Patent Description:
The demand for a certain minimum water pressure at multi-story buildings like hotels, offices or other large buildings at all times of the day may require one or more pressure-boosting systems to raise incoming municipal water pressure to sufficiently serve upper floors. Booster systems typically contain one or more powerful multi-stage circulation pumps and related accessories and controls.

Until the early <NUM>, pressure regulator valves were typically used to control booster system pressure. Many times, these pump systems operated all pumps at maximum speed and "bled off" excess pressure to reach the desired output. This was quite inefficient in terms of energy consumption. The more energy-efficient option is to design a booster system that ramps up the optimal number of pumps to the optimal speed for meeting the specific demand.

Modern booster systems therefore integrate multiple multi-stage pumps with variable frequency drive-controlled motors, along with software that adjusts pump speed and the number of pumps in operation to meet frequently changing system demand. These systems are designed to deliver the minimal pump output necessary to achieve optimal performance. This means that not all pumps of a booster system run at the same time or at the same speed. Some of the pumps may be idle while others are running.

The parallel connection of the pumps of such a booster system to a piping thus requires that currently running pumps do not pump "backwards" through currently idle pumps. This may be achieved by installing a non-return valve, e.g. a check valve, at each pump. Furthermore, for each pump a shut-off valve is required at the inlet side as well as at the outlet side to allow maintenance and/or disassembling of a pump while the other pumps remain operational. The at least three required valves per pump typically use up significant space for installing the booster system. Furthermore, each of the valves adds a certain pipe resistance which reduces the efficiency of the booster system. <CIT> describes a valve assembly installed between an inlet pipe and an outlet pipe. <CIT> describes a valve for an internal combustion engine.

It is thus an object of the present disclosure to provide a valve system for equipping a piping manifold for connecting a pump system that allows installing the booster system with less space consumption. Moreover, it is an object of the present disclosure to provide for a more efficient flow from the pumps into the piping, i.e. providing a valve system inducing less pipe resistance.

The valve system, piping manifold and pump system according to the present disclosure allows for a smaller and more efficient booster system.

According to a first aspect of the present disclosure, a valve system is provided that is fluidly connectable to a pump system comprising at least one pump assembly being fluidly connectable to a pipe. The valve system comprises at least one valve comprising a pipe section of the pipe, wherein the pipe section defines a primary flow direction. The at least one valve further comprises a valve opening in the pipe section, a valve seat and a valve body, wherein the valve opening, the valve seat and the valve body define a common valve axis extending transversely to the primary flow direction. The at least one valve further comprises an operating element arranged at the pipe section diametrically opposite from the valve opening,.

The at least one valve thereby combines both the functionality of a check-valve and the functionality of a shut-off valve in order to save space. The pipe section being part of the valve further saves space.

According to the present disclosure, the at least one valve comprises a pump connection being connectable to the at least one pump assembly, wherein the valve seat is an integral part of the pump connection. This is also beneficial in terms of space consumption and to reduce the diversity of parts.

The at least one valve comprises a valve control shaft extending along the valve axis and operatively connecting the operating element and the valve body. The valve control shaft may thus transversely cross the pipe section, so that it should preferably be as thin as possible for least flow resistance, but stable enough for operating the valve body.

Optionally, the operating element may be configured to determine the position of the valve control shaft along the valve axis. Strictly speaking, only in the shut off-valve mode the operating element unambiguously determines the position of the valve control shaft along the valve axis, i.e. the valve body is fixed against the valve seat to close the valve opening for any fluid flow direction. In the check-valve mode, the operating element allows for a defined range of axial movability of the valve body along the valve axis, so that the exact position of the valve control shaft along the valve axis also depends on the flow direction. The range of axial movability is, however, at least the maximum opening position, determined by the operating element. A fluid flow from the valve opening towards the valve body pushes the valve body into the maximum opening position, which is determined by the operating element. A fluid flow from the valve body towards the valve opening pushes the valve body against the valve seat.

Optionally, the valve body may be movably coupled to the valve control shaft to move along the valve axis in a range between an opening position and a closing position in the check-valve mode,
wherein the position of the valve control shaft along the valve axis determines the range.

Optionally, the range is zero in an end position of the valve control shaft so that the valve body is fixed in the closing position in the shut off-valve mode.

Optionally, the operating element may comprise an adjustment wheel manually rotatable about the valve axis to determine a range between an opening position and a closing position of the valve body. The adjustment wheel may comprise thread for positioning the valve control shaft along the valve axis.

Optionally, the valve body may have a drop-like shape with a first surface portion having a normal vector with a component facing the valve opening and a second surface portion having a normal vector with a component facing away from the valve opening. Optionally, the first surface portion may be convex and the second surface portion is concave. Optionally, the second surface portion may be longer in direction of the valve axis than the first surface portion. Such a drop-like shape significantly reduces the flow resistance induced by the valve.

Optionally, the pipe section may comprise an insertion opening diametrically opposite from the valve opening, wherein the insertion opening has a larger diameter than the valve body. This is particularly advantageous to allow for a quick and easy assembly of the valve system. Furthermore, if need be, inner parts of the valve can be easily replaced without disassembling the piping manifold as a whole.

Optionally, the operating element may be configured to control the valve body for selectively operating in an always open-valve mode, in which the valve body is fixed in an opening position to open the valve opening for any fluid flow direction. This is particularly advantageous for using the valve system at the inlet side of the booster pump system. At the inlet side, only the shut-off mode is required, so that no movability of the valve body relative to the valve control shaft is needed. For those valves of the valve system at the inlet side, the valve body may therefore be fixed to the valve control shaft along the valve axis. The position of the valve control shaft determined by the operating element therefore unambiguously determines whether the valve is open or closed, independent of the flow direction.

According to a second aspect of the present disclosure, a piping manifold is provided comprising.

Optionally, the pipe may extend essentially straight along the primary flow direction and the valve axes of the at least two valves are arranged in parallel to each other. This allows for a very compact setup.

Optionally, the at least two valves may be evenly distributed along the pipe with the same distance to each other in the primary flow direction.

According to a third aspect of the present disclosure, a pump system is provided comprising.

wherein the pipe section of each first valve forms a part of the common outlet pipe.

Optionally, the pump system may further comprise a common inlet pipe and a second valve system, wherein the pump assemblies are fluidly connected in parallel to each other to the common inlet pipe, wherein the second valve system comprises at least one second valve for each pump assembly, wherein the at least one second valve comprises a pipe section, wherein the pipe section of each second valve defines a primary flow direction and forms a part of the common inlet pipe.

Optionally, the at least one second valve may further comprise a valve opening in the pipe section, a valve seat and a valve body, wherein the valve opening, the valve seat and the valve body define a common valve axis extending transversely to the primary flow direction, wherein the at least one second valve further comprises an operating element arranged at the pipe section diametrically opposite from the valve opening, wherein the operating element is configured to control the valve body for selectively operating in an always open-valve mode, in which the valve body is fixed in an opening position to open the valve opening for any fluid flow direction, and wherein the operating element is configured to control the valve body for selectively operating in a shut off-valve mode, in which the valve body is fixed against the valve seat to close the valve opening for any fluid flow direction. Thus, the second valve system at the inlet side therefore differs from the first valve system at the outlet side by not comprising a check-valve mode, but an always open-mode instead.

<FIG> shows a booster pump system <NUM> as known from the prior art. The booster pump system <NUM> comprises three pump assemblies <NUM> being connected in parallel to each other to a pipe system. The pump assemblies <NUM> are connected with their outlet side to a common outlet pipe <NUM> as a part of the piping system. Analogously, the pump assemblies <NUM> are connected with their inlet side to a common inlet pipe <NUM> as part of the piping system. The outlet pipe <NUM> and the inlet pipe <NUM> are arranged in parallel to each other with a distance D to each other to allow accommodating the parallel pump assemblies <NUM> in a row between the outlet pipe <NUM> and the inlet pipe <NUM>. The booster pump system <NUM> further comprises six shut-off valves <NUM>, of which three shut-off valves <NUM> are arranged between the outlet side of the pump assemblies <NUM> and the common outlet pipe <NUM>, and of which three shut-off valves <NUM> are arranged between the inlet side of the pump assemblies <NUM> and the common inlet pipe <NUM>. Furthermore, the booster pump system <NUM> comprises three check valves <NUM> between the inlet side shut-off valves <NUM> and the inlet side of the pump assemblies <NUM> in order to prevent a backflow towards the inlet pipe <NUM>. Therefore, the booster pump system <NUM> in <FIG> must accommodate in sum three valves <NUM>, <NUM> in line between the outlet pipe <NUM> and the inlet pipe <NUM>. Thus, the distance D between the outlet pipe <NUM> and the inlet pipe <NUM> is relatively large and consumes significant installation space. Furthermore, the flow resistance induced by the three valves <NUM>, <NUM> per pump assembly <NUM> is relatively high.

<FIG> shows a booster pump system <NUM> according to the present disclosure. Compared to the known system as depicted in <FIG>, the booster pump system <NUM> consumes significantly less installation space and is more efficient, i.e. induces less flow resistance. The booster pump system <NUM> comprises three pump assemblies <NUM> arranged in parallel to each other and connected with their outlet side to a common outlet pipe <NUM> as part of an outlet side pipe manifold <NUM>. At their inlet side, the pump assemblies <NUM> are connected to a common inlet pipe <NUM> as part of an inlet side pipe manifold <NUM>. The outlet side pipe manifold <NUM> comprises a first valve system <NUM> with three first valves <NUM>. The inlet side pipe manifold <NUM> comprises a second valve system <NUM> with three second valves <NUM> arranged at the inlet side of the pump assemblies <NUM> analogous to the first valves <NUM>. The outlet pipe <NUM> and the inlet pipe <NUM> extend essentially in parallel to each other with a distance d, wherein the distance d is significantly shorter than the distance D in <FIG>. The outlet pipe <NUM> and the inlet pipe <NUM> extend both straight in a primary flow direction <NUM>. The pump assembly <NUM> comprises a stack of impellers (not shown) rotatable about a vertical rotor axis R. The details of the valves <NUM>, <NUM> are better visible in <FIG>.

<FIG> shows a bottom part <NUM> of a pump housing of one of the pump assemblies <NUM> connected with its outlet side to one of the first valves <NUM>. The bottom part <NUM> of the pump housing defines a central low-pressure region <NUM> in fluid connection with a pump inlet <NUM> of the pump assembly <NUM> and an annular high-pressure region <NUM> arranged radially outward from the low-pressure region <NUM> and being fluidly connected to a pump outlet <NUM> of the pump assembly <NUM>. Both the pump inlet <NUM> and the pump outlet <NUM> comprise essentially identical flange connections <NUM>, <NUM> at the inlet side and the outlet side, respectively. The first valve <NUM> is connected to the outlet flange connection <NUM> by a pump connection <NUM> in form of a flange that corresponds to the outlet flange connection <NUM>. The pump connection <NUM> is fixed to the outlet flange connection <NUM> by two bolts <NUM>. The pump inlet <NUM> and the pump outlet <NUM> are coaxially arranged along a pump flow axis X at diametrically opposite lateral sides of the pump assembly <NUM>.

The first valve <NUM> comprises a pipe section <NUM> of the outlet pipe <NUM>, wherein the pipe section <NUM> extends along the primary outlet flow direction <NUM>. The primary outlet flow direction <NUM> extends transverse, preferably orthogonal to the pump flow axis X. The first valve <NUM> further comprises a valve opening <NUM> in the pipe section <NUM>, a valve seat <NUM> and a valve body <NUM> (see <FIG>). The valve opening <NUM>, the valve seat <NUM> and the valve body <NUM> define a common valve axis <NUM> to which they are coaxially aligned. The valve axis <NUM> is preferably identical to the pump flow axis X as shown in all embodiments of <FIG>. The first valve <NUM> further comprises an operating element <NUM> in form of an adjustment wheel manually rotatable about the valve axis <NUM>. The operating element <NUM> is arranged at the pipe section <NUM> diametrically opposite from the valve opening <NUM> being connected to the pump outlet <NUM> of the pump assembly <NUM>.

<FIG> gives a view on the inner parts of the first valve <NUM>. The operating element <NUM> is operatively connected to the valve body <NUM> by a valve control shaft <NUM> extending along the valve axis <NUM>. The axial position of the valve control shaft <NUM> along the valve axis <NUM> is adjustable by rotating the operating element <NUM> about the valve axis <NUM> by means of a thread connection <NUM>. <FIG> shows the valve <NUM> in a shut-off valve mode, in which the valve body <NUM> is fixed against the valve seat <NUM> to close the valve opening <NUM> for any fluid flow direction. The valve control shaft <NUM> comprises a first stop surface <NUM> facing along the valve axis <NUM> towards the valve opening <NUM> and a second stop surface <NUM> facing along the valve axis <NUM> towards the operating element <NUM>. The first stop surface <NUM> and the second stop surface <NUM> have an axial distance S to each other. The axial distance S determines the maximal range of movability of the valve body <NUM> relative to the valve control shaft <NUM>. In the shut-off valve mode shown in <FIG>, the first stop surface <NUM> pushes the valve body <NUM> against the valve seat <NUM> to close the valve opening <NUM>. The valve control shaft <NUM> has, in the shut-off valve mode as shown in <FIG>, an axial position closest to the valve opening <NUM>, i.e. the operating element <NUM> is fully screwed inward towards the valve opening <NUM>. The range of movability is then zero, because the valve body <NUM> cannot move relative to the valve control shaft <NUM> towards the second stop surface <NUM>.

<FIG> shows the first valve <NUM> before the inner parts of the first valve <NUM> are assembled. In order to easily assemble the first valve <NUM>, the pipe section <NUM> comprises an insertion opening <NUM> diametrically opposite from the valve opening <NUM> and coaxial to the valve axis <NUM>. The insertion opening <NUM> has a larger diameter than the valve body <NUM>. The operating element <NUM>, the valve shaft <NUM> and the valve body <NUM> can therefore be preassembled and then inserted through the insertion opening <NUM> along the valve axis <NUM> as a preassembled unit <NUM>. The preassembled unit <NUM> further comprises a plug <NUM> with an outer thread connection for being screwed into the insertion opening <NUM>. The parts of the preassembled unit <NUM> may be made of a plastic material. However, it is preferred that at least the valve control shaft <NUM> is made of metal in order to insure sufficient stability. The valve control shaft <NUM> should be as thin as possible in order to minimise the induced flow resistance along the primary flow direction <NUM> and as thick as necessary to insure sufficient stability.

<FIG> shows the individual parts of the preassembled unit <NUM> separately in an exploded view. The unit <NUM> may comprise O-rings <NUM> for sealing purposes. The valve body <NUM> is here composed of a first valve body portion 45a and a second valve body portion 45b. The first valve body portion 45a comprises a convex first surface portion <NUM> having a normal vector with a component facing the valve opening <NUM> and the second valve body portion 45b has a second surface portion <NUM> with a normal vector with a component facing away from the valve opening <NUM>. When assembled together, the first valve body portion 45a and the second valve body portion 45b form the valve body <NUM> having a drop-like shape. The first valve body portion 45a further comprises an inner sleeve <NUM> for receiving a spring <NUM> into which a first end <NUM> of the valve control shaft <NUM> extends. The spring <NUM> is pushed against a first spring stop surface <NUM> of the valve control shaft <NUM>, wherein the first spring stop surface <NUM> faces towards the valve opening <NUM>. The first valve body portion 45a further comprises an inner second spring stop surface <NUM> facing away from the valve opening <NUM> towards the first spring stop surface <NUM>. Depending on the axial position of the valve body <NUM> relative to the valve control shaft <NUM>, the distance between the first spring stop surface <NUM> and the second spring stop surface <NUM> determines how much the spring is pressed together or released.

This is much better visible in <FIG> show a cross section of the first valve <NUM> along the valve axis <NUM>, wherein the first valve <NUM> is operating in a check valve mode. For selecting the check valve mode, the operating element <NUM> is fully screwed outward to position the valve control shaft <NUM> axially furthest away from the valve opening <NUM>. In the check valve mode as shown in <FIG>, the valve body <NUM> is axially movable relative to the valve control shaft <NUM> within a range defined by the stop surfaces <NUM>, <NUM>. In <FIG> an inward fluid flow <NUM> from the valve opening <NUM> towards the valve body <NUM> is present. This is the normal situation when the connected pump assembly <NUM> is operating and pumping fluid into the outlet pipe <NUM>. The fluid flow <NUM> pushes the valve body <NUM> towards an open position against the stop surface <NUM>. It should be noted that the spring <NUM> is compressed in the open position of the valve body <NUM>. This means that the opening of the valve body <NUM> upon the fluid flow <NUM> from the valve opening <NUM> towards the valve body <NUM> loads the spring <NUM>. Without a sufficient flow <NUM> from the valve opening <NUM> towards the valve body <NUM>, the spring <NUM> pushes the valve body <NUM> towards the valve seat <NUM> into a closing position as shown in <FIG>.

<FIG> shows the situation when the pressure in the outlet pipe <NUM> is higher than the pressure at the pump outlet <NUM> of the connected pump assembly <NUM>. This is typically the case when the connected pump assembly <NUM> is idle and not pumping fluid while the other parallel pump assemblies are operating and pumping. The pressure difference in addition to the spring force of the spring <NUM> pushes the valve body <NUM> into a sealing contact with the valve seat <NUM>. Thereby, an undesirable backflow through an idle pump assembly <NUM> is prevented.

<FIG> shows the first valve <NUM> in a shut-off valve mode, in which the operating element <NUM> is fully screwed inward so that the valve control shaft <NUM> is in a position closest to the valve opening <NUM>. In the shown shut-off valve mode, the valve body <NUM> is not movable anymore in axial direction relative to the valve control shaft <NUM>, because the stop surface <NUM> is pushed against the valve body <NUM> to fix it against the valve seat <NUM> to close the valve opening <NUM> for any fluid flow direction. If the operating element <NUM> is in an intermediate position between fully opened (<FIG>) and fully closed (<FIG>), the initial spring load in the check-valve mode as shown in <FIG> is adjustable. As the initial spring load for pressing the valve body <NUM> against the valve seat <NUM> is to be overcome by the pressure differential for opening the first valve <NUM> as shown in <FIG>, the minimum pressure differential for opening the first valve <NUM> in the check-valve mode is adjustable by an intermediate position of the operating element <NUM>. However, if the minimum pressure differential is increased by operating the first valve <NUM> in the check-valve mode at an intermediate position of the operating element <NUM>, this may come at the cost of a reduced opening degree of the first valve <NUM>.

<FIG> show a second valve <NUM> as part of the second valve system <NUM> to be installed at the inlet side of a pump assembly <NUM>. The second valves <NUM> of the second valve system <NUM> are almost identical to the first valves <NUM> of the first valve system <NUM> with the difference that the second valve <NUM> does not have a check valve mode. The second valve <NUM> is selectively operable in an always open-mode as shown in <FIG> and a shut-off mode as shown in <FIG>. Therefore, there is no need for the spring <NUM> in the second valve <NUM>. The valve body <NUM> is always fixed relative to the valve control shaft <NUM> and is not movable between the stop surfaces <NUM>, <NUM>. This is achieved by an additional blocking body <NUM> between the valve body and the stop surface <NUM> in form of a sleeve. For a normal operation of the pump, the operating element <NUM> is fully screwed outward as shown in <FIG> to operate the valve in an always open valve mode. When the pump assembly must be disconnected from the inlet pipe <NUM>, e.g. for maintenance, repair or exchange, the operating element <NUM> may be screwed inward to push the valve body <NUM> into a closing position against the valve seat <NUM> as shown in <FIG>. The second valve <NUM> is then in a shut-off valve mode.

The use of the first valve system <NUM> described herein for an outlet side pipe manifold <NUM> and, preferably in addition, of the second valve system <NUM> for an inlet side pipe manifold <NUM> as part of a booster pump system <NUM> has the advantage that less installation space is needed and less pipe resistance is introduced compared to the systems known in the prior art. Furthermore, the valve systems are more cost efficient in production and assembly.

will be appreciated by the reader that integers or features of the disclosure that are described as optional, preferable, advantageous, convenient or the like are optional and do not limit the scope of the independent claims.

The above embodiments are to be understood as illustrative examples of the disclosure. It is to be understood that any feature described in relation to any one embodiment may be used alone, or in combination with other features described, and may also be used in combination with one or more features of any other of the embodiments, or any combination of any other of the embodiments.

Claim 1:
A valve system (<NUM>) fluidly connectable to a pump system (<NUM>) comprising at least one pump assembly (<NUM>) being fluidly connectable to a pipe (<NUM>),
wherein the valve system (<NUM>) comprises at least one valve (<NUM>) comprising a pipe section (<NUM>) of the pipe (<NUM>), wherein the pipe section (<NUM>) defines a primary flow direction (<NUM>),
wherein the at least one valve (<NUM>) further comprises a valve opening (<NUM>) in the pipe section (<NUM>), a valve seat (<NUM>) and a valve body (<NUM>), wherein the valve opening (<NUM>), the valve seat (<NUM>) and the valve body (<NUM>) define a common valve axis (<NUM>) extending transversely to the primary flow direction (<NUM>),
wherein the at least one valve (<NUM>) further comprises an operating element (<NUM>),
wherein the at least one valve (<NUM>) further comprises a valve control shaft (<NUM>) extending along the valve axis (<NUM>) and operatively connecting the operating element (<NUM>) and the valve body (<NUM>),
wherein the valve control shaft (<NUM>) comprises a first stop surface (<NUM>) facing along the valve axis (<NUM>) towards the valve opening (<NUM>),
the operating element (<NUM>) being arranged at the pipe section (<NUM>) diametrically opposite from the valve opening (<NUM>), wherein the operating element (<NUM>) is configured to control the valve body (<NUM>) for selectively operating in a check-valve mode, in which the valve body (<NUM>) is movable along the valve axis (<NUM>) to open the valve opening (<NUM>) upon a fluid flow from the valve opening (<NUM>) towards the valve body (<NUM>), characterized in that
the operating element (<NUM>) is configured to control the valve body (<NUM>) for selectively operating in a shut off-valve mode, in which the valve body (<NUM>) is fixed against the valve seat (<NUM>) by the first stop surface (<NUM>) pushing the valve body (<NUM>) against the valve seat (<NUM>) to close the valve opening (<NUM>) for any fluid flow direction, wherein the at least one valve (<NUM>) further comprises a pump connection (<NUM>) being connectable to the at least one pump assembly (<NUM>), wherein the valve seat (<NUM>) is an integral part of the pump connection (<NUM>).