Abstract:
The invention pertains to a method and a device for desalting water by reverse osmosis, particularly for desalting seawater, in which saltwater is introduced under a first pressure into a pressure-compensation device and conducted from pressure-compensation device at a second, higher pressure into a membrane module, wherein desalted water and concentrated saltwater are conducted out of membrane module, wherein the concentrated saltwater conducted out of membrane module is continuously introduced at roughly second pressure into pressure-compensation device and used there to apply roughly second pressure to saltwater introduced into pressure-compensation device and to introduce saltwater into membrane module, and wherein the introduction of concentrated saltwater into pressure-compensation device and the conduction of concentrated saltwater out of pressure-compensation device are accomplished by means of controlled main valves. The main valves are subject to high mechanical stresses, particularly during the opening and closing of the valves. To reduce or avoid these, it is provided according to the invention that secondary valves arranged in parallel with main valves are controlled such that load peaks during opening and/or closing of main valves are reduced.

Description:
FIELD OF THE INVENTION 
     The invention pertains to a method for desalting water by reverse osmosis according to the preamble of claim  1 , as well as to a device for carrying out this method. 
     BACKGROUND OF THE INVENTION 
     Such a method and such a device are described in German Patent Application No. 199 33 147.2. Therein, the saltwater is introduced under a first pressure into a pressure-compensation device and introduced from the pressure-compensation device, under a second, higher pressure, into a membrane module, desalted water and concentrated saltwater being removed from the membrane module. Desalted water is to be understood here as water with a salt content reduced in relation to the saltwater introduced into the device. To increase the efficiency and thus the energy balance for such a method and such a device, it is proposed there that the concentrated saltwater removed from the membrane module be introduced continuously under the second pressure into the pressure-compensation device, and be used there to apply the second pressure to the saltwater introduced into the pressure-compensation device and to introduce the saltwater out of the membrane module. Introduction of the concentrated saltwater into the pressure-compensation device is accomplished with check valves, and draining of the concentrated saltwater out of the pressure compensation device is accomplished here by means of controlled main valves. These controlled main valves are preferably actively controllable, and are arranged in the appropriate connecting lines between the membrane module and the pressure-compensation device or between the pressure-compensation device and the output for the concentrated saltwater. 
     A method as mentioned initially and a device as mentioned initially are known from EP 0 028 913. There, a pump is provided to compensate for pressure losses. 
     The recovery of energy from a highly pressurized fluid by means of a hydraulic motor driven by this fluid is known from DE 24 48 985. Cylinder/piston combinations operating in opposite phase are provided here, but they are connected mechanically by way of connecting rods to a crankshaft, which is in turn driven by a drive unit, to compensate for pressure losses. Several disadvantages are inherent to this system, however, such as a complicated bearing method and guidance of the pistons and connecting rods, since they are subjected to movements in two directions by the crankshaft. A device for desalting water by reverse osmosis, in which main valves and parallel secondary valves are provided for deriving concentrated saltwater from a membrane module and from exchange means, is known from FIG. 1 in U.S. Pat. No. 5,797,429. 
     A device for desalting water by reverse osmosis with two piston/cylinder devices operating in opposite phase is known from U.S. Pat. No. 6,017,200. 
     In known methods and devices, a high pressure is applied to the main valves. If the main valves, are operated, then a high mechanical stress results precisely at the moment of initial opening or at the last moment of closing such a main valve. However, since these main valves are designed for high flow rates, they must be correspondingly large and massive. 
     Since the main valves are relatively slow due to their size and mass, they are exposed to large pressure changes for a relatively long time, particularly at the beginning of the opening process and at the end of the closing process. Since such devices are intended to operate without interruption, if possible, these main valves are thus under a high long-term stress, due to the magnitude and duration of the stress on the one hand, and to the frequency of load alternations on the other. 
     BRIEF SUMMARY OF THE INVENTION 
     The invention is thus based on improving the initially mentioned method and device with regard to the aforesaid disadvantages, and configuring them such that the main valves undergo less wear. 
     The basis of the invention is the knowledge that load peaks occur especially during the opening and closing of the main valves, and the point is to avoid these. This is achieved by the secondary valves, also known as bypass valves, that are provided according to the invention, via which a part of the pressure occurring during opening and closing of the main valves is conducted around the main valves. For this purpose, appropriate secondary lines, in which the secondary valves are arranged, are provided around the main valves. 
     The secondary valves are preferably controlled such that they are opened shortly before the opening or closing of the main valves, and/or that they are opened only during the opening or closing process of the main valves. Otherwise, the secondary valves are normally closed. 
     In an advantageous configuration, the secondary valves have a narrower cross section than the main valves. The cross section of the secondary valves can even be markedly smaller than the cross section of the main valves, and the secondary valves can have a considerably higher pressure resistance. Thus the stress on the main valves can be markedly reduced by suitable control of the secondary valves, and thus their service life can be proportionally increased. 
     The cross section of the secondary valves can be chosen arbitrarily in an alternative configuration of the invention. A contribution to the fluid transport can also be supplied via the cross section of the secondary valves, as can be provided by the appropriate controllers. This means that the secondary valves are opened or closed at the same time as the corresponding main valves arranged in parallel with them, with the difference that the secondary valves are opened somewhat earlier than the parallel main valves, and closed somewhat later than the parallel main valves, to relieve the load on them. 
     A pressure reservoir that is connected to the output for conducting the concentrated saltwater out of the membrane module, and to the input of the pressure compensation device, is provided in a preferred embodiment of the invention. This pressure reservoir is therefore subjected to the same pressure as the concentrated saltwater itself. The purpose of this pressure reservoir is to compensate for the pressure fluctuations that unavoidably occur during valve actuations because of the losses of volume; thus an optimally constant operating pressure is assured in the membrane module. 
     In an additional advantageous configuration of the invention, flow limiters that prevent an abrupt equalization of pressure by limiting the maximum quantity passed are provided in the supply lines to the secondary valves, and thus contribute to a gradual pressure compensation and slow changes of pressure instead of abrupt fluctuations. These [flow limiters] can be differently dimensioned so as to create “flow resistances” of different magnitudes. The flow limiters can also be integrated into the secondary valves, since these have a narrow cross section in any event. 
     In a refinement of the invention, it is provided that the pressure compensation device comprises two piston/cylinder combinations operating in opposite phase, and that the pistons of the piston/cylinder devices are connected by a connecting rod. Such a connecting rod and its functioning is known from EP 0 028 913. Differently from this known connecting rod, however, no pump to compensate for pressure losses is provided in this refinement of the invention. 
     Instead, a drive unit for the connecting rod is provided in a secondary configuration of the invention to compensate for pressure losses. This drive unit can consist in the connecting rod&#39;s having, in a center section, teeth with which appropriately driven pinions engage. The desired operating pressure can thereby be maintained. 
     In the device according to the invention, a high-pressure pump creating a high pressure can be completely omitted, and can be replaced by a pump creating a considerably lower pressure if the pressure that the concentrated saltwater necessarily has at the output of the membrane module is exploited by continuous feedback of this concentrated saltwater into the pressure compensation device to apply pressure to the saltwater pumped into the pressure compensation device. The essential point is for this to take place continuously, since otherwise the pressure in the saltwater supply line from the pressure-compensation device to the membrane module would ease, and would have to be restored by a high-pressure pump. Continuous production of desalted water would not be possible, either. 
     Additional advantageous refinements of the method and device according to the invention can be deduced from the subordinate claims. It should be pointed out that the device according to the invention can be refined and have the corresponding configurations analogously to that described above and in the subordinate claims referring to claim  1 , in conjunction with the method according to the invention. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention will be described below on the basis of the drawings. They show in: 
         FIG. 1 , a schematic circuit diagram to explain the method according to the invention; 
         FIG. 2 , an embodiment of the device according to the invention in a first operational state; 
         FIG. 3 , an illustration of this embodiment in a second operational state; 
         FIG. 4 , an illustration of the operational states of this embodiment during a complete operating cycle. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The schematic diagram in  FIG. 1  shows a supply pump  1  for introducing saltwater  10  into a pressure-compensation device  2  under a first pressure pi. The same saltwater  11 , which is now, however, under a high working pressure, is fed from pressure-compensation device  2  to membrane module  3 . There a part of the saltwater  11  (e.g., 25% of saltwater  11 ) passes through membrane  6 , is desalted in the process and is drawn off as desalted water  12 . The remainder of the saltwater  11  (75%, for instance) cannot pass through membrane  6  and is fed back by means of connecting line  5  to pressure-compensation device  2  as concentrated saltwater  13 , which is still at nearly the high pressure p 2 . There, this high pressure is exploited, in a manner yet to be explained, to apply this high pressure to the saltwater  10  introduced into pressure-compensation device  2 , and to feed it to membrane module  3  at the input of the latter. At the same time, this pressure is used in pressure-compensation device  2 , in a manner also to be explained, to finally conduct the concentrated saltwater  14  present there away via drain line  4 , and to feed unconcentrated saltwater  10  to pressure-compensation device  2 . All the described processes take place simultaneously and continuously, so that a high pressure pump to supplement the high working pressure is not necessary, and a desalted water  12  is continually available. 
     Based on the embodiment of the invention illustrated in  FIG. 2 , the configuration and functioning of pressure-compensation device  2  will in particular be explained further. Here, the latter comprises two identical piston/cylinder devices  401 ,  402 , with two opposing aligned cylinders, each comprising an inlet chamber  201 ,  202  for accommodating saltwater  10  and an outlet chamber  101 ,  102  for accommodating concentrated saltwater  13 . Inside piston/cylinder devices  401 ,  402  are respective special pistons  301 ,  302 , which divide the piston interior into the aforesaid chambers and can be moved horizontally in the figure. Respective feed lines with (passive) check valves  7  lead from supply pump  1  to inlet chambers  201 ,  202 . Check valves  7  are configured such that they open and allow a flow whenever the pressure in the feed line is greater than that in inlet chambers  201 ,  202 . Comparable check valves  8 , but having another flow direction, are found in the feed lines from inlet chambers  201 ,  202  to membrane module  3 . 
     In the feed lines  5  from membrane module  3  to outlet chambers  101 ,  102  and in the drain lines  4  from outlet chambers  101 ,  102 , on the other hand, actively switchable main valves V 3 , V 6  and V 1 , V 4 , respectively, are arranged, by means of which the inflow of concentrated saltwater  13  from membrane module  3  to, or the outflow of concentrated saltwater  14  from, pressure-compensation device  2  can be controlled. 
     Pistons  301 ,  302  are permanently connected to one another by means of a connecting rod  30 . Pinions  40 , which can be driven, for instance, by geared electric motors and engage with a toothing cut on connecting rod  30 , can drive connecting rod  30 , and thus pistons  301 ,  302 , in order to compensate for pressure losses. 
     The pistons are arranged such that they operate in opposite phase. If, then, a piston is in a position in which the volume of inlet chamber  202  is maximal and the volume of outlet chamber  102  is minimal, then the other piston, connected via connecting rod  30 , is in a position in which the volume of inlet chamber  201  is minimal and the volume of outlet chamber  101  is maximal (compare to  FIG. 2 ). In this situation, inlet chamber  202  is filled with water and outlet chamber  101  is filled with concentrated saltwater. Valves V 1 , V 3 , V 4  and V 6 , represented here as switches, are controlled such that V 3  and V 4  are now closed, while VI and V 6  are opened. 
     In this context, the opening of a valve signifies the creation of a flow connection to allow a through-flow, for which the valve is opened by purely mechanical means. Analogously, the closure of a valve signifies the interruption of a flow connection to interrupt a through-flow, for which the valve is closed by purely mechanical means. 
     By virtue of opening main valve V 1 , the pressure of the concentrated saltwater in outlet chamber  101  is first discharged. By opening main valve V 6 , outlet chamber  102  is subjected to pressure (e.g., 70 bar) and the concentrated saltwater flows into this chamber. Simultaneously, the saltwater present in inlet chamber  202  is pressed towards membrane module  3  by the pressure applied to the piston 
     Since the pistons are arranged such that they operate in opposite phase, the introduction of the pressurized concentrate (at 70 bar, for instance) into outlet chamber  102  causes, via connecting rod  30 , a movement of the other piston  301  which thereby empties unpressurized outlet chamber  101 . At the same time, a negative pressure results in inlet chamber  201 , which draws in saltwater and fills this chamber. 
     If outlet chamber  102  is filled, the main valves are appropriately controlled and the opposite process runs. 
     Since the membrane module is preferably operated at ca. 80 bar in order to realize a sufficiently high production of fresh water, and at most 10 bar pressure loss appears at the membrane, at least the aforesaid 70 bar pressure is available at concentrate drain  5  of membrane module  3  as the pressure of the concentrated saltwater. 
     To relieve the main valves from the large pressure changes, particularly while opening and closing, that could cause them to wear, secondary or bypass valves V 2 , V 2 ′, V 5 , V 5 ′ provided, according to the invention, in parallel with main valves VI, V 3 , V 4 , V 6 . These secondary valves have a markedly smaller cross section than the main valves, and a considerably higher pressure resistance. Therefore the stress on the main valves can be markedly reduced by suitable control of the secondary valves, and thus their service life can be proportionally increased. 
     Also provided is a pressure reservoir P that is connected to the concentrated saltwater output of membrane module  3  and is therefore subjected to the same pressure as the concentrated saltwater itself, for instance, roughly 70 bar. The pressure fluctuations that unavoidably occur with valve actuations as a result of volume losses are thereby to be compensated for, in order to produce as much as possible a constant operating pressure in membrane module  3 . 
     Between the concentrated saltwater output of membrane module  3  and outlet chambers  101 ,  102  there are also provided several flow limiters R 1 , R 2 , R 3 , drawn as resistors, which are intended to prevent an abrupt pressure compensation by limiting the flow rate, therefore contributing to a gradual pressure compensation and thus to slow pressure changes in place of abrupt fluctuations. These flow limiters acting as “flow resistors” can be differently dimensioned. 
     The two flow limiters R 2 , R 3  between node K 2  and secondary valves V 2 , V 2 ′, and between node K 3  and secondary valves V 5 , V 5 ′, respectively, can permit a greater amount of flow than flow limiter R 1  between node K 1  and pressure reservoir P, since flow limiters R 2  and R 3  are supposed to allow pressure compensation within an acceptable time at every actuation of the adjacent secondary valves V 2 , V 2 ′ and V 5 , V 5 ′, respectively. R 1 , on the other hand, is always connected to the concentrate outlet of membrane module  3 , so that pressure compensation can take place uninterruptedly in pressure reservoir P. Flow limiter R 1  can thus have a high flow resistance and allow only a slight flow. Decoupling of the concentrate circuit from membrane module  3  is correspondingly strong, so that the reactions of pressure fluctuations on membrane module  3  are negligibly small. In this context, it should also be mentioned that main valves V 3  and V 6  are always actuated only when a pressure compensation between node K 1  and nodes K 2 , K 3  has already been established by secondary valves V 2  and V 5 . Main valves V 3  and V 6  are thus always actuated unpressurized, so that no pressure fluctuations result. 
     The maximum flow amount is limited in any case by the construction of secondary valves V 2 , V 2 ′, V 5 , V 5 ′, so that these secondary valves can automatically participate in the function of the flow limiters. 
     An operating cycle of a device according to the invention will be described below on the basis of the schematic diagrams shown in  FIGS. 2 and 3  as well as the process diagram shown in  FIG. 4 . The numerical values entered in the diagram shown in  FIG. 4  indicate the pressure drop across the respective valve at the time of actuation. 
     The starting situation is the situation shown in  FIG. 2 . Pistons  301 ,  302  in the two piston/cylinder devices have just reached the leftmost position. This is also indicated in the process diagram of  FIG. 4  (see the two columns on the right). Main valves V 3  and V 4  are still opened. Since the pressure drop across these valves is 0, both valves close unpressurized (time t 1 ). By this point at the latest, secondary valves V 2  and V 5 ′ must also close, so as to separate nodes K 2  and K 3  from the concentrate outflow and the concentrate outlet of membrane module  3 , respectively. At this point, all valves are closed. 
     To prepare for the opposite motion of pistons  301 ,  302 , secondary valve V 2 ′ is now opened (time t 2 ) to reduce the pressure of ca. 70 bar present at node K 2  vis-à-vis the concentrate outflow. Since valve V 2 ′ is a secondary valve with a small cross section, the volume flow is small. A sudden pressure fluctuation is inhibited by flow limiter R 2  or secondary valve V 2 ′ itself. 
     Simultaneously, main [sic; secondary] valve V 5  is opened to apply pressure to node K 3 , which is unpressurized after the emptying of concentrated saltwater from outlet chamber  102 . This application of pressure also takes place gradually since flow limiter R 3  has limited the flow. The pressure that is also present at K 1  therefore builds up at node K 3 . 
     Since node K 1  is decoupled from main valve V 5  by a flow limiter R 1  with a high flow resistance, the compensation is effected from pressure accumulator P, which is in turn filled by way of node K 1  via flow limiter R 1 . The pressure fluctuation at the concentrate outlet of membrane module  3  is thus determined in essence by the dimensioning of this flow limiter R 1 , so that a relatively constant pressure can be achieved at node K 1 . 
     As soon as the pressure at node K 2  has been reduced by secondary valve V 2 ′ and the pressure at node K 3  has been built up by secondary valve V 5 , main valves V 1  and V 6  can open unpressurized (time t 3 ) and the opposite piston movement begins. This is indicated by arrows pointing to the right in  FIG. 4 . 
     At time t 4 , secondary valves V 2 ′ and V 5  can again be closed. This closing of secondary valves V 2 ′ and V 5  must take place at the latest by time t 5 , when pistons  301 ,  302  have reached their rightmost positions (see  FIG. 3 ). 
     Because of the concentrated saltwater flowing into outlet chamber  102  due to the piston movement from the leftmost to the rightmost position, the saltwater has been pressed out of inlet chamber  202  into membrane module  3  with a pressure of ca. 80 bar (70 bar from the inflowing concentrate and 10 bar from a drive unit). At the same time, the concentrated saltwater has been transported without pressure from outlet chamber  101  to the concentrate drain and saltwater has flowed into inlet chamber  201 . Thus all valves are again closed at time t 5 , and the same process takes place in the opposite direction by appropriate controlling. 
     It should be noted at this point that pump  1  is not provided mainly for introducing saltwater  10  into inlet chambers  201 ,  202 , but is intended instead to prevent the occurrence of so-called cavitation, that is, areas of negative pressure in the stream of saltwater  10  flowing into inlet chambers  201 ,  202 . Because of their turbulent flow, such areas are not stable. Ambient water is drawn into these areas by this negative pressure and penetrates them. Thereby it can reach such high speeds that it can easily knock particles out of the line walls and fittings, which can cause damage relatively soon that will require regularly recurring replacement of such parts. In the two-chamber system of the invention, pump  10  [sic;  1 ] thus does not have a high operating pressure, as in known devices, but operates, as it were, like a turbo charger in internal combustion engines, with a low pressure that suffices to prevent cavitation from appearing when saltwater is drawn in. 
     The starting situation is that shown in  FIG. 3 . Pistons  301 ,  302  in the two cylinders have just reached the rightmost position. This is also indicated in the process diagram shown in  FIG. 4 . Valves V 1  and V 6  are still opened. Since the pressure drop across the valves is 0, both valves close unpressurized (time t 5 ). By this point at the latest, secondary valves V 2 ′ and V 5  must also close, so as to separate nodes K 2  and K 3  from the concentrate outflow and the concentrate outlet of membrane module  3 , respectively. Now all valves are closed. 
     To prepare for the opposite motion of pistons  301 ,  302 , secondary valve V 5 ′ is now opened (time t 6 ) to reduce the pressure of ca. 70 bar present at node K 3  vis-à-vis the concentrate outflow. Since valve V 5 ′ is a secondary valve with a small cross section, the volume flow is small. A sudden pressure fluctuation is inhibited by flow limiter R 3 . 
     Simultaneously, secondary valve V 2  is opened to apply pressure to node K 2 , which is unpressurized after the emptying of concentrated saltwater from outlet chamber  101 . This application of pressure also takes place gradually, since flow limiter R 2  has limited the flow. The pressure that is also present at K 1  therefore builds up at node K 2 . Since node K 1  is decoupled from secondary valve V 2  by a flow limiter R 1  with a high flow resistance, the compensation is effected from pressure accumulator P, which is in turn filled via flow limiter R 1 . 
     As soon as the pressure at node K 3  has been reduced by secondary valve V 5 ′ and the pressure at node K 2  has been built up by secondary valve V 2 , main valves V 3  and V 4  can open unpressurized (time t 7 ) and the opposite piston movement begins. This is indicated by arrows pointing to the left in  FIG. 4 . 
     At time t 8 , secondary valves V 5  and V 2  can again be closed. This closing of secondary valves-V 5  and V 2  must take place at the latest by time t 1 , when pistons  301 ,  302  have reached their leftmost positions (see  FIG. 2 ). 
     Because of the concentrated saltwater flowing into outlet chamber  101  due to the piston movement from the rightmost to the leftmost position, the saltwater has been pressed out of inlet chamber  201  into membrane module  3  with a pressure of ca. 80 bar. At the same time, the concentrated saltwater has been transported without pressure from outlet chamber  102  to the concentrate drain, and saltwater has flowed into inlet chamber  202 . 
     Thus all valves are again closed at time t 1  of the next cycle and the same process takes place in the opposite direction by appropriate controlling. The dot-dash line in  FIG. 4  indicates at the same time the end of one cycle and the beginning of a new cycle. 
     From the pressures indicated for the individual valves it is understood that the main valves always switch unpressurized, while the secondary valves, which are suitably dimensioned, are subjected to a high pressure only when opening. This is a very decisive advantage of the present invention. 
     A seal between the piston and the respective cylinder of the piston/cylinder device is not strictly necessary, since a slight mixture of the two fluids does not significantly affect the action of the device. Sealing of the cylinder at the exit point of the connecting rod, on the other hand, is strictly necessary. 
     It can also be provided for the current position of the piston to be continuously detected. This position detection is necessary since a collision between piston and cylinder must be prevented to avoid damage. In this case, the piston position can be detected either directly or indirectly on, for instance, the connecting rod. 
     Since a pump to make up for the pressure loss is heavily stressed, on the one hand, by the high pressure and, on the other, by the aggressive saltwater medium and is in corresponding danger of failure, the present invention replaces such a pump in essence or completely by driving the connecting rod, whereby pressure losses are compensated for. 
     The pressure reservoir smoothes out the pressure fluctuations at the membrane module. An additional smoothing of pressure fluctuations results from multiple placement of a device according to the invention per membrane module, that is by placing at least two pressure compensation devices, each comprising a pair of piston/cylinder devices, per membrane module, particularly if they operate offset in phase from one another, so that at a given point in time t only the pistons of one pressure compensation device are in the extreme right or extreme left position. Depending on the design, one drive unit can be provided for all pressure compensation devices, or a separate one for each pressure compensation device. 
     The invention is not restricted to the illustrated embodiment; in particular, the pressure compensation device can also be designed differently. For instance, designs with several pairs of piston/cylinder devices and/or with piston/cylinder devices of different design are conceivable. The listed pressure values are also only example values to illustrate the invention, so that with a different piston geometry, for instance, other pressure conditions could also result. 
     With the device and method according to the invention, a very high efficiency in energy recovery is achieved, on the level of at least 90%. The feed pump need generate only a portion of the operating pressure of roughly 70–80 bar necessary for reverse osmosis; this portion is a function of the amount of water taken in and brings about an enormous reduction in costs and maintenance. In general, therefore, the production costs for a device for desalting water and preparing potable water are markedly reduced. The geometry of the pistons is not limited to a single possibility. The osmotic pressure can or should be adjusted depending on the salt content of the water. For brackish water—the lowest salt content—a lower pressure can be chosen.