EP1268993A1

EP1268993A1 - Sealing cap

Info

Publication number: EP1268993A1
Application number: EP01927773A
Authority: EP
Inventors: Heinrich Reutter
Original assignee: Individual
Current assignee: Individual
Priority date: 2000-03-31
Filing date: 2001-03-21
Publication date: 2003-01-02
Anticipated expiration: 2021-03-21
Also published as: EP1268993B1; US20040056034A1; DE10034761A1; WO2001075282A1; DE50108797D1; US7104415B2

Abstract

The invention relates to a sealing cap (11), for openings and containers. The valve arrangement (15) comprises an axiallly displaceable valve body (17), which is held in the direction of the container interior by means of a spring (22) against a first sealing seat (34), on the cap interior. The valve arrangement (15) comprises one single valve body (17), provided with a first axially effective sealing surface arrangement (20) and a second radially effective sealing surface arrangement (21). The axially effective sealing surface arrangement (20) co-ordinates with an axial seal seat (34), surrounding a defined opening (32), connecting to the container interior on the cap inner part (14). The radially effective sealing surface arrangement (21) co-ordinates with a first radial counter sealing surface (61, 62), comprising a bypass (39), for the first flow connection and a second radial counter sealing surface (61), comprising a safety relief opening (69), for the second flow connection.

Description

Title: Cap

description

The present invention relates to a closure lid for openings on containers, in particular on motor vehicle radiators, according to the preamble of claim 1.

In such a closure cover known from DE 197 53 592 AI, the valve arrangement has two valve bodies, of which, in the idle state, the first valve body rests directly against a sealing seat of the inner cover part and the second valve body is pressed against a further compression spring by the spring-loaded first valve body. The release and blocking of the flow connections in a two-stage form is achieved in that the first valve body is lifted from its sealing seat on the inner cover part by means of the second valve body when the first limit value is exceeded, and that the second valve body contacts another sealed seat of the inner cover part when the second limit value is reached creates and thus closes the first flow connection again, and that for the safety level, an intermediate valve body arranged between the first and second valve bodies stands out with its sealing seat from a sealing surface of the second valve body.

Such a cover is, in terms of its valve arrangement, complex in terms of construction, production technology and assembly technology due to the large number of components.

From DE 41 07 525 Cl a closure cover is also known, which may be in two stages for one necessary pressure equalization of the closed container ensures. In this closure cover, the valve arrangement also has two valve bodies which are arranged nested one inside the other, the second valve body being pressed against a sealing seat on the inner cover part by the spring loading of the first valve body. In this arrangement, if the first limit value of the internal container pressure is exceeded, the second valve body lifts off its sealing seat on the inner cover part, taking the first valve body with it, and rests on an opposite sealing surface of the inner cover part when the second limit value is reached. In the security level, the first valve body is lifted off the second valve body.

The valve arrangement of this known closure cover has the same disadvantages as the closure cover mentioned above and, moreover, there is the problem that the sealing seats and sealing surfaces of the two valve bodies and the cover inner part and the axial path of the second valve body have to be coordinated with one another in close tolerances.

The object of the present invention is therefore to provide a cover of the type mentioned, the valve arrangement is structurally, manufacturing and assembly technically united eight.

To achieve this object, the features specified in claim 1 are provided in a closure cover of the type mentioned.

The measures according to the invention ensure that considerably fewer components are required for the valve arrangement of the closure cover, without disadvantages with regard to the two-stage effect in pressure equalization having to be accepted. Furthermore, there are no special ones Measures of tolerance-related adjustment. The individual components are structurally simpler and cheaper to manufacture and assemble.

According to a preferred embodiment, the features are provided according to claim 2, so that a single sealing element is sufficient.

An advantageous embodiment of the axial sealing seat results from the features of claim 3.

With the features of claim 4, an advantageous embodiment of the first radial counter-sealing surface is achieved in such a way that the inner wall of the inner cover part is directly available for this. If the measures according to claim 5 and / or 6 are provided, it is achieved that the closing of the flow connection in the area of the bypass is primarily given by the presence of liquid coolant and not by the increased gas pressure, since then when liquid coolant is present at the entrance of the bypass, a back pressure builds up which moves the valve body further in the axial direction and thus prevents ejection of liquid coolant. In other words, when the internal pressure of the container is increased, the air cushion located above the liquid coolant can escape and contribute to pressure equalization until it is broken down and the liquid coolant is present.

An advantageous embodiment of the radially acting sealing surface arrangement results from the features of claim 7 and / or the features from one or more of claims 8 to 10.

Advantageously, the valve body is in accordance with the features of claim 11 and / or 12 on the inner cover part guided .

In order to simplify assembly, the inner cover part is formed in two parts according to the features of claim 13.

With the features according to one or more of claims 14 to 16, an advantageous arrangement of a vacuum valve body in the sealing cover is achieved.

From DE 197 32 885 AI a cover with safety lock for openings on containers is also known. This safety lock makes it possible to prevent the closure cap from being unscrewed in the event of excess pressure in the container, namely by blocking the closure cover against the filler neck on the container in a non-rotatable manner. This known safety lock uses an axially movable insert which surrounds the inner lid part or its valve arrangement and which is thereby directly exposed to the overpressure prevailing in the container by arranging its inner bottom in the opening of the filler neck. This axially movable insert is axially movable but non-rotatably held in a tubular additional inner part, which sits non-rotatably in the filler neck of the container and against which the closure cap can be rotated. If there is overpressure in the container, the insert is moved axially in the direction of the closure cover and engages in this in a non-rotatable manner. This results in a rotating blockage of the closure lid over the insert and the additional inner part with the filling opening of the container.

The measures taken there for an anti-rotation device or a safety lock are constructive and complex in terms of the number of components to be used. In addition, both the axially movable insert and the tubular additional inner part enlarge the Diameter of the inner cover part of the closure cover or reduce the effective area of the valve arrangement of the closure cover, which has negative effects on the response behavior of the valve arrangement.

In order to remedy this situation, the features according to claim 17 are provided in such a closure cover, so that its anti-rotation device can be manufactured in a structurally and technically simpler manner and thus more cost-effectively in the event of overpressure. This is because the direct derivation of movement from the single valve body means that no additional components are necessary, but also creates an idle between the closure part carrying the thread or the like and the handle element or actuating handle in the event of overpressure. This no-load connection in the event of overpressure has the essential advantage over blocking the sealing cover in the event of overpressure in that the activation of the anti-rotation device becomes apparent and possible use of force in the event of a blockage is excluded.

A further space saving for the valve arrangement results if the features are provided according to claim 18.

With the features according to claim 19, there is a support for the axial movement of the clutch insert. The features according to claim 20 are advantageously provided for guiding the valve body and the coupling insert during the forward and backward movement. It may be expedient to design the guide element in accordance with the features of claim 21. The sleeve element can thus actively return the clutch insert from its disengaged position to its engaged position in connection with the spring coupling. Advantageously, the features according to claim 22 are also provided. Preferred features and arrangements of the compression springs of the spring coupling of the valve body, guide element and inner cover part result from the features from one or more of claims 23 to 26.

In a further embodiment of the engagement and disengagement of the clutch insert, the features according to claim 27 and possibly according to claim 28 are provided.

Further details of the invention can be found in the following description, in which the invention is described and explained in more detail with reference to the exemplary embodiments illustrated in the drawing. Show it:

Fig. 1 in a longitudinal section

Overpressure / underpressure valve arrangement of a closure cover for a motor vehicle radiator in the closed starting position according to a first exemplary embodiment of the present invention,

Fig. 2 in a slightly enlarged half section

1 in a position after a first limit value of the internal container pressure has been exceeded,

3 shows a representation corresponding to FIG. 2, but in a position after reaching a second limit value of the internal container pressure or application of a liquid dynamic pressure,

4 shows a representation corresponding to FIG. 2, but in a position after a third or safety limit value of the internal container pressure has been exceeded, Fig. 5 in a longitudinal section

Closure cover for a motor vehicle radiator with an overpressure / underpressure valve arrangement and an anti-rotation device in the respectively closed or non-activated starting position according to a second exemplary embodiment of the present invention,

6 shows a representation corresponding to FIG. 5, but in each case in one position during the build-up of an excess pressure in the interior of the container,

7 shows a representation corresponding to FIG. 5 in a position after a first limit value has been exceeded, but before a second limit value of the internal container pressure has been reached,

8 shows a representation corresponding to FIG. 5, but in a position after a third or safety limit value of the internal container pressure has been exceeded, and

Fig. 9 is a representation corresponding to FIG. 5, but in a position after reaching the normal pressure inside the container and before returning or canceling the anti-rotation device.

The cover 11 shown in FIGS. 1 to 4 for a motor vehicle radiator, for example, has a cover outer part, which is provided with an actuating handle and on which a cover inner part 14 is held with a vacuum / pressure valve arrangement 15. In the position of use, the closure cover 11 is fixed, for example screwed on, to a radiator neck, not shown. The inner cover part 14 protrudes toward the inside of the radiator in the radiator socket. An O-ring 16 seals the inner cover part 14 against the radiator nozzle wall from. The overpressure part of the valve arrangement 15 is designed in two stages and serves to prevent the cooler from boiling dry in a first overpressure stage and to ensure security against damage to the cooler system due to excessive overpressure in a second overpressure stage.

The overpressure part of the valve arrangement 15 has a single valve body 17 which can be moved axially within the cover inner part 14 between two end positions. The valve body 17 has a profiled ring seal 18, which has both an axially acting sealing surface arrangement 20 and a radially acting sealing surface arrangement 21. The valve body 17 is biased axially inwards towards the inside of the container by means of a compression spring 22 supported on the inner cover part 14.

The inner cover part 14 is formed in two parts and is thus composed of an inner, upper element 25 and an outer main element 26, which is not shown in the outer cover part and in which the inner, upper element 25 is fixed in a sealed manner. The inner, upper element 25 has a coaxial guide ring extension 27 which projects inwards from the ceiling 28 of the element 25. This guide ring extension 27 receives one end of the compression spring 22, which is supported on the inside of the ceiling 28. On the outer circumference side, the guide ring extension 27 serves to axially guide the valve body 17. At the level of the guide ring extension 27, the inner cover part 14 is provided on the outer circumference side with radial outflow openings 29. An O-ring 24 is provided between the inner, upper element 25 and the main element 26 for a tight connection.

The main element 26 of the inner lid part 14 has at its bottom 31 a coaxial throughflow opening 32 which forms a connection between the interior of the container and the interior of the inner lid part 14. The flow opening 32 is

radially outer sealing surface 51, a radially central sealing surface 52 and a radially inner sealing surface 53. The radially inner sealing surface 53 interacts with a vacuum valve body 71 to be described, the radially central sealing surface 52 lies in the rest position of the valve arrangement 15 on the sealing seat 34 of the inner cover part 14 and the radially outer sealing surface 51 lies at the bottom of the annular space 36. In contrast, the radial sealing surface arrangement 21 has two sealing surfaces 56 and 57 arranged at a certain axial distance, between which a recess 58 is provided. Both the upper sealing surface 56 and the lower sealing surface 57, which merges into the radially outer sealing surface 51, lie sealingly against the inner wall 61 and / or 62 of the main element 26 of the inner cover part 14 or the ring insert 38, which is designed as a sealing seat.

In the center of the valve body 17 there is an opening 66 which is closed on the side facing the interior of the cooler by the vacuum valve body 71 of the valve arrangement 15. The vacuum valve body 71 protrudes with its main part 72 through the central opening 66 and is acted upon at its end region by a compression spring 67, which is located at one end on a shoulder of the main portion 72 and at the other end on the outer surface of the inner shoulder of the valve body 17, on which the compression spring 22 rests, supports. In this way, the vacuum valve body 71 with its annular sealing seat 73 is sealingly applied to the radially inner sealing surface 53 of the axial sealing surface arrangement 20 of the profile ring seal 18 of the valve body 17.

In the rest or

The starting operating position, in which a first limit value of the container internal pressure has not yet been exceeded, is any flow connection between the interior of the container and the exterior of the container through the sealing contact of all sealing surfaces O 01/75282

11

51 to 53 of the axial sealing surface arrangement 20 of the profile seal 18 of the valve body 17 on the respective sealing seats 36, 34, 73 of the inner cover part 14 or of the vacuum valve body 71 are closed. In other words, on the profile ring seal 18 of the valve body 17 and on the underside of the vacuum valve body 71, the pressure prevailing in the interior of the container in the form of the air cushion located above the liquid coolant is present through the throughflow opening 32.

If the internal pressure of the container rises above the predetermined first limit value, the valve arrangement 15 of the closure cover 11 reaches the operating state shown in FIG. 2, according to which the valve body 17 lifts against the action of its compression spring 22 with its radially central sealing surface 52 from the sealing seat 34 and the profiled ring seal 18 enters the area of the ring insert 38 such that the two radial sealing surfaces 56 and 57 of the radial sealing surface arrangement 21 of the profile ring seal 18 of the valve body 17 are located below or above the radial channel parts 41 and 42 and thus open the throttle channel 39 at both ends. In this operating state, there has been a balance between the effect of the internal pressure of the container and the counteraction of the compression spring 22. This opens a first flow connection between the interior of the container and the exterior of the container, which leads from the throughflow opening 32 via the U-shaped throttle duct 39 to the outflow openings 29. As a result, air can flow outward from the air cushion located above the liquid coolant and compensate or reduce the excess pressure. If the overpressure is reduced below the first limit value as a result, the valve body 17 again comes into sealing contact with the axial sealing seat 34 of the inner cover part 14.

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Ventilkδrpers 17 given on the free annular face of the guide ring extension 27 of the inner cover part 14. As a result, the above-mentioned overpressure can be reduced via a second flow connection, after which the valve body 17 can be appropriately returned via the various operating states.

The valve arrangement 15 assumes the initial position shown in FIG. 1 when the internal cooler pressure moves between a negative pressure limit value and the first positive pressure limit value. Such pressure conditions prevail, for example, when the vehicle is parked for a longer period of time or when the vehicle is in operation and the cooling fluid in the interior of the cooler is adequately cooled by the wind and / or with fan support. If, for example, the vehicle is stopped after a long journey, a pressure increase may result in the interior of the cooler, due to which the valve arrangement 15 cooler contents (air or water or water vapor) can flow in. If the volume of coolant expands as a result of this after-heating effect in such a way that the container volume is exceeded, this would inevitably lead to coolant emissions. This undesirable effect is prevented in the manner described above in that the operating state of the valve arrangement 15 shown in FIG. 3 is established. If there is a further uncontrolled increase in pressure in the cooling system in this operating state, leakages and other adverse effects due to excessive stress on the cooler container and / or the hose connection points must be prevented. These effects are prevented by the second valve stage according to the state of FIG. 4, which limits the container pressure to a predetermined safety pressure value.

If there is negative pressure inside the cooler and if it falls below a predetermined negative pressure limit, 1, the vacuum valve body 71 with its sealing seat 73 is lifted from the radially inner sealing surface 53 of the profile ring seal 18 of the valve body 17 towards the interior of the cooler. The vacuum valve body 71 is lowered against the biasing force of the compression spring 67, so that a third flow connection between the interior of the cooler and the exterior of the cooler opens in a manner not shown.

The cover 111 shown in FIGS. 5 to 9 for a motor vehicle radiator, for example, has an outer cover part 110 provided with a grip element or an actuating handle 112, on the closure element 113, which is designed here as a screw-on element, an inner cover part 114 with a vacuum / excess pressure valve arrangement 115 hanging and is held relatively rotatable. In the position of use, the cover 111 is fixed, for example screwed on, to a radiator neck, not shown. The inner cover part 114 protrudes toward the inside of the cooler in the cooler neck. An O-ring 116 seals the inner cover part 114 against the radiator nozzle wall. In the two-part outer cover part 110, the cap-like actuation handle 112 is axially fixed on the screw-on element 113, but can be rotated in the circumferential direction. This rotatability is blocked at normal pressure in the interior of the cooler by an axially movable coupling insert 180 for screwing the cap 111 on and off.

The overpressure part of the valve arrangement 115 is designed in two stages and serves to prevent the cooler from boiling dry in a first overpressure stage and to ensure security against damage to the cooler system due to excessive overpressure in a second overpressure stage. The overpressure part of the valve arrangement 115 has a single valve body 117 which can be moved axially within the cover inner part 114 between two end positions. The ti

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Valve body 117 closed on the respective sealing seats 136, 134, 173 of the inner cover part 114 or of the vacuum valve body 171. In other words, on the profile ring seal 118 of the valve body 117 and on the underside of the vacuum valve body 171, the normal or ambient pressure prevailing in the interior of the container in the form of the air cushion located above the liquid coolant is present through the throughflow opening 132.

If the internal pressure of the container rises to a certain amount, which is above the normal pressure, but below a first limit value of the internal pressure of the container, the unscrewing protection of the cover 111 is activated. 6, the valve body 117 is moved upward, so that the profiled ring seal 11§ with its central sealing surface 152 lifts off the sealing seat 134. As a result, the effective area acted upon by the excess pressure, which was previously formed only by the underside of the vacuum valve body 171, increases by the inner axial area of the profile ring seal 118. This larger effective area causes a greater force on the valve body 117 at the same pressure and results in its increased stroke , By means of the lifting movement of the valve body 117, which, however, has not yet released the throttle channel 139, contrary to the action of the first pressure coil spring 183 and the second pressure coil spring 184, the guide element 147 is initially displaced axially relative to the clutch insert 180. Since the first compression coil spring 183, which is supported on the clutch insert 180, is biased by this stroke movement, the clutch insert 180 is axially displaced. As a result of this axial movement of the coupling insert 180 outwards in the direction of arrow A and up to an inner stop on the underside of the actuating handle 112, the coupling insert 180 with its outer diameter larger end is released from the toothing on the screw-on element 113. This disengaging movement of the coupling insert 180 causes the actuating handle 112 relative to the screw-on element 113 Turned empty, so that from a certain defined overpressure (here, for example, 0.3 bar) it is no longer possible to unscrew the cover 111.

If the tank pressure continues to increase, i. H. Above the predetermined first limit value (for example 1.4 bar), the valve arrangement 115 of the closure cover 111 reaches the operating state shown in FIG. 7, according to which the valve body 117 lifts further against the action of its compression spring 122 and the profile ring seal 118 in the region of the Ring insert 138 arrives in such a way that the two radial sealing surfaces 156 and 157 of the radial sealing surface arrangement 121 of the profile ring seal 118 of the valve body 117 are located below or above the radial channel parts 141 and 142 and thus open the throttle channel 139 at both ends. In this operating state, in which the unscrew protection continues to be activated, a balance has been established between the effect of the internal container pressure and the counteracting action of the compression spring 122. This opens a first flow connection between the interior of the container and the exterior of the container

Flow opening 132 leads via the U-shaped throttle channel 139 to the outflow openings 129. As a result, air can flow outward from the air cushion located above the liquid coolant and compensate or reduce the excess pressure. If the overpressure is reduced below the first limit value as a result, the valve body 117 again comes into sealing contact with the axial sealing seat 134 of the inner cover part 114.

On the other hand, if the internal pressure of the container continues to increase during or after the air cushion has escaped and this leads to liquid coolant reaching the underside of the profile ring seal 118 and the vacuum valve body 171, this results due to the very narrow throttle channel 139 (for example in a cross-sectional order of magnitude of a few) CQ X 4-J <#

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can take place, as shown in Fig. 9.

FIG. 9 also shows a possible short-term state of the unscrew protection when the valve body 117 has been returned to its starting position and the actuation handle 112 has been rotated during the activation of the unscrew protection. In this case it could have happened that the coupling insert 180 with its toothing is not exactly over the tooth gaps of the toothing of the screw-on element 113. In this case, in order to return the unscrewing protection from its activated to its deactivated state according to FIG. 5, a short rotary actuation of the actuation handle 112 is sufficient, which causes the outer second compression spring 184, which is under considerable prestress, to guide the guide element 147 downward, contrary to arrow A. emotional. The inner first compression spring 183 is thus relaxed and the guide element 147 takes its outer ring shoulder 181 against the arrow A by contacting the inner ring shoulder 182 of the coupling insert 180, so that the coupling connection between the actuating handle 112 and the screwing element 113 engages again or becomes effective comes. 5 and the cover 111 can be unscrewed from the filler neck of the cooler without risk.

The valve arrangement 115 assumes the initial position shown in FIG. 5 when the internal cooler pressure moves between a negative pressure limit value and a very low positive pressure value of less than 0.3 bar here. Such pressure conditions prevail, for example, when the vehicle is parked for a longer period of time or when the vehicle is in operation and the cooling fluid in the interior of the cooler is adequately cooled by the wind and / or with fan support. If, for example, the vehicle is stopped after a long journey, the interior of the radiator may become blocked result in an increase in pressure, due to which the cooler content (air or water or water vapor) can flow into the valve arrangement 115. If the volume of coolant expands as a result of this after-heating effect in such a way that the container volume is exceeded, this would inevitably lead to coolant emissions. This undesirable effect is prevented in the manner described above. If there is a further uncontrolled increase in pressure in the cooling system in this operating state, leakages and other adverse effects by overstressing the cooler container and / or the hose connection points must be prevented. These effects are prevented by the second valve stage according to the state of FIG. 8, which limits the container pressure to a predetermined safety pressure value.

If there is negative pressure in the interior of the cooler and this falls below a predetermined negative pressure limit value, starting from the operating position according to FIG. 5, the vacuum valve body 171 with its sealing seat 173 is lifted from the radially inner sealing surface 153 of the profile ring seal 118 of the valve body 117 toward the interior of the cooler. The vacuum valve body 171 is lowered against the biasing force of the compression spring 167, so that a third flow connection between the interior of the cooler and the exterior of the cooler opens in a manner not shown.

Claims

claims

Sealing cover (11) for openings on containers, in particular on motor vehicle coolers, with an inner cover part (14) and a first and a second flow connection between the inside and outside of the container and a valve arrangement (15) for releasing and blocking the flow connections in such a way that when exceeded a first limit value of the container internal pressure, the first flow connection is opened, which is then closed again when a second higher limit value is reached, and the second flow connection is opened if a third limit value of the container internal pressure, which is higher than both the first and the second limit value of the container internal pressure, is opened, wherein the valve arrangement (15) has an axially reciprocable valve body (17) which is pressed by a spring (22) in the direction of the interior of the container against a first sealing seat (34) on the inner cover part (14), characterized in that shows that the valve arrangement (15) has a single valve body (17) which is provided with a first axially acting sealing surface arrangement (20) and a second radially acting sealing surface arrangement (21), the axially acting sealing surface arrangement (20) being a one on the inner part of the cover (14) is assigned a predetermined connection opening (32) to the axial sealing seat (34) surrounding the interior of the container and the radially acting sealing surface arrangement (21) has a first radial counter sealing surface (61, 62) which has a bypass (39) of the first flow connection and a safety outflow opening ( 69) is assigned to the second radial counter-sealing surface (61) having the flow connection.

2. Closure cap according to claim 1, characterized in that the axially acting sealing surface arrangement (20) and the radially acting sealing surface arrangement (21) of the valve body (17) are combined in a profile sealing ring (18).

3. Closure cap according to claim 1 or 2, characterized in that the axial sealing seat (34) on the cover inner part (14) is formed by a ring projection (33) projecting from the bottom (31) provided with the connecting opening (32).

4. Closure cover according to at least one of claims 1 to 3, characterized in that the first radial counter-sealing surface is formed by the inner wall (61, 62) of the inner cover part (14), in which a ring insert (38) is received in a first axial region which forms the bypass (39) of the first flow connection.

5. Closure cover according to claim 4, characterized in that the bypass is formed by a U-shaped throttle channel (39) at at least one peripheral point of the inner cover part (14).

6. Cover according to claim 5, characterized in that the ring insert (38) has two axially spaced radial channels (41, 42) through an axial channel (43) between the outer surface of the ring insert (38) and the inner surface of the lid inner part ( 14) is formed.

7. Cap according to claims 1 and 6, characterized in that the radially acting sealing surface arrangement (21) has two sealing surface areas (56, 57), the axial distance between which is smaller than the axial distance between the two radial channels (41, 42) of the bypass (39).

8. Cover according to claims 2 and 7, characterized in that the sealing surface areas (56, 57) are formed by a circumferential clearance (58) in the profile sealing ring (18).

9. Closure cover according to at least one of the preceding claims, characterized in that the second radial counter-sealing surface is formed by the inner wall (61) of the inner cover part (14), in which the safety outflow openings (69) are formed in a second axial region.

10. Cap according to claims 4 and 9, characterized in that the two axial regions of the inner wall (61) of the inner cover part (14) overlap.

11. Closure cover according to at least one of the preceding claims, characterized in that the valve body (17) has a guide sleeve (47) which faces away from the profile sealing ring (18) and which cooperates with a guide ring (27) projecting axially from the inner cover part (14).

12. Closure cover according to claim 11, characterized in that within the guide ring (27) the pressure spring acting on the valve body (17)

(22) is held.

13. Closure cover according to at least one of the preceding claims, characterized in that the inner cover part (14) is axially divided into two.

14. Closure cover according to at least one of the preceding claims, characterized in that the valve body (17) has a central opening (66) through which a vacuum valve body (71) projects, the sealing seat (73) surrounding the central opening (66) on a another axial sealing surface (53) of the valve body (17).

15. Closure cover according to claim 14, characterized in that the further axial sealing surface (53) is part of the axially acting sealing surface arrangement (20) or the profile sealing ring (18).

16. A closure cap according to claim 14 or 15, characterized in that the vacuum valve body (71) is biased against the further axial sealing surface (53) of the valve body (17) by means of a spring (67) supported on the upper side of the valve body (17) ,

17. Closure cover (111) according to at least one of the preceding claims, characterized in that an outer cover part (110), on which the inner cover part (114) is held suspended, is formed by handle and closure elements (112, 113) which can be rotated relative to one another, an axially movable coupling insert (180) is provided for the releasable, rotationally fixed connection thereof, the axial movement of which is derived from the pressure-dependent axial movement of the single valve body (117).

18. Closure cover according to claim 17, characterized in that the axially movable coupling insert (180) within the handle element

(112) of the outer cover part (110) is arranged.

19. Closure cover according to claim 17 or 18, characterized in that between the axially movable coupling insert (180) and the valve body (117) an axial spring coupling (183, 184) is provided for disengaging and / or engaging the coupling insert (180).

Cap according to at least one of claims 17 to 19, characterized in that between the axially movable coupling insert (180) and the valve body

(117) an axially movable guide element (147) is provided.

21. Closure cover according to claim 20, characterized in that the guide element (147) is axially movable within the hollow coupling insert (180) and is held in a maximum pull-out position by end stop elements (181, 182).

22. Closure cover according to claim 21, characterized in that the guide element (147) and the coupling insert (180) are held rotatable relative to one another.

23. Closure cover according to at least one of claims 19 to 22, characterized in that the axial spring coupling (183, 184) surrounds the guide element (147).

24. Closure cover according to at least one of claims 19 to 23, characterized in that the axial spring coupling has a first compression coil spring (183) which is provided between the guide element (147) and the coupling insert (180).

25. Closure cover according to at least one of claims 19 to 24, characterized in that the axial Spring coupling has a second compression coil spring (183) which is arranged between the guide element (147) and the cover inner part (114).

26. Closure cover according to one of claims 23 to 25, characterized in that the pressure coil spring acting on the only valve body (117)

(122) surrounds the compression spring or springs (183, 184) of the axial spring coupling.

27. Closure cover according to at least one of claims 17 to 26, characterized in that the axially movable coupling insert (180) with the handle element (112) of the cover outer part (110) is connected non-rotatably and axially movable relative to this and with the closure element (113) of the The outer cover part (110) can be detachably connected in the circumferential direction by axial engagement and disengagement.

28. Closure cover according to claim 27, characterized in that the connectivity which can be released in the circumferential direction is by an axially directed one

Circumferential toothing of the closure element (113) and coupling insert (180) is formed.