EP0295445B1 - Flüssigkeits-Kühlkreis für Kraft- und Arbeitsmaschinen, insbesondere Brennkraftmaschinen - Google Patents

Flüssigkeits-Kühlkreis für Kraft- und Arbeitsmaschinen, insbesondere Brennkraftmaschinen Download PDF

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Publication number
EP0295445B1
EP0295445B1 EP88107940A EP88107940A EP0295445B1 EP 0295445 B1 EP0295445 B1 EP 0295445B1 EP 88107940 A EP88107940 A EP 88107940A EP 88107940 A EP88107940 A EP 88107940A EP 0295445 B1 EP0295445 B1 EP 0295445B1
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EP
European Patent Office
Prior art keywords
pressure
valve
coolant
cooling circuit
air separator
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
Application number
EP88107940A
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German (de)
English (en)
French (fr)
Other versions
EP0295445A3 (en
EP0295445A2 (de
Inventor
Erwin Schweiger
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.)
Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of EP0295445A2 publication Critical patent/EP0295445A2/de
Publication of EP0295445A3 publication Critical patent/EP0295445A3/de
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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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • 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
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0238—Closure caps with overpressure valves or vent valves
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/028—Deaeration devices
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0285—Venting devices
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/029—Expansion reservoirs
    • 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
    • F01P2005/105—Using two or more pumps
    • 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
    • F01P2005/125—Driving auxiliary pumps electrically
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • F01P2011/0252—Venting before opening
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • F01P2011/0261—Safety; Locking against opening activated by temperature
    • 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
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • F01P2011/0266—Safety; Locking against opening activated by pressure
    • 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
    • F01P2060/08—Cabin heater

Definitions

  • the invention relates to a liquid cooling circuit in engines and machines, in particular internal combustion engines, according to the type of claim 1. Furthermore, the invention relates to cooling circuits of similar types of claims 4 and 6.
  • the air separation container is via a return suction line as a filling line with the suction side of the Coolant pump connected.
  • the coolant flows from the bottom area of the air separation tank via the return line to the low-lying coolant pump and from there into the cooling jacket of the machine. Since the direct connection between the coolant pump and the return water tank of the cooler is closed by the cooler valve with the thermostat arranged in the cooler return line when the machine, which is always largely cold, is filled, the coolant can initially only flow into the cooling jacket and fill it.
  • This filling process is also in the case of thermostat arrangements at the cooling jacket outlet due to the narrow internal cross section of the Vent line from the cooler flow to the filler neck is delayed, through which the air to be displaced can only escape from the cooling jacket and from the cooler.
  • the resulting low filling speed not only increases the amount of work required, but also the volume of residual air remaining in the cooling jacket and other line sections with little or no gradient.
  • the coolant only enters the cooler after the cooling jacket has been completely filled, via the flow line, which usually has hardly any gradient, which further reduces the filling speed and also favors residual air volumes in the cooler. An additional lengthy venting process with the machine running and the cover removed is therefore necessary.
  • Residual air still remaining in the cooling circuit can only be discharged to the atmosphere via the expansion tank acting as an air lock even after its failure from the solution at high temperature and its upstream at the pressure relief valves if the pressure relief valve opening values are exceeded.
  • the advantages of an air-free cooling circuit such as steeper pressure build-up when the coolant temperature rises and the reduced risk of corrosion for the cooling circuit components and the coolant itself, due to its extensive degassing, are therefore hardly or mostly delayed after numerous machine hot / cold cycles .
  • the operating temperature Due to the thermal expansion of the coolant that occurred before the closing of the closure cap without pressure build-up, the operating temperature then increases as the temperature rises further the boiling limit or the pump cavitation limit is quickly reached and machine overheating is unavoidable when operating immediately afterwards under high load.
  • the object of the invention is to overcome the disadvantages described above in the area of the operating boundary conditions - filling, venting, degassing, pump cavitation, overheating, shutdown reheating, for the course of the coolant temperature unnecessarily excessive course of the coolant pressure at low start or ambient temperatures and when fuel gases penetrate into the Cooling circuit in the medium operating temperature range - to be overcome by liquid-cooled machines and at the same time to reduce construction costs, costs, weight, variety of components, and possibilities for incorrect operation. Furthermore, overdimensioning of cooling circuit components and, above all, the cooling capacity, which have so far been necessary to compensate for the described interference, are to be avoided.
  • the temperature-controlled vent valve improves both venting and degassing as well as the system pressure build-up via temperature and speed, and the cooling circuit pressure which is excessive due to fuel gas leakages is reduced again during cooling phases.
  • the line connection from the air separation tank to the expansion tank, which is opened by the thermo valve at low operating temperature, also enables a very simple venting process after filling, with a constant change in engine speed when the cover is closed, which means that coolant and residual air flow to the expansion tank and coolant flow into the air separation tank becomes. This results from the increase in the pump suction pressure when the speed drops and its drop when the speed increases.
  • the progressive ventilation can be tracked or assessed by the start of the lighting of a switched on indicator light at ever higher speed.
  • the closing temperature of the ventilation valve which is dependent on the pressure build-up dependent on the cooling circuit elasticity, especially hose length and elasticity, the temperature and the pump speed, avoids unnecessarily high cooling circuit overpressure values with relatively low coolant temperature values and on the other hand, ensures a sufficient distance between the pump suction pressure curve and the pump cavitation limit.
  • the features of claim 2 enable a particularly compact spatial allocation of the air separation container to the cooler flow and to the filler neck, whereby a very small space requirement is achieved.
  • the assignment of a coolant level sensor to the air separation container according to claim 3 results in a safe level monitoring of the overpressure cooling circuit and a warning display even if the coolant content is still safe to operate, because the temperature-related change in volume of the coolant triggers a display when the cooling circuit is cold when the coolant that warms up during operation again exceeds the display level and guarantees operational safety.
  • the fill level warning display forms a monitoring display when the cooling circuit is vented after it has been refilled or refilled.
  • the features of claim 4 contain the basic arrangement of the air separation container with filler neck and filler cap at the high point of the cooler flow in the course of the venting bypass line, whereby a large part of the advantages regardless of the arrangement and design of the overpressure, underpressure and venting valves according to claim 1 is achieved, namely advantageous filling and venting and rapid warm-up.
  • the valves can be selected in any known or previously proposed configuration and arrangement or connection, namely on the air separation tank, on the expansion tank or on both in series connection, with the latter two arrangements requiring an expansion tank with an air expansion volume.
  • Claim 5 provides for the additional control of a pressure relief valve from the pressure in the cooler flow for the immediate limitation of the pressure value acting on the cooler, since the valves are effective in the cooler return in all arrangements according to claim 4.
  • the features of claim 6 provide a temperature-controlled vent valve, which is located in the connecting line from the air separation tank to the expansion tank regardless of its arrangement. Apart from a small additional construction effort and weight, this design enables all other functional advantages of the features according to claim 1, in particular in connection with an additional filling lid arranged in a known manner at the high point of the cooler flow.
  • the design of the vent valve according to claim 7 has a particularly low construction cost and provides the simplest maintenance and repair options by checking and / or replacing the sealing cover as a unit. Individual components that have been tried and tested in automotive engineering are used. The assignment of the components of the valve also favors its function, since the snap spring is only acted upon by the coolant temperature after the air has been completely pushed out, so that the venting is promoted by the coolant itself when the closing / switching temperature is reached. A float instead of a closing spring is therefore only necessary in particularly difficult ventilation conditions.
  • the closed vent valve also increases with increasing coolant pressure increasingly favored in its sealing function, because the thermal snap spring is pressed more and more against the sealing ring.
  • This valve design can also be used advantageously in cooling circuits of a type which differs from that according to claims 1 and 6, but has at least one atmospheric expansion tank.
  • the features of claim 8 also favor the filling and the operating ventilation by discharging the residual air to the air separation tank, which remains when filling in the return water tank of cross-flow coolers or which collects there during operation. A passage of cold coolant is prevented in normal warm-up operation and thus an influence on the warm-up time is avoided.
  • the ventilation valve by opening the ventilation valve after warming up at a coolant temperature above the ambient temperature of, for example, 60 ° C in the return water tank, fuel gas leaks and residual air volume parts which are preferably collected therein are immediately discharged into the air separation container.
  • the features of claim 9 contain a functional and structurally particularly advantageous embodiment of the vent / degassing valve according to claim 8 in accordance with the vent valve according to claim 7, apart from the exclusive float arrangement and the reverse temperature control with opening instead Closing above the switching temperature of the valve.
  • a conventional closing spring and a separate ball or Schwengel vent valve can also be used, as is common in coolant thermostatic valves.
  • the features of claim 10 enable a constant flow pressure control of the pressure relief valve in the closure cover without the pressure increase in the flow area increasing with the pump delivery rate without having to adapt this separately to the necessary highest pressure opening value of the respective application.
  • the overpressure valve for the forward and return areas can be designed with the same overpressure opening value, which additionally favors the construction effort and avoids or at least reduces the variety of valve and closure covers for different engine and vehicle models.
  • the claim 12 includes a manually operable venting device which without - with the venting rotary position of the closure cover - or with very little construction effort - with a vent screw -
  • cooling circuit ventilation is possible in particularly difficult conditions.
  • the venting process is limited to operating the machine at a rapidly changing speed, possibly with short switch-off pauses, in order to allow any air bubbles to accumulate at the pump inlet to the pump pressure side.
  • claim 13 make it possible in a simple manner and secured against pressure overloading of the expansion tank to ensure the projected operating pressure of the cooling circuit even when the cooling circuit is closed at such a high coolant temperature during maintenance and / or repair work that the required pressure build-up is no longer possible due to thermal expansion of the coolant. This is particularly true in connection with the manually operated venting device according to claim 12 and difficult venting conditions in the case of cooling circuits which are inadequately designed in this regard.
  • An additional one Construction costs for the proposed construction details can be completely avoided according to the training options according to claims 14 and 15 compared to known cooling circuits, since only existing known components are to be dimensioned accordingly, namely the pressure resistance of the expansion tank, the attachment of the associated filler cap and the dimensions of the connector for the associated overflow hose.
  • An internal combustion engine 1 contains a cooling jacket 2 (arrow), into which the coolant is conveyed under pressure by a coolant pump 3.
  • a cooler flow 5 is connected with a free passage to a cross-flow cooler 6 and opens into its flow water tank 7.
  • a short circuit 8 branches off from the cooler flow 5 to a mixing thermostat 9.
  • a return line 11 also leads from the return water tank 10 out of the cooler 6 into the thermostat 9.
  • a pump suction line 12 connects the thermostat 9 to the suction side 13 of the pump 3.
  • a bypass vent line 14 is connected, which is unthrottled in a flow pressure control chamber 15 and via a throttle point 16 opens into the bottom area of an air separation container 17. This mouth is turned away from the bottom area to secure the air separation from the mouth of the bypass vent line 14, which leads to the suction side 13 of the pump 3.
  • An electrical level sensor 18 is arranged on the underside of the air separation container 17, which controls a warning instrument in a commercially available design in the event of an air and / or gas accumulation in the air separation container 17 which endangers the function.
  • the air separator tank 17 concentrically surrounds the area of the high point 5 'of the cooler flow 5 and the area of the bypass vent line 14 connected to it increasing (Fig. 2).
  • This area of the bypass vent line 14 is at the same time designed as a filler neck 19 and partially arranged within a closure cover 20.
  • the filler neck 19, the control chamber 15 and the throttle point 16 in the closure cover 20 and the line part in the bottom region of the air separation container 17 are flowed through in succession.
  • the usual overpressure and underpressure valves 21 and 22 are arranged in the closure cover 20, but are substantially modified and functionally developed according to the invention.
  • the pressure relief valve 21 is on the one hand directly controlled via a line connection 21 'to the high point of the air separation container 17 from the overpressure in the latter and on the other hand indirectly by means of a control membrane 15' from the supply overpressure in the control chamber 15 and in both cases opens the line connection 21 'from the high point of the Air separation container 17 to the atmosphere.
  • the vacuum valve 22 is installed in the usual way in the valve housing of the pressure relief valve 21 and at the same time is designed as a temperature and alternatively additionally float-controlled vent valve (FIG. 2). Except when there is negative pressure in the air separation container 17, the vacuum valve 22 closes by the interaction of a bimetallic snap plate spring 23 with an O-ring seal on the one hand and alternatively with a spring 24 or a float 24 'on the other hand only if both the switching temperature of the bimetal -Feather 23 exceeded and the air separation container 17 is vented, because the bimetallic spring 23 is always switched to the closed position only when it is acted upon by coolant at a sufficiently high temperature. Bleeding is additionally promoted.
  • a float also opens the vent valve when the air system is renewed, regardless of its switching status, as long as there is no pressure difference and leads to even more residual venting.
  • An overpressure in the air separation container keeps the bimetallic spring 23 in the closed position even when air and / or fuel gas accumulates in the air separation container 17, thereby preventing a dangerous drop in the coolant pressure during operation of the machine 1.
  • the air separation container 17 and thus the entire cooling circuit are completely vented. Furthermore, due to its switching temperature (50 ° C. in FIG.
  • the bimetallic spring 23 closes the cooling circuit only at a temperature of the coolant displaced from the air separating container 17 by the vacuum valve 21, at which the build-up at idle speed and the machine being switched off effective static system pressure SD by further thermal expansion of the coolant in cooperation with the elasticity of the entire cooling circuit, in particular of the coolant hose lines, in relation to the pump cavitation limit KG and the coolant boiling limit SG, there is a sufficient profile of the lowest possible pump suction pressure PD at maximum speed (FIG. 4).
  • both a dangerously low pump suction pressure PD and an unnecessarily high cooler supply pressure VD are thus excluded.
  • a line connection 25 to the atmosphere is led to the overpressure and underpressure valves 21 and 22 via a temperature-controlled additional overpressure valve 26 to the bottom area of an atmospheric expansion, storage and air-blocking container 27.
  • This further pressure relief valve 26 contains - like the vacuum valve 22 - a bimetallic snap disc spring 28 which interacts with an O-ring seal and is pressed against the seal by a cone spring 29 which determines the pressure value.
  • the housing of this pressure relief valve 26 is arranged in thermal connection with the flow line 5 and / or the housing of the air separation container 17 in such a way that the temperature of the coolant there acts on the bimetal spring 28.
  • Their switching temperature is set approximately according to the upper limit of the control temperature range of the thermostat 9, usually approximately 90-100 ° C.
  • the sum of the overpressure values of the overpressure valves 21 and 26 thus only comes into effect (FIG. 4) if the thermostat control range is exceeded, that is only if high ambient temperature and high engine load occur at the same time. Even due to fuel gas leaks at high engine loads, the cooling circuit is not unnecessarily loaded with excessive system pressure SD, flow pressure VD and pump suction pressure PD, but the fuel gas leaks are continuously increased by the only effective first pressure relief valve 21 excreted via the expansion tank 27 to the atmosphere.
  • the expansion tank 27 contains a part of its volume a coolant supply 30 and the rest of an expansion volume 31.
  • the filler cap 32 of the expansion tank 27 is equipped with a conventional locking bead attachment, which, however, is coordinated according to the invention such that an overpressure valve function is achieved by detaching the cover 32 at a certain excess pressure in the expansion tank 27.
  • the cover 32 is provided with a hose connector 33, which both carries an overflow hose 34 and after its removal for the connection of a tire inflation device or an air pump suitable is.
  • the functional reliability of the cooling circuit can be guaranteed in a simple, cost-effective manner even after it has been closed while the machine is already at operating temperature, in particular after a lengthy venting process or after a pressure-releasing process that requires repair and subsequent high-load operation at a high ambient temperature.
  • a further vent line 37 is connected to the bypass vent line 14 via a vent valve 35 and a throttle point 36.
  • the vent valve 35 in turn consists of a bimetallic snap disc spring 38 which interacts with an O-ring seal and which is brought into and out of operation by a float 39 when coolant or air or fuel gas is at the high point 10 ' is present.
  • the bimetal disc spring 38 has a switching temperature of about 60 ° C, so that at normal operating temperature of the cooling circuit there is a constant venting and degassing bypass flow to the air separation container 17.
  • the vent valve 35 is always closed after the outflow of air or fuel gas, so that the warm-up of the machine is not prolonged by a cooling effect of this vent stream.
  • a vehicle interior heater with a left and right heater heat exchanger 42 and 43 and a left and right heater control valve 44 and 45, respectively, is connected to the cooling circuit via a heater supply and return line 40 and 41, respectively and an additional electric heater pump 46 connected in a conventional manner.
  • the heating flow line 40 branches off from the cooler flow 5 and the heating return line 41 opens into the elevated thermostat 9.
  • a changeover valve 47 is arranged, which by means of a not shown electrical control circuit when the machine 1 is turned off at a high operating temperature, the heating flow line 40 is reversed into a cylinder head return line 48.
  • the coolant flow through the hot cylinder head that can be achieved when the machine 1 is switched off immediately flushes away coolant vapor bubbles that occur at hot spots and achieves their immediate subsequent condensation in the further coolant flow, as a result of which local vapor bubble accumulations with corresponding pressure build-up in the entire cooling circuit and consequent ejection of coolant, in extreme cases even up to overflow of the expansion tank 27 is avoided.
  • FIGS. 5 to 10 show different assignment options for the cooling circuit components according to the invention using the same basic principle.
  • FIGS. 1 to 3 the arrangements of the air separation tank 17 at the high point 5 'of the cooler flow 5, the atmospheric expansion tank 27 in a separate design and the vent valve 35 on the return water tank 10 are shown in accordance with FIGS. 1 to 3.
  • the cooler flow 5 at its high point 5 ' is only equipped with a filler neck 19 and a valveless cap 20'.
  • the air separator tank 17 is attached or molded to the return water tank 10 and combined with the expansion tank 27.
  • Whose filling cover 32 has a molded cover 32 'for the closure cover 20 of the expansion tank 27, which largely precludes incorrect operation when refilling the expansion tank 27 and thus a loss of overpressure when the coolant is warm.
  • the air separation tank 17 and the atmospheric expansion tank 27 are combined in accordance with FIG. 6, but are arranged separately from the cooler 6.
  • an additional filling line 19 ' is branched off from the cooler flow 5, which is completed by the cap 20 immediately.
  • a filler neck 19 is arranged next to the air separation container 17, while in Fig. 10 the filling line 19 'within the air separation container 17 connects to the closure cap 20.
  • the cooler inlet 5 on the one hand and the air separation container 17 and the filler neck 19 on the other hand are not arranged coaxially and concentrically with one another but mutually intersecting and arranged side by side.
  • the filler neck 19 can also be arranged centrally within an annularly branched section of the cooler inlet 5, the insert 49 closing a connection opening between the filler neck 19 and the radiator inlet 5, which is then also circular.
  • the filler neck 19 opens in both cases down into the coaxial air separator tank 17 and to the side in the cooler flow 5, so that each a large connection opening 17 'and 5' are available with the cap 20 removed for rapid filling.
  • the closure cover 20 closes in addition to the filling opening of the filler neck 19 and the connection openings 17 'and 5' against each other.
  • a hollow cylindrical insert 49 closes tightly on the underside of the closure cover 20 and is supported with its lower end face by an O-ring 50 at the upper edge of the air separation container 17. The interior of the insert 49 continues the air separation container 17 upwards towards the underside of the closure cover 20.
  • the inner structure of the closure cover 20 corresponds to that of FIG.
  • a float chamber 57 of an electrical coolant level sensor 18 is connected at the bottom to the air separation container 17 and at the top to the valves 21 and 22 in the closure cover 20.
  • Another vent line 37 which starts from the return water tank 10 of the cross-flow cooler 6 (FIGS. 1 and 3), can be connected to the float chamber 57 in a simple manner, since its connections are also suitable as an effective venting and degassing volume.
  • a one-piece design with the filler neck 19, the air separating container 17 and the cooler flow section (5) can also be advantageously carried out.
  • each a fine screen 58 is arranged, which are acted upon exclusively by the coolant flowing in and out through the valves 21 and 22 and are therefore not subject to unnecessary contamination from the circulating coolant.
  • the filler cap 32 (FIG. 1) of the expansion tank 27 can be equipped with corresponding overpressure and underpressure valves which replace the valves 21 and 22 in the closure cover 20 of the filler neck 19 or are in line with these, so that there is an overpressure reservoir with air cushion.
  • the mode of operation of the air separation container 17 with improved filling and venting and shortened warm-up of the machine cooling circuit is also used.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Temperature-Responsive Valves (AREA)
EP88107940A 1987-05-18 1988-05-18 Flüssigkeits-Kühlkreis für Kraft- und Arbeitsmaschinen, insbesondere Brennkraftmaschinen Expired - Lifetime EP0295445B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3716555 1987-05-18
DE19873716555 DE3716555A1 (de) 1987-05-18 1987-05-18 Befuell-, entlueftungs- und drucksteuer-vorrichtung fuer den fluessigkeits-kuehlkreis von kraft- und arbeitsmaschinen, insbesondere brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0295445A2 EP0295445A2 (de) 1988-12-21
EP0295445A3 EP0295445A3 (en) 1989-05-03
EP0295445B1 true EP0295445B1 (de) 1991-12-27

Family

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EP88107940A Expired - Lifetime EP0295445B1 (de) 1987-05-18 1988-05-18 Flüssigkeits-Kühlkreis für Kraft- und Arbeitsmaschinen, insbesondere Brennkraftmaschinen

Country Status (6)

Country Link
US (1) US4913107A (enrdf_load_stackoverflow)
EP (1) EP0295445B1 (enrdf_load_stackoverflow)
JP (1) JPH01503320A (enrdf_load_stackoverflow)
DE (2) DE3716555A1 (enrdf_load_stackoverflow)
ES (1) ES2028939T3 (enrdf_load_stackoverflow)
WO (1) WO1988009429A1 (enrdf_load_stackoverflow)

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CN103867282A (zh) * 2014-03-10 2014-06-18 中国北方发动机研究所(天津) 一种主动式增压蒸汽压力系统
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CN105298622B (zh) * 2015-11-19 2017-12-01 中国北车集团大连机车车辆有限公司 柴油机冷却水系统的自动排气系统
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DE102022128616B3 (de) 2022-10-28 2024-01-04 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Phasenwechselkühlkreislauf mit Drucksteuereinrichtung

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Also Published As

Publication number Publication date
DE3716555A1 (de) 1988-12-08
DE3867142D1 (de) 1992-02-06
JPH01503320A (ja) 1989-11-09
EP0295445A3 (en) 1989-05-03
DE3716555C2 (enrdf_load_stackoverflow) 1989-05-11
ES2028939T3 (es) 1992-07-16
WO1988009429A1 (en) 1988-12-01
EP0295445A2 (de) 1988-12-21
US4913107A (en) 1990-04-03

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