WO2009027047A2

WO2009027047A2 - Negative stream pressure rinse

Info

Publication number: WO2009027047A2
Application number: PCT/EP2008/006873
Authority: WO
Inventors: Frank R. Kolb
Original assignee: Kolb Frank R
Priority date: 2007-08-27
Filing date: 2008-08-21
Publication date: 2009-03-05
Also published as: DE102007040624A1; WO2009027047A3

Abstract

At least one rinse container is utilized for the cleaning of structures and containers used for storing fluids charged with solids, such as rain water, mixed water, or waste water, wherein the fill level of the fluid in the storage basin may vary per filling process. Said rinse container contains a rinsing fluid, such as well or ground water, or the storage fluid itself. In order to be able to store a rinse fluid in the rinse container, a pressure differential device and a closing device are required. The pressure differential device generates a low pressure in the rinse container as opposed to the ambient pressure, by means of which the rinse fluid is pushed into the container. In order to convert the full potential energy of said fluid column into kinetic energy, and thus into a friction force for the distance of coarse materials, the pressure differential must be balanced as quickly as possible such that the ambient gas can flow into the rinse container through a large balancing orifice. A closing device is utilized in order to close the balancing orifice, wherein the closing device is pressed onto a sealing element always with the same force by an actuating device. The closing device is opened for the rinsing operation, and the potential energy of the rinsing fluid is utilized for cleaning the base of the storage container.

Description

Beam vacuum flushing

description

For the cleaning of buildings and containers, which serve for the storage of solids-laden liquids (storage liquid) such as rainwater, mixed water or wastewater, at least one washing container is used, the level of liquid in the storage tank can vary per filling. This rinsing container contains a rinsing liquid, such as well or groundwater, or the storage liquid itself. For the rinsing container there are mainly two variants, on the one hand, in which the container is open at the top and has at least one flushing opening, which is closed by at least one flap and, on the other hand, the one in which the rinsing container is completely closed except for the at least one rinsing and equalizing opening.

After emptying the storage tank in the first variant, the rinsing liquid is mechanically retained in the washing container by flaps or released for the flushing process by opening the flaps in the basin for cleaning the bottom. In the second variant, a differential pressure is generated in the washing container, which is less than the ambient pressure, so that the ambient pressure, in particular the atmospheric air pressure, pushes the liquid into the washing. The differential pressure (negative pressure) is maintained until the reservoir is emptied and the flushing process is triggered. By opening a compensation opening in the upper region of the washing container, which is closed by a closure element, in particular by a valve, a pressure compensation can take place and the liquid column is discharged through the flushing opening for cleaning the bottom of the storage tank.

For the further embodiments, the first variant is not considered further, since the disadvantages of this variant due to the process and by the surrounding medium are too pronounced (tightness, clogging of the mechanical connecting parts, low storage height and thus low spud lengths, etc.).

The other versions relate exclusively to the second variant, which works with a differential pressure to fill the rinse tank. The essential components of this system are a device for opening and closing the compensation opening of the washing container, a device for generating the pressure difference and at least one connecting line between the at least one rinsing and storage container. In order to convert the full potential energy of the liquid column into kinetic energy and thus a high drag force for the bottom cleaning, the pressure difference must be compensated as quickly as possible and the ambient gas can flow into the washing container through a large compensation opening. For this reason, the compensation opening of the washing container must have a large passage cross-section, wherein the diameter of the compensation opening should advantageously be at least 0.5 m.

A closure element, which is a device for opening or closing the compensation opening, initiates and regulates the pressure compensation during the flushing process. A device for generating the pressure difference leads to a lowering of the pressure in the at least one rinsing container, in which the at least one compensation opening is closed. Before and during the filling process of the washing container due to the higher ambient pressure, the at least one washing opening of the washing container is sealed by the washing liquid with respect to the surrounding atmosphere. In order for the liquid column to flow from the washing container into the storage tank as loss-less as possible, it is advantageous to design the flushing opening as a connecting line

For closing the compensation opening different closure elements are known. In DE 39 15 076 C2, a float-operated valve body closes the compensation opening. The valve body is directly connected to a lever on which the float in the vertical direction applies a closing force. If the storage tank is emptied, then the flushing process is then triggered directly because the necessary control line has also run empty and so takes place aeration of the washing. The compensation opening in the washing compartment is severely limited in its area, since the closing pressure of the valve body during emptying of the storage tank can correspond at most to the ambient pressure, ie at the given boundary conditions of 1 bar. In addition, the lever mechanism is wetted by the grog-loaded liquid, so that the float weight is changed by deposits and braided fiber materials. As a result, the force on the valve body for closing or opening the compensation opening varies because it reduces the closing force by additional deposits and increases the opening force. The maintenance of a secure operation of the device is thus substantially increased. The opening process of the closure device can not be defined, since the pressure difference for venting the rinsing chamber on the weight of the float, the bearing losses of the lever and the pressure difference in the control line and thus of contamination in this depends. Due to the selected configuration of the connecting line in DE 39 15 076 C2 between the washing and the storage tank arise high deflection losses of the washing liquid during the rinsing process. This reduces the energy needed to clean the bottom of the storage tank. The variants in DE 42 21 569 A1, EP 0 576 981 B1 and in DE 296 OO 520 U1 each show different embodiments of a diaphragm valve. In DE 42 21 569 A1 and EP 0 576 981 B1, the sealing on the valve seat takes place in a radially inclined direction and in DE 296 00 520 U1 in a radially horizontal direction. When closed, the membrane balloon, which is a combination of valve body and valve stem, projects beyond the valve seat. At the beginning of the rinsing process there is a pressure relief of the membrane balloon, which does not abruptly coincide due to its geometric expansion and its elasticity, and thus can not directly release the entire surface of the compensation opening for pressure equalization. As a result, an opening delay occurs, which prevents the ambient gas at the pressure equalization, which leads to an energy loss of slower flowing water column and extremely noisy flow noise. In addition, the membrane material is subject to increased aging due to the mechanical pressure load, since it is also used as a sealing element, and the chemical stress. As a result, the expansion of the membrane and thus its volume increases, so that the time for pumping the membrane to achieve the same pressure, longer. Another disadvantage is that the membrane for the sealing line abuts the usually sharp-edged seat of the closure element. This leads to microcracks in the membrane and with increasing operating time to leaks, so that the function of the closure element is no longer guaranteed.

In US 4,905,325 a generic device for sealing a container for an aircraft toilet is shown. The device for sealing consists of a valve with a two-day valve body. The valve body consists of a carrier plate which is coated in the direction of the valve seat with a frusto-conical elastomer cap. The elastomer cap has the function of a sealing element, which can compensate for unevenness on the valve seat at the same time. Since the sealing between the valve body and the valve seat by a sealing element which is attached directly to the valve seat, this acts on the same force or the same pressure as on the valve seat. In US 4,905,325 the sealing is provided by this valve construction for liquids, whereby the forces due to the much higher density and viscosity of liquid fluids to the sealing element are substantially lower than compared to gaseous fluids. Therefore, for the present application for gaseous fluids, the sealing element would be subjected to a high sealing force on the valve seat in order to ensure a secure closing of the compensation opening. As a result, a large mechanical wear on the sealing element is caused and it can lead to jamming of the valve in the necessary large passage area of the valve in this, which limits a cleaning of the storage tank or makes impossible. The wear on the sealing element leads to increased maintenance, especially for earth covered reservoir with rinse tank to a high operating cost both cost and Safety reasons. Furthermore, the structure and the control of the valve in US 4,905,325 are very expensive and therefore associated in the production with high production costs.

The invention is intended to provide a method and / or a device which are easy to handle and inexpensive in the production and operation of the flushing device, and in particular allow a level independent operation, the closing of the compensation opening as fast as possible and at almost maximum Level in the storage tank is to minimize the energy input to produce the pressure difference, and allow a quick full release of the entire surface of the compensation opening, so that the maximum energy is provided for the flushing process.

This is achieved with the features of claims 1 and 7, respectively. Preferred developments are specified in the subclaims.

The invention is based on a method for storing a rinsing liquid, which consists of a reservoir with a rinsing container, which have a quadrangular, circular or polygonal base surface and may be constructed symmetrically or asymmetrically, and a storage container which may be open or covered, wherein the Rinse tank includes the rinse liquid. So that the washing compartment can be filled into the storage tank regardless of the filling level, the filling level in the storage tank must completely cover the opening or the connecting pipe in the bottom area of the washing compartment. The maximum filling level of the rinsing liquid can go almost to the ceiling of the rinsing container.

In order to minimize the hydraulic losses, the two containers are connected by at least one connecting line, the inlet / outlet opening for the rinsing liquid in the storage container advantageously at least the same height of the outlet opening in the storage container of coarse and solids-laden liquid or above.

For opening and closing the compensation opening of the washing container is located above the liquid level, a closure device, which is hereinafter referred to as a valve. The valve can be installed standing or hanging. To assist the opening process by the pressure equalization, preferably offers a standing installation method. The valve preferably has a planar valve body with an actuator, whereby the vertical position of the valve body can be changed. The valve body is pressed against the valve seat by means of the actuating device. The valve body and / or the valve seat can be designed as a statically acting sealing element or a statically acting sealing element. element included. With this closure device equalization openings with a diameter of up to 2 m and more can be realized.

When opening the valve, the entire area of the valve body is suddenly released by the valve body and thus the slightest delay of the pressure equalization is made possible. As a result, the potential energy of the liquid column can be almost completely used for the bottom cleaning of the storage container or the storage tank.

Due to the fact that the valve body does not protrude into the compensation opening and by limiting the maximum flow velocity through the compensation opening, the flow noise during pressure equalization between the purge and the storage tank are minimized. This noise minimization is particularly advantageous in reservoirs that are near residential areas and / or not covered by earth. The use of multiple equalization ports on a purge chamber further reduces the ventilation noise and provides even ventilation of the purge bin.

The planar valve body allows small actuation paths to be achieved, so that the installation height of the closure device or of the valve can be minimized. The actuating force of the valve for controlling the actuator is independent of the liquid level in the storage container and can be made by mechanical, hydraulic and pneumatic means. Particularly advantageous is the structure of the actuating force pneumatically, since due to the low viscosity of gases, the opening process for the valve can be done fastest.

By means of the valve seat is a Wegbegrenzung of the valve, so that in a corresponding embodiment of the valve seat and / or the valve body always applied the same force on the sealing element and the yield strength is met, whereby the wear of the sealing element is almost negligible or minimized. By a flat valve seat or valve body, the seal can be achieved with a flat support position of the sealing element.

The opening and closing of the valve is controlled by the level in the storage tank. The level per accumulation event is evaluated via a tendency detection, which determines, for example, the rise in the liquid level per unit time by means of an ultrasound probe, or via the inflowing amount into the storage container. When the rate of increase of the liquid level over a defined time interval or amount is nearly zero or zero, the equalization port is closed by the valve. As a result of this procedure, the rinsing chamber can be filled to the maximum with no additional energy in the free-flow inlet. Another advantage of this type of valve control is that the operation of the pressure differential device and thus the energy costs can be reduced, since the gas space between the rinsing liquid and the boundary cover of the washing minimized and thus the running time (operating and maintenance costs) of Druckdifferen-in- u ng is limited to the pressure reduction to the almost smallest degree.

The pressure differential device serves to lower the pressure in the washing container relative to the ambient pressure. The pressure difference can be generated by vacuum pumps or blowers as well as by jet pumps. However, a system inherent disadvantage of vacuum pumps or blowers is when the sucked gas, as in this application, has a high moisture content. The seal within the vacuum pump is made by a liquid film, for which almost exclusively low-viscosity oil is used as the sealing liquid. The sealing liquid is hygroscopic and thereby absorbs a high proportion of the liquid from the sucked gas. The movements of the pistons and the difference in temperature between the aspirated gas and the pump head, a liquid portion of the gas is mixed into the sealing liquid, so that an emulsion is formed which does not allow complete sealing of the pump. Because of this, the pump can only produce little or no vacuum. In order to prevent the complete failure of the pump, the operating time must be increased until the pump head has heated enough so that the liquid portion from the emulsion can be discharged back to the pressure side exhaust gas. However, this increases the wear on the pump and increases the maintenance and maintenance costs.

The use of a gas dehumidifier leads to a cost disadvantage and to a dwell time and maintenance problem due to the necessary gas flow rates. The gas dehumidifier increases the suction side inlet pressure of the vacuum pump, so a higher performance pump must be used. As a result, the cost share increases both by the vacuum pump and by the dehumidifier. Furthermore, a sufficiently dimensioned gas dehumidifier must be used to compensate for all media and seasonal fluctuations in the gas humidity. However, the large fluctuation range in the gas humidity causes the maintenance intervals to be short and the exchange rate of the dehumidifying element to be high, which on the one hand reduces the operational stability and on the other hand increases the operating cost.

By using a jet pump, the disadvantages of the vacuum pump or a vacuum blower can be completely avoided. A jet pump has no moving parts and the seal to the negative pressure side can be done statically, for example with a ball valve. The jet pump uses to generate the difference express the pressure shift between the static and dynamic pressure components (Bemoulli equation). The jet pump consists of a main pipe and a suction pipe for gas suction, which are interconnected. In the area of the gas-tight connection, the main pipe has a constriction (Venturi), which is provided with at least one opening to the side of the suction pipe. Through the main pipe, a fluid (for example water or air) is conveyed at a relatively high speed. In the region of the constriction, an increase in the velocity of the fluid occurs and thus a pressure shift between the potential and the kinetic component. Due to this displacement, ambient gas is forced into the suction pipe, which mixes with the fluid in the main pipe and exits at the end thereof, for example, into the storage container for the solids-laden liquid. By the jet pump, a negative pressure of about 85% (at 1 bar ambient pressure about 150 mbar) are generated to the ambient pressure. Since the jet pump does not require a separate seal such as a vacuum pump, the operating time depends only on the vacuum to be generated or the level in the washing container.

The driving medium for the jet pump can be fluids, for example the liquid in the storage tank or a gaseous medium such as ambient air. When using the liquid in the storage tank as a driving medium, it proves to be particularly advantageous to install the jet pump at the bottom of the storage or Spülbehälters to minimize the intake losses, and the suction pipe must end above the highest level in the washing. With the use of a gaseous fluid, such as ambient air, as the driving medium, the suction pipe of the jet pump is to be arranged above the highest liquid level of the washing container, for example on its ceiling or side wall. As a result, a short gas pipe can be realized with low pressure losses, which can be installed, for example, in an opening in the ceiling or the valve seat. By this arrangement, the washing container can be completely filled with rinsing liquid and thereby the greatest benefit-cost factor can be achieved because the freeboard between level and upper level is not present or is minimized.

If the jet pump is used on the bottom of the storage or rinsing container, the solids-laden liquid can be used as the driving medium for the jet pump during differential pressure generation. By the differential pressure, the driving medium is enriched with gas from the intermediate space above the rinsing liquid and discharged with the driving medium into the storage container. The biphasic jet exiting at high pressure into the surrounding liquid of the storage container can be used during the pressure difference generation to resuspend coagents located on the storage container bottom. By this pre-cleaning of the storage tank sole is already a large part of the solid or contaminants discharged during the storage tank emptying and improves the subsequent flushing of the storage tank bottom by the rinsing liquid.

When using a gaseous fluid as a driving medium for the jet pump, this fluid can also be used inexpensively as the actuating medium of the actuator, if it consists for example of a bellows or a pneumatic cylinder.

In order to store the rinsing liquid in the rinsing container or to release it as soon as possible during rinsing, a conventional valve, which constitutes a rigid unit of valve body and valve stem, can not be used. To carry out the method presented here, a valve is used, which consists of at least one valve body with at least one actuating device, wherein the actuating device has the function of a variable valve stem. Due to the necessary surface of the compensation opening for ventilation of the washing container, which has a diameter of more than 0.5 m in many applications, it is advantageous to form the valve body as a separate element relative to the actuating device.

Through this functional separation preferably a plurality of similar actuators can be used, which can exert a uniform operating force on the valve body and the actuation volume is small. During the opening process, the actuating medium, such as air or low-viscosity oil, is suddenly released from the actuator and pressed by the differential pressure and gravity (vertical installation) of the valve body in the direction of the support plate. The actuating device, in particular a bellows, opposes the valve body during the opening process only a small inertia, whereby the entire opening area for pressure equalization is available and thus the potential energy contained in the liquid column can be used almost completely for cleaning. Since the vertical travel of the valve body is low, no further guidance of the valve body is necessary other than the actuator, whereby the costs for the production of the closure device are minimized. If the separate actuator consists of an elastic material such as rubber or silicone, positional deviations of the valve seat can be compensated.

In order to completely release the entire cross section of the compensation opening during the opening process, a planar element, in particular a plate, for example of steel or stainless steel, can be used for the valve body. In addition to elastic elements, such as in particular bellows or rubber cylinders, sliding elements can also be used for the actuating device, in particular threaded rods. The actuating device can also consist of at least one threaded rod, which is arranged displaceably in a two-part nut. During the rinsing process, the two halves of the nut are pulled apart and thereby the threaded rod dearretiert, so that the valve body releases the compensation opening.

The diameter of the valve body can be made from several decimeters to several meters in diameter and used. To ensure a gastight seal between valve seat and valve body, a sealing element must be present. Since the contact pressure of the valve body on the valve seat on the diameter of the valve seat / body, the lifting height and aging phenomena and other boundary conditions depends, the valve seat and / or the valve body should be designed so that the closing pressure on the sealing element is always constant. This can be achieved, for example, in that the sealing element is inserted into an annular groove which limits the stroke of the valve body and thereby the sealing element can be compressed only in a defined area. By this structure is excluded that the yield value of the material for the sealing element is exceeded and destroyed by an excessive pressing force, the restoring force of the sealing element. In an example flat sealing element, the stroke can be limited by a simple rolled ring, which can serve as a holding element for the sealing element at the same time.

Due to the size of the valve body and the necessary closing pressure to push the liquid column in the washing or to keep in this, increases in a completely flat valve body, the material thickness with increasing diameter disproportionately. In order to be able to apply the same forces with a smaller thickness of the valve body and thereby reduce the material costs, the valve body may have a more favorable shape of the forces of the cross-sectional shape such as a semicircle or an ellipsoid. The cross-sectional shape can be used for any opening surfaces of the valve or the valve body, for example, round, square or polygonal. In order to release the full passage area, the height position, in the inlet direction of the gaseous medium, for pressure equalization of the highest point of the cross-sectional shape should be identical to the valve seat. This can be done for example by an outer collar on which, for example, at the same time the sealing element is present.

By a special configuration of the valve seat and / or body, in at least one of the two (seat or body) a sloping sealing surface or

Having sealing edge, the sealing element, for example, a metallic or composite organic material may be applied directly to the valve seat or the valve body or both. This embodiment variant has the advantage that the sealing element can not be loosened or jammed during the flushing process, wherein in this variant the yield strength of the material of the sealing element can be exceeded in order to increase the sealing ability.

In order to accelerate the opening operation of the valve with respect to a pressure and gravity operation, the valve body may be provided with a pulling or pushing element which pushes or pulls it when opened in the direction of the carrier plate. In order to achieve an automatic acceleration of the opening process, the tension or pressure element can be performed, for example, as a spring, which is stretched when the valve is closed and relaxed when it opens. Thereby, the speed of the valve opening can be advantageously increased.

It is advantageous for the pressure differential device to have as few moving parts as possible, in order to achieve a high level of operational reliability with respect to the contents (for example moisture, dust particles, solvent vapors, fibrous substances, etc.) of the removed gas from the rinsing container. For this reason, a jet pump is particularly suitable as a pressure differential device. A jet pump has no moving built-in parts. The suction pipe is connected to the main pipe so that the taper expands again for internal pressure displacement. As a result, solid particulate matter in the gas, especially air, can not cause clogging in the pressure differential device. The gas humidity has no influence on the operation of the jet pump, since it has no sealing elements or sealing liquid. Likewise, a solvent-containing gas can be removed without any problems, since no organic materials have to be used for the construction of a jet pump.

In order to minimize the hydraulic inlet and outlet losses and the entrance vortex during the flushing process in the washing with the rinsing liquid through the connecting line, constrictions are provided on at least two sides of the washing container, which favor the entry of the washing liquid in the connecting line from a hydraulic point of view. The constrictions should preferably be performed symmetrically and in parallel, so that mixing within the water body of the washing liquid are low and a uniform outlet of the washing liquid is achieved in the storage container. The transition angle to the side wall of the storage container or to the partition wall should preferably be between 120 to 150 ° to the vertical. Due to the constrictions results in a nozzle-shaped cross-sectional area, which should have the geometry of a Laval nozzle in the washing container for hydraulic reasons. If the entrance surface in the washing container and the outlet surface in the storage container were almost at a height, then the connecting line would have to allow a strong deflection of the washing liquid during the flushing process, thereby resulting in high hydraulic losses. From a hydraulic point of view, it is therefore better to arrange the entry surface in the washing container at least partially above the entry surface into the storage container. As a result, the turbulence during the flushing process are reduced and designed the deflection hydraulically cheaper. Due to the symmetrical design of the connecting line with the almost identical entry and exit angles, the loss values of the connecting line can be minimized.

In industrial applications, the liquid in the reservoir may also contain volatile hydrocarbons (refineries) or odorous substances (slaughterhouses). By lowering the pressure difference during the filling of the washing container, these critical substances from the liquid in the gas phase of the washing can solve. For these reasons, it may be necessary that the connecting line, which allows a gas exchange between the two containers after flushing and may contain a residual amount of liquid, can be closed between the successive flushing and filling operations of the storage container. It is particularly advantageous if the closure can act automatically on at least one surface of the connecting line in the flushing or storage tank. This can be done for example by at least one automatic buoyancy-controlled cover plate. In this case, the material of the cover plate may have a lower density than the liquid in the storage container or the cover plate may be connected to a buoyant body, so that the connecting line is opened during the filling process of the storage container. At the end of the filling process, the cover plate can be locked in this position or close again during emptying of the storage container. In the second variant, it is particularly advantageous to make the entire mechanism of the cover plate made of low-density materials and the joints smooth, so that the hydraulic resistance of the cover plate during the flushing process is low.

In the following the invention will be explained with reference to drawings. Show it:

Fig. 1 Schematic structure of the storage tank with purging in a sectional view, each with a storage and washing and closure and pressure differential device

Fig. 2 Schematic structure of the storage tank with purging in a sectional view, each with a storage and washing container and closure and pressure differential device, wherein the storage and the washing container are connected by a connecting line

Fig. 3a Schematic diagram of the closure device shown in section in the open state

Fig. 3b Schematic diagram of the closure device shown in section in the closed state Fig. 4a Schematic diagram of the closure device shown in section in the actuated and closed state with a flat valve seat

Fig. 4b schematic diagram of the closure device shown in section in the actuated and closed state with prism-shaped valve seat

4c schematic diagram of the closure device shown in section in the activated and closed state with stepped valve seat

Fig. 5 schematic diagram of the closure device shown in section in the actuated and closed state with a spring to assist the opening process

Fig. 6 Schematic diagram of the top view from the washing on the split valve seat with sealing element and side boundary

Fig. 7a sectional view of the groove-like valve seat without sealing element

Fig. 7b sectional view of the groove-like valve seat with sealing element in the open state

7c sectional view of the groove-like valve seat with sealing element in the closed state

Fig. 8 sectional view of the connecting line between the memory and

rinse tank

Fig. 9a Schematic diagram in section of a temporarily acting cover plate in the closed state Fig. 9b Schematic diagram in section of a temporarily acting cover plate in the opening state Fig. 1 shows the sectional side view of the rinsing process, consisting of at least one storage tank 1, which serves through a partition in the storage container 2, which serves for intermediate storage of coarse and solid laden liquid, and the rinse tank 3, for the intermediate storage of the rinsing liquid, the the liquid of the storage container can exist, is divided. In order to be able to produce a pressure difference between the storage and washing container, the liquid level in the storage container must be higher than the backflow element 5. As a result, a minimum liquid level HR forms, which closes the rinsing container with respect to the storage container by ΔH. During the intermediate storage of the solids-laden liquid in the storage container, it can be stowed up to the operating liquid level HB.

In order to fill the washing container as completely as possible and to minimize the operating time of the jet pump 6, 27 and thus the energy consumption, the closure device 7 closes only at the time at which the maximum operating fluid level is reached. Thereafter, the jet pump 6, 27 generates a pressure difference, which causes the liquid in the rinse tank to rise to the height Hs. When the storage container has been emptied through the discharge opening 4, the closure device is opened, the pressure difference is compensated and the liquid flows from the washing container into the storage container, the kinetic energy of the liquid at the sole or the deposits in the storage container producing a dragging force, whereby the existing deposits are removed from the sole.

If the suction tube 27 of the jet pump 6, 27 executed only to the lower edge of the closure device 7, the liquid level can be stowed in the storage tank to the height HM and also be present in the washing. The height of the closure device 7 must be limited to the thickness of the ceiling of the washing container 3.

In FIG. 2, the identical rinsing process has been shown in section for at least two separate containers 2, 3. The two containers are hydraulically coupled by a connecting line 25. This embodiment is particularly advantageous if the topological or geological boundary conditions or the land ownership conditions do not allow a combination of flushing and storage tanks in a storage tank.

3a shows the section through the closure device 7 in the unactuated open state. The actuating medium for the actuator 10 is compressed air, which is supplied via the supply line 14 of this, which is designed as a bellows. At the top of the washing container 3, the compensation opening 9, which is surrounded by a cover plate 26, is present. The compensation opening 9 is associated with the 1.4

The sealing of the end plate 26 takes place with respect to the washing container 3 by a sealing strip 18. The actuator 10 is connected to a support plate 12, the force stresses on the holding plate 13 again transferred to the end plate 26 and from this in the building of the Rinse tank 3 are introduced. The introduction of force can also be made directly from the holding plate 13 into the structure of the washing container 3. During the flushing process, the flow guidance of the gaseous ambient fluid is indicated as indicated by the flow filaments 15.

3b shows the sectional view of the closure device 7 in the closed state. The actuating device 10 has pressed through the actuating medium, the valve body 8 against the sealing element 11 on the end plate 26 and thus completed the compensation opening 9 of the washing compartment 3 with respect to the surrounding medium.

For the function of the closure device 7, due to the size of the valve body 8, the valve seat 16 is of great importance. In Fig. 4a, the closure device 7 is shown with a flat valve seat 16 in the actuated and closed state in section. The stroke of the valve body 8 is adjusted by the stroke limiter 17 so that the peripheral sealing element 11, which is designed in this illustration as a flat membrane, can only be compressed to the upper edge of the stroke limiter 17. The stroke limiter 17 ensures that the elastic limit of the sealing element 11 is not exceeded, regardless of how high the contact pressure between the valve seat 16 and the valve body 8 is. The end plate 26 of the compensation opening 9 is sealed relative to the cover 19 of the washing container with an additional sealing strip 18 with respect to the surrounding atmosphere.

4b shows the section of the closure device 7 in the actuated and thus closed state for a composite valve body 8. The valve body 8 consists of two layers, wherein the upper layer acts as a sealing element 11 and for example made of a soft flowable material such as polytetrafluoride may consist of ethylene. The second layer acts as a support member for receiving the closure and liquid holding forces, it can be made for example of stainless steel. The valve seat 16 is designed in this variant as a circulating prism, which penetrates the sealing element 11 except for the support element. Due to the composite construction of the valve body no additional receiving or fixing element for the sealing element 11 must be provided. Due to the flow behavior of the material for the sealing element, the pressure difference between the rinsing and the storage tank is maintained. In Fig. 4c, the cut-off closure element is shown with a stepped valve body 8 in the actuated and closed state. The circumferential sealing element 11 seals here on two sides, once in the vertical and inclined directions. As a result, the reliability of the sealing element is increased and the sealing element is not overstressed by the additional mechanical stroke limitation. Another advantage of this exemplary embodiment of the closure device is that no solid particles can be deposited on the inclined surface of the sealing element 11 from the surrounding gaseous fluid. As a result, the probability that the sealing element 11 could be destroyed by mechanical means, almost impossible.

Fig. 5 shows the section through the closure device, in which the opening operation of the valve body 8 by a pressure element, in particular a spring 20, is supported. During the lifting operation of the valve body 8 for closing the closure device, the spring 20 is biased. The bias voltage is held by the pressure element frame 21 and the spring 20 on the valve body 8 to its opening. During the opening process, the valve body 8 is additionally pushed away from the valve seat 16 by the force of the spring 20 and thus the opening process for the inflowing gaseous fluid is shortened. As a result, the flow noise can be minimized and the sinking of the liquid in the rinse tank without delay.

In Fig. 6 is a plan view of the washing container 3 is shown on the compensation opening 9 without valve body. Due to the required passage cross-section of the compensation opening 9, the valve seat 16 and the valve body, there is a need, for manufacturing reasons, to introduce only low stresses, in particular in the welding configuration of the valve seat, into the end plate 26 or the valve body , The entry of the material stresses can be minimized by a split valve seat 16. The split valve seat 16 consists of individual segments, which are arranged so that they form, for example, a circumferential groove in which the sealing element 11 is inserted. Due to the segmented structure, the stresses can be distributed better by heat input or by the use of two different materials. Another advantage is that the sealing element 11 can move freely in the valve seat 16 regardless of the load condition (closed, open) and thus does not exceed the yield point or jamming can take place within the valve seat 16. By the side boundary 33 of the valve seat 16 transverse forces can be intercepted on the valve body, since the side boundaries 33 have a greater height than the valve seat. At the same time, the side delimitations 33 can be designed so that the valve body is centered by them during the closing process. FIG. 7 a shows the cross section of a two-part valve seat 16, which is fastened to the end plate 26 in the region of the compensation opening 9. The valve seat 16 consists of an outer 34 and inner 35 delimiting element delimiting a U-shaped inner surface 36, in which the sealing element is inserted. In this case, the height HD of the valve seat 16 is designed such that the sealing element sits in a freely movable manner in the delimited area 36.

Fig. 7b shows the cross section of the valve seat 16 with inserted sealing element 11. The sealing element 11 is loosely on the two cam-shaped projections of the outer 34 and inner 35 delimiting element of the valve seat 16 at. The lower ends of the two limiting elements 35, 35 are not completely connected to the end plate 26, since in the production of the end plate 26 with valve seat 16, the lowest stresses are introduced into the material.

If the closure element is closed, as shown in cross-section in FIG. 7 c, the freely movable sealing element 11 is compressed between the valve body 8 and the end plate 26. The height HD ensures that the pressure on the sealing element 11 is independent of the pressure on the valve seat 16 and thus the yield strength of the sealing element 11 is not exceeded. The expansion of the sealing element 11 in the radial direction can be compensated by the valve seat 16 shown here. Due to the closing pressure, two sealing surfaces Do, Du form, which ensure that the rinsing container in the ceiling area is closed in a gas-tight manner.

In order to convert the potential energy of the liquid column as completely as possible into kinetic energy and then into a drag force, the design of the connecting line between the flushing and the storage tank is of great importance. In Fig. 8, a possibility of the configuration of the connecting line 25 is shown in section. The inlet filling of the end wall 22 and the inlet filling of the partition wall 23 should have a hydraulically favorable angle α, which should preferably be in a range of 120 to 150 °. The profiles for the preparation of the inlet filling can be made for example of concrete or steel sheet. The radii of the infill fillings depend on the volume of liquid in the rinse tank. The outlet filling at the sole 24 should, in order to make the deflection of the flow direction of the liquid column from the vertical to the horizontal hydraulically favorable, seamlessly without jump and with a large outlet radius, preferably of 5 times ΓM. By this shaping of the connecting line 25 of the Coanda effect can be used for fluid media, whereby less turbulence of the liquid occur at the outlet of the connecting line. The height ΔH indicates the smallest hydrau- lically possible deflection radius, which in turn depends on the amount of liquid and in which preferably the deflection angle in the connecting line 25 is between 120-150 °.

9a shows in cross-section a closed cover plate 31, which automatically closes the connection line 25 to the outlet opening into the storage container after the rinsing process until the next filling of the storage container 2. When the storage container 2 is emptied, the float 32 acts as closing weight on the cover plate 31, which rests on the backwater element 5. The liquid level FL in the connecting line 25 can reach a maximum height HBI after emptying the storage container 2. If volatile or odor-intensive substances are present in this liquid or in the rinsing container 3, they can not escape into the atmosphere of the storage container 2, or only to a limited extent, since this is prevented by the closed cover plate 31. Since the existing volume in the washing container 3 is substantially smaller than in the storage container 2, the volatile or odor-intensive substances in the washing container 3 can be sucked off, treated or compensated by a modified process strategy.

9b shows in cross-section the cover plate 31 during the filling process of the storage container 2. By the flowing liquid into the storage container, the liquid level FL increases over the height HB1, so that lifted by the float 32, the cover plate 31 of the sole 29 of the backwater element 5 becomes. As a result, the liquid can flow into the connecting line 25 and the rinsing container 3 with the volatile and / or odorous substances again close to the storage container 3. By the rotary joint 30, the cover plate 31 is able to float with increasing liquid level FL so far until the float 32 abuts against the partition wall of the storage container. When emptying, the cover plate 31 lowers again down to the sole 29 of the backwater element 5. In order to minimize the hydraulic losses during the flushing process, the inlet surface A in the washing container 3 is arranged partially higher than the inlet surface B into the storage container 2.

LIST OF REFERENCE NUMBERS

1 = storage tank

2 = storage tank 3 = washing container

4 = exhaust vent

5 = backwater element

6 = main pipe

7 = closure device 8 = valve body

9 = equalization opening

10 = actuating device

11 = sealing element

12 = support plate 13 = retaining plate

14 = supply line for the actuating medium

15 = Streams of gas flow during the cleaning process

16 = valve seat

17 = stroke limitation 18 = sealing strip

19 = cover of the washing container

20 = spring

21 = printing element frame

22 = inlet filling of the end wall 23 = outlet filling of the sole

24 = inlet filling of the partition

25 = connecting line

26 = end plate

27 = suction pipe 28 = obturator

29 = sole of the storage container

30 = rotary connection

31 = cover plate

32 = float 33 = side boundary of the valve seat

34 = outer limiting element

35 = inner boundary element

36 = inner surface between the two boundary elements

Claims

claims

1. A method for rinsing a storage tank (1), which includes at least one storage container (2) for storing coarse and solids-laden liquid, wherein the liquid level per filling process in the storage container (2) may vary, and a rinsing device (3, 5 28) for storing and releasing a rinsing liquid for rinsing the at least one storage container, wherein the rinsing device comprises: a rinsing container (3) for receiving the rinsing liquid; at least one arranged in the lower region, in particular in the bottom region of the washing container

Opening and / or connecting line (25) for discharging the rinsing liquid from the washing and / or at least one connecting line for supplying the rinsing liquid into the washing, wherein the discharging and feeding the

Rinsing fluid can also be carried by the at least one opening and / or connecting line in the ground, and at least one in the upper region, in particular in the ceiling region of the washing compartment arranged equalization opening (9); and a closure device (7) associated with the compensation opening, with which the compensation opening can be closed; and at least one pressure differential device (6, 27, 28), with which the gas, in particular air, in the washing container above the

Liquid level of the rinsing liquid removed and thereby a differential pressure is generated so that the liquid is pressed by the ambient pressure from the storage container into the washing, which can thus be used as a cleaning liquid, characterized in that the closure device (7) is closed only at the time if in the storage container (2) almost no increase in the liquid level through the inflowing and / or outflowing, loaded with coarse and solids liquid is more observed.

2. The method according to claim 1, characterized in that the passage area of the compensation opening or the compensation openings is designed for the gaseous fluid such that a maximum velocity of the fluid during the rinsing process of about 10 m ³ / (m ² s) may occur.

3. The method according to claim 1 or 2, characterized in that the at least one compensation opening (9) with at least one valve seat (16) and at least one closure device (7) is configured so that the force for closing the closure device (7) regardless of the force is that acts on the at least one sealing element (11).

4. The method according to claim 1, 2 or 3, characterized in that for generating the pressure difference in the washing container, a jet pump (6, 27) is used.

5. The method of claim 1, 2, 3 or 4, characterized in that the jet pump (6, 27) both for differential pressure generation in the washing container (3) and for resuspension of coarse and solids in the storage container (2) or for cleaning the sole of the storage container (2) is used.

6. The method according to one or more of claims 1-5, characterized in that the driving medium of the jet pump (6, 27) for the differential pressure generation and / or as an actuating medium of the actuating device (10) is used.

7. rinsing device (3, 5-28) for storing and releasing a rinsing liquid for rinsing a storage tank (1), wherein the rinsing device comprises: a rinsing container (3) for receiving the rinsing liquid; an opening and / or connecting line (25) arranged in the lower region, in particular in the bottom region, of the washing container (3) for discharging the washing liquid from the washing container, and in particular for feeding the washing liquid into the washing container; a compensation opening (9) arranged in the upper area, in particular in the ceiling area, of the washing compartment; and a closure device (7) associated with the compensation opening, with which the compensation opening can be closed; wherein the closure means comprises a valve body (8) and a

Actuating device (10) for actuating the valve body, and wherein the compensation opening is associated with a valve seat (16) for the valve body (8) and at least one sealing element (11) on the valve seat and / or valve body, characterized in that the valve body (8 ) is formed as a rigid element separately from the actuator (10).

8. Apparatus according to claim 7, characterized in that the valve body (8) is designed as a flat element, in particular as a plate.

9. Apparatus according to claim 7 or 8, characterized in that the actuating device (10) consists of at least one elastic, in particular a pleated or rubber bellows, and / or displaceable body, in particular a threaded rod exists.

10. Apparatus according to claim 7, 8 or 9, characterized in that the valve body (8) and / or the valve seat (16) is formed, in particular with an annular groove or a raised edge, that regardless of the actuating force of the actuating device (10 ) is always the same force on the at least one sealing element (11), advantageously an elastic plastic ring or a rubber flat membrane, is exercised.

11. The device according to one or more of claims 7-10, characterized in that the valve body (8) consists of a pressed semicircular or ellipsoidal hollow body, in particular in the form of a basket arch bottom, with circumferential edge, wherein the center of the body and the sealing element or the inclusion of the sealing element (11) on the body have the same height.

12. The device according to one or more of claims 7-11, characterized in that the sealing element (11), which consists in particular of a plastic or rubber disc or a rubberized steel or stainless steel disc or a soft metal disc of copper, lead or gunmetal, at the same time the valve body (8) and / or the valve seat (16).

13. Device according to one or more of claims 7-12, characterized in that the valve body (8) with at least one pressure or tension element, in particular a spring (20) is connected, which is arranged so that the opening operation by supports the pressure or tension element and thus the valve body is moved faster in the direction of the support plate (12).

14. The device according to one or more of claims 7-13, characterized marked, that the pressure differential device is a jet pump (6, 27), the at least one main tube (6) for a driving medium, in particular gas or liquid and at least one suction pipe (27) having a shut-off device (28), wherein the main tube includes a taper, in particular a Venturi, whereby a pressure shift takes place, so that the ambient pressure pushes the rinsing liquid into the washing and the gas above the rinsing liquid can escape through the suction tube.

15. Device according to one or more of claims 7-14, characterized in that the connecting line (25) between the rinsing (3) and the storage container (2) is designed so that the hydraulic losses are minimized during the rinsing process by advantageously the inlet filling of the end wall 22 and the inlet filling of the partition wall 24 preferably have the same angle α and thereby form a nozzle-shaped cross-section, wherein the angle α is preferably in a range of 120 ° to 150 °.

16. The device according to one or more of claims 7-15, characterized in that the connecting line (25) is designed so that the inlet height of the rinsing liquid in the washing container above the outlet height in the storage tank and / or the connecting line is a cross-sectional area in the form of a ring segment , wherein preferably the deflection angle in the input and

Outlet range between 120 to 150 °.

17. Device according to one or more of claims 7-16, characterized in that the connecting line (25) at least on one side, preferably in

Storage tank, at times by a closing device, such as a buoyancy-actuated flap, is closed, so that if volatile or odorous liquid components, such as hydrocarbons, are present in the rinsing liquid, this not emptied storage tank from the remaining in the connecting line rinsing liquid or only to a limited extent can escape into the atmosphere of the storage container.