EP0100917B1 - 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
EP0100917B1
EP0100917B1 EP83106971A EP83106971A EP0100917B1 EP 0100917 B1 EP0100917 B1 EP 0100917B1 EP 83106971 A EP83106971 A EP 83106971A EP 83106971 A EP83106971 A EP 83106971A EP 0100917 B1 EP0100917 B1 EP 0100917B1
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EP
European Patent Office
Prior art keywords
pressure
over
coolant
valve
cooling circuit
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
Application number
EP83106971A
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German (de)
English (en)
Other versions
EP0100917A1 (fr
Inventor
Erwin Dipl.-Ing. Schweiger
Erwin Dipl.-Ing. Starmühler
Axel Dipl.-Ing. Temmesfeld
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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
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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 known to fill the filler neck and thus also the pressure and vacuum valves contained in the filler neck cover either in the flow area of the cooler between the cooling jacket of the internal combustion engine and the cooler - Arrange the flow water box or in the return area of the cooler between the cooler return water box and the suction side of the coolant pump (Technical Review No. 46, 1971, page 9).
  • the pressure relief valve is located at a point in the cooling circuit at which its function accordingly occurs and is at least approximately the highest pressure during operation of the machine and is limited. At this point, however, the vacuum valve cannot fully serve its purpose, because the lowest pressure in the cooling circuit occurs on the suction side of the coolant pump during operation and therefore cannot be used by the vacuum valve.
  • the pressure relief valve is due to the aforementioned relationships at a point where it cannot perform its function, while the vacuum valve is fully effective.
  • the object of the invention is to develop the cooling circuit of the known type of claim 1 so that the favorable summary of the pressure and vacuum valves in the filler cap can be maintained and still both valves on the one hand at the highest overpressure occurring in the flow area and on the other hand at the lowest negative pressure that occurs in the return area has a functional effect.
  • the invention provides the features according to the characterizing part of patent claim 1.
  • the separate control of the pressure and vacuum valves is achieved with the low construction costs of a further separate control room in the filler neck cover and a further line connection.
  • Claims 2 to 16 contain preferred refinements and developments of the invention.
  • the features of claims 2 and 3 contain the additional use and design of the line connection acting as an overpressure control line to the overpressure valve as an outflow line for the coolant to be discharged from the overpressure valve or as a continuously effective throttled vent line with a throttle connected in parallel with the overpressure valve. that secures the supply of the pre-opening pressure to the pressure relief valve without pressure drop.
  • a ventilation line that is often present in known cooling systems and is connected to the flow area.
  • Claims 4 and 5 contain preferred configurations of the invention for the arrangement of the throttle for the ventilation line.
  • the features of claim 6 provide to combine further control elements for the cooling circuit in the filler neck and filler neck cover.
  • the features of claim 7 include the arrangement and dimensioning of a further pressure relief valve, which ensures that at low engine speeds and therefore low pump delivery capacity, a lower overpressure is built up in the entire cooling circuit than is determined by the pressure relief valve controlled by the flow area according to claim 1. On the one hand, this reduces the pressure load on the cooling circuit during part-load operation of the machine and achieves the venting effect by opening the additional pressure relief valve by pushing out any air that may have accumulated at a lower pressure without, on the other hand, impairing the advantageous limitation of the coolant pressure by the pressure relief and vacuum relief valves.
  • claim 8 contain a structurally advantageous summary of the two pressure relief valve functions according to the training according to claims 1 and 7 in a double valve.
  • the features of claim 9 contain a pressure control valve which is remotely controlled from the supply pressure and which controls the coolant from the pressure region of the suction side of the coolant pump. which also promotes ventilation of the cooling system.
  • a single pressure relief valve is actuated by both pressure areas, namely the flow area and the return area, thus combining the functions of two pressure relief valves in it.
  • the features of claim 11 contain a coordination of the two overpressure opening values for the overpressure valve according to claim 10.
  • the features of claim 12 include the structural design of a cooling circuit with a pressure relief valve according to claims 10 or 11 in connection with a particularly effective ventilation device.
  • the features of claims 13 and 14 further develop the objects according to claims 10 to 12 such that according to claim 15, in connection with a bypass expansion tank with expansion air space through the pressure relief valve and the vacuum valve, only portions of the air space content - And are derived or 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.
  • Claims 16 and 17 contain features for the dimensionally reliable dimensioning of the overpressure opening value for an overpressure valve controlled by the flow area, which at the same time excludes higher overpressure values which occur with known return area control of an overpressure valve due to an aging-related increase in the cooler flow resistance.
  • An internal combustion engine 1 contains a cooling jacket 2, indicated by an arrow, into which the coolant is conveyed under pressure by means of a coolant pump 3.
  • a flow line 5 is connected 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 connected to the cooler flow water tank 7 by means of an outflow line 18 in order to be connected to an expansion tank 19 open to the atmosphere by means of a suction line 20.
  • the expansion tank 19 is equipped with a slotted sealing disk 19 'in its filling opening.
  • the pressure relief valve 17 can alternatively be connected to the flow 5 or to the cooling jacket 2 of the machine.
  • the expansion tank 19 is connected to the suction side 16 of the coolant pump 3 via the suction line 20 and a vacuum valve 21, which preferably acts as a non-return valve.
  • the suction line 20 opens out from the interior of the expansion tank 19 near the floor.
  • One or more relatively large-area fine screens 22 and 23 in the cooler 6 and in the expansion tank 19 prevent the valves from becoming leaky due to dirt particles entrained by the coolant.
  • the pressure relief valve 17 and the vacuum relief valve 21 are combined in a filler neck 21 'to form a structural unit.
  • a further pressure relief valve 24 is arranged in the filler neck 21 ′ and is effective via the suction line 20 directly on the suction side 16 of the coolant pump 3 and thus on its suction pressure.
  • the outflow line 18 opens into the interior of the filler neck 21 'as a vent line by means of a throttle 26 for reducing the pressure difference between its connections on the one hand on the flow 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, which controls a display circuit when air accumulates in the filler neck 21 ', irrespective of whether the reservoir 19 still contains an optically recognizable reserve quantity or not.
  • the pressure relief valves 17 and 24 are actuated by their respective control chambers 17 'and 2T in the opposite opening directions and in the likewise opposite closing directions by a single valve spring 24'.
  • Different overpressure opening values of, for example, 2 or 1.5 bar are achieved by an inversely proportional dimensioning of the opening cross sections of the two valves.
  • the respective connection of the outflow line 18 and the expansion tank 19 via the suction line 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 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 environment in the entire cooling circuit before the start pressure and on the other hand builds up an excess pressure in the coolant pump 3 downstream cooler sections, cooling jacket 2, flow 5, short circuit 8, cooler 6 and return 12. 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.
  • the Opening value of the pressure relief valve 17 of, for example, 2 bar or of the pressure relief valve 24 of, for example, 1.5 bar was 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 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 that builds up between standstill or idling speed and maximum speed of the machine at the connection point of the pressure relief valve 17. At low engine speeds, the pressure relief valve 24 responds, which is connected to the suction side 16 of the coolant pump 3 via the control chamber 27 'and the suction line 20. Only in the range of the maximum speed of the machine is the overpressure opening value of the overpressure valve 17 connected via the control chamber 17 ′ and the outflow line 18 to the cooler flow water tank 7.
  • an internal pressure from the ambient pressure up to the opening pressure value of the pressure relief valve 17 and during operation of the machine 1 in the cooling jacket 2 and in the feed line 5 as well as in the short circuit 8 can therefore result in an overpressure depending on the flow resistance of the cooling circuit.
  • a pressure overload of the cooling circuit components does not exist due to this relatively low, exclusively statically effective overpressure.
  • the higher overpressure determined by the pressure relief valve 17 is limited to the operation of the machine 1 at relatively high engine speeds, at which the pressure difference between the suction side 16 of the coolant pump 3 and the connection point of the pressure relief valve 17 is greater than the difference in the pressure opening values between the pressure relief valves 17 on the one hand and 24 on the other. This higher overpressure is thus limited to a relatively small proportion of the operating time of the machine, especially when driving vehicles.
  • the durability of the cooling circuit components, in particular the cooler and the hose lines, is thereby favored.
  • the cooling circuit When the machine starts operating after the cooling circuit has been filled with coolant, the cooling circuit also begins to be vented automatically from residual air components which remain at various points during filling ben or get into the cooling circuit during operation, for example through the seals of the coolant pump 3, which are briefly loaded with negative pressure during the cold start. 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.
  • Venting also occurs when the overpressure opening value of approximately 2.0 bar of the overpressure valve 17 is reached in the cooler flow water tank. However, no upstream residual air fractions are removed, but only residual air fractions directly contained or dissolved in the emerging coolant are discharged into the expansion tank 19 and thus into the atmosphere.
  • a further venting and pushing out of coolant with residual air from the filler neck 21 'into the expansion tank 19 through the pressure relief valve 24 also occurs whenever, after a warm-up operating time with a high engine speed of approximately 5,000 to 6,000 / min and a high pressure difference of about 1 bar between the cooler flow water tank 7 and the suction side 16 of the coolant pump 3, the engine speed drops considerably, in particular to the idling speed.
  • the overpressure opening value of about 2 bar of the overpressure valve 17 is namely at least approximately reached at first and, in contrast, the overpressure opening value of about 1.5 bar of the further overpressure valve 24 is substantially undercut.
  • 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.
  • the configuration of the cooling circuit according to FIG. 2 largely corresponds to that according to FIG. 1 both in terms of structure and function. Only the filler neck 21 'is alternatively combined with a secondary flow expansion tank 28 with air space 29 or designed as a filler neck 21' without air space 29 (shown in dashed lines).
  • the evaporation line 20 'opening into 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 secondary flow expansion tank 28 without air space 29 and with a filler neck 21' without air space.
  • a single pressure relief valve 24 and a piston 32 acting as a servomotor on this are arranged in the cover 27 of the filler neck 21 '.
  • the piston 32 is acted upon by the excess pressure in the cooler flow water tank 7 by 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 24.
  • the effective cross sections of the piston 32 and the pressure relief valve 24 are matched to the valve spring 24' of the pressure relief valve 24 in such a way that the pressure relief valve is at about 2 bar pressure on the suction side 16, for example the coolant pump 3 is opened directly by this overpressure, while it is actuated by the predominant compressive force of the piston 32 via the push rod 32 'at about 1 bar overpressure on the suction side 16 and at the same time about 2 bar overpressure in the cooler flow water tank 7.
  • a static pressure of about 2 bar is made available in the entire cooling circuit when the machine 1 is at a standstill or when the coolant pump 3 is missing or has only a low delivery head for the reheating process with an increase in temperature and pressure against boiling in the machine.
  • the pressure curve in the cooler flow water tank 7, which is subject to a relatively high local overpressure, is likewise limited to the then effective maximum value of approximately 2 bar.
  • Lower overpressure values occur on the suction side 16 of the coolant pump 3 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 is connected to an upper space of the cover 27 outside the pressure and vacuum valves 17 and 22.
  • the cover 27 is designed as a two-part glued or welded plastic molding. It contains the pressure and vacuum valves 24 and 21 as well as the control chambers 17 'and 27' to the piston or to the diaphragm 32 of the servomotor for the pressure relief valve 24.
  • the cover 27 has holes and connection openings for the pressure relief valve 24 with valve spring 24 'and spring sleeve 40 for the last section 18 'of the outflow line 18 and for the vacuum valve 21 and for a cylindrical air separation space 41, into which a narrow vent hole 26' opens tangentially as the throttle 26 corresponding in FIG. 2.
  • the resulting gyro flow during operation favors the separation of the residual air carried in the ventilation flow.

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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)

Claims (17)

1. Circuit de refroidissement pour moteurs à combustion interne avec une pompe de fluide de refroidissement (3) disposée sur l'arrivée à la chemise de refroidissement (2) du moteur (1), cette pompe assurant dans la chemise de refroidissement (2), dans un radiateur (6), dans un thermostat (9), et dans leurs canalisations de liaison, entrée (5), retour (12) et dérivation (8), une circulation de fluide de refroidissement avec des chutes de pression, tandis qu'il est prévu dans un couvercle (27) de tubulures de remplissage, une soupape de surpression (17) et une soupape de dépression (21) s'ouvrant vers l'atmosphère, circuit de refroidissement caractérisé en ce que la soupape de surpression (17) et la soupape de dépression (21) sont commandées séparément, dans les chambres de commande respectives (17' ou bien 27') dans le couvercle (27) de la tubulure de remplissage, et par l'intermédiaire de canalisations de liaison respectives (gorges annulaires 31 et canalisation d'écoulement 18 ou bien tubulure de remplissage 21', récipient de compensation 28 et canalisation d'aspiration secondaire 20), d'une part, par la pression maximale du fluide de refroidissement dans la zone d'entrée (chemise de refroidissement 2, entrée 5 et caisse à eau d'entrée 7 du radiateur), et d'autre part, par la pression minimale du fluide de refroidissement dans la zone de retour (caisse à eau de retour 11 du radiateur, retour 12 et côté aspiration 16 de la pompe de fluide de refroidissement 3).
2. Circuit de refroidissement selon la revendication 1, caractérisé en ce que la seconde liaison par canalisations constitue également la canalisation d'évacuation (18) pour le fluide de refroidissement s'écoulant par la soupape de surpression (17).
3. Circuit de refroidissement selon la revendication 1, caractérisé en ce que
la seconde liaison par canalisations (canalisation d'évacuation 18) constitue en même temps une canalisation de désaération
qui est reliée à la zone de retour (caisse à eau de retour 11 du radiateur, retour 12 et côté aspiration 16 de la pompe de fluide de refroidissement 3) parallèlement à la soupape de surpression (17) par l'intermédiaire d'un étranglement (26) avec un emplacement de désaération (tubulure de remplissage 21') et par l'intermédiaire de la première liaison par canalisations (canalisation d'aspiration secondaire 20).
4. Circuit de refroidissement selon la revendication 3, caractérisé en ce que l'étranglement (26) débouche dans une tubulure de remplissage (21') qui est reliée au côté aspiration (16) de la pompe de fluide de refroidissement (3).
5. Circuit de refroidissement selon la revendication 4, caractérisé en ce que la tubulure de remplissage (21') fait partie d'un récipient de désaération et/ou d'un récipient de compensation de volume (28) avec une chambre pneumatique d'expansion (29).
6. Circuit de refroidissement selon la revendication 4 ou 5, caractérisé en ce que la tubulure de remplissage (21') et le couvercle (27) de la tubulure de remplissage, reçoivent à côté de la soupape de surpression (17), de la soupape de dépression (21), et de l'étranglement (26), également une soupape de désaération et/ou un commutateur à flotteur (21").
7. Circuit de refroidissement selon une des revendications 1 à 6, caractérisé en ce
qu'une autre soupape de surpression (24) est raccordée au côté aspiration (16) de la pompe de fluide de refroidissement (3),
la valeur d'ouverture en surpression de cette soupape dépassant la pression d'ébullition du fluide de refroidissement à la température la plus élevée admissible pour ce fluide de la différence de pression (environ de 0,2 à 0,6 bar) qui existe sur le côté aspiration (16) de la pompe de fluide de refroidissement (3) entre la puissance de refoulement minimale et maximale de cette pompe pour une vitesse minimale ou maximale du moteur (1).
8. Circuit de refroidissement selon la revendication 7, caractérisé en ce que
la soupape de surpression (17) et l'autre soupape de surpression (24) sont disposées co-axialement l'une par rapport à l'autre,
les sections transversales d'ouverture des deux soupapes (17 et 24) étant dimensionnées de façon inversement proportionnelle à leur valeur d'ouverture en surpression,
et les deux soupapes (17 et 24) étant maintenues fermées devant les sens inverses par un unique ressort de soupape (24').
9. Circuit de refroidissement selon une des revendications 1 et 3 à 7, caractérisé en ce que la soupape de surpression (24) comporte un moteur de réglage (piston ou membrane 32) qui est sollicité par la surpression dans la zone d'entrée (chemise de refroidissement 2, entrée 5, et caisse à eau d'entrée 7 du radiateur) par l'intermédiaire de la canalisation de commande (canalisation d'écoulement 18).
10. Circuit de refroidissement selon la revendication 9, caractérisé en ce qu'une soupape de surpression unique (24), commandée par la pression de fluide de refroidissement dans la zone de retour (caisse à eau de retour 11 du radiateur, retour 12 et côté aspiration 16 de la pompe de fluide de refroidissement 3), est actionnée aussi bien par la pression du fluide de refroidissement dans la zone d'entrée (chemise de refroidissement 2, entrée 5, et caisse à eau d'entrée 7 du radiateur), par l'intermédiaire de la canalisation de commande (canalisation d'écoulement 18) du moteur de réglage (piston 22 ou bien membrane), qu'également aussi directement par la pression du fluide de refroidissement dans la zone de retour (caisse à eau de retour 11 du radiateur, retour 12 et côté aspiration 16 de la pompe de fluide de refroidissement 3).
11. Circuit de refroidissement selon la revendication 10, caractérisé en ce que le moteur de réglage (piston 32 ou bien membrane) et la soupape de surpression (24) sont sélectivement raccordés l'un à l'autre en ce qui concerne leurs surfaces sollicitées par la pression et/ou les forces de leurs ressorts de fermeture, de façon que des valeurs d'ouverture par surpression identiques ou différentes de la zone d'entrée et de la zone de retour, provoquent l'ouverture de la soupape de surpression (24).
12. Circuit de refroidissement selon la revendication 10 ou 11 caractérisé en ce que :
- la membrane (32) ou le piston du moteur de réglage délimite une chambre de commande (17') ,
- la canalisation de commande (canalisation d'écoulement 18) débouche dans la chambre de commande (17)
- le moteur de réglage (membrane 32 ou piston) actionne par l'intermédiaire d'une tige de poussée (32') la soupape de surpression (24),
- cette soupape ferme une autre chambre de commande (27') et est disposée coaxialement par rapport à la tige de poussée (32') et à la membrane (32) ou bien au piston du moteur de réglage,
- cette autre chambre de commande (27") est reliée à l'espace interne de la tubulure de remplissage (21'), et la pression du fluide de refroidissement dans la zone de retour (caisse à eau de retour 11 du radiateur, retour 12, et côté aspiration 16 de la pompe de fluide de refroidissement 3) sollicitent directement la soupape de surpression (24).
13. Circuit de refroidissement selon une des revendications 10 à 12, caractérisé en ce que :
- la canalisation de commande (canalisation d'écoulement 18) débouche dans le couvercle (27) de la tubulure de remplissage par l'intermédiaire d'une gorge radiale (38) de ce couvercle,
- la tubulure de remplissage (21') comporte respectivement une tubulure de raccordement de tubes souples (34 et 35) pour la canalisation de commande (canalisation d'écoulement 18) et pour une canalisation de trop-plein (20')
- ces tubulures de raccordement débouchant dans une partie (36) de la paroi cylindrique interne (37) de la tubulure de remplissage au voisinage de la gorge annulaire (38) du couvercle (27) de la tubulure de remplissage ou bien dans la paroi cylindrique interne (37) d'un espace creux (39) se situant en dehors des soupapes (24 et 21) de la tubulure de remplissage (21') et du couvercle (27) de la tubulure de remplissage.
14. Circuit de refroidissement selon la revendication 13, caractérisé en ce que la canalisation de commande (canalisation d'écoulement 18) se termine à l'intérieur du couvercle (27) de la tubulure de remplissage selon un perçage d'étranglement (26') placé parallèlement au moteur de réglage et qui débouche tangentiellement dans une chambre cylindrique de séparation d'air (41) ouverte vers la chambre d'air (29).
15. Circuit de refroidissement selon la revendication 13 ou 14, caractérisé en ce que la tubulure de remplissage (21') fait partie d'un réservoir de compensation (28) comportant une chambre d'air (29) jouant le rôle de chambre d'expansion thermique et de compensation de pression.
16. Circuit de refroidissement selon une des revendications 1 à 15, caractérisé en ce que la soupape de surpression (17 ou bien 24), commandée par la pression du fluide de refroidissement dans la zone d'entrée (chemise de refroidissement 2, entrée 5, et caisse d'eau d'entrée 7 du radiateur), comporte une valeur d'ouverture à la surpression qui dépasse la pression d'ébullition de fluide de refroidissement pour une température maximale admissible de ce fluide sur le côté aspiration (16) de la pompe de fluide de refroidissement (3), d'au moins approximativement la même différence de pression qui intervient entre le côté aspiration (16) de la pompe de fluide de refroidissement (3) et le point de raccordement de la soupape de surpression (17 ou bien 24) lorsqu'on a, en pratique, la puissance maximale de refoulement de la pompe de fluide de refroidissement (3) alors que la soupape de radiateur (13) du thermostat (9) est complètement ouverte.
17. Circuit de refroidissement selon la revendication 16, caractérisé en ce que la soupape de surpression (17 ou bien 24) comporte une valeur d'ouverture à la surpression de 1,5 à 2,2 bars pour une température maximale admissible du fluide de refroidissement sur le côté aspiration (16) de la pompe de fluide de refroidissement (3) de 90 à 120 OC, pour une différence de pression entre le côté aspiration (16) de la pompe de fluide de refroidissement (3) et le point de raccordement de la soupape de surpression (17 ou bien 24) de 0,5 à 1,2 bar.
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
DE3226508 1982-07-15
DE3226508A DE3226508C2 (de) 1982-07-15 1982-07-15 Kühlkreis für Brennkraftmaschinen

Related Child Applications (2)

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EP85101659.2 Division-Into 1985-02-15
EP85102118.8 Division-Into 1985-02-27

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

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EP85102118A Expired EP0157167B1 (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
EP83106971A Expired EP0100917B1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement pour moteurs à combustion interne

Family Applications Before (2)

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
EP85101659A Withdrawn EP0163006A1 (fr) 1982-07-15 1983-07-15 Circuit de refroidissement à suspension pour des moteurs à combustion interne à refroidissement liquide

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Country Link
US (1) US4510893A (fr)
EP (3) EP0157167B1 (fr)
JP (1) JPH071005B2 (fr)
DE (3) DE3226508C2 (fr)
ES (1) ES524135A0 (fr)

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Also Published As

Publication number Publication date
JPS5923029A (ja) 1984-02-06
US4510893A (en) 1985-04-16
DE3374143D1 (en) 1987-11-26
DE3366593D1 (en) 1986-11-06
DE3226508A1 (de) 1984-01-26
DE3226508C2 (de) 1985-12-12
ES8404010A1 (es) 1984-04-16
EP0100917A1 (fr) 1984-02-22
EP0157167B1 (fr) 1987-10-21
ES524135A0 (es) 1984-04-16
JPH071005B2 (ja) 1995-01-11
EP0163006A1 (fr) 1985-12-04
EP0157167A1 (fr) 1985-10-09

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