EP0100917A1 - 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
EP0100917A1
EP0100917A1 EP83106971A EP83106971A EP0100917A1 EP 0100917 A1 EP0100917 A1 EP 0100917A1 EP 83106971 A EP83106971 A EP 83106971A EP 83106971 A EP83106971 A EP 83106971A EP 0100917 A1 EP0100917 A1 EP 0100917A1
Authority
EP
European Patent Office
Prior art keywords
coolant
pressure
relief valve
cooling circuit
pressure relief
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
EP83106971A
Other languages
German (de)
English (en)
Other versions
EP0100917B1 (fr
Inventor
Erwin Dipl.-Ing. Schweiger
Erwin Dipl.-Ing. Starmühler
Axel Dipl.-Ing. Temmesfeld
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
Priority to DE8585102118T priority Critical patent/DE3374143D1/de
Publication of EP0100917A1 publication Critical patent/EP0100917A1/fr
Application granted granted Critical
Publication of EP0100917B1 publication Critical patent/EP0100917B1/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.
  • 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 arrangement of the pressure relief valve in the flow area of the cooling circuit results in the operation of the machine with the highest delivery rate of the coolant pump and thus the highest pressure difference between the suction side of the coolant pump and the connection point of the pressure relief valve a regular decrease in the coolant pressure on the suction side of the coolant pump to the boiling pressure of the coolant.
  • a further pressure drop is not possible due to physical laws, because at least the proportion of water in the coolant changes to steam when the pressure drops to boiling pressure, which is sufficient to establish an equilibrium state between liquid and vaporous parts at boiling pressure.
  • the overpressure on the suction side of the coolant pump always lies with sufficient certainty above the boiling pressure of the coolant, so that vapor bubbles form on the suction side and largely also cavitation within the coolant pump excluded are.
  • an at least brief drop in engine speed occurs, in particular until idling, after the opening value of the pressure relief valve has been reached, there is both a drop in the flow pressure and an increase in the pressure drop on the pump suction side.
  • the pressure on the suction side of the coolant pump also drops by a corresponding value up to the boiling pressure of the coolant at the given coolant temperature.
  • This functional sequence there is no security against boiling on the suction side of the coolant pump and cavitation in the coolant pump even after this one-time drop in the engine speed even with this arrangement and dimensioning of the pressure relief valve.
  • due to the lower pressure and the resulting reduced delivery capacity of the coolant pump there is also increased vapor bubble formation at the hottest points of the machine's cooling jacket, especially in the cylinder head.
  • the heat transfer to the coolant is impaired by an insulating vapor boundary layer and the efficiency of the cooling as a whole is reduced.
  • the reduced heat transfer to the environment due to the lower flow velocity in the cooler also contributes to this.
  • the object of the invention is to design a cooling circuit for internal combustion engines so that a drop in pressure on the suction side of the coolant pump to the boiling pressure is avoided and an excessively high pressure build-up in the flow area, in particular in the flow water box of the cooler, is excluded. Rather, with a clear limitation of both pressure values downwards and upwards, a cooling circuit is to be created which has a largely constant high efficiency over the entire working range.
  • the invention solves this problem by arranging and 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 at the maximum permissible coolant temperature at this point and that at the same time the pressure in the flow area of the cooling circuit does not reach higher values than has hitherto been the case with known cooling circuits.
  • 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 results in connection with the pressure drop at the outlet of the cooling jacket of the machine Advantage that during the operation of the machine, the pressure curve of the coolant is within the usual limits, but that after the machine has been switched off for the post-heating process by the temperature compensation between the components and the coolant, an overpressure which is higher by the mentioned pressure drop is available to avoid re-boiling stands. Since only a static pressure load of the cooling circuit occurs, this is within the usual limits.
  • the feature of claim 4 enables a separate arrangement of the pressure relief valve from its connection point, whereby the pressure relief valve is independent in its arrangement of the location of the pressure to be controlled and also the control is made possible at a location with coolant pressure deviating from the control pressure.
  • the features of claims 5 and 6 result in the design of the control line of the pressure relief valve at the same time as an outflow line for the coolant to be deactivated and as a vent line for the cooling circuit.
  • claims 7 to 9 show advantageous structural designs for combining different components of the cooling circuit on a filler neck, thereby reducing the construction costs of the cooling circuit.
  • the features of claim 9 result in a summary of all the control elements provided for the pressure control and the level display in the cooling circuit.
  • the features of claim 10 include the arrangement, ing and dimensioning of a further pressure relief valve, which ensures that at low engine speeds and thereby pump delivery rates, a lower overpressure is built up in the entire cooling circuit than is determined by the pressure relief valve according to claim 1. On the one hand, this reduces the pressure load on the cooling circuit during partial load operation of the machine and the venting effect achieved by opening the additional pressure relief valve with pushing out any air that may have accumulated there at a lower pressure without, on the other hand, impairing the advantageous properties of the cooling circuit at low engine speeds or when suddenly increasing to the maximum speed.
  • claims 11 and 12 include a structurally advantageous combination of the two pressure relief valve functions in a double valve according to claim 11 and in a single pressure relief valve controlled by two different overpressure ranges according to claim 12.
  • claim 13 enable a tuning of the single valve in the same way as is possible with the separate pressure relief valves according to claims 10 and 11, in such a way that either the same overpressure is defined as the maximum pressure either in the flow and on the pump suction side or a higher overpressure is determined on the pump suction side than in the flow and vice versa.
  • the first vote against overcooking when reheating the coolant provides the same static overpressure in the entire cooling circuit as is limited as a dynamic maximum pressure during operation of the machine in the lead.
  • the second tuning results in a higher static pressure than the maximum operating pressure limited during the pre-heating, and the third tuning enables a reverse overpressure ratio, in which the overpressure on the suction side of the coolant pump is set to about the average value that occurs when the Maximum speed when the machine is idling or at a standstill due to the elimination of the pressure difference from the pump delivery rate.
  • claims 14 and 15 contain particularly advantageous constructive designs of the double-actuated pressure relief valve, according to claim 15 also in connection with a bypass expansion tank with an expansion air space, such that only portions of the air space through the pressure relief valve and the vacuum valve -Contents are fed in and out and that the ventilation bypass flow is introduced as a ventilation vortex into the expansion tank in order to effectively separate air residues distributed in the cooling circuit from the coolant.
  • the features of claim 16 provide a lesson for coordinating the elasticity of the cooling circuit and the pressure profile of the coolant over the change in temperature, whereby with a suitable choice of elastic line parts, such as hose lines, and / or elastically flexible cavity walls, such as spring-loaded or gas-cushioned pistons or membranes, when the coolant temperature drops below the boiling pressure due to the relatively faster pressure drop in relatively rigid walls can be ruled out.
  • elastic line parts such as hose lines
  • elastically flexible cavity walls such as spring-loaded or gas-cushioned pistons or membranes
  • claims 17 and 18 complicate or prevent the opening of the filler cap in the event of overpressure in the cooling circuit, thereby making it both functional and immediate subsequent operation disadvantageous reduction of the overpressure and scalding of the handling person by escaping coolant is largely excluded.
  • 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 lead 5 opens into a cooler-Vor running 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.
  • 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 17 ′′) be connected to the feed line 5 or to the cooling jacket 2 of the machine 1.
  • the expansion tank 19 with the suction side 16 of the coolant pump 3 is connected via a suction line 20 and a vacuum valve 21, which preferably acts as a non-return valve While the outflow line 18 can alternatively (18 ') also be connected to the upper region of the interior of the expansion tank 19, the after-suction line 20 opens out from the interior of the expansion tank 19 near the floor.
  • the outflow line 18 can also be separated (18 ") open into the expansion tank 19 near the bottom thereof.
  • 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 pressureless cooling circuit are applied by the action of gravity.
  • this vent valve 22 is at the high point the cooler flow water tank 7 of a vertical flow cooler 6, from which the outflow line 18 extends.
  • a cross-flow cooler is even more suitable for this arrangement for the particularly effective ventilation of the cooling circuit, because starting from its cooler flow water tank, starting from the uppermost cooler pipes, only a very small coolant flow is generated in the cooler return water tank, which separates out Air in the area of the vent valve arranged there favors.
  • the vent valve 22 can be designed regardless of its arrangement according to the pressure relief valve 17, 17 'or 17 "as a float valve, the sealing seat surface is matched to the weight of the float so that the float valve opens when air accumulates even if Relatively low overpressure values prevail in the cooling circuit.
  • 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 built in, which controls a display circuit when air accumulates in the filler neck 21 ', regardless of whether or not there is an optically recognizable reserve quantity in the expansion tank 19.
  • 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 supports 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 case 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 which is displaced from the cooling circuit by the pressure relief valves 17, 17 'or 17 "and 24.
  • the expansion tank 19 When operating the internal combustion engine 1, which usually begins with a cold start after prolonged cooling, in which the likewise cooled coolant content of the entire cooling circuit has a certain minimum volume, ent the expansion tank 19 holds a corresponding minimum content.
  • a coolant volume corresponding to the loss of volume flows out of the expansion tank 19 through the suction line 20 and through the vacuum valve 21 and through the coolant pump 3 into the cooling circuit which is otherwise closed on all sides by the pressure valve 17 and which is made up of the cooling jacket 2, the flow 5, the cooler 6, the return line 12, the suction line 15 and the short circuit 8.
  • the content of the expansion tank 19 is dimensioned such that a complete emptying of the expansion tank 19 is largely ruled out at the lowest ambient temperatures customary in the region.
  • the cooling circuit is still functional even if a certain amount of air is sucked into the cooling circuit at exceptionally low ambient temperatures, because due to the volume expansion of the coolant occurring during the warming-up of the machine, this proportion of air returns through the pressure relief valve 17 before the operating temperature is reached the expansion tank 19 is displaced.
  • the switching path of the level float switch 21 "can be adapted to this change in volume but also to a minimum air volume in the filler neck 21 '.
  • the total volume of the expansion tank 19 is finally determined additionally from the total content of the cooling circuit, the highest possible thermal expansion of the coolant in the cooling circuit and an additional holding volume for a possibly overheating-related ejection quantity through the pressure relief valve 17.
  • 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 given before the start in the entire cooling circuit and on the other hand builds up an overpressure in the coolant pump 3 switched cooling circuit sections, cooling jacket 2, flow 5, short circuit 8, cooler 6 and return 12 causes. While this overpressure does not reach the opening pressure value of the overpressure valve 17, 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. During this process, 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, which is sucked out of the expansion tank 19 during this process.
  • the opening pressure value of the pressure relief valve 17 or the pressure relief valve 24 reached more or less early before or after opening the cooler valve 13 of the mixing thermostat 9.
  • the engine speed is decisive because the delivery head of the coolant pump 3 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 the standstill of the machine or idling speed and maximum speed at the location of the pressure relief valve 17, 17 'or 17 ".
  • the pressure relief valve 24 responds in each case, which on the suction side 16 of the coolant pump 3 via the non-suction line 20
  • the pressure opening value of the pressure relief valve 17, 17 'or 17 is decisive only in the area of the maximum speed of the machine.
  • the pressure on the suction side 16 of the coolant pump 3 is even substantially below the pressure opening value of the pressure relief valve 24 active there This is due to the suction effect of the coolant pump 3 and the elasticity, above all of the hose lines, distributed over the entire cooling circuit.
  • the pressure differences are very small and, as when the machine 1 is at a standstill, the entire cooling circuit takes on one Overpressure corresponding to the opening value of the relief valve 24.
  • 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 due 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 thereby 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 elastic walls of the cooling circuit, in particular the hose lines and a possibly provided ela static gas or air cushion or an elastic piston or membrane spring device, adjusted in its overall elasticity accordingly.
  • 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 venting current flows to the filler neck 21 ', which directs the remaining smaller portions of residual air into the filler neck and there upstream of the further pressure relief valve 24.
  • the machine 1 and the coolant are warmed up, and as a result of the thermal expansion and pressure increase of the coolant de r pressure value of about 1.5 bar of this pressure relief valve 24 is reached, this opens and leaves the residual air collected flows through the suction line 20 into the expansion tank 19. This process continues or repeats itself until the heat steady state of the cooling circuit is reached. Venting also occurs when the overpressure opening value of the relief valve 17 is reached in the cooler flow water tank.
  • the overpressure values then largely adapt 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 overpressure 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.
  • B Engine compartment temperature from vehicles emitting air in the coolant as bubbles or in solution into the atmosphere.
  • 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.
  • FIGS. 2 and 3 largely correspond to that according to FIG. 1 both in structure and in function. Only the two pressure relief valves 17 and 24 are combined in the filler neck 21 'or in the cover 27 of the filler neck 21' of a secondary flow expansion tank 28 with air space 29. Furthermore, the vent valve 22 is omitted, the outflow line 18 is connected to the filler neck 21 ′ or its cover 27 via the pressure relief valve 17 and the throttle 26 ′ in the cover 27 is arranged parallel to the pressure relief valve 17.
  • FIG. 2 shows alternative connections 18 ′ of the outflow line 18 on the flow line 5 and on the cooling jacket 2 in accordance with the alternative arrangements of the pressure relief valve 17 ′ and 17 ′′.
  • the pressure relief valves 17 and 24 in FIG. 2 are in the opposite closing directions of a single valve spring 24
  • the different overpressure opening values of approximately 1.5 or 2 bar are achieved by dimensioning the opening cross sections of the two valves in an inversely proportional manner.
  • the respective connection of the outflow line 18 and the suction line 20 or the alternatively provided steam line in FIG 20 'on the cover 27 takes place via sealed ring grooves 30 and 31 which are arranged between the filler neck 21' and cover 27.
  • the secondary flow expansion tank 28 is alternatively also shown in dashed lines as a filler neck 21 'without an air space 29.
  • the evaporation line 20 'leading to the atmosphere should therefore only be provided in combination with an air space 29, while the expansion tank 19 and the suction line 20 can interact both with a bypass expansion tank 28 without air space 29 and with a filler neck 21' without air space.
  • the pressure relief valve 17 in FIG. 2 has the same function as in FIG. 1. However, in FIG. 2 it is not controlled directly, but rather via the outflow line 18 by the excess pressure in the cooler flow water tank 7.
  • the throttle 26 ' is arranged parallel to the pressure relief valve 17 in the cover 27 such that the pressure drop in the throttle 26' cannot affect the function of the pressure relief valve 17.
  • the outflow line 18 thus also acts as a control line for the pressure relief valve 17 and as a ventilation line for the filling and operating ventilation in the filler neck 21 '.
  • a piston 32 acting as a servomotor is arranged in the cover 27 of the filler neck 21 'instead of a further pressure relief valve 24.
  • the piston 32 is acted upon by the overpressure in the cooler supply water tank 7 through the outflow line 18, which is only effective as a control and ventilation line.
  • a push rod 32 'transmits the control movement of the piston 32 to the pressure relief valve 17.
  • the effective cross sections of the piston 32 and the pressure relief valve 17 are matched with the valve spring 24' of the pressure relief valve 17 such that the pressure relief valve is at about 2 bar overpressure on the suction side 16, for example the coolant pump 3 is opened directly by this overpressure, while it is at about 1 bar overpressure on the suction side 16 and at the same time about 2 bar overpressure in the cooler flow line.
  • Water box 7 is actuated by the predominant compressive force of the piston 32 via the push rod 32 '. In this way, when the machine 1 is at a standstill or idling and thus there is no or only a low delivery head for the coolant pump 3, a static pressure of approximately 2 bar is made available in the entire cooling circuit for the post-heating process with temperature and pressure rise against boiling in the machine.
  • the pressure curve in the cooler flow water tank 7 which is subjected to a relatively high local overpressure is likewise limited to the dynamically effective maximum value of approximately 2 bar.
  • Lower overpressure values occur on the suction side 16 of the coolant pump and at all cooling circuit points which are downstream of the cooler flow water tank 7. With a maximum pressure difference of about 1 bar between the suction side 16 and the cooler flow water tank 7, the overpressure on the suction side 16 does not fall below about 1 bar, so that the boiling pressure falls below the usual maximum temperatures of about 120 ° C. at this point cannot occur.
  • the filler neck 21 ' is designed as a one-piece plastic molded part, to which a hose connection piece 34 and 35 for the outflow line 18 and for the overflow line 20' or suction line 20 are molded.
  • the outflow line 18 opens into a narrower lower cylindrical part 36 of the filler neck inner wall 37, to which an annular groove 38 of the cover 27 which is sealed on both sides is assigned.
  • the overflow or suction line 20 'or 20 opens into a further upper cylindrical part 39, which with an upper space of the cover 27 outside the pressure and vacuum valves 17 and 22nd connected is.
  • the cover 27 is designed as a two-part glued or welded plastic molding. It has in addition to the holes and communication holes for the pressure relief valve 24 with valve spring 24 'and the spring sleeve 4 0, for the piston 32 and the corresponding final section of the effective as a control line discharge line 18 and the negative pressure valve 21 includes a cylindrical air separation chamber 41, close to the a Vent hole 26 "as the corresponding throttle 26 'in Fig. 3 opens tangentially. The resulting gyro flow during operation favors the separation of the residual air carried in the ventilation flow.
  • a locking device 42 is shown schematically, which locks the cover 27 against dangerous opening when there is an overpressure in the cooling circuit. It consists of a locking piston or the like, which holds a locking pin in engagement with a ribbed, toothed or similarly configured area of the inner wall of the filler neck 21 '.
  • the blocking effect increases with increasing overpressure and complicates or prevents inadvertent opening of the cover 27 with an expected hot water or steam leak and with the risk of fire or scalding injuries to the handling person.
  • the locking device 42 consists of a coupling 43 which connects the cover 27 in the absence or low overpressure in the filler neck 21 'with its turning handle 44 and releases this connection from a certain overpressure.
  • the clutch 43 consists of a bow spring 45 which interacts with teeth 46 and 47 on the cover 27 and on the rotary handle 44.
  • a pressure pin 40 'of the spring sleeve 40 of the cover 27 is moved by the action of the excess pressure inside the expansion tank 28 together with the attached inner parts of the cover 27 relative to the filler neck 21' and thereby the clutch 43 by jerky engagement or disengagement Bow spring 45 actuated in or out of the toothing 46.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Closures For Containers (AREA)
EP83106971A 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne Expired EP0100917B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE8585102118T DE3374143D1 (en) 1982-07-15 1983-07-15 Cooling system for internal-combustion engines

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 Child Applications (2)

Application Number Title Priority Date Filing Date
EP85101659.2 Division-Into 1983-07-15
EP85102118.8 Division-Into 1983-07-15

Publications (2)

Publication Number Publication Date
EP0100917A1 true EP0100917A1 (fr) 1984-02-22
EP0100917B1 EP0100917B1 (fr) 1986-10-01

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 Before (1)

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

Family Applications After (1)

Application Number Title Priority Date Filing Date
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) ES524135A0 (fr)

Cited By (3)

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FR2740830A1 (fr) * 1995-11-08 1997-05-09 Journee Paul Sa Bouchon de circuit de refroidissement de vehicule automobile muni d'un dispositif de degazage
FR2741132A1 (fr) * 1995-11-15 1997-05-16 Journee Paul Sa Dispositif d'obturation d'un circuit de refroidissement muni de moyens perfectionnes d'etancheite

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3716555A1 (de) * 1987-05-18 1988-12-08 Bayerische Motoren Werke Ag Befuell-, entlueftungs- und drucksteuer-vorrichtung fuer den fluessigkeits-kuehlkreis von kraft- und arbeitsmaschinen, insbesondere brennkraftmaschinen
FR2740830A1 (fr) * 1995-11-08 1997-05-09 Journee Paul Sa Bouchon de circuit de refroidissement de vehicule automobile muni d'un dispositif de degazage
FR2741132A1 (fr) * 1995-11-15 1997-05-16 Journee Paul Sa Dispositif d'obturation d'un circuit de refroidissement muni de moyens perfectionnes d'etancheite

Also Published As

Publication number Publication date
EP0100917B1 (fr) 1986-10-01
EP0157167A1 (fr) 1985-10-09
DE3226508C2 (de) 1985-12-12
ES8404010A1 (es) 1984-04-16
EP0163006A1 (fr) 1985-12-04
EP0157167B1 (fr) 1987-10-21
DE3366593D1 (en) 1986-11-06
JPH071005B2 (ja) 1995-01-11
DE3374143D1 (en) 1987-11-26
DE3226508A1 (de) 1984-01-26
US4510893A (en) 1985-04-16
ES524135A0 (es) 1984-04-16
JPS5923029A (ja) 1984-02-06

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