Abstract:
The invention relates to a valve, in particular for a fluid-regulated heating and/or cooling system of a motor vehicle, having a valve chamber ( 18, 218 ), with at least one inlet conduit ( 14, 214 ) and at least one outlet conduit ( 16, 216 ) branching off from it, and having a displacement rod ( 26, 226 ) movable by an actuator, and having at least one valve member ( 20, 220 ), which is located on the displacement rod ( 26, 226 ) and cooperates with at least one valve seat ( 24, 224 ) of the valve chamber ( 18, 218 ), and at least one damping element ( 20, 220 ) is provided, which slows down the speed of the displacement rod ( 26, 226 ) upon closure of the valve ( 10, 12 ). 
     According to the invention, it is provided that the at least one damping element ( 20, 220 ) simultaneously acts as a valve member ( 20, 220 ).

Description:
BACKGROUND OF THE INVENTION 
   The invention is based on a valve for a fluid-regulated heating and/or cooling system of a motor vehicle. 
   Such valves are known, for instance from fluid-regulated heating and/or cooling systems of motor vehicles. A valve member secured to a displacement rod of the valve regulates the flow between an inlet conduit and at least one outlet conduit. The valve can be triggered for instance as a function of temperatures in the heating and/or cooling system of the motor vehicle, or in the passenger compartment. Valves of this type at present primarily still have an electromagnetic actuator, which closes the valve by means of an excited magnet coil, causing the actuator to act on an armature connected to the displacement rod of the valve. A disadvantage of this type of valve is that the actuation of the actuator causes an abrupt closure and thus leads to pressure disturbances in the fluid system of the cooling system. 
   The water valves known at present for the heating and/or cooling system of motor vehicles are moreover sometimes very loud when they perform the switching function described. The noise develops among other reasons because of inadequate damping of the mechanical operating motion of the displacement rod. 
   From German Patent Disclosure DE 197 54 257 A1, a magnet valve for a fluid-regulated heating and/or cooling system is known which has an inlet conduit and at least one outlet conduit, whose mutual communication is established in a first switching position and blocked in a second switching position by an electromagnetically switched valve member. The valve of DE 197 54 257 A1, on its valve shaft, has an elastic element in the form of a spring, which slow down the speed of the valve shaft upon closure of the valve member. To that end, the spring element is disposed between the valve member and the valve shaft. 
   In a second version of the water valve of DE 197 54 257 A1, a damping disk is also solidly disposed on the valve shaft and moves within a damping chamber that is filled with a viscous fluid. To adapt the damping action for the valve member, a plurality of throttle bores are provided in the damping disk, which determine the resistance of the damping disk to the viscous fluid and thus slow down the motion of the displacement rod in the desired way. 
   From U.S. Pat. No. 4,364,541, a safety valve is know that has a two-piece displacement rod. While the first part of the displacement rod is connected to an actuator for the valve, the second part of the valve has two valve members spaced apart from one another. The two parts of the displacement rod of U.S. Pat. No. 4,364,541 are displaceable counter to one another in the axial direction of the displacement rod. The relative movability of the two parts of the displacement rod is mediated via an elastic spring element. 
   A disadvantage of the safety valve described in U.S. Pat. No. 4,364,541 is that complicated mutual decoupling of the two parts of the displacement rod. In addition, the relative movability of the two parts of the displacement rod in this prior art must be adjusted by an additional spring element. A valve of this kind, like the valve of DE 197 54 257 A1, requires complicated assembly, not least because there are so many individual parts. Furthermore, the complex design of the moving parts of the valve makes increased demands on the actuator, which in turn means increased weight and a large installed volume of the valve unit. 
   SUMMARY OF THE INVENTION 
   The valve according to the invention, having the characteristics of the main claim, has the advantage over the prior art that simple, fast assembly in the production of valves of this generic type is possible. Furthermore, the weight of the valve can be reduced markedly. The damping element advantageously also takes on the sealing function at the valve seat of the valve. In this way, many components are eliminated in the assembly of the valve, further reducing its complexity and likelihood of failure. 
   Because the valve member is at the same time designed as an elastic damping element, additional elastic components, such as spring elements, can be omitted. 
   Advantageously, the valve member is mounted movably on the displacement rod of the valve. The damping element, for instance in the form of a rubber seal, can be displaced axially in certain regions on the displacement rod. Because of this displaceability of the damping element, combined with a limiter for its displacement travel, damping in the operating direction of the displacement rod of the valve upon closure is achieved. Both the elastic properties of the material comprising the valve member, which advantageously simultaneously acts as a damping element, and the relative movability of the displacement rod with respect to the valve member lead to a slowing down of the speed of the displacement rod upon closure of the valve. This is associated with a reduction in noise development and in the mechanical stress upon activation of the valve of the invention. 
   The limiter for the displacement travel of the damping element can be achieved in a simple, advantageous way as a mechanical stop for the valve member. For that purpose, a damper ring or stop plate can be connected, for instance integrally, with the displacement rod. 
   Advantageously, on its side toward the damping element, this mechanical stop has a surface contour which is designed such that upon closure of the valve, this surface contour can plunge successively into the elastic damping element. In this way, a damping characteristic curve for the valve that leads to progressive damping of the displacement rod of the valve in the closing operation can be achieved. 
   In an advantageous embodiment, the surface contour of the motion limiter for the damping element has a spokelike basic structure originating at the central displacement rod. In this way, as the contour plunges into the elastic damping element, there is a constant increase in the contact area of the damping element on the mechanical stop of the damper ring, leading to progressive braking of the displacement rod. 
   In a further advantageous embodiment of the valve of the invention, the surface contour of the mechanical stop tapers to a point in the direction of the damping element. Because of the modification of the surface contour and/or by an adaptation of the elasticity of the damping element, the damping behavior and thus the noise development in valve operation can be favorably affected and adapted to requirements. 
   Advantageously, besides having a special surface contour, the mechanical stop can be embodied integrally with the displacement rod. Alternatively, however, limiters for the stroke of the elastic damping element that can be mounted and thus replaced are also possible. By changing the mechanical stops, the damping characteristic of the valve of the invention can then be varied easily for specific applications. 
   In an advantageous feature of the valve of the invention, the valve member acting as a damping element can be pressed onto the displacement rod in a simple way. 
   The use of the valve of the invention, for instance in the embodiment of an electromagnetic timing valve for the cooling and/or heating system of a motor vehicle, is possible with advantages, compared to the corresponding valves in the prior art. 
   The valve of the invention in a simple way enables a marked reduction in noise development upon switching of the valve with a simultaneous reduction in the structural parts and components required for the damping. The valve of the invention furthermore assures faster installation, and thus reduced costs in the production of the generic valves. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     In the drawing, one exemplary embodiment of a valve of the invention is shown, which is to be explained in further detail in the ensuing description. The drawing figures, their description, and the claims include numerous characteristics in combination. One skilled in the art will also consider these characteristics individually and put them together to make further useful combinations. 
     Shown are: 
       FIG. 1 , a cross section through a valve of the invention in the embodiment as an electromagnetic timing valve; 
       FIG. 2 , a section through the valve chamber of a valve of the invention in the open valve position; 
       FIG. 3 , a section through the valve chamber of a valve of the invention of  FIG. 2 , as closure of the valve begins; 
       FIG. 4 , a section through the valve chamber of a valve of the invention of  FIGS. 2 and 3 , with the valve closed. 
       FIG. 5 , the valve member of a valve of the invention in a detail view; and 
       FIG. 6 , the displacement rod of a valve of the invention, in perspective, in the region of the valve member. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   The valve  10  of the invention, in the embodiment of a magnet valve  12  of  FIG. 1 , has an inlet conduit  14  and an outlet conduit  16 , which communicate with one another via a valve chamber  18 . The valve chamber  18  is formed by a valve chamber unit  21  inserted into the valve housing  19 . Between the conduits  14  and  16 , a valve member  20  is provided, which is disposed movably in the valve chamber  18  and which cooperates, via an elastic valve cone  22 , with a valve seat  24  of the valve chamber  18 . The valve seat  24 , in the exemplary embodiment of  FIG. 1 , is embodied as an elastic ring that defines the valve chamber  18  relative to the inlet conduit  14 . 
   Because of the elastic valve seat  24 , the valve cone  22  of the valve member  20  need not necessarily also be elastic, in this exemplary embodiment. 
   The valve member  20  is axially displaceably supported on a displacement rod  26 , and on the end of the displacement rod  26  toward the valve seat  24 , it is secured on the displacement rod  26  by a securing plate  28 . On the side of the valve member  20  remote from the valve seat  24 , there is a damper ring  30 , in the form of a mechanical stop plate  32 , which is solidly connected to the displacement rod  26  and which, as a limiter, restricts the axial movability of the valve member  20  along the displacement rod  26 . 
   Also secured to the displacement rod  26  are a stripper ring  33  and an actuator  34  that cooperates with a magnet coil  36  and forms the electromagnetic actuator  60  for the valve of the invention, in the embodiment of FIG.  1 . The armature  34  is axially displaceably guided in an armature chamber  38  of the actuator  60  by a guide bush  40 . 
   The fluid pressure, which prevails for instance in a heating and/or cooling system to be regulated in a motor vehicle, and which is established in the inlet conduit  14  of the valve of the invention, displaces the valve member  20  into its open position, so that the valve cone  22  is lifted from the valve seat  24 . If the magnet coil  36  is excited, an armature core  42 , which is connected to a short-circuit yoke  44  of the actuator  60 , attracts the armature  34 , counter to the force of a valve spring  46  disposed in the armature chamber  38  and counter to the fluid pressure in the inlet conduit  14 , and the valve member  20  closes the communication between the inlet conduit  14  and the outlet conduit  16  of the valve  12  by pressure the valve cone  22  against the valve seat  24 . 
   In  FIGS. 2 ,  3  and  4 , this closing operation is shown once again in its essential phases, in order to illustrate the valve of the invention clearly.  FIG. 2  is a detail of a valve  10  of the invention in the region of its valve chamber  218 . An inlet conduit  214  and an outlet conduit  216  lead into the valve chamber  218 , which in this exemplary embodiment is formed by a one-piece valve chamber unit  221 . The communication between the inlet conduit  214  and the outlet conduit  216  is mediated by a valve member  220 , which cooperates with a valve seat  242  of the valve chamber  218 . In the exemplary embodiment of  FIG. 2 , the valve seat  242  is embodied integrally with the valve housing  248 . It is understood that other versions of the valve seat of a valve  10  of the invention are equally possible. 
   The valve member  220  is actuated via a displacement rod  226  by an actuator, not identified by reference numeral, which need not necessarily be a magnetic activator. Also located on the displacement rod  226 , in the region of the valve member  220 , is a securing plate  228 , which on one side limits the axial movability of the valve member  220  on the displacement rod  226 . 
   In  FIG. 5 , the end of the displacement rod  226  toward the valve seat  224  is shown once again in detail. The valve member  220  comprises an elastic valve cone  222 , which cooperates with the valve seat  224 . On the side of the valve cone  222  remote from the valve seat  224 , the valve member  220 , in the exemplary embodiment of  FIGS. 2 and 5 , comprises an elastic valve ring  250 , which in this exemplary embodiment is solidly connected to the valve cone  222 . 
   In other embodiments of the valve  10  of the invention, the elastic valve ring  250  can be embodied integrally with the valve cone  222  and can for instance comprise the same elastic sealing rubber material as the valve cone  222 . 
   On the side of the displacement rod  226  toward the valve seat  224 , the valve member  220  is locked on the displacement rod by means of the securing plate  228 . to that end, the valve member  220  can be everted over the stop plate  228 , which in the exemplary embodiment has a larger diameter than the displacement rod  226 . The stop plate  228  can be embodied integrally with the displacement rod  226 , or it can be fixed on the displacement rod by means of currently used joining methods. 
   On the side of the valve member  220  remote from the valve seat  224 , a stop plate  232  acting as a limiter is fixed on the displacement rod  226  in such a way that a relative motion of the valve member  220  between the securing plate  228  and this stop plate  232  is possible. The stop plate  232  can be either embodied integrally with the displacement rod or joined solidly to the displacement rod in other ways quite familiar to one skilled in the art. On its underside  252  oriented toward the valve member  220 , as can be seen particularly from  FIG. 6 , the stop plate  232  has a spokelike surface structure  254 , which protrudes from the surface  256  of the underside  252  of the stop plate. 
   A detail of the stop plate  232  is shown in perspective in  FIG. 6 , with the valve member removed for the sake of simplicity and clarity. In this exemplary embodiment, the stop plate  232  mounted on the displacement rod  226  has three spokelike protuberances  258 , pointing radially outward from the displacement rod  226 , which taper to a point in the direction of the valve member  220 , for instance in the direction toward the securing plate  228 , and which decrease in their height radially outward over the surface  256  of the underside  252  of the stop plate  232 , beginning at the displacement rod  226 . 
   Surface contours  254  of the underside  252  of the stop plate  232  that are different from that shown in  FIG. 6  are understood to be equally possible. 
   In the case of the open valve, as shown for instance in  FIG. 2 , the valve member  220  is spaced apart from the underside  252  of the stop plate  232  on the displacement rod. If the valve is closed by actuation of its actuator, then by the mediation of the displacement rod  226 , first the valve cone  222  takes a seat on the valve seat  242 , as is also shown in FIG.  3 . The further closing motion of the displacement rod  226  then leads to a relative motion of the displacement rod  226 , with the stop plate  232  secured to it, relative to the valve member  220 . In the process, the surface contour  254  on the underside  252  of the stop plate  232  plunges into the elastic material of the valve member  220 . This brakes the downward motion of the displacement rod  226  and markedly reduces any possible noise development upon closure of the valve. 
   The surface contour  254  on the underside  252  of the stop plate  232 , in the exemplary embodiment shown in  FIG. 6 , is characterized by a constant increase in the cross section counter to the operating direction of the displacement rod  226 . As the surface contour  254  of the stop plate  232  plunges into the elastic material of the valve ring  250 , the result is therefore a progressive damping characteristic curve. 
   The damping behavior of the valve of the invention and thus also its noise development in valve operation can be affected positively by the modification of the surface structure  254  of the stop plate  232  and by a variation in the hardness of the valve ring  250 . This can advantageously also be accomplished without changing the material properties of the actual valve cone  222 . To that end, the valve ring  250  can for instance have a different material from the valve cone  222 . It is also possible to separate the valve ring  250  from the valve cone  222  and to embody the valve member  220  in multiple parts, so that an additional relative motion becomes possible between these two elements of the valve member  220 . 
   At the end of an operating stroke, mediated by the actuator, for closing the valve of the invention, the underside  252  of the stop plate  232  rests virtually flat on the surface of the valve ring  250 , as  FIG. 4  shows. 
   The valve of the invention is not limited to the embodiments shown in  FIGS. 1-6 . 
   In particular, the valve of the invention is not limited to an embodiment as an electromagnetically activated timing valve. Hydraulic or pneumatic actuators are for instance equally possible, along with further embodiments for the valve of the invention. 
   Nor is the valve of the invention limited to the presence of only a single valve member with an associated stop plate; it can advantageously also be used for valves with two outlet conduits, for instance, with correspondingly two associated valve seats. In that case, an embodiment of the valve of the invention with two valve members and the associated stop plates may be provided. 
   The valve of the invention is not limited to the fluid direction of the fluid to be regulated that is shown in the exemplary embodiment of FIG.  1 . 
   The valve of the invention is in particular not limited to the form of the surface contour of the stop plate for the valve member as shown in the exemplary embodiments. In particular, this surface contour is not limited in its shape to the embodiment shown in FIG.  6 . Other surface structures, tapering to a point or to a blunt tip toward the valve member, depending on the damping behavior desired, can also be realized for the valve of the invention. The number and shape of the protuberances, which are shown as spokelike in  FIG. 6 , on the underside of the stop plate are not limited to any numerical boundary or other restriction in shape, either. It is understood that damping contours other than spokelike ones are equally possible. 
   The valve of the invention is furthermore not limited to use in fluid-regulated heating and/or cooling systems for motor vehicles.