CA2400891A1 - Pressure cap - Google Patents
Pressure cap Download PDFInfo
- Publication number
- CA2400891A1 CA2400891A1 CA002400891A CA2400891A CA2400891A1 CA 2400891 A1 CA2400891 A1 CA 2400891A1 CA 002400891 A CA002400891 A CA 002400891A CA 2400891 A CA2400891 A CA 2400891A CA 2400891 A1 CA2400891 A1 CA 2400891A1
- Authority
- CA
- Canada
- Prior art keywords
- valve body
- pressure
- cap according
- pressure cap
- interior
- 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.)
- Abandoned
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
- F01P11/0285—Venting devices
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- 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
- F01P11/0214—Mounting
- F01P2011/0228—Sealing
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
- Closures For Containers (AREA)
Abstract
A sealing cap (11) for openings on containers, especially on the radiators of motor vehicles, comprising an inner part (14) possessing at least one fluidic connection between the inside and outside of a container in addition to a valve arrangement (15) which is used to release or lock said fluidic connection. The valve arrangement (15) consists of a first and second valve body (17, 18) which can move back and forth. The first valve body (17) is pre-tensed by a first spring (22) in the direction of the inside of the container against a tight seat (24) on the second valve body (18) which is pressed against a second tight seat (32) on the inside of the cap (14). The first and second valve bodies (17, 18) can be lifted when a respective limiting value for pressure inside the container is exceeded, whereby the fluidic connection (50, 51)is released, between the inside and the outside of the container.In order to simplify the production and assembly of the sealing cap and achieve better hysteresis behavior, a third valve body (19) is arranged in the second valve body (18), between which valve body and the second valve body (18), a first fluidic connection (50) is embodied in the form of a throttle gap (47) between the inside of the container and the first valve body (17).
Description
t r Pressure Cap Description The present invention relates to a pressure cap for openings in tanks, in particular motor-vehicle radiators, according to the generic part of Claim 1.
In a pressure cap of this kind, which is known from DE
41 07 525 C1, the first and the second valve bodies are concentrically nested in each other, whereby the second valve body can be axially moved back and forth between two end positions limited by a sealing seat or an axially opposite sealing surface of the internal cap component, and whereby in rest position the first valve body is provided with spring-loaded support by the second valve body which is supported by the internal cap component. The sealing surface of the second valve body, which is supported by the sealing seat of the interior cap component, lies radially outside in relation to the sealing seat of the second valve body which supports the sealing surface of the first valve body. This results in the following two-step operating state for the reduction of overpressure: When a first threshold value of the interior tank pressure is exceeded, the radially exterior effective surface of the second valve body causes it to be lifted off the sealing seat of the interior cap component, which facilitates the reduction of overpressure via a first flow connection. As the second valve body is lifted off, the first valve body is lifted as well against the effect of its first pressure r
In a pressure cap of this kind, which is known from DE
41 07 525 C1, the first and the second valve bodies are concentrically nested in each other, whereby the second valve body can be axially moved back and forth between two end positions limited by a sealing seat or an axially opposite sealing surface of the internal cap component, and whereby in rest position the first valve body is provided with spring-loaded support by the second valve body which is supported by the internal cap component. The sealing surface of the second valve body, which is supported by the sealing seat of the interior cap component, lies radially outside in relation to the sealing seat of the second valve body which supports the sealing surface of the first valve body. This results in the following two-step operating state for the reduction of overpressure: When a first threshold value of the interior tank pressure is exceeded, the radially exterior effective surface of the second valve body causes it to be lifted off the sealing seat of the interior cap component, which facilitates the reduction of overpressure via a first flow connection. As the second valve body is lifted off, the first valve body is lifted as well against the effect of its first pressure r
-2-spring. If the interior tank pressure continues to rise, the second valve body is moved against the axially upper sealing surface of the interior cap component, which causes the first flow connection to close again, thus preventing the liquid medium, such as a coolant, to erupt. The second valve stage, which is represented by the first valve body, affects the safety function of the pressure cap in such a way that the first valve body is lifted off the second valve body if the internal tank pressure continues to rise and the safe threshold value is exceeded, causing a second flow connection between the interior and the exterior of the tank to open.
A disadvantage with this prior-art pressure cap is that the sealing seats and sealing surfaces of the two valve bodies and the interior cap component as well as the axial path of the second valve body must be adapted to each other with close tolerances. Furthermore, the individual components must be of a relatively complex design, which also applies to the installation of the components. Furthermore, the hysteresis behaviour in opening and closing of the flow connections) between pressure rise and pressure fall is unsatisfactory.
Also known from DE 197 53 592 Al is a pressure cap of the type named above, in which in rest position the first valve body is directly contiguous to a sealing seat of the interior cap component, and the second valve body, which in rest position is pressed by a first pressure spring of the first valve body against a second pressure spring, is in the first valve step, after the first threshold value of the interior tank pressure is i
A disadvantage with this prior-art pressure cap is that the sealing seats and sealing surfaces of the two valve bodies and the interior cap component as well as the axial path of the second valve body must be adapted to each other with close tolerances. Furthermore, the individual components must be of a relatively complex design, which also applies to the installation of the components. Furthermore, the hysteresis behaviour in opening and closing of the flow connections) between pressure rise and pressure fall is unsatisfactory.
Also known from DE 197 53 592 Al is a pressure cap of the type named above, in which in rest position the first valve body is directly contiguous to a sealing seat of the interior cap component, and the second valve body, which in rest position is pressed by a first pressure spring of the first valve body against a second pressure spring, is in the first valve step, after the first threshold value of the interior tank pressure is i
-3-exceeded, pressed against another axially opposite sealing seat on the interior cap component when the second threshold value is reached, whereby the first valve body is lifted off its sealing seat on the interior cap component. This determines the first flow connection between the two valve seats on the interior cap component on one side and the first or second valve body on the other side, and it is closed first by the first valve body and then by the second valve body. When the point of safe overpressure is exceeded, the first valve body is lifted axially by a thus affected vacuum valve body which establishes the second flow connection by lifting off the second valve body. In this case, it is not as critical to adapt the individual components to each other with close tolerances, but the design of the interior cap component is somewhat more complex.
It is the objective of the present invention to create a pressure cap of the type mentioned above, which is simpler to manufacture and easier to install while it has a better hysteresis behaviour.
This objective is achieved with a pressure cap of the type mentioned above which has the characteristics named in Claim I. _ With the measures according to the invention it can be achieved that the tolerances required in manufacturing the individual components and adapting them to each other do not have to be as close, and that assembly can be quicker. The hysteresis behaviour is improved as the result of a throttle gap arranged ahead of the seal.
It is the objective of the present invention to create a pressure cap of the type mentioned above, which is simpler to manufacture and easier to install while it has a better hysteresis behaviour.
This objective is achieved with a pressure cap of the type mentioned above which has the characteristics named in Claim I. _ With the measures according to the invention it can be achieved that the tolerances required in manufacturing the individual components and adapting them to each other do not have to be as close, and that assembly can be quicker. The hysteresis behaviour is improved as the result of a throttle gap arranged ahead of the seal.
-4-Furthermore, the flow connection between the second and third valve body is achieved primarily due to the presence of liquid coolant and not because of a higher gas pressure. In other words, when the interior tank pressure is increased, the air cushion above the liquid coolant can flow off and contribute to pressure equalization until it is eliminated and the liquid coolant is in place.
Advantageous embodiments of the configuration of the third valve body in the second valve body result from the characteristics named in one or more of Claims 2 to
Advantageous embodiments of the configuration of the third valve body in the second valve body result from the characteristics named in one or more of Claims 2 to
5.
With the characteristics according to Claim 6 it is achieved that the second valve body is pressed against the sealing seat on the interior cap component by the pressure existing in the chamber above the throttle gap between the second and the third valve bodies.
Advantageous configurations of the individual sealing seats in relation to each other result from the characteristics named in one or more of Claims 7 to 9.
With the characteristics according to Claim 10 and/or I1, an advantageous configuration of the vacuum valve body in the pressure cap is achieved.
Also known from DE 197 32 885 A1 is a pressure cap with a safety locking mans for openings in tanks. This safety locking means makes it possible to prevent the pressure cap being unscrewed when positive pressure r prevails, namely by locking the pressure cap so that the filler neck on the tank cannot be rotated. This prior-art safety lock uses an axially movable insert which - surrounds the interior cap component and/or its valve assembly, and which is therefore directly exposed to the positive pressure prevailing in the tank, since its inner floor is arranged in the opening of the filler neck. This axially movable insert is held in an additional tubular interior component so that it is axially movable while the pressure cap cannot be rotated against it. When positive pressure occurs in the tank, the insert is moved axially in the direction of the pressure cap and engages in same but cannot be rotated.
This results in the anti-rotational locking of the pressure cap via the insert and the additional interior component with the filler neck of the tank.
The measures to be taken in accordance with that prior art, to ensure anti-rotation and/or a safety lock, are complex in terms of the design, and they require a large number of components. Furthermore; the axially movable insert as well as the additional tubular interior component increase the diameter of the internal cap component of the pressure cap or reduce the effective surface of the valve arrangement of the pressure cap, which has negative implications for the response behaviour of the valve arrangement.
To remedy this situation, such a pressure cap is provided with the characteristics according to Claim 12, which means that its anti-rotation at positive pressure can be ensured in a manner that is simple to design and
With the characteristics according to Claim 6 it is achieved that the second valve body is pressed against the sealing seat on the interior cap component by the pressure existing in the chamber above the throttle gap between the second and the third valve bodies.
Advantageous configurations of the individual sealing seats in relation to each other result from the characteristics named in one or more of Claims 7 to 9.
With the characteristics according to Claim 10 and/or I1, an advantageous configuration of the vacuum valve body in the pressure cap is achieved.
Also known from DE 197 32 885 A1 is a pressure cap with a safety locking mans for openings in tanks. This safety locking means makes it possible to prevent the pressure cap being unscrewed when positive pressure r prevails, namely by locking the pressure cap so that the filler neck on the tank cannot be rotated. This prior-art safety lock uses an axially movable insert which - surrounds the interior cap component and/or its valve assembly, and which is therefore directly exposed to the positive pressure prevailing in the tank, since its inner floor is arranged in the opening of the filler neck. This axially movable insert is held in an additional tubular interior component so that it is axially movable while the pressure cap cannot be rotated against it. When positive pressure occurs in the tank, the insert is moved axially in the direction of the pressure cap and engages in same but cannot be rotated.
This results in the anti-rotational locking of the pressure cap via the insert and the additional interior component with the filler neck of the tank.
The measures to be taken in accordance with that prior art, to ensure anti-rotation and/or a safety lock, are complex in terms of the design, and they require a large number of components. Furthermore; the axially movable insert as well as the additional tubular interior component increase the diameter of the internal cap component of the pressure cap or reduce the effective surface of the valve arrangement of the pressure cap, which has negative implications for the response behaviour of the valve arrangement.
To remedy this situation, such a pressure cap is provided with the characteristics according to Claim 12, which means that its anti-rotation at positive pressure can be ensured in a manner that is simple to design and
-6-to manufacture and is therefore more cost-effective to produce. This is the case because thanks to the direct deflection of movement from the first valve body, no additional components are necessary, but instead, at positive pressure, an idling connection is created between the cap component comprising the thread or such and the manipulating element or handling lid. This idling connection within the exterior cap component at positive pressure has the considerable advantage, in comparison with locking the pressure cap at positive pressure, that the activation of the anti-rotational means becomes evident, thus eliminating the possibility that force is used in case of a blockage.
Another space-saving feature for the valve arrangement results when the characteristics in accordance with Claim 13 are provided. The characteristics according to Claim 14 are provided to support a return movement of the coupling insert.
An advantageous embodiment of the coupling insert results from the characteristics according to Claim 15.
It can be practical to provide suitable claw elements having the characteristics in accordance with Claim 16.
In accordance with the characteristics of Claim 17, a guide element. is provided for the direct transmission of movement from the first valve body to the coupling insert.
For the favourable control of the coupling insert even at low positive pressure, it is provided to design the
Another space-saving feature for the valve arrangement results when the characteristics in accordance with Claim 13 are provided. The characteristics according to Claim 14 are provided to support a return movement of the coupling insert.
An advantageous embodiment of the coupling insert results from the characteristics according to Claim 15.
It can be practical to provide suitable claw elements having the characteristics in accordance with Claim 16.
In accordance with the characteristics of Claim 17, a guide element. is provided for the direct transmission of movement from the first valve body to the coupling insert.
For the favourable control of the coupling insert even at low positive pressure, it is provided to design the
-7-first valve body in two parts in accordance with the characteristics of Claim 18. Embodiments of this are based on the characteristics of one or more of Claims 19 to 21.
Further details of the invention are described below, where the invention is described in with reference to the embodiments shown in the drawings, where Fig. 1 shows the partly longitudinal section of a pressure cap for a motor-vehicle radiator, with a positive-pressure / vacuum valve arrangement in closed initial position, in accordance with a first embodiment of the present invention;
Fig. 2 shows the pressure cap according to Fig. 1 in a position after the internal tank pressure has exceeded a first threshold value;
Fig. 3 shows the pressure cap according to Fig. 1 after the internal tank pressure has exceeded a second threshold value, or when dynamic pressure prevails;
Fig. 4 shows the pressure cap according to Fig. 1 when the internal tank pressure has exceeded a third safety threshold value; -Fig. 5 shows the partly longitudinal section of a pressure cap for a motor-vehicle radiator, with a positive-pressure / vacuum valve arrangement in closed initial position and with an engaged anti-rotational means in accordance with a second embodiment of the present invention;
_8-Fig. 6 shows the pressure cap according to Fig. 5 in a position at slight positive pressure inside the tank and a disengaged anti-rotational means;
Fig. 7 shows the pressure cap according to Fig. 1 in a position after the interior tank pressure has exceeded a first threshold value;
Fig. 8 shows the pressure cap according to Fig. 1 after the interior tank pressure has reached a second threshold value or when dynamic pressure prevails; and Fig. 9 shows the pressure cap according to Fig. 5 when the interior tank pressure has exceeded a third safety threshold value.
The pressure cap I1 for tanks such as motor-vehicle radiators, shown in Fig. 1 to 4 in accordance with a first embodiment, has an exterior cap component 13 which is provided with a handling lid 12 and to which an interior cap component 14 with a vacuum / positive-pressure valve arrangement 15 is mounted. When in use, the pressure cap II is fixed, for example screwed, to a radiator neck (not shown). The interior cap component 14 extends inside the radiator neck toward the interior of the radiator. -An O ring 16 seals the interior cap component against the wall of the radiator neck. The overpressure part of the valve arrangement 15 is designed in two steps, and it has the purpose of preventing the radiator from boiling over in a first overpressure stage and protecting the radiator system against damage due to excessive overpressure in a second overpressure stage.
Inside the interior cap component, the overpressure part of the valve arrangement 15 has a first valve body 17 and a second valve body 18 as well as a third valve body 19.
The first valve body l7 is arranged in the direction of the outside of the cap above the second valve body 18, while the third valve body 19 is placed coaxially inside the second valve body 18, The first valve body 17 is designed in the farm of an upside-down valve disk, the side of which facing the inside of the radiator is provided with a ring seal 21 whose sealing surface faces axially inside. The first valve body 17, at its side facing away from the inside of the radiator, is compressed by a recoil spring 22 whose end facing away from the first valve body 17 is supported by a spring plate 23, which in turn is supported by the interior cap component 19. The first valve body 17 is biased by the recoil spring 22 in the direction of the inside of the radiator. Over seal 21, which is designed as a flat ring seal, the first valve body 17 bears on a first ring-shaped sealing seat 24 of the second valve body 18.
The one-piece second valve body 18 has a hood element 26, whose free face is provided with the first sealing seat 24, and a concentric hollow cylindrical receptacle 27 for the third valve body 19 pointing from the floor 28 of the hood element 26 to the inside of the radiator.
Floor 28 between hood element 26 and receptacle 27 is provided around its outer circumference with a flange whose peripheral groove incorporates a second ring seal in the form of an 0 ring 31. Added to this O ring 31 is a second sealing seat 32 which is designed as a collar rim on interior cap component 14. This collar rim 32 is formed between an upper section of interior cap component 14 (the hollow cylindrical section that has a greater interior diameter and accommodates the first valve body 17 and the hood element 26 of the second valve body 18) and a lower section of interior cap component 14 (the section that has a smaller interior diameter and surrounds the receptacle 27 of the second valve body 18) . On this lower section, the interior cap component 14 is provided with an axial opening 33. By means of recoil spring 22, the first ring seal 21 of first valve body 17 is pressed against the first sealing seat 24 of the second valve body 18, whose second ring seal 31 in turn is pressed against interior cap component 14. Between the underside of the first ring seal 2I of the first valve body 17 and the upper side of floor 28 of the second valve body 18 is a cylindrical chamber 34 whose outer circumference in axial direction between floor 28 and the underside of the first ring -seal 21 is constant. In the middle, chamber 34 is in communication with recess 37 in the second valve body 18 via a hole 35 in floor 28. At a cone-shaped section 38 at one free end of receptacle 27, recess 37 opens into the axial opening 33 of the interior cap component 14, Between hole 36 and recess 37, the second valve body 18 is provided with a shoulder which points toward the , inside of the radiator and holds a third flat ring seal 39.
The third valve body 19, which can be designed for example as a rotating element stepped in axial direction around the periphery, is axially movable in recess 37 of the second valve body 18. The third valve body 19 has a neck section 41 of small diameter, which is movable within hole 36 and inside the third ring seal 39, as well as a shoulder section 42 whose slanted shoulder area forms a third sealing seat 43 allocated to the third ring seal 39 on the second valve body 18, and also a cylindrical bulge section 44 which is supported in a manner not shown in detail by the inner wall of cone-shaped section 38 of the second valve body 18. For this purpose, inside recess 37, a second pressure spring 46 is provided, one end of which is supported by the underside of the third ring seal 39 of the second valve body 18, while the other end is supported by a shoulder between shoulder section 42 and the bulge section 44 of the third valve body 19: The third valve body 19 is biased toward the inside of the radiator by means of the second pressure spring 46. Between the bulge section 44 of the third valve body 19 and the interior circumference of recess 37 of the second valve body 18, a very narrow annular gap is provided whose width is in the magnitude of just a few hundredths of a millimeter.
This annular gap 47, as are hole 36 and chamber 34, forms part of a first flow connection 50 between the inside and the outside of the cap. A second flow connection 51 bypasses the outer circumference of the second valve body 18 (see Fig. 4).
In the centre of the first valve body 17 is an opening 56 which on the side facing the inside of the radiator is closed by a vacuum valve body 57 of valve arrangement 15. The main section 58 of this vacuum valve body 57 extends through the central opening 56. The end of the main section is under pressure from a third pressure spring 59, the one end of which is supported by a shoulder of the main section 58 and the other end of which is supported by the surface of valve body 17 that faces the outside of the cap. In that manner, the annular sealing seat 61 of vacuum valve body 57 seals and is contiguous to the underside of the first ring seal 21 of the first valve body 17. The sealing seat 61 of the vacuum valve body 57 lies radially inside the first sealing seat 24 of the second valve body 18, while the latter lies radially outside the second sealing seat 32 of the interior cap component 14, and the latter in turn lies radially outside the third sealing seat 43 on the third valve body 19. All sealing seats 24, 32, 43, 61 point axially outside, while all sealing surfaces 21, 31, 39 point axially inside.
In the initial operating position shown in Fig. 1, in which a first threshold value of the inside tank pressure is not yet exceeded, the first flow connection -50 is closed by the sealing contiguity of the first valve body I7 with its first ring seal 21 on the first sealing seat 24 of the second valve body. In other words, in chamber 34 and thus on the underside of the first ring seal 41 of the first valve body 17, the pressure prevailing inside the tank extends through annular gap 47 in the form of the air cushion existing -z3-over the liquid coolant. The second flow connection 51 along the outer periphery of the second valve body 18 is closed by the sealing contiguity of the second seal 31 of the second valve body 18 on the second sealing seat 32 of the interior cap component 14.
If the inside tank pressure rises above a predetermined first threshold value, the pressure cap 1l reaches the operating state shown in Fig. 2, in which due to the increased inside tank pressure, the first valve body 17 is lifted against the effect of its first pressure spring 22 with its first ring seal 21 from the first sealing seat 24 of the second valve body 18, thus opening the first flow connection 50, so that air can flow outside from the air cushion over the liquid coolant and- thus can compensate or reduce the overpressure. Due to the overpressure in chamber 34, the second valve body I8 with its second ring seal 31 continues to be pressed against the second sealing seat 32 of the interior cap component 14. If this causes the overpressure to be reduced again below the first threshold value, the first valve body 17 again seals and is contiguous to the second valve body 18.
If on the other hand the inside tank pressure continues to rise during or after the deflation of the air cushion, and if this leads to a state where the liquid coolant reaches the underside of the second and third valve bodies 18, 19, the liquid coolant will accumulate at the entrance of annular gap 47, due to the very narrow width of the latter, thus causing the accumulation of dynamic pressure on the full-surface underside of the third valve body 19. This dynamic pressure results in an axial movement of the third valve body 19 against the effect of its third pressure spring 59 at the end of which the third sealing seat 43 of the third valve body 19 is contiguous to the third ring seal 39 of the second valve body 18, closing the first flow connection 50 (see Fig. 3).
The closing of the first flow connection 50 between the second and third valve bodies 18, 19 results in the reduction of pressure in chamber 34 to below the above named predetermined threshold value, so that the first valve body 17 is moved toward the second valve body 18 by the effect of its first pressure spring 22. This state is shown in Fig. 3 as well. If the inside tank pressure is reduced because the radiator is cooling down, and the liquid coolant is therefore returned, the third valve body 19 is returned under the effect of its second pressure spring 46, so that the first flaw connection 50 in this section opens again, as shown in Fig. 1 If, on the other hand, the inside tank pressure continues to rise and exceeds an upper safety value, the second valve body 18 is lifted (against the first -pressure spring 22 that presses upon valve body 17) from the second sealing seat 32 on the interior cap component 14, so that the second flow connection 51 is opened, which allows the reduction of the said overpressure (see Fig. 4). The lifting of the second valve body 18 from the inside cap component 14 can be supported by an additional (fourth) pressure spring 54 surrounding the receptacle 27. This fourth spring is supported at one end by the underside of the floor 28 of the second valve body 18 and at the other end by an inner shoulder of the Lower section of the interior cap component 14 (drawn as a dotted line in Fig. 4).
Valve arrangement 15 assumes the initial position shown in Fig. 1 when the pressure inside the radiator varies between a vacuum and a first overpressure value. Such pressure conditions occur, for example, in a vehicle that has been parked for some time, or when the coolant inside the radiator of a moving vehicle is sufficiently cooled by the outside wind stream and/or with support from the fan. If, for example, the vehicle is parked after a long drive, pressure may rise so much inside the radiator that the valve arrangement 15 is supplied with coolant (air, water or water vapour). If due to this after-heating effect, the coolant volume expands so much that it exceeds the tank volume, this would necessarily result in the expulsion of coolant. As described above, this undesirable effect can be prevented by valve arrangement 15 assuming the operating state shown in Fig. 2 and 3. If there is any further uncontrolled pressure increase in the cooling system in that operating state, the eruption of coolant and other detrimental effects caused by excessive demands on the radiator tank and/or the hose connections must be prevented. Such effects can be prevented by the second valve stage according to the state shown in Fig. 4, which limits the tank pressure to a predetermined safety value.
If there is vacuum pressure inside the radiator, and if this vacuum exceeds a predetermined vacuum threshold value, the vacuum valve body 57 with its sealing seat 61 will be lifted - starting from the operational state according to Fig. 1 - from the underside of the first ring seal 21 of the first valve body 17 to the inside of the radiator. The vacuum valve body 57 is lowered against the bias of the third pressure spring 59, so that a flow connection path will open (in a manner not shown) between the inside and the outside of the radiator.
The pressure cap 111 shown in Fig. 5 to 9 according to another embodiment, for example for a motor vehicle radiator, has an exterior cap component 113 provided with a manipulating element or handling lid 112, from which an interior cap component 114 with a vacuum /
overpressure valve arrangement 1I5 is suspended. When in use, the pressure cap 111 is fixed, for example screwed, to a radiator neck (not shown). The interior cap component 114 extends inside the radiator neck toward the interior of the radiator. An O ring 116 seals the inferior cap component 114 against the wall of the radiator neck.
In the case of the two-part exterior cap component 113, the cap-like manipulating element or handling lid 112 is axially fixed to the pressure cap element 113, here designed as a screw cap element, but it can be rotated in circumferential direction. This rotatability is blocked when pressure inside the radiator is normal, by means of an axially movable coupling insert 180 for screwing and unscrewing the pressure cap 111.
The overpressure part of the valve arrangement 115 is formed in two steps and has the purpose of preventing the radiator from boiling over in a first overpressure stage, and of ensuring protection against damage to the radiator system due to excessive overpressure in a second overpressure stage. Inside the interior cap component 114, the overpressure part of valve arrangement 115 has a first valve body 117 and a second valve body 118, as well as a third valve body 1I9. The first valve body 117 is arranged in the direction of the cap's outside above the second valve body 118, while the third valve body 119 is accommodated coaxially inside the second valve body 118.
The first valve body 117, designed in two parts, is provided with a radially interior valve body part 165 roughly in the form of a valve disk, and a-radially exterior valve body part 166; these overlap on the edges, whereby the radially interior part sits on top of the radially exterior valve body part. On the side of the two valve body parts 165, 166 facing the inside of the radiator, an annular membrane seal 121 is provided -with sealing surfaces axially turned inward. The radially exterior stepped valve body part ,166 of the first valve body 117 is compressed by a recoil spring 122 on the side facing away from the inside of the radiator. The end of this spring which faces away from the first valve body 117 is supported by a valve disk 123 which in turn is supported by the interior cap r component 114. By means of the recoil spring 122, the radially exterior valve body part 166 of the first valve body 117 is biased in the direction of the inside of the radiator. Over the radially exterior flat sealing rim 168 of annular membrane seal I21, the radially exterior valve body part 166 sits on a first annular sealing seat 124 of the second valve body 118. The radially interior valve body part 165 of the first valve body 117 is provided with a central recess 137 whose annular limiting edge is surrounded by the interior part of annular membrane seal 121. Toward the inside of the radiator, this radially interior U-shaped sealing rim 167 of annular membrane seal 121 forms a sealing surface for a vacuum valve 157 still to be described. On the side of the outer edge, the radially interior valve body part 165 bears directly on the inner edge of the radially exterior valve body part 16& of the first valve body 117.
The radially interior valve body part 165 is provided, near its radial outer edge, with an axially projecting annular edge 169 on which sits a guidance sleeve I71 the inner end of which overlaps the annular edge 169 radially on the inside in offset fashion. Directly bearing on the other axial end of the guidance sleeve -171, which is formed by one-piece projecting fingers 172, is the coupling insert 180 under the effect of a pressure spring 181 which is supported by the inside of handling lid 112 of exterior cap component 113. The coupling insert 180 is provided with a disk 185 in turn provided with axially downward extending finger-like claws 182 whose cross section corresponds to the fingers r 172 of guidance sleeve 171. As shown in Fig. 5, in s state without pressure, the fingers 172 of guidance sleeve 171 as well as the claws 182 of the coupling insert 180 engage in axial recesses 173 of closure element 110 of the exterior cap component 112.
Furthermore, axially toward the outside, i.e. facing away from claws 182, the coupling insert disk 185 is provided with projecting claws 183 which in positive connection grasp between an axially aligned circumferential serration 184 of handling lid 112. The inward facing claws 182 are lying on a radially interior ring, while the axially outward pointing claws 183 lie on a radially exterior ring. In the initial or normal position shown in Fig. 5, an anti-rotational connection exists between the handling. lid 112 and the closure element I10 of exterior cap component 113, so that the pressure cap 111 can be screwed to and unscrewed from the filler neck (not shown) of a tank.
The one-piece second valve body 118 is provided with a hood element 126 whose free face is provided with the first sealing seat 124, and a concentric and hollow cylindrical receptacle 127 (pointing away from the floor 128 of hood element 126 and toward the inside of the radiator) for the third valve body 119. The floor 128 between the hood element 126 and the receptacle 127 is provided with a flange in whose circumferential groove a second ring seal in the form of an 0 ring 131 is incorporated. Added to 0 ring 131 is a second sealing seat 132 which is designed as a collar rim on the interior cap component 119. This collar rim 132 is formed between an upper section of interior cap s component 114 (the hollow cylindrical section that has a greater interior diameter and accommodates the first valve body 117 and the hood element 126 of the second valve body 118) and a lower section of interior cap component 114 (the section that has a smaller interior 20 diameter and surrounds the receptacle 127 of the second valve body 118). On this lower section, the interior cap component 114 is provided with an axial opening 133. By means of recoil spring 122, the first ring seal 121 of first valve body I7 is pressed against the first sealing seat 24 of the second valve body 118, whose second ring seal 131 in turn is pressed against interior cap component 1I4.
Between the underside of the first annular membrane seal 121 of the first valve body 117 and the upper side of floor 128 of the second valve body 118 is a cylindrical chamber 134 whose outer circumference in axial direction between floor 128 and the underside of the first annular membrane seal 121 is constant. In the middle, chamber 134 is in communication with recess 137 in the second valve body 118 via a hole 135 in floor 128. At a cone-shaped section 138 at one free end of receptacle 127, recess 137 opens into the axial opening 133 of the interior cap component II4. Between hole 136 and recess 137, the second valve body 118 is provided with a shoulder which points toward the inside of the radiator and holds a third flat ring seal I39.
The third valve body 119, which can be designed for example as a rotating element stepped in axial direction around the periphery, is axially movable in recess 137 a of the second valve body 118. The third valve body 119 has a neck section I41 of small diameter, which is movable within hole 136 and inside the third ring seal 139, as well as a shoulder section 142 whose slanted shoulder area forms a third sealing seat 143 allocated to the third ring seal 139 on the second valve body 118, and also a cylindrical bulge section I44 which is supported in a manner not shown in detail by the inner wall of cone-shaped section 138 of the second valve body 118. For this purpose, inside recess 137, a second pressure spring 146 is provided, one end of which is supported by the underside of the third ring seal 139 of the second valve body 118, while the other end is supported by a shoulder between shoulder section 142 and the bulge section 144 of the third valve body 119. The third valve body 119 is biased toward the inside of the 'radiator by means of the second pressure spring 146.
Between the bulge section 144 of the third valve body 119 and the interior circumference of recess 137 of the second valve body 118, a very narrow annular gap is provided whose width is in the magnitude of just a few hundredths of a millimeter. This annular gap 147, as are hole 136 and chamber 34, forms part of a first flow connection 150 between the inside and the outside of the cap. A second flow connection 151 bypasses the outer circumference of the second valve body 118 (see Fig. 9).
In the centre of the radially interior valve body part 165 of the first valve body 117 is an opening 156 which on the side facing the inside of the radiator is closed by a vacuum valve body 157 of valve arrangement 115. The main section 158 of this vacuum valve body 157 extends through the central opening 156. The end of the main section is under pressure from a third pressure spring 159, the one end of which is supported by a shoulder of the main section 158 and the other end of which is supported by the surface of valve body 117 that faces the outside of the cap. In that manner, the annular sealing seat 161 of vacuum valve body 157 seals and is contiguous to the underside of the first annular membrane seal 121 of the first valve body 117. The sealing seat 161 of the vacuum valve body 157 lies radially inside the first sealing seat 124 of the second valve body 118, while the latter lies radially outside the second sealing seat 132 of the interior cap component 114, and the latter in turn lies radially outside the third sealing seat 143 on the third valve body 119. All sealing seats 124, 132, 143, 161 point axially outside, while all sealing surfaces 121, 131, 139 point axially inside.
In the initial operating position shown in Fig. 5, in which a first threshold value of the inside tank pressure is not yet exceeded, the first flow connection 150 is closed by the sealing contiguity of the first valve body 117 with its first annular membrane seal 121 on the first sealing seat 124 of the second valve body -118. In other words, in chamber 134 and thus on the underside of the first annular membrane seal 121 of the first valve body 117, the pressure prevailing inside the tank extends through annular gap 147 in the form of the air cushion existing over the liquid coolant. The second flow connection 151 along the outer periphery of the second valve body 118 is closed by the sealing contiguity of the second seal 131 of the second valve body 118 on the second sealing seat 132 of the interior cap component 114.
If the inside tank pressure rises to a certain value which lies above the normal or ambient pressure, but below a first threshold value of the inside tank pressure, the unscrew protection of pressure cap 111 is activated. As shown in Fig. 6, the radially interior valve body part 165 of the first valve body 117 is moved upward, while the second valve body 118 remains in its sealing position. Furthermore, the radially exterior valve body part 166 of the first valve body 117 remains in its sealing position in relation to the second valve body 118. The annular membrane seal 121 allows this relative movement between the radially interior valve body part 165 and the radially exterior valve body part 166 due to the membrane seal's meandering shape between its two sealing rims 167 and 168. The guidance sleeve 171, which sits on the radially interior valve body part 165 is moved along with said part toward the outside in the direction indicated by arrow A. The said guidance sleeve 171 in turn moves the coupling insert 180 against the effect of pressure spring 181, and the guidance sleeve's fingers 172 push the claws 183, which are pointing axially inward, out of the recesses 183 in closure element 110. This axial movement ends when the inner shoulder of guidance sleeve 171 strikes ,against closure element 110. The disengagement of the coupling element 180 from the closure element 110 of exterior cap component 112 has the effect that the handling lid 112 idles in relation to the closure element 110; so that starting at a certain predetermined overpressure (in this case, for example, 0.3 bar), it is no longer possible for the pressure cap I11 to unscrew from the filler neck.
I0 If the inside tank pressure rises further, i.e. above the predetermined first threshold value (for example 1.4 bar), the valve arrangement II5 reaches the operating state shown in Fig. 7. Tn this state, due to the increased inside tank pressure, the radially exterior I5 sealing rim 168 of the radially exterior valve body part 166 of the first valve body 117 lifts off the first sealing seat 124 of the second valve body I17 against the effect of its first pressure spring 122, thus opening the first flow connection 150 and allowing air 20 to flow outside from the air cushion above the liquid coolant, thus compensating or reducing the overpressure.
Due to the overpressure in chamber 134, the second valve body 118 with its second ring seal 131 continues to be pressed against the second sealing seat 132 of the 25 interior cap component 114. If this causes the overpressure to be reduced again below the first threshold value, the radially exterior valve body part 166 again is contiguous to the second valve body 118.
The unscrew protection remains activated as before.
If on the other hand the inside tank pressure continues to rise during or after the deflation of the air cushion, and if this leads to a state where the liquid coolant reaches the underside of the second and third valve bodies 118, I19, the liquid coolant will accumulate at the entrance of annular gap 147, due to the very narrow width of the latter, thus causing the accumulation of dynamic pressure on the full-surface underside of the third valve body 119. This dynamic pressure results in an axial movement of the third valve body 119 against the effect of its second pressure spring 146 at the end of which the third sealing seat 143 of the third valve body I19 is contiguous to the third ring seal 139 of the second valve body 118, closing the first flow connection 150 (see Fig. 8).
The closing of the first flow connection 150 between the second and third valve bodies I18, 119 results in the reduction of pressure in chamber 134 to below the above named predetermined threshold value, so that the radially exterior first valve body 117 is moved toward the second valve body 118 by the effect of its first pressure spring 122. This state is shown in Fig. 8 as well. If the inside tank pressure is reduced because the radiator is cooling down, and the liquid coolant is therefore returned, the third valve body 119 is returned under the effect of its second pressure spring 146, so that the first flow connection 150 in this section opens again, as shown in Fig. 5.
If, on the other hand, the inside tank pressure continues to rise and exceeds an upper safety value, the second valve body 118 is lifted (against the first pressure spring 122 that presses upon valve body 117) from the second sealing seat 132 on the interior cap component 114, so that the second flow connection 151 is opened, which allows the reduction of the said overpressure (see Fig. 9). The unscrew protection v remains activated as before. Thus, the said overpressure can be reduced via the second flow connection, after which it is possible to return the valve bodies via the various operating states through the individual pressure springs and coupling insert 180, as shown in Fig. S. If the lower claws 183 of the coupling insert 180 are radially offset in relation to the recesses 173 in the closure element 110, it is enough to turn the handling lid 110 [sicJ to bring the claws 183 and the recesses 173 into alignment again, so that the compressed 1S pressure spring 181 brings the coupling element into he non-activated position again opposite to the direction indicated by arrow A.
Valve arrangement 115 assumes the initial position shown in Fig. 5 when the pressure inside the radiator varies between a vacuum and the first overpressure value. Such pressure conditions occur, for example, in a vehicle that has been parked for some time, or when the coolant inside the radiator of a moving vehicle is sufficiently cooled by the outside wind stream and/or with support from the fan. If, for example, the vehicle is parked after a long drive, pressure may rise so much inside the radiator that the valve arrangement 115 is supplied with coolant (air, water or water vapour). If due to this -after-heating effect, the coolant volume expands so much that it exceeds the tank volume, this would necessarily result in the expulsion of coolant. As described above, this undesirable effect can be prevented by valve arrangement 115 assuming the operating state shown in Fig. 6 to 8. If there is any further uncontrolled pressure increase in the cooling system in that operating state, the eruption of coolant and other detrimental effects caused by excessive demands on the radiator tank and/or the hose connections must be prevented. Such effects can be prevented by the second valve stage according to the state shown in Fig. 9, which limits the tank pressure to a predetermined safety value.
If there is vacuum pressure inside the radiator, and if this vacuum exceeds a predetermined vacuum threshold value, the vacuum valve body 157 with its sealing seat 161 will be lifted - starting from the operational, state according to Fig. 5 - from the underside of the first annular membrane seal 121 of the first valve body 117 to the inside of the radiator. The vacuum valve body 157 is lowered against the bias of the-third pressure spring 159, so that a flow connection path will open (in a manner not shown) between the inside and the outside of the radiator.
In a version (not shown) of one or-both of the above embodiments, the sealing seat 61 or 161 of the vacuum valve body 57, 157 is provided not on a level plate arranged in a chamber 34, 134, but provided on a plate whose cross section toward the outer periphery is sawtooth-shaped and is arranged in a cylindrical. chamber 34, 134. Furthermore, in versions of one or both of the said embodiments, the second sealing seat 32, 132 for 0 ring 31, 131 is designed as a conical surface.
In accordance with another version (not shown) of one and/or the other embodiment of Fig. 1 to 4 or 5 to 9, the third valve body 19 or 119 is cup-shaped and able to open toward the opening into the cylindrical chamber 34 or 134. The upper rim of this cup-shaped valve body forms a ring seat for a sealing gasket which surrounds the said opening into the cylindrical chamber 34, 134.
The cup-shaped third valve body accommodates a pressure spring which corresponds to pressure spring 46, 146 which presses it down and away from the said sealing gaket. The function of this third valve body remains the same as that of the third valve body 19, 119 of the said embodiments. In other words, when the ring seat of this cup-shaped third valve body presses against the sealing gasket, the respective flow connection is closed.
Further details of the invention are described below, where the invention is described in with reference to the embodiments shown in the drawings, where Fig. 1 shows the partly longitudinal section of a pressure cap for a motor-vehicle radiator, with a positive-pressure / vacuum valve arrangement in closed initial position, in accordance with a first embodiment of the present invention;
Fig. 2 shows the pressure cap according to Fig. 1 in a position after the internal tank pressure has exceeded a first threshold value;
Fig. 3 shows the pressure cap according to Fig. 1 after the internal tank pressure has exceeded a second threshold value, or when dynamic pressure prevails;
Fig. 4 shows the pressure cap according to Fig. 1 when the internal tank pressure has exceeded a third safety threshold value; -Fig. 5 shows the partly longitudinal section of a pressure cap for a motor-vehicle radiator, with a positive-pressure / vacuum valve arrangement in closed initial position and with an engaged anti-rotational means in accordance with a second embodiment of the present invention;
_8-Fig. 6 shows the pressure cap according to Fig. 5 in a position at slight positive pressure inside the tank and a disengaged anti-rotational means;
Fig. 7 shows the pressure cap according to Fig. 1 in a position after the interior tank pressure has exceeded a first threshold value;
Fig. 8 shows the pressure cap according to Fig. 1 after the interior tank pressure has reached a second threshold value or when dynamic pressure prevails; and Fig. 9 shows the pressure cap according to Fig. 5 when the interior tank pressure has exceeded a third safety threshold value.
The pressure cap I1 for tanks such as motor-vehicle radiators, shown in Fig. 1 to 4 in accordance with a first embodiment, has an exterior cap component 13 which is provided with a handling lid 12 and to which an interior cap component 14 with a vacuum / positive-pressure valve arrangement 15 is mounted. When in use, the pressure cap II is fixed, for example screwed, to a radiator neck (not shown). The interior cap component 14 extends inside the radiator neck toward the interior of the radiator. -An O ring 16 seals the interior cap component against the wall of the radiator neck. The overpressure part of the valve arrangement 15 is designed in two steps, and it has the purpose of preventing the radiator from boiling over in a first overpressure stage and protecting the radiator system against damage due to excessive overpressure in a second overpressure stage.
Inside the interior cap component, the overpressure part of the valve arrangement 15 has a first valve body 17 and a second valve body 18 as well as a third valve body 19.
The first valve body l7 is arranged in the direction of the outside of the cap above the second valve body 18, while the third valve body 19 is placed coaxially inside the second valve body 18, The first valve body 17 is designed in the farm of an upside-down valve disk, the side of which facing the inside of the radiator is provided with a ring seal 21 whose sealing surface faces axially inside. The first valve body 17, at its side facing away from the inside of the radiator, is compressed by a recoil spring 22 whose end facing away from the first valve body 17 is supported by a spring plate 23, which in turn is supported by the interior cap component 19. The first valve body 17 is biased by the recoil spring 22 in the direction of the inside of the radiator. Over seal 21, which is designed as a flat ring seal, the first valve body 17 bears on a first ring-shaped sealing seat 24 of the second valve body 18.
The one-piece second valve body 18 has a hood element 26, whose free face is provided with the first sealing seat 24, and a concentric hollow cylindrical receptacle 27 for the third valve body 19 pointing from the floor 28 of the hood element 26 to the inside of the radiator.
Floor 28 between hood element 26 and receptacle 27 is provided around its outer circumference with a flange whose peripheral groove incorporates a second ring seal in the form of an 0 ring 31. Added to this O ring 31 is a second sealing seat 32 which is designed as a collar rim on interior cap component 14. This collar rim 32 is formed between an upper section of interior cap component 14 (the hollow cylindrical section that has a greater interior diameter and accommodates the first valve body 17 and the hood element 26 of the second valve body 18) and a lower section of interior cap component 14 (the section that has a smaller interior diameter and surrounds the receptacle 27 of the second valve body 18) . On this lower section, the interior cap component 14 is provided with an axial opening 33. By means of recoil spring 22, the first ring seal 21 of first valve body 17 is pressed against the first sealing seat 24 of the second valve body 18, whose second ring seal 31 in turn is pressed against interior cap component 14. Between the underside of the first ring seal 2I of the first valve body 17 and the upper side of floor 28 of the second valve body 18 is a cylindrical chamber 34 whose outer circumference in axial direction between floor 28 and the underside of the first ring -seal 21 is constant. In the middle, chamber 34 is in communication with recess 37 in the second valve body 18 via a hole 35 in floor 28. At a cone-shaped section 38 at one free end of receptacle 27, recess 37 opens into the axial opening 33 of the interior cap component 14, Between hole 36 and recess 37, the second valve body 18 is provided with a shoulder which points toward the , inside of the radiator and holds a third flat ring seal 39.
The third valve body 19, which can be designed for example as a rotating element stepped in axial direction around the periphery, is axially movable in recess 37 of the second valve body 18. The third valve body 19 has a neck section 41 of small diameter, which is movable within hole 36 and inside the third ring seal 39, as well as a shoulder section 42 whose slanted shoulder area forms a third sealing seat 43 allocated to the third ring seal 39 on the second valve body 18, and also a cylindrical bulge section 44 which is supported in a manner not shown in detail by the inner wall of cone-shaped section 38 of the second valve body 18. For this purpose, inside recess 37, a second pressure spring 46 is provided, one end of which is supported by the underside of the third ring seal 39 of the second valve body 18, while the other end is supported by a shoulder between shoulder section 42 and the bulge section 44 of the third valve body 19: The third valve body 19 is biased toward the inside of the radiator by means of the second pressure spring 46. Between the bulge section 44 of the third valve body 19 and the interior circumference of recess 37 of the second valve body 18, a very narrow annular gap is provided whose width is in the magnitude of just a few hundredths of a millimeter.
This annular gap 47, as are hole 36 and chamber 34, forms part of a first flow connection 50 between the inside and the outside of the cap. A second flow connection 51 bypasses the outer circumference of the second valve body 18 (see Fig. 4).
In the centre of the first valve body 17 is an opening 56 which on the side facing the inside of the radiator is closed by a vacuum valve body 57 of valve arrangement 15. The main section 58 of this vacuum valve body 57 extends through the central opening 56. The end of the main section is under pressure from a third pressure spring 59, the one end of which is supported by a shoulder of the main section 58 and the other end of which is supported by the surface of valve body 17 that faces the outside of the cap. In that manner, the annular sealing seat 61 of vacuum valve body 57 seals and is contiguous to the underside of the first ring seal 21 of the first valve body 17. The sealing seat 61 of the vacuum valve body 57 lies radially inside the first sealing seat 24 of the second valve body 18, while the latter lies radially outside the second sealing seat 32 of the interior cap component 14, and the latter in turn lies radially outside the third sealing seat 43 on the third valve body 19. All sealing seats 24, 32, 43, 61 point axially outside, while all sealing surfaces 21, 31, 39 point axially inside.
In the initial operating position shown in Fig. 1, in which a first threshold value of the inside tank pressure is not yet exceeded, the first flow connection -50 is closed by the sealing contiguity of the first valve body I7 with its first ring seal 21 on the first sealing seat 24 of the second valve body. In other words, in chamber 34 and thus on the underside of the first ring seal 41 of the first valve body 17, the pressure prevailing inside the tank extends through annular gap 47 in the form of the air cushion existing -z3-over the liquid coolant. The second flow connection 51 along the outer periphery of the second valve body 18 is closed by the sealing contiguity of the second seal 31 of the second valve body 18 on the second sealing seat 32 of the interior cap component 14.
If the inside tank pressure rises above a predetermined first threshold value, the pressure cap 1l reaches the operating state shown in Fig. 2, in which due to the increased inside tank pressure, the first valve body 17 is lifted against the effect of its first pressure spring 22 with its first ring seal 21 from the first sealing seat 24 of the second valve body 18, thus opening the first flow connection 50, so that air can flow outside from the air cushion over the liquid coolant and- thus can compensate or reduce the overpressure. Due to the overpressure in chamber 34, the second valve body I8 with its second ring seal 31 continues to be pressed against the second sealing seat 32 of the interior cap component 14. If this causes the overpressure to be reduced again below the first threshold value, the first valve body 17 again seals and is contiguous to the second valve body 18.
If on the other hand the inside tank pressure continues to rise during or after the deflation of the air cushion, and if this leads to a state where the liquid coolant reaches the underside of the second and third valve bodies 18, 19, the liquid coolant will accumulate at the entrance of annular gap 47, due to the very narrow width of the latter, thus causing the accumulation of dynamic pressure on the full-surface underside of the third valve body 19. This dynamic pressure results in an axial movement of the third valve body 19 against the effect of its third pressure spring 59 at the end of which the third sealing seat 43 of the third valve body 19 is contiguous to the third ring seal 39 of the second valve body 18, closing the first flow connection 50 (see Fig. 3).
The closing of the first flow connection 50 between the second and third valve bodies 18, 19 results in the reduction of pressure in chamber 34 to below the above named predetermined threshold value, so that the first valve body 17 is moved toward the second valve body 18 by the effect of its first pressure spring 22. This state is shown in Fig. 3 as well. If the inside tank pressure is reduced because the radiator is cooling down, and the liquid coolant is therefore returned, the third valve body 19 is returned under the effect of its second pressure spring 46, so that the first flaw connection 50 in this section opens again, as shown in Fig. 1 If, on the other hand, the inside tank pressure continues to rise and exceeds an upper safety value, the second valve body 18 is lifted (against the first -pressure spring 22 that presses upon valve body 17) from the second sealing seat 32 on the interior cap component 14, so that the second flow connection 51 is opened, which allows the reduction of the said overpressure (see Fig. 4). The lifting of the second valve body 18 from the inside cap component 14 can be supported by an additional (fourth) pressure spring 54 surrounding the receptacle 27. This fourth spring is supported at one end by the underside of the floor 28 of the second valve body 18 and at the other end by an inner shoulder of the Lower section of the interior cap component 14 (drawn as a dotted line in Fig. 4).
Valve arrangement 15 assumes the initial position shown in Fig. 1 when the pressure inside the radiator varies between a vacuum and a first overpressure value. Such pressure conditions occur, for example, in a vehicle that has been parked for some time, or when the coolant inside the radiator of a moving vehicle is sufficiently cooled by the outside wind stream and/or with support from the fan. If, for example, the vehicle is parked after a long drive, pressure may rise so much inside the radiator that the valve arrangement 15 is supplied with coolant (air, water or water vapour). If due to this after-heating effect, the coolant volume expands so much that it exceeds the tank volume, this would necessarily result in the expulsion of coolant. As described above, this undesirable effect can be prevented by valve arrangement 15 assuming the operating state shown in Fig. 2 and 3. If there is any further uncontrolled pressure increase in the cooling system in that operating state, the eruption of coolant and other detrimental effects caused by excessive demands on the radiator tank and/or the hose connections must be prevented. Such effects can be prevented by the second valve stage according to the state shown in Fig. 4, which limits the tank pressure to a predetermined safety value.
If there is vacuum pressure inside the radiator, and if this vacuum exceeds a predetermined vacuum threshold value, the vacuum valve body 57 with its sealing seat 61 will be lifted - starting from the operational state according to Fig. 1 - from the underside of the first ring seal 21 of the first valve body 17 to the inside of the radiator. The vacuum valve body 57 is lowered against the bias of the third pressure spring 59, so that a flow connection path will open (in a manner not shown) between the inside and the outside of the radiator.
The pressure cap 111 shown in Fig. 5 to 9 according to another embodiment, for example for a motor vehicle radiator, has an exterior cap component 113 provided with a manipulating element or handling lid 112, from which an interior cap component 114 with a vacuum /
overpressure valve arrangement 1I5 is suspended. When in use, the pressure cap 111 is fixed, for example screwed, to a radiator neck (not shown). The interior cap component 114 extends inside the radiator neck toward the interior of the radiator. An O ring 116 seals the inferior cap component 114 against the wall of the radiator neck.
In the case of the two-part exterior cap component 113, the cap-like manipulating element or handling lid 112 is axially fixed to the pressure cap element 113, here designed as a screw cap element, but it can be rotated in circumferential direction. This rotatability is blocked when pressure inside the radiator is normal, by means of an axially movable coupling insert 180 for screwing and unscrewing the pressure cap 111.
The overpressure part of the valve arrangement 115 is formed in two steps and has the purpose of preventing the radiator from boiling over in a first overpressure stage, and of ensuring protection against damage to the radiator system due to excessive overpressure in a second overpressure stage. Inside the interior cap component 114, the overpressure part of valve arrangement 115 has a first valve body 117 and a second valve body 118, as well as a third valve body 1I9. The first valve body 117 is arranged in the direction of the cap's outside above the second valve body 118, while the third valve body 119 is accommodated coaxially inside the second valve body 118.
The first valve body 117, designed in two parts, is provided with a radially interior valve body part 165 roughly in the form of a valve disk, and a-radially exterior valve body part 166; these overlap on the edges, whereby the radially interior part sits on top of the radially exterior valve body part. On the side of the two valve body parts 165, 166 facing the inside of the radiator, an annular membrane seal 121 is provided -with sealing surfaces axially turned inward. The radially exterior stepped valve body part ,166 of the first valve body 117 is compressed by a recoil spring 122 on the side facing away from the inside of the radiator. The end of this spring which faces away from the first valve body 117 is supported by a valve disk 123 which in turn is supported by the interior cap r component 114. By means of the recoil spring 122, the radially exterior valve body part 166 of the first valve body 117 is biased in the direction of the inside of the radiator. Over the radially exterior flat sealing rim 168 of annular membrane seal I21, the radially exterior valve body part 166 sits on a first annular sealing seat 124 of the second valve body 118. The radially interior valve body part 165 of the first valve body 117 is provided with a central recess 137 whose annular limiting edge is surrounded by the interior part of annular membrane seal 121. Toward the inside of the radiator, this radially interior U-shaped sealing rim 167 of annular membrane seal 121 forms a sealing surface for a vacuum valve 157 still to be described. On the side of the outer edge, the radially interior valve body part 165 bears directly on the inner edge of the radially exterior valve body part 16& of the first valve body 117.
The radially interior valve body part 165 is provided, near its radial outer edge, with an axially projecting annular edge 169 on which sits a guidance sleeve I71 the inner end of which overlaps the annular edge 169 radially on the inside in offset fashion. Directly bearing on the other axial end of the guidance sleeve -171, which is formed by one-piece projecting fingers 172, is the coupling insert 180 under the effect of a pressure spring 181 which is supported by the inside of handling lid 112 of exterior cap component 113. The coupling insert 180 is provided with a disk 185 in turn provided with axially downward extending finger-like claws 182 whose cross section corresponds to the fingers r 172 of guidance sleeve 171. As shown in Fig. 5, in s state without pressure, the fingers 172 of guidance sleeve 171 as well as the claws 182 of the coupling insert 180 engage in axial recesses 173 of closure element 110 of the exterior cap component 112.
Furthermore, axially toward the outside, i.e. facing away from claws 182, the coupling insert disk 185 is provided with projecting claws 183 which in positive connection grasp between an axially aligned circumferential serration 184 of handling lid 112. The inward facing claws 182 are lying on a radially interior ring, while the axially outward pointing claws 183 lie on a radially exterior ring. In the initial or normal position shown in Fig. 5, an anti-rotational connection exists between the handling. lid 112 and the closure element I10 of exterior cap component 113, so that the pressure cap 111 can be screwed to and unscrewed from the filler neck (not shown) of a tank.
The one-piece second valve body 118 is provided with a hood element 126 whose free face is provided with the first sealing seat 124, and a concentric and hollow cylindrical receptacle 127 (pointing away from the floor 128 of hood element 126 and toward the inside of the radiator) for the third valve body 119. The floor 128 between the hood element 126 and the receptacle 127 is provided with a flange in whose circumferential groove a second ring seal in the form of an 0 ring 131 is incorporated. Added to 0 ring 131 is a second sealing seat 132 which is designed as a collar rim on the interior cap component 119. This collar rim 132 is formed between an upper section of interior cap s component 114 (the hollow cylindrical section that has a greater interior diameter and accommodates the first valve body 117 and the hood element 126 of the second valve body 118) and a lower section of interior cap component 114 (the section that has a smaller interior 20 diameter and surrounds the receptacle 127 of the second valve body 118). On this lower section, the interior cap component 114 is provided with an axial opening 133. By means of recoil spring 122, the first ring seal 121 of first valve body I7 is pressed against the first sealing seat 24 of the second valve body 118, whose second ring seal 131 in turn is pressed against interior cap component 1I4.
Between the underside of the first annular membrane seal 121 of the first valve body 117 and the upper side of floor 128 of the second valve body 118 is a cylindrical chamber 134 whose outer circumference in axial direction between floor 128 and the underside of the first annular membrane seal 121 is constant. In the middle, chamber 134 is in communication with recess 137 in the second valve body 118 via a hole 135 in floor 128. At a cone-shaped section 138 at one free end of receptacle 127, recess 137 opens into the axial opening 133 of the interior cap component II4. Between hole 136 and recess 137, the second valve body 118 is provided with a shoulder which points toward the inside of the radiator and holds a third flat ring seal I39.
The third valve body 119, which can be designed for example as a rotating element stepped in axial direction around the periphery, is axially movable in recess 137 a of the second valve body 118. The third valve body 119 has a neck section I41 of small diameter, which is movable within hole 136 and inside the third ring seal 139, as well as a shoulder section 142 whose slanted shoulder area forms a third sealing seat 143 allocated to the third ring seal 139 on the second valve body 118, and also a cylindrical bulge section I44 which is supported in a manner not shown in detail by the inner wall of cone-shaped section 138 of the second valve body 118. For this purpose, inside recess 137, a second pressure spring 146 is provided, one end of which is supported by the underside of the third ring seal 139 of the second valve body 118, while the other end is supported by a shoulder between shoulder section 142 and the bulge section 144 of the third valve body 119. The third valve body 119 is biased toward the inside of the 'radiator by means of the second pressure spring 146.
Between the bulge section 144 of the third valve body 119 and the interior circumference of recess 137 of the second valve body 118, a very narrow annular gap is provided whose width is in the magnitude of just a few hundredths of a millimeter. This annular gap 147, as are hole 136 and chamber 34, forms part of a first flow connection 150 between the inside and the outside of the cap. A second flow connection 151 bypasses the outer circumference of the second valve body 118 (see Fig. 9).
In the centre of the radially interior valve body part 165 of the first valve body 117 is an opening 156 which on the side facing the inside of the radiator is closed by a vacuum valve body 157 of valve arrangement 115. The main section 158 of this vacuum valve body 157 extends through the central opening 156. The end of the main section is under pressure from a third pressure spring 159, the one end of which is supported by a shoulder of the main section 158 and the other end of which is supported by the surface of valve body 117 that faces the outside of the cap. In that manner, the annular sealing seat 161 of vacuum valve body 157 seals and is contiguous to the underside of the first annular membrane seal 121 of the first valve body 117. The sealing seat 161 of the vacuum valve body 157 lies radially inside the first sealing seat 124 of the second valve body 118, while the latter lies radially outside the second sealing seat 132 of the interior cap component 114, and the latter in turn lies radially outside the third sealing seat 143 on the third valve body 119. All sealing seats 124, 132, 143, 161 point axially outside, while all sealing surfaces 121, 131, 139 point axially inside.
In the initial operating position shown in Fig. 5, in which a first threshold value of the inside tank pressure is not yet exceeded, the first flow connection 150 is closed by the sealing contiguity of the first valve body 117 with its first annular membrane seal 121 on the first sealing seat 124 of the second valve body -118. In other words, in chamber 134 and thus on the underside of the first annular membrane seal 121 of the first valve body 117, the pressure prevailing inside the tank extends through annular gap 147 in the form of the air cushion existing over the liquid coolant. The second flow connection 151 along the outer periphery of the second valve body 118 is closed by the sealing contiguity of the second seal 131 of the second valve body 118 on the second sealing seat 132 of the interior cap component 114.
If the inside tank pressure rises to a certain value which lies above the normal or ambient pressure, but below a first threshold value of the inside tank pressure, the unscrew protection of pressure cap 111 is activated. As shown in Fig. 6, the radially interior valve body part 165 of the first valve body 117 is moved upward, while the second valve body 118 remains in its sealing position. Furthermore, the radially exterior valve body part 166 of the first valve body 117 remains in its sealing position in relation to the second valve body 118. The annular membrane seal 121 allows this relative movement between the radially interior valve body part 165 and the radially exterior valve body part 166 due to the membrane seal's meandering shape between its two sealing rims 167 and 168. The guidance sleeve 171, which sits on the radially interior valve body part 165 is moved along with said part toward the outside in the direction indicated by arrow A. The said guidance sleeve 171 in turn moves the coupling insert 180 against the effect of pressure spring 181, and the guidance sleeve's fingers 172 push the claws 183, which are pointing axially inward, out of the recesses 183 in closure element 110. This axial movement ends when the inner shoulder of guidance sleeve 171 strikes ,against closure element 110. The disengagement of the coupling element 180 from the closure element 110 of exterior cap component 112 has the effect that the handling lid 112 idles in relation to the closure element 110; so that starting at a certain predetermined overpressure (in this case, for example, 0.3 bar), it is no longer possible for the pressure cap I11 to unscrew from the filler neck.
I0 If the inside tank pressure rises further, i.e. above the predetermined first threshold value (for example 1.4 bar), the valve arrangement II5 reaches the operating state shown in Fig. 7. Tn this state, due to the increased inside tank pressure, the radially exterior I5 sealing rim 168 of the radially exterior valve body part 166 of the first valve body 117 lifts off the first sealing seat 124 of the second valve body I17 against the effect of its first pressure spring 122, thus opening the first flow connection 150 and allowing air 20 to flow outside from the air cushion above the liquid coolant, thus compensating or reducing the overpressure.
Due to the overpressure in chamber 134, the second valve body 118 with its second ring seal 131 continues to be pressed against the second sealing seat 132 of the 25 interior cap component 114. If this causes the overpressure to be reduced again below the first threshold value, the radially exterior valve body part 166 again is contiguous to the second valve body 118.
The unscrew protection remains activated as before.
If on the other hand the inside tank pressure continues to rise during or after the deflation of the air cushion, and if this leads to a state where the liquid coolant reaches the underside of the second and third valve bodies 118, I19, the liquid coolant will accumulate at the entrance of annular gap 147, due to the very narrow width of the latter, thus causing the accumulation of dynamic pressure on the full-surface underside of the third valve body 119. This dynamic pressure results in an axial movement of the third valve body 119 against the effect of its second pressure spring 146 at the end of which the third sealing seat 143 of the third valve body I19 is contiguous to the third ring seal 139 of the second valve body 118, closing the first flow connection 150 (see Fig. 8).
The closing of the first flow connection 150 between the second and third valve bodies I18, 119 results in the reduction of pressure in chamber 134 to below the above named predetermined threshold value, so that the radially exterior first valve body 117 is moved toward the second valve body 118 by the effect of its first pressure spring 122. This state is shown in Fig. 8 as well. If the inside tank pressure is reduced because the radiator is cooling down, and the liquid coolant is therefore returned, the third valve body 119 is returned under the effect of its second pressure spring 146, so that the first flow connection 150 in this section opens again, as shown in Fig. 5.
If, on the other hand, the inside tank pressure continues to rise and exceeds an upper safety value, the second valve body 118 is lifted (against the first pressure spring 122 that presses upon valve body 117) from the second sealing seat 132 on the interior cap component 114, so that the second flow connection 151 is opened, which allows the reduction of the said overpressure (see Fig. 9). The unscrew protection v remains activated as before. Thus, the said overpressure can be reduced via the second flow connection, after which it is possible to return the valve bodies via the various operating states through the individual pressure springs and coupling insert 180, as shown in Fig. S. If the lower claws 183 of the coupling insert 180 are radially offset in relation to the recesses 173 in the closure element 110, it is enough to turn the handling lid 110 [sicJ to bring the claws 183 and the recesses 173 into alignment again, so that the compressed 1S pressure spring 181 brings the coupling element into he non-activated position again opposite to the direction indicated by arrow A.
Valve arrangement 115 assumes the initial position shown in Fig. 5 when the pressure inside the radiator varies between a vacuum and the first overpressure value. Such pressure conditions occur, for example, in a vehicle that has been parked for some time, or when the coolant inside the radiator of a moving vehicle is sufficiently cooled by the outside wind stream and/or with support from the fan. If, for example, the vehicle is parked after a long drive, pressure may rise so much inside the radiator that the valve arrangement 115 is supplied with coolant (air, water or water vapour). If due to this -after-heating effect, the coolant volume expands so much that it exceeds the tank volume, this would necessarily result in the expulsion of coolant. As described above, this undesirable effect can be prevented by valve arrangement 115 assuming the operating state shown in Fig. 6 to 8. If there is any further uncontrolled pressure increase in the cooling system in that operating state, the eruption of coolant and other detrimental effects caused by excessive demands on the radiator tank and/or the hose connections must be prevented. Such effects can be prevented by the second valve stage according to the state shown in Fig. 9, which limits the tank pressure to a predetermined safety value.
If there is vacuum pressure inside the radiator, and if this vacuum exceeds a predetermined vacuum threshold value, the vacuum valve body 157 with its sealing seat 161 will be lifted - starting from the operational, state according to Fig. 5 - from the underside of the first annular membrane seal 121 of the first valve body 117 to the inside of the radiator. The vacuum valve body 157 is lowered against the bias of the-third pressure spring 159, so that a flow connection path will open (in a manner not shown) between the inside and the outside of the radiator.
In a version (not shown) of one or-both of the above embodiments, the sealing seat 61 or 161 of the vacuum valve body 57, 157 is provided not on a level plate arranged in a chamber 34, 134, but provided on a plate whose cross section toward the outer periphery is sawtooth-shaped and is arranged in a cylindrical. chamber 34, 134. Furthermore, in versions of one or both of the said embodiments, the second sealing seat 32, 132 for 0 ring 31, 131 is designed as a conical surface.
In accordance with another version (not shown) of one and/or the other embodiment of Fig. 1 to 4 or 5 to 9, the third valve body 19 or 119 is cup-shaped and able to open toward the opening into the cylindrical chamber 34 or 134. The upper rim of this cup-shaped valve body forms a ring seat for a sealing gasket which surrounds the said opening into the cylindrical chamber 34, 134.
The cup-shaped third valve body accommodates a pressure spring which corresponds to pressure spring 46, 146 which presses it down and away from the said sealing gaket. The function of this third valve body remains the same as that of the third valve body 19, 119 of the said embodiments. In other words, when the ring seat of this cup-shaped third valve body presses against the sealing gasket, the respective flow connection is closed.
Claims (21)
1. Pressure cap (11, 111) for openings in tanks, particularly in motor-vehicle radiators, with an internal cap component (14, 114) that is provided with at least one flow connection between the inside and the outside of the tank, and with a valve arrangement (15, 115) for releasing and blocking the flow connection, whereby the said valve arrangement (15, 115) has a first and a second valve body (17, 118; 18, 118) that can be moved back and forth, whereby the first valve body (17, 117) is biased in the direction of the inside of the tank against a first sealing seat (24, 124) on the second valve body (18, 118), which is pressed against a second sealing seat (32, 132) on the interior cap component (14, 114), and whereby the first and second valve bodies (17 117; 18, 118) can be lifted when a respective threshold value of the inside tank pressure is exceeded and the flow connection (50, 150; 51, 151) between the inside and the outside of the tank is released, characterized in that inside the second valve body (18, 118) a third valve body (19, 119) is placed, between which and the second valve body (18, 118) a first flow connection (50, 150), designed in that section as a throttle gap (47, 147), is provided between the inside of the tank and the first valve body (17, 117), that said valve body (19, 119) is movable between one end position opening the first flow connection (50, 150) and the other end position closing it when a second threshold value of the inside radiator pressure is reached or when a dynamic pressure occurs due to the presence of a liquid medium, that the first valve body (17, 117) is lifted off the second valve body (18, 118) when a first threshold value is exceeded and comes to bear again on same after the flow connection (50, 150) closes, and that the second valve body (18, 118) is lifted off the second sealing seat (32, 132) on the interior cap component (14, 114) while releasing a second flow connection (51, 151) between the inside and the outside of the radiator when a third threshold value of the inside radiator pressure is exceeded, which is higher than the first and the second threshold value of the inside radiator pressure and also higher than the dynamic pressure.
2. Pressure cap according to Claim 1, characterized in that the third valve body (19, 119) is held axially movable inside a concentric recess (37, 137) of the second valve body (18, 118), whereby said recess is in communication with the inside of the radiator.
3. Pressure cap according to Claim 1 or 2, characterized in that the third valve body (19, 119) in the second valve body (18, 118) is biased by a second spring (46, 146) in the direction of its opening position that is supported by the second valve body.
4. Pressure cap according to at least one of Claims 1 to 3, characterized in that a third sealing seat (43, 143) an the third valve body (19, 119) is added to an axially inward pointing annular sealing surface (39, 139) of the second valve body (18, 118).
5. Pressure cap according to at least one of the previous claims, characterized in that the annular throttle gap (47, 147) of the first flow connection (50, 150) is so narrow that when pressure is applied through a liquid medium, a dynamic pressure occurs and overcomes the force of the second pressure spring (46, 146).
6. Pressure cap according to one of the previous claims, characterized in that between the first valve body (17, 117) and the second valve body (18, 118), a cylindrical chamber (34, 134) is provided which is in communication with the throttle gap (47, 147) between the second and third valve bodies (18, 19; 118, 119).
7. Pressure cap according to one at least one of the previous claims, characterized in that the first sealing seat (24, 124) on the second valve body (18, 118) lies radially outside the second sealing seat (32, 132) on the interior cap component (14, 114).
8. Pressure cap according to at least one of the previous claims, characterized in that the second sealing seat (32, 132) on the interior cap component (14, 114) lies radially outside the third sealing seat (43, 143) on the third valve body (19, 119).
9. Pressure cap according to at least one of the previous claims, characterized in that the sealing surfaces (21, 31, 39; 121, 131, 139) assigned to the respective sealing seats (24, 32, 43; 124, 132, 143) on the first valve body (17, 117), the second valve body (18, 118) or the third valve body (19, 119) point axially inward.
I0. Pressure cap according to at least one of the previous claims, characterized in that the first valve body (17, 117) is provided with a central opening (56, 156) through which a vacuum valve body (57, 157) extends whose sealing seat (61, 161) surrounds the central opening and is contiguous to the sealing surface (21, 121) of the first valve body (17, 117).
11. Pressure cap according to Claim 10, characterized in that the vacuum valve body (57, 157) is biased against the sealing surface (21, 121) of the first valve body (17, 117) with the aid of a spring (59, 159) supported by the top surface of the first valve body (17, 117).
12. Pressure cap according to at least one of the previous claims, characterized in that an exterior cap component (113) from which the interior component (114) is suspended, is formed by the handling lids or closure elements (112, 110) which are connected via an axially movable coupling insert (180) which makes the said elements releasable and anti-rotational and whose axial movement is derived from the pressure-controlled axial movement of the first valve body (117).
13. Pressure cap according to Claim 12, characterized in that the axially movable coupling insert (180) is arranged axially above the first valve body (117) within the handling lid (112) of the exterior cap component (113).
14. Pressure cap according to Claim 13, characterized in that the a coupling insert (180) inside the handling lid (112) is biased by a pressure spring (181) in the direction of the closure element (110).
15. Pressure cap according to at least one of Claims 12 to 14, characterized in that the coupling insert (180) is constantly in anti-rotational communication with the handling lid (212) and is axially movable for engaging in and disengaging from the closure element (110).
16. Pressure cap according to Claim 15, characterized in that the coupling insert (180) is provided with a disk (185), from whose two surfaces claw elements (182, 183) extend which act jointly with axial recesses (173) in the handling lid or closure element (110, 112).
17. Pressure cap according to at least one of Claims 12 to 16, characterized in that a guidance element (171) for transferring the axial movement is provided between the coupling insert (180) and the first valve body (117).
18. Pressure cap according to at least one of the previous claims, characterized in that the first valve body (117) is divided in two in radial connection and is provided with a radially interior valve body part (165) and a radially exterior valve body part (166) which axe axially movable in relation to each other and are in communication with each other via an annular membrane seal (121).
19. Pressure cap according to Claim 18, characterized in that the guidance element (172) sits on the radially interior valve body part (165) of the first valve body (117), and that the radially exterior valve body part (166) of the first valve body (117) is biased by the pressure spring (122) for the first valve body (117).
20. Pressure cap according to Claim 18 to 19, characterized in that the sealing surface of the radially exterior valve body part (166) of the first valve body (117) bears on the sealing seat of the second valve body (118).
21. Pressure cap according to at least one of Claims 18 to 20, characterized in that the radially interior valve body part (165) of the first valve body (117) accommodates the vacuum valve body (157).
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2000112184 DE10012184A1 (en) | 2000-03-13 | 2000-03-13 | Sealing cap for vehicle radiator; has inner part with valve arrangement having valve bodies biased against seal seats inside cap, where valve bodies are lifted by excess pressure inside radiator |
| DE10012184.5 | 2000-03-13 | ||
| DE10034762.2 | 2000-07-18 | ||
| DE2000134762 DE10034762A1 (en) | 2000-03-13 | 2000-07-18 | Sealing cap for vehicle radiator; has inner part with valve arrangement having valve bodies biased against seal seats inside cap, where valve bodies are lifted by excess pressure inside radiator |
| PCT/EP2001/002734 WO2001069057A1 (en) | 2000-03-13 | 2001-03-12 | Sealing cap |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2400891A1 true CA2400891A1 (en) | 2001-09-20 |
Family
ID=26004817
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002400891A Abandoned CA2400891A1 (en) | 2000-03-13 | 2001-03-12 | Pressure cap |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1264087B1 (en) |
| CA (1) | CA2400891A1 (en) |
| DE (2) | DE10034762A1 (en) |
| WO (1) | WO2001069057A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114856795A (en) * | 2022-04-25 | 2022-08-05 | 周辉 | Automobile water storage bottle pressure cap with good sealing performance |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006050845A1 (en) | 2004-11-09 | 2006-05-18 | Reutter Metallwarenfabrik Gmbh | Safety closure for steam-pressurized containers of household appliances |
| DE202004017790U1 (en) * | 2004-11-09 | 2006-03-23 | Reutter Metallwarenfabrik Gmbh | Security lock for steam pressure container in household appliance such as steam iron has connecting drive between inner and outer parts controlled through valve |
| CN101303090B (en) * | 2007-05-11 | 2011-11-23 | 厦门灿坤实业股份有限公司 | Steam pressure release valve |
| DE202007017507U1 (en) | 2007-12-05 | 2009-04-16 | Heinrich Reutter Gmbh & Co. Kg | Spring for valve assembly and valve assembly with such a spring |
| DE102011078293B4 (en) * | 2011-06-29 | 2017-06-29 | Röchling Automotive AG & Co. KG | Expansion tank with a liquid check valve body and a relative to this movably received on this gas vacuum valve body and such a valve structure supporting lid for a surge tank |
| FR3011306B1 (en) * | 2013-10-01 | 2016-02-05 | Illinois Tool Works | VALVE, COOLANT DEGASSING ASSEMBLY, AND COOLANT DEGASSING METHOD |
| DE102018000707A1 (en) | 2018-01-30 | 2019-08-01 | Daimler Ag | closure element |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH326823A (en) * | 1955-02-04 | 1957-12-31 | Theodor Bell & Cie Ag | Pressure equalization arrangement, in particular as a vent and ventilation valve for fuel containers |
| DE3436702A1 (en) * | 1984-10-06 | 1986-04-10 | Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart | DEVICE FOR SECURING THE COOLANT CIRCUIT OF AN INTERNAL COMBUSTION ENGINE |
| DE4220631C1 (en) * | 1992-06-24 | 1993-03-11 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | Valve arrangement for cooling circuit of IC engine - has at least two excess pressure valves and switch valve for change of pressure between excess pressure valves |
| DE19753592A1 (en) * | 1997-12-03 | 1999-06-10 | Heinrich Reutter | Sealing cover |
-
2000
- 2000-07-18 DE DE2000134762 patent/DE10034762A1/en not_active Withdrawn
-
2001
- 2001-03-12 EP EP01931510A patent/EP1264087B1/en not_active Expired - Lifetime
- 2001-03-12 WO PCT/EP2001/002734 patent/WO2001069057A1/en active IP Right Grant
- 2001-03-12 CA CA002400891A patent/CA2400891A1/en not_active Abandoned
- 2001-03-12 DE DE50109001T patent/DE50109001D1/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114856795A (en) * | 2022-04-25 | 2022-08-05 | 周辉 | Automobile water storage bottle pressure cap with good sealing performance |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1264087A1 (en) | 2002-12-11 |
| EP1264087B1 (en) | 2006-02-22 |
| WO2001069057A1 (en) | 2001-09-20 |
| DE10034762A1 (en) | 2002-01-31 |
| DE50109001D1 (en) | 2006-04-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |