Patent Application
20060054224
The invention relates to a control valve for feeding a cleaning fluid to the nozzle opening of a nozzle of a washing bay for vehicle windscreens, as well as a nozzle arrangement and a washing device.
A control valve for feeding a cleaning fluid to nozzle openings of nozzle of a washing device for vehicle windscreens has become known from FR 0 102 306, with the valve having two outlets that are couplable with the nozzle openings, the valve having an inlet that is couplable with a feed pump for the cleaning fluid, and a valve body influencing the path of the cleaning fluid from the inlet to the outlets being provided. The valve is controlled electromagnetically. It has been proven disadvantageous that a power supply must be provided at the valve to control it. Moreover, the provision of such a valve is complicated and expensive on account of the electromagnetic components.
The object of the present invention is therefore to provide a control valve of the type mentioned initially, as well as a nozzle arrangement and a washing device enabling the purposeful control of the valve to be accomplished with ease. In particular, the valve is to be controlled without the use of electricity.
The aforementioned object is achieved by a control valve characterised in that the valve body is controllable in at least two valve positions via the cleaning-fluid pressure.
This entails the advantage that no electrically powered components are to be provided at the control valve. Moreover, there is no need for components that control the valve body by additional means. The invention has the advantage that control of the valve body is accomplished exclusively via the cleaning-fluid pressure. Depending on the pressure of the cleaning fluid, the valve body will be found in a predetermined valve position that influences the path of the cleaning fluid from the inlet to the outlets.
An advantageous embodiment of the invention is characterised in that the valve body is constructed as a sliding element, particularly as a longitudinal sliding element. Longitudinal sliding elements have the advantage of being displaceably mounted in an axial direction between the valve positions. Such a mounting can be effected quite simply. Indeed, instead of longitudinal sliding elements, rotary slide elements can be provided for which have the advantage of being rotatably mounted around their longitudinal axis for controlling the cleaning fluid. This leads to a very compact control-valve construction.
A particularly advantageous embodiment is yielded when the valve body is constructed as a piston slide element, in particular with two piston sections having different-sized pressure-application surfaces. Piston slide elements of this type can be manufactured with little effort and expense, and are easily mountable in appropriate cylinders. In the case of piston-sliding elements with different-sized pressure-application surfaces, different-sized surface forces prevail at the piston sections, depending on the pressure of the cleaning fluid; these surface forces effect a displacement of the piston-sliding element into the respective valve position, according to the pressure of the cleaning fluid.
A particularly favoured embodiment of the invention is characterised in that the valve is constructed as a multi-way slide valve, in particular as a 3/2-way longitudinal slide valve or as a 3/3-way longitudinal slide valve. Valves of this type provide for a total of three connections, to wit, one inlet and two outlets. Depending on the application, two or three valve positions are conceivable.
The use of a valve body in the form of a ball element can also be provided for according to the invention.
A control valve of simple construction is yielded when the valve body can be toggled back and forth between at least two valve positions. In the case of a longitudinal sliding element, the valve positions lie in the axial direction of the valve body. If the valve body is constructed as a rotary slide element, then the valve positions are dependent upon the angle of rotation of the valve body. The provision of just two valve positions has the advantage of both valve positions being final valve positions, in which the location of the valve body can be defined by stops.
An advantageous valve is characterised in that, in a first valve position, especially in a low-pressure position, the valve body connects the inlet with the first outlet, or with the first and second outlet. This allows in the first valve position, cleaning fluid to be fed to the nozzle opening or openings, which is/are coupled with the first outlet or with the first and second outlet.
According to the invention, provision can preferably be made for the valve body in a second valve position—in particular in a high-pressure position—to separate the inlet from the first outlet, and to connect the inlet with the second outlet. In this way, the cleaning fluid is rerouted to the nozzle opening or openings that is/are coupled with the second outlet.
A particularly favoured embodiment of the invention is yielded when a bypass circumventing the valve body in one valve position and connecting the inlet with an outlet is provided for, the input or output of the bypass being closed in at least one other valve position. This has the advantage that a cylindrical valve body can be used that is cost-efficient to manufacture and fit. Depending upon the valve position, the inlet is connected with the one outlet via the cylinder recess that takes the valve body, and/or the inlet is connected with the other outlet via the bypass.
It is particularly advantageous when, in a first valve position, for example in the case of low pressure, the input and output of the bypass (and hence the one outlet as well) are open. In this instance, the other outlet is closed off by the valve body. In a second valve position, for example in the case of high pressure, the output of the bypass is closed via axial displacement of the valve body, causing the one outlet to be separated from the inlet. In this valve position the other outlet is then released, so that cleaning fluid can then flow from the inlet into this outlet.
Furthermore, it is conceivable for a basic position of the valve body to be provided for, in particular a zero-pressure position, in which the valve body separates the inlet from both outlets. In this basic or zero-pressure position, the valve body is advantageously in a non-return valve position. This prevents leakage of the cleaning fluid from the openings in the nozzle body.
In order to allow a planned position of the valve body in the different valve positions, provision can be made for the valve body to be supplied in at least one valve position by the spring force of a spring element, in particular of a helical spring.
Here it is advantageous if the valve body is driven by the spring force against a stop in at least one valve position, enabling a defined position of the valve body to be provided.
Moreover, it is conceivable for the valve body in at least one valve position to act solely against the spring force of the spring element, without being driven against a stop. In this case the valve body is to be found in a floating valve position, in which a balance of forces between the spring force and the force arising from the pressure of the cleaning fluid prevails.
The valve is advantageously disposed in the nozzle body of a nozzle. The nozzle encompassing the valve can be manufactured, handled and fitted as a one-part component. A further advantage of this embodiment is that separate connections between the valve and the nozzle, for example in the form of hoses, are not necessary.
On the other hand, it is conceivable for the valve to be disposed between the feed pump and the nozzle. Here, the valve can be constructed as a separate component.
As an alternative to this, it is also possible according to the invention for the valve to be a part of the feed pump and to be disposed inside the feed pump.
The task mentioned at the outset is furthermore solved by a nozzle arrangement with at least one nozzle, and with a control valve according to the invention connected with the nozzle opening of the nozzle and housed in particular in the nozzle body of the nozzle.
Such a nozzle arrangement advantageously provides for the nozzle's suitability for creating different types of fluid jets, depending on the pressure of the cleaning fluid, and hence depending on which fluid channel carries the cleaning fluid to the nozzle opening in question. It is conceivable, for example, that fluid jets in the form of spot jets are created when the cleaning fluid is fed via the one fluid channel, and that a fluid jet in the form of a flat jet is created when the cleaning fluid is fed via the other fluid channel.
Moreover, the aforementioned task is solved via a washing device for vehicle windscreens with a nozzle arrangement according to the invention, and with a feed pump coupled to the nozzle arrangement for the cleaning fluid.
In this connection, it is advantageous if the valve inlet is connected via a fluid pipe to a feed pump controlling the supply of the cleaning fluid and feeding it at different pressures. Here, the feed pump can be a pump whose speed is controlled or regulated. It is especially advantageous if the pump supplies the cleaning fluid at a different pressure for a different direction of rotation.
The pressure of the feed pump is advantageously controlled as a function of vehicle speed. At a vehicle speed of under 80 km/h, for example, a low pressure of between e.g. 0.2 and 1.4 bar may be created. If the vehicle speed increases to above 80 km/h, the cleaning-fluid pressure achieved by the feed pump is increased e.g. to 1.4 or more bar. At lower speed or pressure, the output of the valve leading to the creation of a flat and/or extensive jet is advantageously opened. At a vehicle speed in excess of 80 km/h, the inlet leading to the creation of a spot jet or a plurality of spot jets is advantageously controlled.
Further advantageous details and embodiments of the invention will be apparent from the following description, in which the invention is described and explained in greater detail by means of the embodiments illustrated in the drawing, which shows:
If the cleaning fluid enters the vortex chamber 34 via the outlet 28, it is vortexed there and fed to the nozzle opening 23 via the outlet section 38. Because of the vortexing, the cleaning fluid leaves the nozzle opening 23 as a flat or tapered jet 46 and strikes the windscreen 42 over a wide area. The geometry of the jet shape 40, 46 consequently depends on which outlet 26, 28 or channel 30, 32 is used to feed the cleaning fluid to the vortex chamber 34. Moreover, it is conceivable for both outlets 26, 28 to be supplied with cleaning fluid, so that a hybrid jet form of both jets 40 and 46 is created.
The feed pump 16 can, for example, be a pump whose speed is controlled or regulated. It supplies the cleaning fluid at different pressures, to wit, on the one hand at a low pressure P1 and a high pressure P2. The low pressure P1 lies advantageously between 0.2 und 1.4 bar. The high pressure P2 lies advantageously above 1.4 bar. It is conceivable for the feed pump 16 to be controlled as a function of the vehicle's speed. Here, provision can be made for the pump to supply the cleaning fluid at the pressure P1 at vehicle speeds below 80 km/h, and at high pressure P2 at vehicle speeds above 80 km/h.
The path of the cleaning fluid coming from the feed pump 16 to the outlets 26, 28 is influenced via the control valve. The control valve 14 is controlled here by the cleaning-fluid pressure in place at the inlet 24 of the valve 14. The valve 14 is pressure-controlled.
The nozzle arrangement 12 can be a nozzle arrangement 12.1 according to
In
In FIGS. 3 to 7, differently constructed control valves 14.1 to 14.5 are illustrated that can be used in a washing bay 10 according to
When the pressure at the cleaning fluid is raised to a low pressure P1, the ball element 50 lifts off from its valve seat 54 against the spring force of the spring element 52. Fluid can then flow into the valve space 56. Here, the low pressure P1 and the spring force of the spring element 52 are matched to one another such that the ball element 50 is floating in limbo between the valve seat 54 at the inlet 24 and a second valve seat 58 at the outlet 26. Because of this, the cleaning fluid can flow out to both outlets 26, 28.
When the cleaning-fluid pressure is raised to a high pressure P2, the ball element 50 is driven against the valve seat 28. This closes the outlet 26. Consequently, the cleaning fluid can now only exit from valve 14.1 via the outlet 28.
When the high pressure P2 or the low pressure P1 is removed, the valve 14.1 is closed owing to the spring force of the spring element 52; the valve then acts as a non-return valve.
Valve 14.2 illustrated in
Valve 14.3 illustrated in
Valve 14.4 illustrated in
Valves 14.1 to 14.5 illustrated in FIGS. 3 to 7 have the advantage that only one pressure-controlled valve body 50, 60, 70, 80 is provided between two or three switching positions. No outside means are required to control the valve bodies. The valves can be designed so small that they can be accommodated within a nozzle body of a nozzle, according to the embodiment as per
Such an embodiment of a nozzle arrangement 12.2 according to the invention is illustrated in
When the pressure of the cleaning fluid is raised to the high pressure P2, the valve body 90 is further displaced against the spring force, causing the outlet 26 to be connected with the inlet 24, and the output 98 to be separated from the outlet 28. Consequently, cleaning fluid then flows via the inlet 24 and the outlet 26 or the channel 30 to the nozzle opening 23.1.
The valve 14.6 integrated in the nozzle arrangement 12.2 has the advantage of managing with one piston slide element 90 which is cylindrical, and consequently does not provide for any different piston sections. A valve 14.6 of this type is easy to manufacture and fit.
The cylinder recess 92 provides for a total of five connections, to wit, inlet 24; input 94 of bypass 96, which is adjacent to inlet 24; outlet 26; output 98 of bypass 96, which is adjacent to outlet 28; and outlet 28. Depending upon the axial position of the valve body 90, cleaning fluid can flow via the inlet 24 to the outlets 26, 28. Here, the axial distance between the input 94 and the output 98 of the bypass 96 is designed to be somewhat greater than the axial longitudinal extension of the valve body 90. This ensures the possibility of the valve body 90 being circumvented via the bypass 96. Moreover, the axial distance between the outlet 26 and the output 98 is designed to be slightly smaller than the axial longitudinal extension of the valve body 90. This ensures that the output 98 is closed off before the outlet 26 is opened, which can prevent a drop in pressure from occurring owing to the outlet 26 and the output 98 or the outlet 28 being open at the same time.
The nozzle arrangement 12.2 illustrated in
Contrary to an arrangement according to
All of the features illustrated in the description, in the drawing and in the following claims may be essential to the invention both individually and in any combination with one other.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102 34 872.3 | Jul 2002 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP03/08292 | 7/28/2003 | WO | 1/26/2005 |
