EP0520135B1 - Überdruckventileinrichtung für den Kühlkreislauf einer flüssigkeitsgekühlten Brennkraftmaschine - Google Patents

Überdruckventileinrichtung für den Kühlkreislauf einer flüssigkeitsgekühlten Brennkraftmaschine Download PDF

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Publication number
EP0520135B1
EP0520135B1 EP92101780A EP92101780A EP0520135B1 EP 0520135 B1 EP0520135 B1 EP 0520135B1 EP 92101780 A EP92101780 A EP 92101780A EP 92101780 A EP92101780 A EP 92101780A EP 0520135 B1 EP0520135 B1 EP 0520135B1
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EP
European Patent Office
Prior art keywords
valve
piston
pressure
pressure control
arrangement according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92101780A
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German (de)
English (en)
French (fr)
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EP0520135A1 (de
Inventor
Hartmut Lindner
Armin Dipl.-Ing. Müller (BAMB)
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.)
Laengerer and Reich GmbH and Co
Original Assignee
Laengerer and Reich GmbH and Co
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.)
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Publication of EP0520135A1 publication Critical patent/EP0520135A1/de
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Publication of EP0520135B1 publication Critical patent/EP0520135B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01P3/00—Liquid cooling
    • F01P3/22—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point
    • F01P3/2207—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point characterised by the coolant reaching temperatures higher than the normal atmospheric boiling point
    • 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
    • F01P11/029—Expansion reservoirs

Definitions

  • the invention relates to a pressure relief valve device for the cooling circuit of a liquid-cooled internal combustion engine of the type defined in the preamble of claim 1.
  • a known pressure relief valve device (DE-A1-34 22 705), the pressure relief valve is combined in a single screwable screw directly onto the filler neck of the expansion tank Element, on the one hand, a pressure relief valve to limit the operating pressure and, on the other hand, a pressure relief valve to limit the maximum pressure to prevent damage to the cooling system and loss of coolant, in a single valve with a single valve piston, which has an opening stage, an adjoining throttle stage and an adjoining further one Can pass through the opening step when axially loaded by axial displacement.
  • a known pressure relief valve device has proven itself. It is extremely simple, inexpensive and consists of only a few inexpensive components.
  • valve piston contains an inner piston inside, between which and the valve piston axial channels are formed, which allow passage, which by means of a ring shoulder on the inner piston, which is on a valve seat of the outer valve piston sits and is pressed against it by means of the return spring, is controllable and can be released to the environment or to the container.
  • the inner piston can be designed as a hollow piston, the piston crown of which forms that of the outer valve piston and serves as an abutment for the return spring, which is supported at one end on this inner piston and at the other end on the closure cover, thus for the valve piston and the one located therein Inner piston a single return spring is provided.
  • the known design is a change in the characteristic of the inner piston, for example a change in the opening point, the throughput in the open state or the like. Without at the same time with accompanying change in the characteristic of the valve piston forming the pressure relief valve, it is difficult to access.
  • a pressure relief valve device of the type mentioned at the outset is known (US Pat. No. 2,732,971, FIG. 5), on the closure cover of which a valve piston is held and guided, which is supported by means of a support on the cover and on the valve piston Return spring is pressed against a valve seat when screwing on the cover.
  • the closure cap is screwed onto a filler neck attached to a container, in the lower area of which the valve seat for the valve piston on the container side is formed.
  • the valve piston is guided on a bolt that is fixed to the cover.
  • a disk-shaped inner piston Arranged inside the valve piston is a disk-shaped inner piston, on which a return spring acts axially, which is supported at one end on the inner piston and at the other end on the upper part of the valve piston.
  • the inner piston is pressed with a lower end face against a valve seat formed on the valve piston.
  • the lower part of the valve piston has an inner ring part which forms this lower valve seat with an upwardly projecting annular bead.
  • the valve piston is provided with a second valve seat, which is formed from an upper annular bead projecting downwards. Both ring beads are formed on ring inserts which are firmly connected to the approximately hat-shaped valve piston.
  • the inner piston is only loaded by its return spring but is not guided. In a first pressure stage, the inner piston sits on the assigned lower valve seat of the valve piston and is in the closed position.
  • valve seat surface assigned to the valve piston is provided on the container side and is formed on a fixed part of the filler neck, the return spring of the valve piston is pressed onto the filler neck when the closure cap, which carries the pressure relief device, is screwed on, which thus already has an undefined, more or less, in the screwed-on state lost a large work area.
  • the closure cap which carries the pressure relief device
  • the tension of this return spring is changed when screwing on. This means that the valve has no reproducible opening pressure with regard to its valve piston and the latter cannot be set to reproducible values.
  • the invention has for its object to improve a pressure relief valve device of the type mentioned in the preamble of claim 1 in such a way that it quickly and easily with respect to the operating pressure controlling the inner piston a change in the characteristic and adaptation to the desired values is accessible without changing the characteristic of the pressure relief valve formed by the valve piston, while at the same time a clear separation between the first and second pressure stages should be achievable on the valve side.
  • the object is achieved according to the invention in a pressure relief valve device of the type defined in the preamble of claim 1 by the features in the characterizing part of claim 1.
  • the characteristic of this operating pressure controlling pressure relief valve can be adapted and changed relatively quickly and easily to the respective individual wishes of the user.
  • the spring characteristics of the return spring of the inner piston can be changed, thereby changing the opening and closing points of the inner piston and adapting them to existing needs.
  • the throughput passing through the passage between this and the valve piston can also be changed relatively easily and without problems and adapted to existing requirements.
  • valve seat assigned to the valve piston is part of the guide sleeve and thus part of the valve, the valve piston acted upon by the return spring is always pressed against the valve seat with the same force.
  • the spring tension of the return spring is therefore always the same, regardless of whether the cap carrying the valve is unscrewed or screwed onto the filler neck. This ensures that the return spring has the same spring tension regardless of the screw-in depth when screwing onto the filler neck, so that the valve can be adjusted to a reproducible opening pressure via the spring preload of the return spring of the valve piston.
  • a pressure relief valve device is known (DE-A1- 32 11 449), which automatically opens to the environment in two pressure levels of different heights, in one level at operating pressure and in another level at increased pressure, and has two nested valves , namely a valve responsible for normal operating pressure and also a safety valve responsible for positive pressure.
  • the valve controlling the operating pressure has an inner piston which is guided in the safety valve against its own return spring and is normally pressed into the closed position and does not open any passage. If a first pressure level is exceeded, the inner piston is moved and opened in the opening direction. If the pressure that causes this opening is exceeded, however, the inner piston remains in the open position, so that there is a risk of ejection of coolant if the pressure suddenly increases.
  • the pressure relief valve device shown in the drawings is intended for the cooling circuit of a liquid-cooled internal combustion engine and is intended to limit the pressure to an operating pressure, e.g. in the order of magnitude of 0.6 bar, and when the internal combustion engine is switched off, a pressure limitation to an overpressure which is higher than that, e.g. in the order of magnitude of 1.2 bar, with the pressure relief device starting from an intermediate pressure range, e.g. in the order of magnitude from 0.8 bar until reaching the second pressure stage, e.g. 1.2 bar, should remain closed.
  • the pressure relief valve device is designed as a two-stage pressure relief valve 10, which is integrated in an approximately cap-like closure cover 11, which has an integral cylinder neck 13 on an upper cover part 12, which is screwed with an internal thread 14 onto the external thread 15 of a filler neck 16.
  • the filler neck 16 is firmly and tightly attached to an expansion tank 17, specifically where there is a certain air cushion 20 above the level 18 of the cooling liquid 19 in normal operation.
  • the expansion tank 17 and the filler neck 16 are e.g. made of plastic.
  • the expansion tank 17 is connected in a conventional manner to the cooling circuit of a liquid-cooled internal combustion engine.
  • the two-stage pressure relief valve 10 is able to operate at a first pressure level at operating pressure, e.g. when a pressure of about 0.6 bar is exceeded, and also when the pressure rises more comfortably in a subsequent second pressure level at a higher pressure, i.e. overpressure, e.g. in the order of magnitude above 1.2 bar , each open automatically to the environment or to a container and thus establish a connection between it and the expansion tank 17 for pressure reduction.
  • the two-stage pressure relief valve 10 is closed, so that in this area the interior of the expansion tank 17 to the environment or to one Container is tightly closed.
  • This tightness in this intermediate stage ensures that, in the case mentioned, a pressure increase up to the second pressure stage, for example in the order of magnitude above 1.2 bar, can take place, thus preventing any ejection and thus loss of the coolant from the cooling circuit.
  • the opening points in the first pressure level and in the second pressure level can be determined and set fairly precisely, as is the closing point after the first pressure level has been exceeded and a closing level lying between this and the second pressure level has been reached.
  • the two-stage pressure relief valve 10 is either, as shown, with its individual elements to be described loosely inserted into the filler neck 16 or, in another embodiment, not shown, held on the closure cap 11 and attached in such a way that it is screwed on and off with the closure cap 11 this forms a unity.
  • This training is advantageous, because then there is a complete part for screwing and unscrewing.
  • the connection of the elements of the two-stage pressure relief valve 10 on the closure cover 11 is done in a conventional manner, for example by means of a snap connection or in another positive and / or non-positive manner.
  • the two-stage pressure relief valve 10 has a cylindrical guide sleeve 21 within the filler neck 16. At least one valve piston 22 is accommodated within the guide sleeve 21, which is displaceably guided therein up and down.
  • a return spring 23 acts on the valve piston 22 in the form of a cylindrical coil spring, which is supported at one end on the valve piston 22 and at the other end on the cover part 12 of the closure cover 11.
  • the guide sleeve 21 carries, preferably in one piece with it, a radially inwardly projecting annular collar 24, which forms a valve seat 64 for the valve piston 22.
  • the annular collar 24 carries a molded sealing ring 25, which in cross section has the shape of an outwardly open lip ring with two sealing lips 26 and 27 in the upper region, which encompass the annular collar 24.
  • One sealing lip 26 extends beyond the valve seat 64 of the collar 24 and thus forms a seal in this area.
  • the other sealing lip 27 covers the downwardly facing annular end face 28 of the collar 24 and forms a vacuum compensation element there, which can lift down from the annular end face 28 and release openings 32 in the annular collar 24 when there is negative pressure within the compensating container 17, and against the pressure in the compensating container 17 if there is excess pressure Ring face 28 is pressed.
  • the valve piston 22 is pressed against the sealing lip 26 by means of the return spring 23. It can be acted upon at the end face in the area of the annular surface 29 by the pressure of the cooling liquid in the cooling circuit and thus in the interior of the expansion tank 17.
  • valve piston 22 On its outside, the valve piston 22 has a plurality of, for example six, axial channels 30 which are arranged at equal circumferential angular distances from one another and which open out freely at both ends. It goes without saying that axial channels of this type can instead be provided on the facing inner side of the guide sleeve 21 alone or in addition thereto.
  • the guide sleeve 21 has a collar 34 which is integral therewith and projects radially outwards. This forms a support surface 35 on its underside for placement on the free edge 36 of the filler neck 16, with the intermediary of a seal 37 to be arranged in between. consist of grooves or the like. Wells.
  • the closure cover 11 carries on the inside of its cover part 12 one or more axial projections which press onto the collar 34 of the guide sleeve 21 from above, the projection here being e.g. an annular web 43, as shown, is possible or instead webs, pins or the like.
  • On the inside of the cylinder neck 13 there are several, e.g. four channels 44, placed at equal circumferential angular distances from one another, are arranged in the form of grooves which open out at the free lower edge of the cylinder neck 13 with their end 45 there. In the upper region, the channels 44 are connected to one another in the vicinity of the upper cover part 12 and the web 43 via a circumferential inner annular groove 46 within the cylinder neck 13.
  • the annular groove 46 runs in the axial region of the radial channels 38, which end at the ends in the annular groove 46, so that a connection between the radial channels 30 of the valve piston 22, the interior of the guide sleeve 21 and the external environment through the radial channels 38, the annular groove 46 and the channels 44 is created.
  • the valve piston 22 is hollow on the inside. It contains at least one further inner piston 51 inside, which serves to limit the pressure in the first pressure stage.
  • the inner piston 51 is seated with an end-side ring part 52 on a valve seat 47 of the valve piston 22 and forms with a bottom part 53 a part of the end face acted upon by the pressure in the cooling circuit.
  • the valve piston 22 has a passage inside the ring portion 52 of the inner piston 51 and associated valve seat 47 of the valve piston 22 controllable, the other end of which communicates with the environment or a container.
  • the inner piston 51 is pressed by its own return spring 54 in the form of a cylindrical helical spring with its ring part 52 against the valve seat 47 of the valve piston 22 in the closed position and in this way kept closed in the first pressure stage, as shown in FIG. 1.
  • the inner piston 51 also has a second valve surface 55 which, when the coolant pressure rises above the opening pressure of the first pressure stage, e.g. when reaching about 0.8 bar, which results in a displacement of the inner piston 51 relative to the valve piston 22 against the action of the return spring 54 in the opening direction, can be pressed against a seat 48 of the valve piston 22 while closing the passage.
  • the inner piston 51 is designed as a shuttle valve body which, against the action of its own return spring 54 relative to the valve piston 22, between a first closed position, which is shown in FIG. 1, and which is assumed at a pressure of the cooling liquid below the first pressure level, between an open position, which is shown in FIG. 2 shows and which is taken when the first pressure level is exceeded, for example at a pressure of 0.6 bar, and is movable in a second closed position, which is shown in FIGS. 3 and 4, in which the coolant pressure maintains the pressure in the open position, for example of o , 6 bar, and which is, for example, 0.8 bar and greater.
  • the inner piston 51 can thus be moved from its closed position according to FIG.
  • the second valve surface 55 interacts with the seat surface 48, closing this end of the passage between the valve piston 22 and the inner piston 51, so that the pressure relief valve 10 in 3 is tightly closed.
  • this relative closed position between the inner piston 51 and the valve piston 22 is retained, but here the valve piston 22 is moved against the action of the return spring 23 into its open position, in which its end face 29 from the associated valve seat 64 Annular collar 24, here in particular from the sealing lip 26, is lifted off, so that a passage to the axial channels 30 and thus into the interior of the guide sleeve 21 is created in this area and pressure can be reduced in this way.
  • the inner piston 51 In this open position of the valve piston 22, the inner piston 51 is in the closed position relative to it.
  • the return spring 54 of the inner piston 51 is supported on the one hand on the valve piston 22 and on the other hand on the inner piston 51. It can be adjustable, as is illustrated, for example by means of an adjustable abutment part 56 which is held on the inner piston 51 or, as shown, on the valve piston 22.
  • the abutment part 56 consists, for example, of a threaded part which is adjustably held in a threaded bore 49 of the valve piston 22 and is designed, for example, as a threaded sleeve which is open at the bottom.
  • the return spring 54 is expediently friction-free or at least low-friction axially supported, for example via sliding elements, rolling elements or the like, not shown.
  • the second valve surface 55 of the inner piston 51 is arranged on the axial side of the inner piston 51 pointing in the opening direction and is designed as an axial surface.
  • the valve seat 48 of the valve piston 22 assigned to this valve surface 55 is also designed as an axial surface.
  • the two surfaces 55 and 48 which cooperate for control, in particular sealing in the closed position according to FIG. 3, thus, as axial surfaces, ensure reliable tightness in this closed position of the inner piston 51 and a pressure increase in the cooling system up to the second pressure level of e.g. 1.2 bar, which prevents damage to the internal combustion engine and coolant ejection.
  • the inner piston 51 is designed, for example, as a poppet valve. It has a valve plate 57 which forms axial valve surfaces 52 and 55 on its two axial sides, each of which has an associated valve seat with an axially opposing surface 47 and 48 of the valve body 22 forms, cooperates. Between each axial valve surface 52, 55 of the inner piston 51 on the one hand and the associated axial surface 47 or 48 of the valve piston 22 on the other hand, as the first exemplary embodiment according to FIGS. 1 to 4 shows, a sealing ring 58 or 59, for example an O-ring, can be used , be arranged, which is arranged on or in one of these surfaces.
  • the inner piston 51 ' differs from the first exemplary embodiment solely in that the sealing rings 58, 59 shown in the first exemplary embodiment can be omitted because the inner piston 51', in particular its valve plate 57 ', is made of sealing material, for example Plastic, rubber, hard rubber or the like., And therefore with its axial valve surfaces 52 ', 55' at the same time forms sealing surfaces and therefore sealing rings are unnecessary. Otherwise, the second exemplary embodiment according to FIG. 5 corresponds to the first in FIGS. 1 to 4.
  • the inner piston 51 is guided axially relatively displaceably within the valve piston 22.
  • the valve piston 22 is provided with a cylinder sleeve section 50, in which the inner piston 51 is axially displaceably guided by a guide part 60.
  • the guide part 60 can consist of axial projections, for example of two approximately axially opposite axial webs.
  • the guide part 60 is designed as a cylinder sleeve which strives in the opening direction of the valve plate 57, ie upwards in FIGS. 1 to 4, from the valve plate 57 and which contains passages 61 in the wall near the valve plate 57, which passages with the Inside the guide part 60, in particular the cylinder sleeve, in connection.
  • This interior is open to the interior of the valve piston 22.
  • the guide part 60 in particular that Cylinder sleeve, forms part of the passage of the valve piston 22.
  • the latter has at least one axial opening 39 which is connected to the interior of the guide part 60 of the inner piston 51 designed as a cylinder sleeve and to the interior of the guide sleeve 21 and opens out towards the latter.
  • the valve piston 22 can of course also have at least one radial opening.
  • the axial opening 39 of the valve piston 22 is formed by an axial passage in the abutment part 56, which, for example, is at the same time a tool engagement surface for the rotational adjustment of the abutment part 56, for example is designed as a hexagon socket surface.
  • the spring stiffness of the return spring 23 acting on the valve piston 22 is greater than the spring stiffness of the return spring 54 acting on the inner piston 51. Also adjustable return spring 23 is set so that the valve piston 22 is then moved into the open position shown in Fig. 4 when the pressure of the coolant exceeds the second pressure level, e.g. is greater than 1.2 bar.
  • the valve piston 22 has an approximately cup-shaped housing part 40, in which the inner piston 51, in particular its valve plate 57, is accommodated and displaceable while leaving a radial annular space 62 in between.
  • the cross section of the passage which is formed between the inner piston 51 and the valve piston 22 and, in the open position of the inner piston 51 according to FIG. 2, enables the pressure to be reduced through the interior of the valve piston 22, can be changed to change the throughput, for example by changing the cross section of the annular space 62.
  • This enables quick and easy adaptation to the desired opening points and Closing points of the inner piston 51 possible.
  • the change in cross-section of the annular space 62 can take place, for example, by changing the diameter of the valve plate 57 or the inside diameter of the approximately cup-shaped housing part 40.
  • the approximately pot-shaped housing part 40 is adjoined by a cover part 33, which can thus be integrally or firmly and tightly attached to it and which carries the cylinder sleeve section 50 for guiding the guide part 60 and which also carries the axial seat surface 48 on the end face facing the valve plate 57 , which is assigned to the axial second valve surface 55.
  • the bottom 31 of the cup-shaped housing part 40 contains an opening 81 which can be controlled by the valve plate 57.
  • the cross section of the opening 81 can be changed to change the characteristic of the pressure relief valve 10, e.g. by means of attachable perforated diaphragms or the like.
  • the bottom 31 of the valve piston 22 can be subjected to the pressure of the cooling liquid on the axial side facing away from the valve plate 57, including the surface area of the valve plate 57 which is located in the area of the opening 81.
  • the described valve piston 22 and / or the inner piston 51 can be formed from plastic.
  • the expansion tank 17 has a certain air cushion 20 above the level 18.
  • This liquid level can correspond to a switched off internal combustion engine in the cold state.
  • the pressure in the expansion tank 17 gradually increases as a result of the cooling liquid 19 being heated.
  • this operating pressure has reached a certain excess pressure, for example 0.6 bar, the force acting on the inner piston 51 overcomes that of the return spring 54, so that the inner piston 51 relative to the still closed valve piston 22 into the open position shown in FIG. 2 is moved up by moving, the axial valve surface 52 of the valve plate 57 thus lifts off the valve seat 47 and an opening for the pressure reduction is created there.
  • the pressure of the cooling liquid can thus equalize through the opening 81, the annular space 62, through the passages 61, through the axial opening 39, through the interior of the guide sleeve 21 and from this to the outside, since a connection of the interior of the Expansion tank 17 is created with the environment. Due to this connection of the interior of the expansion tank 17 with the environment, a further increase in pressure during operation is avoided. If, on the other hand, the pressure would continue to rise and, for example, would exceed the point provided by the return spring 54, which ensures the opening position of the inner piston 51, for example, would rise to 0.8 bar, this results in a displacement of the inner piston 51 into the closed position according to FIG. 3.
  • the inner piston 51 is first pressed against the force of its return spring 54 into the open position according to FIG. 2, in which passage is made possible and pressure can be reduced.
  • a further pressure increase for example up to 0.8 bar, has shifted the inner piston 51 into the closed position according to FIG 3 results. If the pressure rises further than 0.8 bar, the inner piston 51 and the valve piston 22 remain in the closed position.
  • a further rapid pressure increase for example up to a value of 1.2 bar
  • the inner piston 51 is shifted into the closed position according to FIG. 3 and the valve piston 22 is shifted upwards against the action of the return spring 23 into the open position according to FIG. 4.
  • the interior of the expansion tank is directly connected to the atmosphere via the axial channels 30, the annular groove 46 and the channels 44. This second pressure stage is selected so that damage to the cooling system of the internal combustion engine is avoided.
  • the pressure relief valve 10 is simple, compact, has small dimensions and consists of simple, inexpensive parts, e.g. by rotating inexpensive to produce rotary parts, for which otherwise inexpensive series parts can also be used. It is also advantageous that by changing the characteristics of the inner piston 51, the opening and closing points of the inner piston 51 can be quickly and easily adjusted to the respective requirements. A change in the characteristic, e.g. of the throughput in the open position between the inner piston 51 and the valve piston 22 is possible with simple means for adaptation to the respective application.
  • the inner piston 51 ensures reliable tightness in its second sealing position according to FIG. 3 and enables an increase in pressure in the cooling system to the second pressure level, e.g. up to 1.2 bar, which prevents coolant ejection.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
EP92101780A 1991-06-26 1992-02-04 Überdruckventileinrichtung für den Kühlkreislauf einer flüssigkeitsgekühlten Brennkraftmaschine Expired - Lifetime EP0520135B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4121086A DE4121086A1 (de) 1991-06-26 1991-06-26 Ueberdruckventileinrichtung fuer den kuehlkreislauf einer fluessigkeitsgekuehlten brennkraftmaschine
DE4121086 1991-06-26

Publications (2)

Publication Number Publication Date
EP0520135A1 EP0520135A1 (de) 1992-12-30
EP0520135B1 true EP0520135B1 (de) 1994-09-07

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EP92101780A Expired - Lifetime EP0520135B1 (de) 1991-06-26 1992-02-04 Überdruckventileinrichtung für den Kühlkreislauf einer flüssigkeitsgekühlten Brennkraftmaschine

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EP (1) EP0520135B1 (enrdf_load_stackoverflow)
DE (2) DE4121086A1 (enrdf_load_stackoverflow)

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Publication number Priority date Publication date Assignee Title
DE19753592A1 (de) * 1997-12-03 1999-06-10 Heinrich Reutter Verschlußdeckel
US7152555B2 (en) 2001-02-20 2006-12-26 Volvo Trucks North America, Inc. Engine cooling system
US6532910B2 (en) 2001-02-20 2003-03-18 Volvo Trucks North America, Inc. Engine cooling system
KR101280397B1 (ko) 2004-09-20 2013-07-01 메델라 홀딩 아게 배출 밸브를 갖는 멤브레인 펌프
CN101858450A (zh) * 2010-06-13 2010-10-13 上海乐高压缩机有限公司 一种安全阀
CN103363170B (zh) * 2012-04-06 2015-08-19 重庆博张机电设备有限公司 压力调节阀
CN103032612B (zh) * 2012-12-12 2015-04-08 中国航天科技集团公司第六研究院第十一研究所 一种双开启压力双排量安全阀
US20240050314A1 (en) * 2020-12-17 2024-02-15 Hoffmann-La Roche Inc. Closure system and kit

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US2732971A (en) * 1956-01-31 Radiator caps
US2147727A (en) * 1936-09-03 1939-02-21 Gen Motors Corp Radiator cap
DE3211449C2 (de) * 1982-03-27 1984-06-20 Daimler-Benz Ag, 7000 Stuttgart Kühlerverschluß
FR2529951A1 (fr) * 1982-07-08 1984-01-13 Renault Vehicules Ind Dispositif de pressurisation du circuit de refroidissement d'un moteur thermique
DE3422705A1 (de) * 1984-06-19 1985-12-19 Kühlerfabrik Längerer & Reich GmbH & Co KG, 7024 Filderstadt Ueberdruckventileinrichtung fuer den kuehlkreislauf einer fluessigkeitsgekuehlten brennkraftmaschine
DE8903708U1 (de) * 1989-03-23 1990-07-26 Blau KG, 4018 Langenfeld Verschlußdeckel für einen Behälterstutzen

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Publication number Publication date
EP0520135A1 (de) 1992-12-30
DE4121086C2 (enrdf_load_stackoverflow) 1993-05-19
DE59200458D1 (de) 1994-10-13
DE4121086A1 (de) 1993-01-14

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