EP0157167A1 - Circuit de refroidissement pour moteurs à combustion interne - Google Patents

Circuit de refroidissement pour moteurs à combustion interne Download PDF

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Publication number
EP0157167A1
EP0157167A1 EP85102118A EP85102118A EP0157167A1 EP 0157167 A1 EP0157167 A1 EP 0157167A1 EP 85102118 A EP85102118 A EP 85102118A EP 85102118 A EP85102118 A EP 85102118A EP 0157167 A1 EP0157167 A1 EP 0157167A1
Authority
EP
European Patent Office
Prior art keywords
coolant
pressure
flow
pump
relief valve
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
EP85102118A
Other languages
German (de)
English (en)
Other versions
EP0157167B1 (fr
Inventor
Erwin Dipl.-Ing. Schweiger (Fh)
Axel Dipl.-Ing. Temmesfeld (Fh)
Erwin Starmühler
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
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0157167A1 publication Critical patent/EP0157167A1/fr
Application granted granted Critical
Publication of EP0157167B1 publication Critical patent/EP0157167B1/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
    • 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
    • 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
    • F01P11/0204—Filling
    • F01P11/0209—Closure caps
    • F01P11/0247—Safety; Locking against opening
    • F01P2011/0266—Safety; Locking against opening activated by pressure

Definitions

  • the invention relates to a cooling circuit according to the design of claim 1.
  • cooling circuits of this type it is customary to arrange a pressure relief valve and a vacuum valve in the filler cap.
  • a pressure relief valve and a vacuum valve in the filler cap.
  • pressure relief valves with an opening value of approx. 0.8 to 1.5 bar overpressure are used.
  • the filler cap and the pressure relief valves are arranged either in the flow or return of the cooling circuit, for example shortly after exiting the machine's cooling jacket and after the cooler valve of a thermostat arranged there, in the flow line itself, in the flow or return water tank of vertical or cross flow -Coolers or also in an expansion tank which absorbs the thermal expansion of the coolant with an air cushion or serves for air collection and separation with a bypass flow and filling connection line to the suction side of the coolant pump.
  • the pressure in the cooling circuit is higher than the pressure difference between the various arrangements, even on the suction side of the coolant pump.
  • This pressure corresponds directly to the opening value of the pressure relief valve.
  • the invention solves this problem by dimensioning the pressure relief valve according to the characterizing part of claim 1. In this way it is ensured that the pressure on the suction side of the coolant pump does not drop to the boiling pressure of the coolant even when the pump delivery capacity changes, if at least approximately the maximum permissible coolant temperature is reached at this point, and that at the same time the pressure in the Flow range of the cooling circuit does not reach higher values than has previously been the case with known cooling circuits with a pressure relief valve controlled by the return range.
  • the features of claim 2 provide values of the pressure relief valve, which are adapted to the usual dimensions of cooling circuits.
  • the arrangement of the pressure relief valve according to claim 3 gives in connection with the pressure drop at the outlet of the cooling jacket of the machine the advantage that during the operation of the machine the pressure course of the coolant is within normal limits, but after the machine has been switched off for the after-heating process the temperature compensation between the components and the coolant, an overpressure higher by the mentioned pressure drop is available to avoid re-boiling. Since only a static pressure load on the cooling circuit occurs, this is within the usual limits.
  • the features of claim 4 provide a lesson for coordinating the overall elasticity of the cooling circuit and the pressure changes of the coolant via its temperature changes by means of elastic hose lines, which means that when the coolant temperature drops below the boiling pressure, particularly on the suction side of the coolant pump, is ruled out without additional construction costs.
  • the invention is shown for example in the drawing. It shows a cooling circuit for internal combustion engines in a schematic representation with a pressure relief valve according to the invention in the flow water tank of a cooler.
  • An internal combustion engine 1 contains a cooling jacket indicated by an arrow 2, into which the coolant is conveyed under pressure by means of a coolant pump 3.
  • a flow 5 is connected as a line connection with a free passage to a cooler 6.
  • the flow 5 opens into a cooler flow water tank 7.
  • a short circuit 8 branches off from the flow 5 and opens into a mixing thermostat 9, this opening being controlled by a short circuit valve 10 of the mixing thermostat 9.
  • From a cooler return water box 11, a line forming the return 12 from the cooler 6 likewise leads into the mixing thermostat 9, which contains a cooler valve 13 for controlling the mouth of the return 12.
  • a suction line 15 opens from a mixing chamber 14 of the mixing thermostat 9 and opens into the suction side 16 of the coolant pump 3.
  • a pressure relief valve 17 is arranged on the cooler flow water tank 7 and is connected by means of an outflow line 18 to an expansion tank 19 which is open to the atmosphere and is equipped with a slotted sealing disk 19 'in its filling opening to prevent evaporation of the coolant.
  • the pressure relief valve 17 can alternatively (17 'or 1711) be connected to the flow 5 or to the cooling jacket 2 of the machine 1.
  • the expansion tank 19 is connected to the suction side 16 of the coolant pump 3.
  • the outflow line 18 can alternatively (18 ') also be connected to the upper area of the interior of the expansion tank 19, the suction line 20 opens out from the interior of the expansion tank 19 near the floor.
  • the outflow line 18 can also open separately (18 ") near the bottom of the expansion tank 19.
  • the vacuum valve 21 is combined with a filler neck 21 'to form a structural unit.
  • the outflow line 18 is connected to a vent valve 22, which is opened by its design as a sniffing, non-return or float valve or the like when air and a pressure-free cooling circuit are applied by the action of gravity.
  • a vent valve 22 which is opened by its design as a sniffing, non-return or float valve or the like when air and a pressure-free cooling circuit are applied by the action of gravity.
  • One or more relatively large-area fine screens 23 in the cooler 6 or in the expansion tank 19 prevent the valves from becoming leaky due to dirt particles entrained by the coolant.
  • a further pressure relief valve 24 is arranged in the filler neck 21 '.
  • This further pressure relief valve 24 is effective via the suction line 20 directly on the suction side 16 of the coolant pump 3 and thus on its suction pressure.
  • a vent line 25 opens into the interior of the filler neck 21 'and is located with a throttle 26 for reducing the pressure difference between its connections on the one hand on the supply water tank 7 and on the other hand via the suction line 20 on the suction side 16 of the coolant pump 3.
  • a level float switch 21 is installed in the filler neck 21 'or in the filler neck cover, which controls a display circuit when air accumulates in the filler neck 21', regardless of whether it is in compensation container 19 still contains an optically recognizable reserve amount or not.
  • the cooling circuit is filled with coolant in the filler neck 21 '.
  • the machine 1 fills through the suction line 20 and the coolant pump 3, while at the same time the air contained therein through the supply line 5, the cooler supply water tank 7 and the ventilation line 25 into the filler neck 21 ′ as well as through the open ventilation valve 22 and the outflow line 18 escapes to the atmosphere in the expansion tank 19.
  • the mixing chamber 14 and the open short-circuit valve 10 of the mixing thermostat 9 in the short-circuit 8 also fill up to the cooler valve 13 , which can also be equipped with a conventional ventilation device.
  • the vent valve 22 in the cooler 6 closes the filled cooler flow water tank 7 towards the outflow line 18, while the vent line 25 and the filler neck 21 fill completely.
  • the level float switch 21 "controls an electrical indicator lamp on the fittings of the machine or the vehicle.
  • the expansion tank 19 can be partially filled with an additional reserve quantity. In the event of thermal expansion, this flows through the ambient and cooling circuit Temperature fluctuations and, in particular, due to the operational heating of the part of the coolant displaced from the cooling circuit by the pressure relief valves 17, 17 'or 17 "and 24.
  • the expansion tank 19 contains a corresponding criminal content.
  • the first increase in speed immediately leads to the build-up of a delivery head of the coolant pump 3, which on the one hand causes the pump suction pressure to drop below the ambient pressure prevailing in the entire cooling circuit before starting and, on the other hand, builds up excess pressure in the cooling circuit sections downstream of the coolant pump 3, cooling jacket 2 , Flow 5, short circuit 8, cooler 6 and return 12 causes.
  • the vacuum valve 21 which responds to the slightest pressure difference and the suction line 20 from the expansion tank 19, draws coolant into the cooling circuit until the ambient pressure is reached on the suction side 16 of the coolant pump 3.
  • the overpressure in the parts of the cooling circuit downstream of the coolant pump 3 simultaneously increases further.
  • the elastic hose lines and any residual air inclusions in this area allow an increase in the volume of coolant contained therein.
  • the opening pressure value of the pressure relief valve 17 of approximately 2 bar or the pressure relief valve 24 of approximately 1.5 bar is reached more or less early before or after the opening of the cooling valve 13 of the mixing thermostat 9 .
  • the engine speed is decisive because the low head of the coolant pump 3 that occurs at low to medium speeds first enables the pressure relief valve 24 to respond, which responds with an overpressure opening value that is just that pressure difference lower than the overpressure opening value of the pressure relief valve 17 which builds up between standstill or idling speed and maximum speed of the machine at the connection point of the pressure relief valve 17, 17 'or 17 ".
  • the pressure relief valve 24 responds, which is connected to the suction side 16 of the coolant pump 3 via the suction line 20
  • the overpressure opening value of the pressure relief valve 17, 17 'or 17 is decisive only in the area of the maximum speed of the machine.
  • an internal pressure in the cooling circuit from the ambient pressure to the opening pressure value of the pressure relief valve 17 and during operation of the machine 1 in the area between the coolant pump 3 and the pressure relief valve 17, 17 'or 17 ", that is, above all in the cooling jacket 2, can be one above it
  • the unambiguous limitation of the maximum and minimum pressure values avoids, on the one hand, a pressure overload of the cooler 6 with corresponding oversizing in its strength and, on the other hand, a pressure drop with an increased risk of cavitation in the coolant pump 3.
  • the safe function with a high level Efficiency of the cooling circuit up to the design limit is guaranteed.
  • the overpressure which is uniformly available in the entire cooling circuit after the machine has been switched off due to the action of the pressure relief valve 24, counteracts the formation of steam during reheating or temperature compensation between the machine and the coolant.
  • a pressure overload of the cooling circuit components does not exist due to this relatively low, exclusively statically effective overpressure.
  • This higher overpressure is therefore limited to a relatively small proportion of the operating time of the machine, in particular when driving vehicles.
  • the durability of the cooling circuit components, in particular the cooler and the hose lines is favored.
  • the negative pressure in the coolant also causes the excess pressure in the cooling circuit to drop. So that the overpressure, especially on the suction side of the coolant pump 3, does not drop below the boiling pressure at the respective temperature of the coolant, the overall elasticity of the cooling circuit is adjusted accordingly, above all by means of the elasticity of the hose lines.
  • the cooling circuit With the start of operation of the machine 1 after the cooling circuit has been filled with coolant, the cooling circuit also begins to be vented automatically from residual air portions which have remained at various points during the filling or during operation, for example through the seals of which are briefly loaded with negative pressure during the cold start Coolant pump 3, get into the cooling circuit. These residual air fractions are flushed with the flow of the coolant from the machine 1 through the free continuous flow 5 into the cooler flow water tank 7, in which only the one determined by the throttle 26 relative to the thermostat 9 during the heating of the machine with the cooler valve 13 closed low ventilation flow.
  • the ventilation flow flows to the filler neck 21 ', which directs the remaining small amounts of residual air into the filler neck and there upstream of the further pressure relief valve 24.
  • the upper pressure value of about 1.5 bar of this pressure relief valve 24 is reached, this opens and allows all the residual air to flow through the suction line 20 into the expansion tank 19. This process takes place s I continue or repeat myself until the heat steady state of the cooling circuit is reached. Venting also occurs when the upper pressure opening value of approximately 2.0 bar of the pressure relief valve 17 in the cooler flow water tank is reached.
  • the overpressure opening Value of about 2 bar of the pressure relief valve 17 is namely at least approximately reached at first, while the pressure opening value of about 1.5 bar of the further pressure relief valve 24 is significantly below.
  • the overpressure values then largely adjust to one another, so that the overpressure in the filler neck 21 ′ increases approximately to the overpressure opening value of the overpressure valve 24 there.
  • the overpressure opening value of the pressure relief valve 24 is exceeded by the corresponding thermal expansion of the coolant.
  • the residual air which may have been upstream in the filler neck 21 ' is discharged into the expansion tank 19 together with a portion of coolant.
  • expansion tank 19 differs at atmospheric pressure and ambient temperature, for.
  • a sealing washer 19 'slotted without waste allows air to enter and leave the expansion tank 19 for volume compensation, but prevents constant air movement due to convection flow. This largely prevents evaporation losses in the coolant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Closures For Containers (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP85102118A 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne Expired EP0157167B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3226508A DE3226508C2 (de) 1982-07-15 1982-07-15 Kühlkreis für Brennkraftmaschinen
DE3226508 1982-07-15

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP83106971.1 Division 1983-07-15

Publications (2)

Publication Number Publication Date
EP0157167A1 true EP0157167A1 (fr) 1985-10-09
EP0157167B1 EP0157167B1 (fr) 1987-10-21

Family

ID=6168511

Family Applications (3)

Application Number Title Priority Date Filing Date
EP85102118A Expired EP0157167B1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne
EP83106971A Expired EP0100917B1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne
EP85101659A Withdrawn EP0163006A1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement à suspension pour des moteurs à combustion interne à refroidissement liquide

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP83106971A Expired EP0100917B1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne
EP85101659A Withdrawn EP0163006A1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement à suspension pour des moteurs à combustion interne à refroidissement liquide

Country Status (5)

Country Link
US (1) US4510893A (fr)
EP (3) EP0157167B1 (fr)
JP (1) JPH071005B2 (fr)
DE (3) DE3226508C2 (fr)
ES (1) ES8404010A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
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FR2639675A1 (fr) * 1988-11-28 1990-06-01 Peugeot Circuit de refroidissement d'un moteur a combustion interne d'un vehicule automobile
DE102011078293B4 (de) * 2011-06-29 2017-06-29 Röchling Automotive AG & Co. KG Ausgleichsbehälter mit einem Flüssigkeitssperrventilkörper und einem relativ zu diesem beweglich an diesem aufgenommenen Gasunterdruckventilkörper sowie eine solche Ventilstruktur tragender Deckel für einen Ausgleichsbehälter
EP3434873A1 (fr) * 2017-07-24 2019-01-30 Volkswagen Aktiengesellschaft Système de refroidissement et véhicule automobile

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2639675A1 (fr) * 1988-11-28 1990-06-01 Peugeot Circuit de refroidissement d'un moteur a combustion interne d'un vehicule automobile
EP0371841A1 (fr) * 1988-11-28 1990-06-06 Automobiles Peugeot Circuit de refroidissement d'un moteur à combustion interne d'un véhicule automobile
DE102011078293B4 (de) * 2011-06-29 2017-06-29 Röchling Automotive AG & Co. KG Ausgleichsbehälter mit einem Flüssigkeitssperrventilkörper und einem relativ zu diesem beweglich an diesem aufgenommenen Gasunterdruckventilkörper sowie eine solche Ventilstruktur tragender Deckel für einen Ausgleichsbehälter
EP3434873A1 (fr) * 2017-07-24 2019-01-30 Volkswagen Aktiengesellschaft Système de refroidissement et véhicule automobile

Also Published As

Publication number Publication date
DE3226508A1 (de) 1984-01-26
DE3374143D1 (en) 1987-11-26
DE3366593D1 (en) 1986-11-06
EP0100917B1 (fr) 1986-10-01
JPH071005B2 (ja) 1995-01-11
ES524135A0 (es) 1984-04-16
EP0100917A1 (fr) 1984-02-22
EP0157167B1 (fr) 1987-10-21
JPS5923029A (ja) 1984-02-06
US4510893A (en) 1985-04-16
EP0163006A1 (fr) 1985-12-04
DE3226508C2 (de) 1985-12-12
ES8404010A1 (es) 1984-04-16

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