydraulic motor or can be arranged separately.
  • the housing 50 has a bore 51, to which a bore 52 connected to the high pressure HD and a bore 53 connected to the back pressure RD are arranged at right angles and at an axial distance from one another.
  • a snap ring 54 is inserted in the bore 51 between the bore 52 and the bore 53.
  • the radial area of the control piston 55 delimiting the control chamber 28 is equal to the area acted upon by the high pressure HD.
  • the control piston 55 has a stepped central bore 56 a, 56 b, the section 56 a being part of the control chamber 28.
  • an insert 57 is guided so as to be pressure-tight, ie the control piston 55 is displaceably mounted on the lateral surface of the insert 57.
  • the insert 57 penetrates the entire control piston 55 and protrudes from the high-pressure side.
  • the insert 57 has a radial collar 58, which lies on a housing of a stepping motor 59.
  • On the radial collar 58 is one Supported control spring 32, which is at its other end on the gradation of the bore 56 a, 56 b and thus loaded the control piston 56 against the snap ring 54.
  • an axial bore 33 lying outside the bore section 56 b is provided with a throttle 34, through which the part of the bore 51 located in front of the check valve is connected to the control chamber 28.
  • the parts comprising the pilot valve 14 are of the same design as those in FIG. 2; the reference symbols for identical parts from FIG. 2 have therefore been adopted.
  • a grub screw 6o is rotated, on the side facing the pilot valve 14, a spacer 61 is arranged, on which the spring 39, which loads the valve cone 41, is supported.
  • the spacer 61 is designed so that it allows the passage of the hydraulic fluid to radial openings 62 which open into an annular space 63 on the lateral surface of the insert 57, which in turn is connected to the bore 53 via a radial bore 48 in the control piston 55.
  • the control piston 55 has no surface effectively acted upon by the back pressure.
  • control valve shown in FIG. 3 corresponds to that already described for FIG. 2, since the changes are of a purely constructive nature, namely that the control valve is a slide valve and the electromechanical actuator is a stepper motor 59.
  • FIG. 4 shows an embodiment variant of the pilot valve in FIG. 2.
  • the same reference numerals have been chosen for those parts which correspond to FIG. 2.
  • the end of the insert 3o adjacent to the pressure outlet chamber 47 has only an annular groove 64 instead of a thread.
  • a support element 65 which consists of a tin pot, on the bottom of which the spring 39 is supported.
  • a plurality of openings 66 are arranged in the bottom of the support element 65, the overall cross section of which is larger than that of the pilot valve 14.
  • the support element 65 has on its cylindrical wall 67 a plurality of projections 68 which engage in the groove 64 of the insert piece 3o.
  • the advantage of this arrangement is that the force of the spring 39 acting on the valve cone 41 can be adjusted in a simple manner during the assembly of the pilot valve without any pressure test.
  • the support element 65 is namely moved in the direction of the valve cone 41, whereby the spring 39 is tensioned.
  • the force acting on the support element 65 is measured.
  • radially outward projections 68 for example by shear, are produced by appropriate tools and engage in the groove 64 of the support element 30. A pressure test to determine the opening pressure and readjustment of the spring 39 are not necessary.
  • the pilot valves 14 are designed as analog valves and are operated by the electromechanical actuators (electro magnet 45, stepper motor 59), the armature or. Spindle stroke is variable depending on the respective output signal of the electronic controller 17. In this way it is achieved that if the cooling water temperature remains constant over a long period of time and therefore also the fan speed is kept constant, the pilot valve remains in its position and does not have to carry out a large number of switching operations.

Landscapes

  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Electric Motors In General (AREA)
  • Control Of Direct Current Motors (AREA)
EP84112506A 1983-11-19 1984-10-17 Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails Expired EP0142713B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84112506T ATE36375T1 (de) 1983-11-19 1984-10-17 Luefterantrieb, insbesondere fuer kuehlanlagen von schienenfahrzeugen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3341795 1983-11-19
DE3341795A DE3341795C2 (de) 1983-11-19 1983-11-19 Regelventil für eine Regeleinrichtung eines hydraulischen Lüfterantriebs, insbesondere für Kühlanlagen von Schienenfahrzeugen

Publications (3)

Publication Number Publication Date
EP0142713A2 true EP0142713A2 (fr) 1985-05-29
EP0142713A3 EP0142713A3 (en) 1986-09-10
EP0142713B1 EP0142713B1 (fr) 1988-08-10

Family

ID=6214690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84112506A Expired EP0142713B1 (fr) 1983-11-19 1984-10-17 Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails

Country Status (6)

Country Link
US (1) US4570849A (fr)
EP (1) EP0142713B1 (fr)
JP (1) JPS6111499A (fr)
AT (1) ATE36375T1 (fr)
DE (2) DE3341795C2 (fr)
ES (1) ES536409A0 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2191847A (en) * 1986-06-17 1987-12-23 Sundstrand Hydratec Ltd Hydraulically driven engine cooling systems
US4738330A (en) * 1985-03-22 1988-04-19 Nippondenso Co., Ltd. Hydraulic drive system for use with vehicle power steering pump
WO2013135348A1 (fr) * 2012-03-15 2013-09-19 Ihi Charging Systems International Gmbh Turbine équipée d'un élément de réglage à déplacement axial pour un turbocompresseur à gaz d'échappement

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JPH059515Y2 (fr) * 1986-06-11 1993-03-09
JPS63124820A (ja) * 1986-11-12 1988-05-28 Toyota Motor Corp 内燃機関の冷却フアンの回転速度制御装置
JPH0650282Y2 (ja) * 1986-11-12 1994-12-21 トヨタ自動車株式会社 冷却フアン駆動用とパワ−ステアリング用の液圧回路
DE3714842A1 (de) * 1987-05-05 1988-11-17 Sueddeutsche Kuehler Behr Luefterantrieb fuer eine kuehlanlage, insbesondere fuer schienenfahrzeuge
GB2266950B (en) * 1992-04-24 1995-11-08 Ingersoll Rand Co Apparatus for and method of inhibiting formation of frozen condensate in a fluid system
US5398794A (en) * 1993-06-02 1995-03-21 Horton Industries, Inc. Overheating protection device for rotational control apparatus
DE19629176B4 (de) * 1996-07-21 2006-07-06 Dürr Dental GmbH & Co. KG Sicherheitseinrichtung an einer Pumpe
US5778693A (en) * 1996-12-20 1998-07-14 Itt Automotive Electrical Systems, Inc. Automotive hydraulic engine cooling system with thermostatic control by hydraulic actuation
SE509903C2 (sv) * 1998-02-27 1999-03-22 Volvo Wheel Loaders Ab Kyl- och värmesystem
US6030314A (en) * 1998-09-28 2000-02-29 Caterpillar Inc. Method and apparatus for retarding a work machine having a fluid-cooled brake system
ITTO20011039A1 (it) * 2001-10-30 2003-04-30 Ct Studi Componenti Per Veicol Valvola di aspirazione per una pompa ad alta pressione, in particolare per combustibile di un motore endotermico.
FR2864197B1 (fr) * 2003-12-18 2006-04-28 Eaton Sa Monaco Vanne hydraulique a rondelle piezoelectrique
US7104382B2 (en) * 2004-10-21 2006-09-12 Kit Masters Inc. Clutch system
US7438169B2 (en) * 2004-10-21 2008-10-21 Kit Masters Inc. Clutch system
US7640735B2 (en) * 2005-09-19 2010-01-05 Parker-Hannifin Corporation Auxiliary pump for hydrostatic transmission
US8100239B2 (en) * 2008-01-18 2012-01-24 Kit Masters Inc. Clutch device and methods
CA2738710C (fr) 2008-11-12 2014-04-22 Horton, Inc. Embrayage a deux vitesses et kit de mise a niveau
US8128379B2 (en) * 2008-11-19 2012-03-06 Wabtec Holding Corp. Temperature management system for a 2CD type air compressor
US8109375B2 (en) * 2009-05-07 2012-02-07 Kit Masters Inc. Clutch systems and methods
US9046137B2 (en) 2010-01-22 2015-06-02 Kit Masters Inc. Fan clutch apparatus and methods
US8360219B2 (en) 2010-04-26 2013-01-29 Kit Masters, Inc. Clutch system and methods
JP6148399B2 (ja) * 2014-03-31 2017-06-14 株式会社クボタ 作業機
CN108138763A (zh) * 2015-10-12 2018-06-08 派克汉尼芬公司 叶片齿轮泵
CN108488079B (zh) * 2018-02-28 2019-08-20 重庆酋创科技有限公司 用于控制风扇转速的装置
HUP1900114A1 (hu) * 2019-04-05 2020-10-28 Kerox Ipari Es Kereskedelmi Kft Vezérelt dugattyús szelep

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CH326068A (fr) * 1955-07-05 1957-11-30 Charles Dubois Roger Vanne électromagnétique
GB864659A (en) * 1957-07-10 1961-04-06 Stanley William Hoskins Improvements in solenoid-operated fluid-flow control valves
US3033228A (en) * 1959-03-23 1962-05-08 Lewis K Rimer Low-force valve control
FR1402416A (fr) * 1964-07-24 1965-06-11 Suedeeutsche Kuehlerfabrik Jul Soupape commandée thermostatiquement
DE1550321A1 (de) * 1966-11-12 1969-05-14 Paul Hess Elektrisch gesteuertes Druckventil
DE1920973A1 (de) * 1968-05-08 1970-01-15 Hyster Co Kuehlanlage fuer Hubstapler und hydraulisches Kuehlgeblaese fuer die Kuehlanlage
US3799497A (en) * 1972-04-20 1974-03-26 Control Concepts Two stage solenoid operated valve
DE2525240A1 (de) * 1975-06-06 1976-12-23 Bosch Gmbh Robert Vorsteuerbares ventil fuer hydraulische anlagen
US4073464A (en) * 1976-08-24 1978-02-14 Chemetron Corporation Cylinder valve for gas fire extinguishing system
EP0097230A2 (fr) * 1982-06-18 1984-01-04 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails

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US3415269A (en) * 1967-01-24 1968-12-10 Vapor Corp Multiple positioned pilot controlled poppet valve
US3664129A (en) * 1968-05-08 1972-05-23 Hyster Co Hydraulic cooling system
DE2424321A1 (de) * 1974-05-18 1975-11-20 Woma Maasberg Co Gmbh W Absperrventil fuer hohe und hoechste drucke, insbesondere fuer hochdruckspritzpistolen
US4065052A (en) * 1976-11-04 1977-12-27 Evans Products Company Dual action control mechanism
US4283009A (en) * 1980-02-07 1981-08-11 The Bendix Corporation Control valve for fluid-operated clutch

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH326068A (fr) * 1955-07-05 1957-11-30 Charles Dubois Roger Vanne électromagnétique
GB864659A (en) * 1957-07-10 1961-04-06 Stanley William Hoskins Improvements in solenoid-operated fluid-flow control valves
US3033228A (en) * 1959-03-23 1962-05-08 Lewis K Rimer Low-force valve control
FR1402416A (fr) * 1964-07-24 1965-06-11 Suedeeutsche Kuehlerfabrik Jul Soupape commandée thermostatiquement
DE1550321A1 (de) * 1966-11-12 1969-05-14 Paul Hess Elektrisch gesteuertes Druckventil
DE1920973A1 (de) * 1968-05-08 1970-01-15 Hyster Co Kuehlanlage fuer Hubstapler und hydraulisches Kuehlgeblaese fuer die Kuehlanlage
US3799497A (en) * 1972-04-20 1974-03-26 Control Concepts Two stage solenoid operated valve
DE2525240A1 (de) * 1975-06-06 1976-12-23 Bosch Gmbh Robert Vorsteuerbares ventil fuer hydraulische anlagen
US4073464A (en) * 1976-08-24 1978-02-14 Chemetron Corporation Cylinder valve for gas fire extinguishing system
EP0097230A2 (fr) * 1982-06-18 1984-01-04 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG Commande du ventilateur pour une installation de refroidissement, notamment pour véhicules sur rails

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4738330A (en) * 1985-03-22 1988-04-19 Nippondenso Co., Ltd. Hydraulic drive system for use with vehicle power steering pump
GB2191847A (en) * 1986-06-17 1987-12-23 Sundstrand Hydratec Ltd Hydraulically driven engine cooling systems
GB2191847B (en) * 1986-06-17 1990-03-28 Sundstrand Hydratec Ltd Hydraulically driven engine cooling systems
WO2013135348A1 (fr) * 2012-03-15 2013-09-19 Ihi Charging Systems International Gmbh Turbine équipée d'un élément de réglage à déplacement axial pour un turbocompresseur à gaz d'échappement

Also Published As

Publication number Publication date
ES8600467A1 (es) 1985-10-16
ES536409A0 (es) 1985-10-16
EP0142713B1 (fr) 1988-08-10
ATE36375T1 (de) 1988-08-15
JPS6111499A (ja) 1986-01-18
DE3341795A1 (de) 1985-05-30
DE3341795C2 (de) 1986-07-10
DE3473321D1 (en) 1988-09-15
US4570849A (en) 1986-02-18
EP0142713A3 (en) 1986-09-10

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