EP3791068B1 - Pulsation damping system - Google Patents

Description

The invention relates to a pulsation damping system for reducing pressure fluctuations in pipelines on the inlet and/or outlet side, in particular in the suction and/or high-pressure area, of piston pumps, in particular for conveying fluids containing solid particles, such as sludge conveying pumps, with at least one piston pump having a pump chamber , wherein the pump chamber for conveying a pumping medium or fluid is fluidically connected via a first fluid connection to a pump inlet channel, also called suction channel, and via a second fluid connection to a pump outlet channel. Furthermore, the invention relates to a pulsation damping system for reducing pressure fluctuations in the inlet and/or outlet-side pipelines, in particular in the suction and/or high-pressure area of piston pumps, with at least one pump inlet channel that can be fluidically connected to a pump chamber of a piston pump for pumping a pumped medium or pumped fluid and Pump outlet duct, with a first storage container being arranged in the pump inlet duct and/or in the pump outlet duct, in which a fluid to be pumped can be temporarily stored in a first region, also known as a pressure chamber, and in a second region, also known as a pressure chamber, a gas volume, in particular a compressible gas volume, is arranged.

Such pulsation damping systems are known in numerous variants and are usually used in pipeline systems in which pressure fluctuations or pressure surges can occur, for example caused by the operation of a pump, an actuator or due to other flow influences. For example, when piston pumps are operated, the oscillating movement of the pump pistons results in non-uniform volume flows both in the intake tract and at the outlet of the pump. These non-uniform volume flows can lead to pressure pulsations, which have a negative impact on the functioning of the pump and can lead to undesirable vibrations in the adjacent pipe system. These pulsations can cause cavitation in the intake tract of the pump, which can lead to a reduction in the efficiency of the pump on the one hand and to damage to the pump on the other.

Known pulsation dampers are usually arranged in the inlet and/or outlet-side pipelines of the pump and usually include a compensating or storage chamber filled with a compressible volume of gas, which is fluidically operatively connected to the pulsating fluid to be pumped. These dampers work in such a way that an increase in pressure is compensated for by a compression of the gas volume in the storage chamber. Since the gas, due to its high compressibility, only has a small change in pressure compared to the fluid, pressure pulsations due to the imposed volume flow pulsations can be reduced.

It should be clear that an inlet-side pipeline means a pump inlet channel or a suction line and the outlet-side pipeline means a pump outlet channel or a high-pressure line, with the pump inlet channel usually being connected to a fluid source for sucking in the pumped fluid and the pump outlet channel being used to transport the pumped fluid further to be pumped fluid is used. In the pump inlet channel and the pump outlet channel, a check valve is usually arranged in each case between the above-mentioned storage chamber and the pump chamber in order to convey the fluid by means of the piston pump. The pump can be designed in particular as a classic piston pump with, for example, a single pump chamber or as a piston diaphragm pump with a pump chamber that includes a pump working chamber and a pump delivery chamber. Furthermore, several pistons or piston pumps are usually used, which suck in the fluid to be pumped from a common intake line with a central reservoir and pump it into a common high-pressure line on the high-pressure side.

From the EP 0 679 832 A1 For example, an embodiment of a damping system is known in which, in order to reduce pressure pulsations in a pipeline, a volume change region is provided with a wall that can be displaced and thereby change the pipe volume.

In addition, the use of known pulsation dampeners to be pumped with fluids containing solids is only possible to a limited extent, since the mostly with a Throttle resistances, compensating chambers or other pressure-damping components connected to the main delivery line tend to clog either due to the constriction created or must be chosen to be so large to avoid clogging that the damping effect decreases significantly. Furthermore, the solid fractions contained in the fluid are often very abrasive, so that a throttling point can wear out quickly when such solid bodies flow through, which in turn has a negative effect on the functioning of the damper.

The document U.S. 5,165,869 discloses a pump system with a damping device, wherein a diaphragm pump is provided and the damping element acts in the chamber facing the drive.

The object of the present invention is therefore to provide a system for reducing pressure fluctuations in the inlet and / or outlet-side pipelines of piston pumps, which improves at least one of the disadvantages mentioned above, and in particular an effective and long-lasting use in the field of pumps for pumping fluids with a particularly large pressure fluctuation range and also with solid parts.

The invention solves the problem by a pulsation damping system with the features of the main claim. Advantageous refinements and developments of the invention are disclosed in the dependent claims, the description and the figures.

The pump chamber of a pulsation damping system according to the invention has at least one further fluid connection, also called damping fluid connection, with which the pump chamber, in particular the fluid located therein, is fluidly connected to a damping device for damping pressure fluctuations. The damping can take place in particular by supplying or discharging a fluid located in the pump chamber in the direction towards or away from the damping device in a time- and/or quantity-regulated manner. In addition, a pressure surge occurring in the pump chamber and/or the adjacent inlet-side and/or outlet-side pipelines can be “intercepted” by means of the damping device, for example by a change in volume. Thus, particularly at high pump frequencies, the acceleration effects caused by the oscillating movement of the piston and exerted on the fluid medium, which in the pump chamber and the adjacent inlet and/or outlet piping relatively high acceleration forces and can lead to pressure pulsations as a result, reduced and thus pressure surges can be reduced in a particularly simple manner. The fluid flowing between the pump chamber and the damping device can advantageously be in the form of an incompressible barrier fluid, such as hydraulic oil, in particular a pump working medium, or alternatively be the fluid medium to be pumped. Due to this configuration, in particular due to a preferred damping fluid acting on the pump chamber independently of the fluid to be conveyed, the present pulsation damping system is particularly suitable for use in pipeline systems for conveying fluids containing solids.

At least one throttle valve is preferably arranged in a pipeline arranged between the pump chamber and the damping device. The throttle valve can be arranged in particular between the pump chamber and a pressure chamber which is fluidically connected to the pump chamber, for example a volume change device or a reservoir. As a result, at least part of the pulsation energy can be converted into heat and the level of the pressure pulsations can thus be reduced particularly effectively and advantageously. In particular, a pressure pulse of a fluid that is at least partially in the pump chamber, for example, and flows through the damping fluid connection in the direction towards or away from the damping device due to a very high or very low pressure, can be converted into heat when flowing through the throttle valve, so that this in particular pressure pulsations can be reduced. Consequently, the throttle valve can also be regarded as part of the damping device. Alternatively, the throttle can in principle also be arranged in an adjacent or downstream pipeline system, which is not directly fluidly connected to the pump chamber, but is operatively connected to the pump with regard to the pressure prevailing in the pump chamber, for example by means of a device for pressure transmission the fluid in the pump chamber to a separate second fluid.

The damping device preferably has a volume change device, also called a volume compensation device, for changing the volume at least a pressure chamber fluidically connected to the pump chamber. As a result, in particular a fluid located in the pump chamber, which is subjected to an increased pressure, for example, can be guided or conveyed in a controllable manner through the damping fluid connection in the direction of or away from the damping device. This control of the fluid flow can be done, for example, by enlarging a pressure chamber downstream of the damping fluid connection to allow the fluid to flow from the pump chamber into the pressure chamber or by reducing the pressure chamber to allow the fluid to flow back or out of the pressure chamber into the pump chamber. When the flow takes place through the throttle preferably arranged in the pipeline between the pump chamber and the pressure chamber, an occurring pressure pulse can be converted into heat, and a pressure pulsation can thereby be reduced particularly effectively and controllably. It should be clear that the term controllable means in particular that a flow through the throttle and a resulting reduction in pressure can take place in a time- and quantity-defined, preferably predictable, particularly preferably automatic manner.

The volume changing device preferably has a displacement body for changing the volume of the at least one pressure chamber, which is designed in particular as a displaceable wall, displaceable piston or displaceable membrane. In order to control or regulate the change in volume of the pressure chamber, the displacement body can be subjected to a counter-pressure with respect to the fluid pressure present on the pressure chamber side, for example via a spring-elastic element. The displacement body is particularly preferably designed as a piston, in particular a separating piston, or as a membrane of a closed system, such as a piston-cylinder unit. In such an embodiment, the counter-pressure acting on the piston or the membrane can take place, for example, by means of a correspondingly arranged and pressurized second pressure chamber. As a result, the displacement of the displacement body can be controlled in a particularly advantageous manner, in particular actively.

The volume change device preferably has a first pressure chamber which is fluidically connected to the pump chamber and a first pressure chamber which is connected by means of the displacement body from this second pressure chamber, which is fluidically separate and operatively connected to it. For this purpose, the second pressure chamber is advantageously filled with a volume of gas. By shifting or shifting the displacement body, the respective volume of the first and the second pressure chamber can be changed relative to one another in a relatively simple manner; in particular, when the first pressure chamber volume is increased, the second pressure chamber volume can be reduced and when the first pressure chamber volume is reduced, the second pressure chamber volume can be increased. As a result, a flow of the fluid in the pump chamber through the damping fluid connection in the direction towards or away from the damping device can be controlled particularly advantageously, and particularly efficient damping, particularly in the area of the throttle point, can be brought about.

In order to regulate a gas pressure prevailing in the second pressure chamber, the second pressure chamber can preferably be fluidically connected directly and/or indirectly via a control valve to a separate gas source. This enables a particularly independent and simple control of the counter-pressure applied to the displacement body. The gas pressure prevailing in the second pressure chamber can be regulated, for example, by means of the previously mentioned separate or external pressure or gas source and the control valve used for regulation, with the control valve being actuated via at least one pressure sensor arranged in the pump inlet channel and/or the pump outlet channel as well as a suitable PID control (proportional-integral-differential control) can be used to control the control valves. When several volume change devices are arranged, for example, the control valve of a volume change device arranged on the pump inlet side can be controlled as a function of a pressure prevailing in the pump inlet channel and/or the control valve of a volume change device arranged on the pump outlet side can be actuated as a function of a pressure prevailing in the pump outlet channel. Alternatively, the respective control valve can also be controlled as a function of a pressure prevailing in the pump chamber, with the pressure sensor advantageously being arranged in the region of the pump chamber for this purpose.

In order to regulate a gas pressure prevailing in the second pressure chamber, the second pressure chamber is preferably directly or indirectly operatively connected to the pressure prevailing in the pump inlet channel and/or in the pump outlet channel. For example, the second pressure chamber can be fluidically connected to a reservoir, such as a pressure air tank, which is fluidically connected to the pump inlet channel or to the pump outlet channel. As a result, the pressure prevailing in the pump inlet duct and/or in the pump outlet duct can serve as the pressure source or pressure measure for the fluid in the second pressure chamber, with the fluid in the second pressure chamber preferably being fluidically derived, for example by means of a membrane, from the delivery fluid located in the pump inlet duct or the pump outlet duct is separated.

The damping device preferably has a reservoir, which is arranged in the pump inlet channel and/or in the pump outlet channel, in particular on a fluid side of a check valve arranged in the respective channel and which faces away from the piston pump, with a delivery fluid inlet and a delivery fluid outlet, with the Conveying fluid and in an upper region a pressurized, that is, a pressurized gas volume is arranged. For this purpose, the reservoir can be designed, in particular with the formation or taking up of a volume in the reservoir, particularly preferably as a volume and/or pressure storage container in which the conveying fluid for conveying can advantageously be temporarily stored. In particular in the case of fluids to be conveyed which have solid particles, this enables reliable and efficient pressure transmission from the conveying fluid to the gas volume, in particular for pressure equalization purposes. The reservoir is preferably designed as a pressure tank. The gas volume can, for example, be directly or indirectly operatively connected to the fluid located in the second pressure chamber. Depending on the direction of movement of the piston of the piston pump, this enables automatic activation of the displacement body by pressure transmission from the pump inlet channel and/or the pump outlet channel to the second pressure chamber. To adjust or regulate the gas pressure prevailing in the storage container, the storage container can be fluidically connected at least temporarily to a separate gas source directly and/or indirectly via a control valve.

The gas volume of the reservoir is preferably fluidically connected to the second pressure chamber of the volume changing device via a pressure line. As a result, the pressure prevailing in the gas volume of the reservoir can act directly on the displacement body. Such a configuration is advantageous in particular for conveying fluids with solid particles and in particular enables a safe and automatic displacement of the displacement body, and thus ultimately a reduction in pulsation pressures. For example, a pressure of the medium to be pumped on the pump inlet side or pump outlet side, in particular a fluid mixed with solids, can be transferred in a particularly simple and reliable manner to a fluidically connected, in particular gaseous fluid with the second pressure chamber. As a result, depending on the direction of movement of the piston of the piston pump, the displacement body is automatically and directly activated by means of the pressure in the second pressure chamber and consequently the fluid in the pump chamber flows in or out in the direction of or from the damping device, while at the same time flowing through a throttle point and this Conversion of a pressure pulse into heat, and thus ultimately enables automatic damping of pressure pulsations.

The piston pump is preferably designed as a diaphragm piston pump with a pump working chamber and a pump delivery chamber which is fluidically separate from this chamber and is in operative connection with it, the first and second delivery fluid connection being arranged on the pump delivery chamber and the at least one damping fluid connection being arranged on the pump working chamber. In this case, a pressure medium can be provided in the pump working chamber, which is fluidically connected to the first pressure chamber of the volume change device via the damping fluid connection. The pump working chamber is arranged on the piston side, in particular in relation to the diaphragm of the pump, and the pump delivery chamber is arranged on the side of the diaphragm facing away from the piston. This fluidic separation of the conveying fluid from a pressure medium enables a particularly efficient and safe reduction of pressure pulsations, in particular in the case of conveying fluids with solid particles. In an alternative embodiment, in particular with a conventional piston pump, form the pump working chamber and the pump delivery chamber a common pump chamber.

Furthermore, in a pulsation damping system according to the invention for damping pressure fluctuations in a pipeline section of the pump inlet channel and/or the pump outlet channel that fluidly connects the first storage container and the pump chamber, a preferably separately designed second storage container, or also called an equalizing container, pressure air tank or volume change device, is additionally arranged. Because of this configuration, the present pulsation damping system is particularly suitable for use in piping systems of piston pumps in which particularly large amplitudes and/or high frequencies of pressure fluctuations and pressure pulses occur. In particular, at high pump frequencies, the acceleration effects caused by the oscillating movement of the piston and exerted on the fluid medium, which can lead to relatively high acceleration and pressure forces in the pump chamber and the adjacent inlet-side and/or outlet-side pipelines, can be reduced and thus recurring pressure surges in particular be reduced in a simple and effective manner. The damping can be achieved in particular by a time- and/or quantity-regulated supply or discharge of a pipe section of the pump inlet channel that is advantageously arranged directly upstream of the pump chamber inlet connection and/or in the pump outlet channel, particularly in the pipe section that is advantageously arranged directly downstream of the pump chamber outlet connection of the pump outlet channel, in the direction towards or away from the respective second storage container. This control of the fluid flow can take place, for example, by allowing the fluid to flow from the pump inlet channel or pump outlet channel into the second storage container or by allowing the fluid to flow out of the second storage container into the pump inlet channel or pump outlet channel. The pressure surge occurring in the inlet-side and/or outlet-side pipelines can be “intercepted” in the second storage container, for example, by a change in volume.

It should be clear that a pump inlet channel is understood to mean a pump inlet-side pipeline or a suction line and a pump outlet channel to be understood as a pump outlet-side pipeline or a high-pressure line, with the pump inlet channel usually being connected to a fluid source for sucking in the pumped fluid and the pump outlet channel being used to transport the pumped fluid further to be pumped fluid is used. The pump can be designed in particular as a classic piston pump with, for example, a single pump chamber or as a piston diaphragm pump with a pump chamber that includes a pump working chamber and a pump delivery chamber. Furthermore, several pistons or piston pumps are usually used, which suck in the fluid to be pumped from a common intake line with a central reservoir and pump it into a common high-pressure line on the high-pressure side.

The second storage container is preferably filled with the delivery fluid to be delivered in a first area and with a compressible gas volume in a second area. Particularly preferably, the conveying fluid is arranged in the second storage container in a lower area and a pressurized gas volume, ie a gas volume that is under pressure, is arranged in an upper area. For this purpose, the second storage tank can be designed, in particular by forming or taking up a volume in the second storage tank, particularly preferably as a volume and/or pressure storage tank in which the conveying fluid for conveying can advantageously be temporarily stored. In the case of fluids to be conveyed which have solid particles, this enables safe and efficient pressure transmission from the conveying fluid to the gas volume, in particular for pressure equalization purposes, as well as safe and particularly residue-free delivery and discharge of the conveying fluid into and out of the storage container. In this way, in particular, deposits of solid particles can be prevented. The second storage container is preferably designed as a pressure vessel. The gas volume located in the second region, which is preferably arranged at the top, can, for example, be directly or indirectly operatively connected to the fluid located in the preferably lower region. To set or regulate the gas pressure prevailing in the storage container, the storage container can be connected directly and/or indirectly via a control valve, at least temporarily, to a separate gas source be fluidly connected. In this case, no additional component, such as a partition wall, can be provided between the fluid to be conveyed and the gas volume, but only a fluid level can be formed. The respective volume of the first and second areas can be changed relative to one another by shifting or shifting the fluid level within the storage container. In particular, the second area can be reduced when the first area is enlarged and the second area can be enlarged when the first area is reduced. Particularly efficient damping can be brought about by the fluid located in the pump inlet channel or pump outlet channel flowing in and out into or out of the second storage container. This flow can preferably be regulated, for example by allowing the fluid to flow in or out of the pump inlet channel or pump outlet channel into or out of the second storage container.

The second storage tank, in particular the first region of the second storage tank, is preferably connected to the pipe section of the pump inlet channel or the pump outlet channel via a branch pipe and a throttle valve is arranged in the branch pipe. In particular, the inlet-side second storage tank, or the first area of this second storage tank, can be connected via a first branch pipe to the pipe section of the pump inlet duct, and the outlet-side second storage tank, or the first area of this second storage tank, can be connected via a second branch pipe to the pipe section of the pump outlet duct be, in each case a throttle valve is arranged in the branch pipes. At least part of the pulsation energy can be converted into heat during the flow through the throttle preferably arranged in the pipeline between the pump chamber and the respective first region of the second storage container, and the level of the pressure pulsations can thus be reduced particularly effectively and controllably. It should be clear that the term controllable means in particular that a flow through the throttle and a resulting reduction in pressure can take place in a time- and quantity-defined, preferably predictable, particularly preferably automatic manner.

Preferably, the first storage tank arranged in the pump inlet channel is directly or indirectly fluidic via a fluid inlet with a delivery fluid source and via a fluid outlet with the second storage tank and/or the first storage tank arranged in the pump outlet channel is directly or indirectly fluidic with the second storage tank via a fluid inlet and via a fluid outlet with a discharge line tied together. As a result, the second storage tank can be arranged in the pump inlet channel downstream of the first storage tank and in the pump outlet channel upstream of the first storage tank.

Preferably, the gas volume of the second storage container and/or the gas volume of the first storage container can be fluidically connected directly and/or indirectly via a control valve to a separate gas source in order to regulate a gas pressure. This enables a particularly independent and simple control of the back pressure present in the second region of the storage container. The regulation can take place, for example, by means of a control valve, wherein the control valve can be actuated, for example, via at least one pressure sensor arranged in the pump inlet duct and/or the pump outlet duct and a suitable PID control (proportional-integral-differential control) for the control of the control valves . In the arrangement of several storage tanks, for example, the control valve of a storage tank arranged on the pump inlet side can be controlled as a function of a pressure prevailing in the pump inlet channel and/or the control valve of a storage tank arranged on the pump outlet side can be controlled as a function of a pressure prevailing in the pump outlet channel. Alternatively, the respective control valve can also be controlled as a function of a pressure prevailing in the pump chamber, with the pressure sensor advantageously being arranged in the region of the pump chamber for this purpose.

The gas volume of the second storage container is preferably fluidically connected to the gas volume of the first storage container, in particular via a separate secondary pipeline, such as a gas pressure line. As a result, the two second areas of the storage containers can be operatively connected, so that the pressure source or pressure measure for the fluid in the second area of one storage container is that in the second area of the other storage container prevailing gas pressure can serve. Furthermore, this enables automatic damping of pressure pulsations.

A check valve and the second storage tank or the branch of the branch pipeline leading into the second storage tank are preferably arranged in the pipe section arranged between the pump chamber and the first storage tank. This allows the pump to work particularly efficiently.

Particularly preferred is the second storage tank on the pump inlet side with the pump inlet channel downstream of the first storage tank on the pump inlet side and upstream of the pump chamber in the direction of flow, in particular upstream of a check valve, and/or the second storage tank on the pump outlet side with the pump outlet channel downstream of the pump chamber, in particular downstream of a check valve, and upstream of the pump outlet side first storage container fluidly connected. In particular, the second reservoir is arranged on a fluid side of the check valve arranged in the respective pump channel, remote from the piston pump. This enables a particularly effective damping of pressure pulsations.

In principle, a fluidic separation of the first area and the second area can take place in the first and second storage containers by means of the different densities of the fluid located in the first area and the gas located in the second area. In this configuration, therefore, no separating means is provided between the first area and the second area. The filling level in the respective storage container can be regulated by regulating the gas pressure. Such an embodiment enables in particular a storage container that is low in weight, maintenance-free and inexpensive to produce. In certain embodiments, however, it can be advantageous for a displacement body to be arranged in the first storage container and/or in the second storage container between the fluid and the gas volume for fluidic separation of the first area and the second area, which in particular can be used as a displaceable wall Piston or movable membrane is formed. This allows in the gas volume of each Storage container prevailing pressure act directly on the displacement body, in particular as a counterforce to a force applied by the fluid. The displacement body is particularly preferably designed as a flexible membrane. As a result, the displacement body can be displaced in a particularly simple manner. The storage container can thus in particular each have a first pressure chamber filled with the fluid and a second pressure chamber which is fluidically separated from the latter by means of the displacement body, is in operative connection therewith and is preferably filled with the gas. Such a design is advantageous in particular for conveying fluids with solid particles and enables reliable and low-maintenance pulsation damping, in particular in the case of such fluids. In this way, a pressure of the medium to be pumped on the pump inlet side or pump outlet side, in particular a fluid mixed with solids, can be transferred in a particularly simple and reliable manner to the second area of the storage container, in particular to a gaseous fluid. In this case, the displacement body can preferably be displaced in the direction of the first or the second region. By relocating or displacing the displacement body separating the areas, the respective volume of the first and second area can be changed relative to one another in a relatively simple manner the second area can be enlarged. As a result, a flow of the fluid located in the pump inlet channel or pump outlet channel into or out of the second storage container can be controlled particularly advantageously, and particularly efficient damping can be brought about. In order to control or regulate the change in volume, the displacement body can be subjected to a counter-pressure with respect to the pressure applied on the conveying fluid side, for example via a spring-elastic element. The displacement body is preferably designed as a piston, in particular a separating piston, of a closed system, such as a piston-cylinder unit. In such a configuration, the counter-pressure acting on the piston or the membrane can be produced, for example, by a medium located in the correspondingly arranged and pressurized second pressure chamber.

The piston pump is preferably designed as a piston membrane pump with a pump working chamber and a pump delivery chamber which is fluidically separate from this chamber and is in operative connection with it. The pump working chamber is arranged on the piston side, in particular in relation to the diaphragm of the pump, and the pump delivery chamber is arranged on the side of the diaphragm facing away from the piston. This fluidic separation of the conveying fluid from a pressure medium enables a particularly efficient and safe reduction of pressure pulsations, in particular in the case of conveying fluids with solid particles. In an alternative embodiment, in particular in a conventional piston pump, the pump working chamber and the pump delivery chamber form a common pump chamber.

Figur 1 -

eine aus dem Stand der Technik bekannte Kolbenmembranpumpe;

Figur 2a -

eine erste Ausgestaltung eines erfindungsgemäßen Pulsationsdämpfungssystems an einer Kolbenmembranpumpe;

Figur 2b -

eine erweiterte Variante des Pulsationsdämpfungssystems aus Fig.2a;

Figur 3 -

eine dritte Ausgestaltung eines erfindungsgemäßen Pulsationsdämpfungssystems an einer klassischen Kolbenpumpe;

Figur 4a -

eine vierte Ausgestaltung eines erfindungsgemäßen Pulsationsdämpfungssystems an einer klassischen Kolbenpumpe;

Figur 4b -

eine erweiterte Variante des Pulsationsdämpfungssystems aus Fig.4a;

Figur 5 -

eine aus dem Stand der Technik bekannte Kolbenmembranpumpe;

Figur 6 -

eine erste Ausgestaltung eines erfindungsgemäßen Pulsationsdämpfungssystems an einer Kolbenmembranpumpe; und

Figur 7 -

eine zweite Ausgestaltung eines erfindungsgemäßen Pulsationsdämpfungssystems an einer Kolbenmembranpumpe;

Exemplary embodiments of the invention are explained in more detail below with reference to the figures. They show schematically:

Figure 1 -

a piston diaphragm pump known from the prior art;

Figure 2a -

a first embodiment of a pulsation damping system according to the invention on a piston diaphragm pump;

Figure 2b -

an extended variant of the pulsation damping system Fig.2a ;

Figure 3 -

a third embodiment of a pulsation damping system according to the invention on a classic piston pump;

Figure 4a -

a fourth embodiment of a pulsation damping system according to the invention on a classic piston pump;

Figure 4b -

an extended variant of the pulsation damping system Figure 4a ;

Figure 5 -

a piston diaphragm pump known from the prior art;

Figure 6 -

a first embodiment of a pulsation damping system according to the invention on a piston diaphragm pump; and

Figure 7 -

a second embodiment of a pulsation damping system according to the invention on a piston diaphragm pump;

In the figure 1 shows the basic structure of a piston membrane pump 101 known from the prior art with the adjoining pipelines 6, 13 and the intermediate storage tank 8, 15, also known as the storage tank, which is advantageous for promoting a pumping requirement.

The oscillating movement of the piston 1 is transmitted to a pressure medium 2a located in a first pressure chamber 2 designed as a pump working chamber. This pressure medium 2a is operatively connected via a flexible membrane 3 to the second pressure chamber 4, which is in the present case designed as a pump delivery chamber, with regard to pressure transmission. Both pressure chambers 2, 4 are surrounded by a pressure-resistant housing 5. In the pump delivery chamber 4 there is in particular the medium 9 to be delivered, which can enter the pump delivery chamber 4 via a fluid inlet 6a and exit from the pump delivery chamber 4 through a fluid outlet 13a. In particular, the medium 9 to be conveyed can be sucked into the pump conveying chamber 4 through the fluid inlet 6a from a suction line 6 in which a suction valve 7 designed as a check valve is located. In the arrangement from the prior art presented here, there is also a reservoir 8, also known as a pressure vessel, in the suction line 6 of the pump 101, which is partly filled with the fluid 9 to be pumped and in the upper part of which there is a pressurized stagnant gas 10, for example compressed air, is located. The reservoir 8 is connected to a source 11 which has a higher geodetic height than the pump 101 in order to be able to provide the necessary suction pressure. Alternatively, the reservoir can also be acted upon by what are known as feed pumps, which are not shown here and which then generate the necessary suction pressure in the suction line 6 . The filling level in the reservoir 8 is controlled via the pressure of the gas 10. By measuring the fill level in the reservoir 8, the gas pressure 10 can be varied in particular via a control valve 12 such that a predetermined fill level in the reservoir 8 is adjusted as precisely as possible. For setting or controlling the prevailing in the reservoir 8 Gas pressure, the reservoir 8 is connected to a gas source via a pneumatic line arranged in the area of the gas volume 10 and via the control valve 12 .

The pump delivery chamber 4 of the pump 101 is connected to a further reservoir 15 via an outlet line 13 in which a pressure valve 14 designed as a check valve is located. Similar to the suction side of the pump 101, in particular to the reservoir 8 arranged thereon, the medium 9 to be pumped is also located in the lower region of the outlet-side reservoir 15, while a pressurized gas or air volume 17 is located above it. Here, too, the filling level of the reservoir 15 can be regulated via a control valve 18 that can be fluidically connected to the air volume 17 and a gas source that is connected thereto and is not shown in detail. The volume flow generated by the pump 101 can then be supplied to the intended application via a discharge line 19 .

The mode of operation of such a pump can be described as follows: During the suction phase of the piston pump 101 shown, the piston 1 moves from the in figure 1 extreme right position shown to the left, which leads to a drop in pressure in the pump working chamber 2. This pressure is transmitted through the flexible membrane 3, which is in position 3a at the beginning of the suction phase, to the pump delivery chamber 4 and thus to the fluid 9 to be delivered. If the pressure in the two pressure chambers 2 and 4 of the pump falls below the pressure prevailing in the reservoir 8, the suction valve 7 opens automatically and the medium 9 to be pumped flows from the reservoir 8 into the pump delivery chamber 4.

As soon as the piston 1 reaches the in figure 1 has reached the extreme left position shown, it then moves to the right again. This results in a compression of the two fluid chambers 2 and 4. This pressure increase causes the suction valve 7 to close and no further medium 9 is sucked in. If the piston 1 moves further and further to the right, the pressure in the two fluid chambers 2, 4 continues to rise until the pressure prevailing in the reservoir 15 is exceeded. As a result, the pressure valve 14 opens and the pump 101 delivers the medium 9 from the pump delivery chamber 4 into the reservoir 15 until the piston 1 has again reached the extreme right position and the process is repeated.

The oscillating movement of the piston 1 causes acceleration effects to be exerted on the fluid medium 9 to be conveyed, which can lead to pulsations in the pressure chambers 2 and 4, the adjacent suction pipe 6 and the discharge pipe 13. In order to reduce these pulsations, the pulsation damper system 100 according to the invention is presented below, by means of which the pulsations that propagate when the medium 9 is sucked on can be reduced in particular.

It should be clear that the configurations of a respective pump with only one piston described here only occur relatively rarely in practice and are only intended to show the operating principle of this type of pump in the present case. Usually, pumps with several pistons are used, which suck in from a common suction line with a central reservoir and in turn pump into a common delivery capacity. The principles of position damping presented here can therefore be applied to pumps with any number of pistons.

In the Figure 2a a first embodiment of the pulsation damping system 100 according to the invention is shown. This configuration can be seen, for example, in figure 1 a damping device 103 is additionally provided. In the present case, the damping device 103 comprises in particular a volume change device 105 embodied as a piston-cylinder unit, or also called a volume displacement unit. The volume change device 105 has a cylinder 21 with a first pressure chamber 22 arranged therein, which is connected to the pump working chamber 2 via a damping fluid connection 20a and a hydraulic connecting line 20, and a second pressure chamber 24 which is fluidically separated from the first pressure chamber 22 by means of a separating piston 23.

As a result of this arrangement, in particular a part of the pressure medium contained in the pump working chamber 2 , in particular a hydraulic oil, can flow into or out of the first pressure chamber 22 of the cylinder 21 . The second pressure room 24 is connected via a pressure line 25 to the gas volume 10 of the pressure vessel 8 arranged on the inlet side, so that an average pressure is established in the second pressure chamber 24 which corresponds to the average pressure in the reservoir 8 .

In order to dampen the pulsations in the pump chambers 2 and 4 and the adjacent pipelines 6 and 13, a throttle point 26 is introduced into the hydraulic connecting line 20. If there is an increase in pressure due to pulsations in the pump chamber 2, this leads to a volume flow from the pump working chamber 2 into the first pressure chamber 22 if the separating piston 23 is not in its, in Figure 2a , Right end position 28 is located. When flowing through the throttle point 26, part of the pulsation energy is converted into heat and thus reduces the level of the pressure pulsations. If the pressure in the pump working chamber 2 then falls, the pressure in the gas-filled pressure chamber 24 leads to a displacement of the piston 23 and consequently to a volume flow of the pressure medium 2a from the first pressure chamber 22 into the pump working chamber 2, with the Throttle point 26 in turn hydraulic energy is converted into heat, and thus the pulsations is further reduced.

The system can thus permanently convert pulsation energy into heat during the suction phase as long as the movement of the separating piston 23 is not prevented by reaching one of the end stops or cylinder stops 27 or 28 .

If, after the end of the suction phase, the above-described compression occurs in the pump working chamber 2, this causes the separating piston 23 to move again for as long as Figure 2a , moves to the right until the piston 23 is stopped by the stopper 28. Only now can the further increase in pressure take place and the medium 9 to be pumped be conveyed via the line 13 into the reservoir. During this discharge phase, the pressure in the pump chambers 2 and 4 is usually so great that the separating piston 23 is permanently on, in Figure 2a , right stop 28 remains.

If the pump piston 1 now moves back, in Figure 2a , left, there is a decompression in chambers 2 and 4, the pressure valve 14 closes again and when the pressure of medium 9 in the reservoir 8 falls below the suction valve 7 opens and the medium 9 flows into the pump delivery chamber 4. Since the gas pressure in the If the pressure chamber 10 is approximately equal to the pressure of the medium 9 in the reservoir 8, there is also a pressure difference between the second pressure chamber 24 and the first pressure chamber 22 of the piston-cylinder unit 105. This pressure difference now accelerates the separating piston 23 again in the direction of the stop 27, so that now the separating piston 23 oscillates freely again due to the pulsations in the pump working chamber 2 and the throttle 26 can reduce the pulsations.

At the in the Figure 2b The arrangement shown is the pulsation damping system 100 according to FIG Figure 2a additionally extended by a damping device 104 on the discharge side of the pump 101. Analogous to the damping of the pulsations during the suction phase, such a damper 103 can also be used for the discharge side of the pump 101. In this case, the pump working chamber 2 is fluidly connected to an additional volume change device 106 via a pressure line 29 . In principle, the volume change device 106 is constructed in the same way as the volume change device 105.

The volume change device 106 in turn has a cylinder 30 with a first pressure chamber 32 arranged therein, which is connected to the pump working chamber 2 via a damping fluid connection 29a and a hydraulic connecting line 29, and a second pressure chamber 33 which is fluidically separated from the first pressure chamber 32 by means of a separating piston 31.

The first pressure chamber 32 is filled with the pressure medium 2a, the second pressure chamber with gas or air. This gas or the second pressure chamber 33 is connected via a pressure line 34 to the gas volume 17 of the reservoir 15 on the discharge side of the pump 101 . During the suction phase of the pump 101, the pressure in the pump chamber 2, 4 is so low that the excess pressure in the gas volume 17 moves the separating piston 31 to a first stop 35, where it remains until the compression phase begins. When the opening pressure of pressure valve 14 is exceeded, it is opened and simultaneously generates an increase in pressure in the first pressure chamber 32, causing a movement of the piston 31 to, in Figure 2b , right in the direction of the second stop 37 is effected. The pulsations that now occur in the fluid 2a and in particular the pump chambers 2 and 4 and the pipelines 6 and 13 lead to an oscillating movement of the separating piston 31, whereby the associated flow through the throttle 36 draws energy from the pressure pulsations and converts this into heat.

In the figure 3 Another application of the pulsation damping system 100 is shown on a conventional or classic piston pump 102, the arrangement shown in the previous figures with the pipelines 6, 13 adjoining the pump 102, in particular the supply line 6 and discharge line 13 for the pumped Fluid medium 2a, as well as the temporary storage containers 8 and 15 advantageously arranged therein to promote a delivery requirement Figure 2b is therefore in figure 3 only the pump 102 is configured differently. In this context it should be pointed out again that the type of piston pump is of secondary importance for the present invention.

In the present piston pump, the fluid medium 2a to be conveyed is used directly as a medium for damping the pressure pulsations occurring in the pump chamber 4 and the pipelines 6 and 13 . For this purpose, the fluid medium 2a can be conveyed not only through the pipelines 6, 13 into and out of the pump chamber 4, but also via the pressure lines 20 and 29, which are additionally connected to the pump chamber 4 via a respective damping fluid connection 20a, 29a functionally the same as in the arrangement according to Figure 2b - now the fluid medium 2a located in the pump chamber 4 for damping is additionally directed towards or away from the respective inlet-side and outlet-side damping device 103, 104, depending on the mode of operation of the piston 1, in particular suction process or pressure process, in particular through the in the respective Pipe 6, 13 arranged throttle point 26, 36 for damping the pressure pulsations, in particular by converting the pressure energy into heat.

In the figures 4a and 4b a further possible application of the pulsation damping system 100 is shown in each case. In some pump applications, the reservoir previously shown in the suction line 6 and/or in the pressure line 13 or in both lines 6, 13 is omitted, as will be shown in this example. Nevertheless, the operating principle of the pulsation damping system 100 according to the invention can also be applied to such a pump arrangement. For this - as in Figure 4a shown - the second pressure chamber 24 provided on the inlet-side volume change device 105 and - as in FIG Figure 4b shown - additionally also the second pressure chamber 33 provided on the outlet-side volume change device 106 via a pressure line - in Figure 4b Pressure line 34 - connected via a control valve 37, 38 with an external compressed air supply, not shown. The gas pressure present in the respective second pressure chamber 24, 33 can consequently be set and regulated via the respective control valve 37, 38, in particular in order to adapt the respective pneumatic pressure in the second pressure chamber 24, 33 to the mean pressures of the suction line 6 or pressure line 13. For example - as in Figure 4b shown - via corresponding pressure sensors 39 and 40, the pressure in the respective line 6, 13 or - as in Figure 4a shown - are determined via at least one pressure sensor 43 directly on the pump chamber 4 and automatically adjusted via control devices 41 and 42 in the second pressure chambers 24 and 33. In addition to the pressure control shown here using pressure sensors/receptacles and electronic controllers, mechanical control valves are also conceivable, which convert the hydraulic pressure into a corresponding pneumatic pressure.

It should be understood that the scope of the present invention is not limited to the embodiments described. In particular, the structure of the piston pump and the main pipelines connected thereto for conveying a fluid medium can be modified without changing the essence of the invention. For example, it is not absolutely necessary for an intermediate storage container 8 to be provided in the supply line and/or for an intermediate container 15 to be provided in the outlet line. Furthermore, the design of the volume change devices 105, 106 can be designed differently, for example, instead of the separating piston 23, 31, a membrane can be provided.

In the figure 5 shows the basic structure of a piston diaphragm pump 2101 known from the prior art with adjoining pipelines 206, 213 and first storage containers 208, 215, also known as intermediate or storage containers, advantageously arranged therein for conveying a pumped medium.

The oscillating movement of the piston 201 is transmitted to a pressure medium located in a first pressure chamber 202 designed as a pump working chamber. This pressure medium is operatively connected via a flexible membrane 203 to the second pressure chamber 204, which is designed here as a pump delivery chamber, with regard to pressure transmission. Both pressure chambers 202, 204 are surrounded by a pressure-resistant housing 205. The pump delivery chamber 204 contains in particular the fluid medium 209 to be delivered, which can enter the pump delivery chamber 204 via a fluid inlet from a pump inlet channel 206 and exit from the pump delivery chamber 204 into a pump outlet channel 213 through a fluid outlet. In particular, the fluid 209 to be delivered can be sucked into the pump delivery chamber 4 from the pump inlet channel 206, also referred to as the suction line, in which a suction valve 207 designed as a check valve is located.

In the arrangement from the prior art presented here, the inlet-side first storage tank 208, also referred to as a reservoir, is also located in the suction line 206 of the pump 2101 stagnant gas 210, such as compressed air filled. The lower region 208a of the first storage tank 208 is fluidically connected to the pump inlet channel 206, in particular via a pumping fluid inlet 206a facing a pumping fluid source 211 (not shown in detail) and via a pumping fluid outlet 206b connected to a pipe section 206c of the pump inlet channel 206 that connects the first storage tank 208 to the pump chamber 204 . The source 211 is usually a tank which has a higher geodetic height than the pump 2101 in order to be able to provide the required suction pressure. The lower portion 208a and the upper portion 208b of the first storage container 208 can in principle be fluidically separated from one another by a displacement body designed, for example, as a membrane. In the present case, the lower partial area 208a and the upper partial area 208b are separated due to the different arrangement and densities of the fluid 209 and the gas 210, which form a filling level 232 at the interface, the respective filling level 232 in the first storage container 208 being above the pressure of the gas 210 is regulated. By measuring the filling level 232 in the first storage container 208, the gas pressure 210 can be varied, in particular via a control valve 212, such that a predefined filling level 232 in the first storage container 208 is regulated as precisely as possible. To adjust or regulate the gas pressure in first storage tank 208, first storage tank 208 on the inlet side is connected to a gas source (not shown) via a pneumatic or pressure line arranged in the area of gas volume 210 and via control valve 212. Alternatively, this first storage tank 208 on the inlet side can also be pressurized via so-called feed pumps, which are not shown here and which then generate the necessary suction pressure in the intake line 6 .

In the outlet line 213, in which there is a pressure valve 214 designed as a check valve, there is a further first storage tank 215 on the outlet side, also designed as a storage tank. The first storage tank 215 on the outlet side, in particular a lower region 215a of the first storage tank 215, is fluidically connected to the pump outlet channel 213, in particular via a delivery fluid inlet 213a connected to a pipeline section 213c of the pump outlet channel 213, which connects the pump chamber 204 to the first storage tank 215 on the outlet side, and via a conveying fluid outlet 213b connected to a conveying fluid discharge line 219, not shown in detail.

Analogously to the suction side of the pump 2101, in particular to the first storage tank 208 arranged thereon, the fluid 209 to be pumped is also located in the lower region 215a of the first storage tank 215 on the outlet side, while above it in the upper region 215b is a pressurized volume of gas or air 217 is located. The lower portion 215a and the upper portion 215b are present also not by a separate release agent, such as a displacement body, fluidly separated from one another, but separated due to the different arrangement and densities of the fluid 209 and the gas 217, which form a filling level 216 at the interface. Here, too, the filling level 216 of the first storage container 215 on the outlet side can be regulated via a control valve 218 that can be fluidically connected to the gas volume 217 and a gas source that is connected thereto and is not shown in detail. The volume flow of the conveying fluid 209 generated by the pump 2101 can be fed to an intended application (not shown) via a discharge line 219 .

The mode of operation of such a pump 2101 can be described as follows: During the suction phase of the piston pump 2101 shown, the piston 201 moves from the in figure 5 extreme right position shown to the left, which leads to a drop in the pressure in the pump working chamber 202. This pressure is transmitted through the flexible membrane 203, which is in position 203a at the beginning of the suction phase, to the pump delivery chamber 204 and thus to the fluid 209 to be delivered. If the pressure in the two pressure chambers 202 and 204 of the pump 2101 falls below the pressure prevailing in the inlet line 206 and in the first storage tank 208 on the inlet side, the suction valve 207 opens automatically and the fluid 209 to be delivered flows from the first storage tank 208 on the inlet side into the Pump delivery chamber 204.

As soon as the piston 201 reaches the in figure 5 has reached the extreme left position shown, it then moves to the right again. This results in a compression of the two pressure chambers 202 and 204. This pressure increase causes the suction valve 207 to close and no further fluid 209 is sucked in. If the piston 201 moves further and further to the right, the pressure in the two pressure chambers 202, 204 continues to rise until the pressure prevailing in the outlet line 213 and in the first storage container 215 is exceeded. As a result, the pressure valve 214 opens and the pump 2101 delivers the fluid 209 from the pump delivery chamber 204 into the reservoir 215 until the piston 201 has again reached the extreme right position and the process is repeated.

The oscillating movement of the piston 201 causes acceleration effects to be exerted on the fluid medium 209 to be conveyed, which can lead to pulsations in the pressure chambers 202 and 204, the adjacent suction pipe 206 and the discharge pipe 213. In order to reduce these pulsations, the pulsation damper system 2100 according to the invention is presented below, through which the pulsations that propagate when the fluid 209 is sucked in can be reduced in particular.

In the figure 6 a first embodiment of the pulsation damping system 2100 according to the invention is shown. This configuration can be seen, for example, in figure 5 shown typical structure of a piston diaphragm pump system additionally a second storage tank 220 arranged on the pump inlet side. The second storage tank 220 is also constructed in the manner of a storage tank or pressure vessel and has a first area or pressure chamber 220a and a second pressure chamber 220b. The present lower region 220a of the second storage tank 220 on the inlet side is fluidically connected to the pump inlet channel 206 via a branch pipeline 221 and is filled with the delivery fluid 209 . The connection of the branch pipeline 221 to the pump inlet channel 206 is in particular as close as possible to the pump chamber 204, but always upstream of the check valve or inlet valve 207 in the direction of flow, i.e. upstream, in particular in the pipeline section 206c. As a result of this arrangement, in particular part of the delivery fluid 209 contained in the pump inlet channel 206 can flow into or out of the first pressure chamber 220a.

A gas volume 225 is formed in the upper region or pressure chamber 220b--as is also the case with the first storage container 208. FIG. The second pressure chamber 220b is connected via a pressure line 223 to the gas volume 210 of the first storage tank 208 arranged on the inlet side, so that an average pressure is established in the second pressure chamber 220b, which corresponds to the average pressure in the first storage tank 208. This leads in particular to the fact that when the pump 2101 is at a standstill in the second storage tank 220 on the inlet side, the same geodetic filling level 2 22 is established, which also prevails in the first storage tank 208 on the inlet side.

If pressure pulsations occur in the suction line 6 of the pump 2101 during the operation of the pump 2101, this leads to a volume flow of the fluid 209 to be pumped from the pump inlet channel 206 through the branch pipe 221 into the first pressure chamber 220a of the second storage tank 220 when the pressure increases. In order to effectively dampen the pulsations in the pump chambers 202 and 204 and the adjacent pipelines 206 and 213, a throttle point 224 is introduced into the branch pipeline 221. When flowing through the throttle point 224, part of the pulsation energy is converted into heat and thus reduces the level of the pressure pulsations. If the pressure in the pump inlet channel 206 then drops, the pressure in the gas-filled pressure chamber 220b leads to an increased back pressure and consequently to a shift, in particular a lowering of the filling level 222 and a volume flow of the fluid 209 from the first pressure chamber 220a to the Pump inlet channel 206, wherein at the throttle point 224 again pressure energy is converted into heat, and thus the pulsation is further reduced.

If compression occurs in the pump chamber 204 after the end of the suction phase, the suction valve 207 closes again and the fluid 209 to be pumped is conveyed via the line 213 into the first storage tank 215 on the outlet side. This can result in a brief drop in pressure in intake manifold 206, as a result of which part of the fluid 209 can flow back out of the second storage tank 220 into the intake line 206, with hydraulic energy being converted into heat when it flows through the throttle 224 and the pulsations being further reduced . In this way, the system can permanently convert pulsation energy into heat, especially during the suction phase.

Because friction losses and flow effects in the suction pipe 206 can result in slightly different mean pressures in the containers 208 and 220, the containers 208, 220 usually have different mean geodetic fill levels 222, 232. In order to prevent the container 220 from running empty or being overfilled, which would significantly impair the function of the damper, the filling level 232 in the container is regulated 208 and the installation height and the size of the container 220 are coordinated.

the inside figure 6 The damper shown thus reduces the pulsations that prevail in the suction area of the pump 2101. However, since comparable pulsations can also occur on the discharge side of pump 2101, in figure 7 a second embodiment of the pulsation damping system 2100 is shown, in which a pulsation damper is provided for the pressure line in addition to the suction damper.

At the in the figure 7 The arrangement shown is the pulsation damping system 2100 according to FIG figure 6 additionally extended by a second storage tank 226 arranged on the discharge side of the pump 2101 and a throttle point 230 in the supply line to this second storage tank 226. Analogously to the arrangement of the second storage container 220 on the suction side, the pressure pulsation energy when the fluid 209 flows through the throttle 230 is also converted into heat in the arrangement on the discharge side. Similar assumptions and prerequisites apply here as for the suction-side damper. The design and functioning of the second storage tank 226 on the outlet side and its integration into the pipeline system on the outlet side therefore essentially correspond to the arrangement of the second storage tank 220 on the pump inlet side.

In the second storage container 226 on the outlet side, an area or pressure chamber 226a filled with the fluid 209 is formed in a lower part and an area or pressure chamber 226b filled with a gas volume 231 is formed in an upper part. The lower portion 226a is fluidly connected to the pump outlet passage 213 via a branch pipe 227 . The connection of the branch pipeline 227 to the pump outlet channel 213 is as close as possible to the pump chamber 204, but always in the direction of flow after, i.e. downstream of, the non-return or outlet valve 214, in particular in the region of the pipeline section 213c. This arrangement allows, in particular, part of the delivery fluid 209 contained in the pump outlet channel 213 to flow into or out of the first pressure chamber 26a. flow out.

A gas volume 231 is formed in the upper pressure chamber 226b--as is also the case with the first storage container 208 on the inlet side. The second pressure chamber 220b is connected via a pressure line 229 to the gas volume 217 of the first storage tank 215 arranged on the outlet side, so that an average pressure is set in the second pressure chamber 226b, which corresponds to the average pressure in the first storage tank 215. This has the effect, in particular, that when the pump is at a standstill, the same geodetic fill level 228 is established in the second storage tank 226 on the outlet side, which also prevails in the first storage tank 215 on the outlet side. If pressure pulsations occur in the high-pressure line 213 of the pump 2101 during operation of the pump, this pressure increase causes the fluid 209 to be pumped to flow out of the pressure line 213 into the second storage tank 226. In this case, when flowing through the throttle point 230, part of the pulsation energy converted into heat, thereby reducing pressure pulsations. If the pressure in the pump outlet channel 213 then drops, the pressure in the gas-filled pressure chamber 226b leads to an increased back pressure and consequently to a shift, in particular a lowering of the fill level 228 and a volume flow of the fluid 209 from the first pressure chamber 226a to the Pump outlet channel 213, wherein at the throttle point 230 again pressure energy is converted into heat, and thus the pulsations are further reduced. Thus, this system can permanently convert pulsation energy into heat not only during the suction phase but also during the pressure phase.

It should be clear that the configurations of a respective pump with only one piston described here only occur relatively rarely in practice and are only intended to show the operating principle of this type of pump in the present case. Usually, pumps with several pistons are used, which suck in from a common suction line with a central reservoir and in turn deliver into a common delivery line. The principles of position damping presented here can therefore be applied to pumps with any number of pistons. Furthermore, it does not necessarily have to be a diaphragm pump; the pulsation damping system can also be used with other, for example classic, piston pumps.

Furthermore, it should be understood that the scope of the present invention is not limited to the described embodiments. In particular, the structure of the piston pump and the main pipelines connected thereto for conveying a fluid medium can be modified without changing the essence of the invention. For example, it is not absolutely necessary for the first storage container to be fluidically connected to the second storage container. Furthermore, the design of the first and second storage container can be designed differently, for example, instead of the membrane arranged therein, a partition wall or a separating piston can be designed.

Reference list:

1

Pistons

2

Pump working chamber, pump chamber, pressure chamber

2a

Pressure medium, fluid, hydraulic oil

3, 3a

membrane

4

Pump delivery chamber, pump chamber, pressure chamber

5

housing

6

Pump inlet port, suction line

6a

conveying fluid connection

7

check valve, suction valve

8th

reservoir, pressure vessel

9

conveying medium, fluid

10

Gas, compressed air, gas volume

11

source

12

control valve

13

Pump outlet channel, outlet line

13a

conveying fluid connection

14

check valve, pressure valve

15

reservoir, storage tank

17

Gas, compressed air, gas volume

18

control valve

19

discharge line

20

Piping, inlet-side damping pressure line

20a

damping fluid connection

21

cylinder

22

first pressure room

23

Displacement body, floating piston

24

second pressure room

25

Pipeline, gas pressure line

26

Throttle valve, throttle

27

first stop

28

second stop

29

Piping, outlet-side damping pressure line

29a

damping fluid connection

30

cylinder

31

Displacement body, floating piston

32

first pressure room

33

second pressure room

34

Pipeline, gas pressure line

35

first stop

36

Throttle valve, throttle

37

second stop

100

pressure pulsation dampening system

101

piston diaphragm pump

102

piston pump

103

damping device

104

damping device

105

volume change device

106

volume change device

201

Pistons

202

Pump working chamber, pump chamber, pressure chamber

203, 203a

membrane

204

Pump delivery chamber, pump chamber, pressure chamber

205

housing

206

Pump inlet port, suction line

206a

fluid inlet

206b

fluid outlet

206c

pipeline section

207

check valve, suction valve

208

first storage tank, pressure vessel

208a

first area

208b

second area

209

conveying medium, fluid

210

Gas, compressed air, gas volume

211

source

212

control valve

213

Pump outlet channel, outlet line

213a

fluid inlet

213b

fluid outlet

213c

pipeline section

214

check valve, pressure valve

215

first storage tank, pressure vessel

215a

first area

215b

second area

216

level height

217

Gas, compressed air, gas volume

218

control valve

219

discharge line, derivation

220

second storage tank, pressure boiler

220a

first area

220b

second area

221

branch pipe

222

level height

223

Secondary pipeline, compressed air line

224

Throttle valve, throttle

225

Gas, compressed air, gas volume

226

second storage tank, pressure boiler

226a

first area

226b

second area

227

branch pipe

228

level height

229

Secondary pipeline, compressed air line

230

Throttle valve, throttle

231

Gas, compressed air, gas volume

232

level height

2100

pressure pulsation dampening system

2101

piston pump

Claims (9)

1. A pulsation damping system (100) for reducing pressure oscillations in inlet and/or outlet side pipelines (6, 13) of piston pumps (101, 102), with at least one piston pump (101, 102) which has a pump chamber (2, 4), wherein the pump chamber (2, 4) for conveying a conveyance medium (9) is connected to a pump inlet channel (6) via a first fluid connection (6a) and is connected to a pump outlet channel (13) via a second fluid connection (13a),
   and wherein the pump chamber (2, 4) further has at least one damping fluid connection (20a, 29a) to which the pump chamber (2, 4) in each case with a damping device (103, 104) for damping pressure oscillations is fluidically connected, characterized in that a throttle valve (26, 36) is arranged in a pipeline (20, 29) which is arranged between the pump chamber (2, 4) and the damping device (103, 104).
2. A system according to claim 1, characterized in that the damping device (103, 104) has a volume changing device (105, 106) for changing the volume of at least one pressure space (22, 32) fluidically connected to the pump chamber (2, 4).
3. A system according to claim 2, characterized in that the volume changing device (105, 106) has a relocation body (23, 31) for changing the volume of the at least one pressure space (22, 24, 32, 33), which is in particular designed as displaceable wall, displaceable piston or relocatable diaphragm.
4. A system according to claim 3, characterized in that the volume changing device (105, 106) has a first pressure space (22, 32) which is fluidically connected to the pump chamber, and a second pressure space (24, 33) which, by means of the relocation body (23, 31), is fluidically separated therefrom and is operatively connected thereto.
5. A system according to claim 4, characterized in that the second pressure space (24, 33) can be fluidically connected to a separate gas source directly and/or indirectly via a regulating valve (12, 18, 37, 38) in order to regulate a gas pressure present in the second pressure space (24, 33).
6. A system according to any one of claims 4 or 5, characterized in that the second pressure space (24, 33) is directly or indirectly operatively connected to the pressure which is present in the pump inlet channel (6) and/or in the pump outlet channel (13) in order to regulate a gas pressure present in the second pressure space (24, 33).
7. A system according to any one of the preceding claims, characterized in that the damping device (103, 104) has a storage container (8, 15) with a conveyance fluid inlet (8a, 15a) and a conveyance fluid outlet (8b, 15b), which storage container is arranged in the pump inlet channel (6) and/or in the pump outlet channel (13), wherein the conveyance fluid (9) can be temporarily stored in the storage container (8, 15) in a lower region and a gas volume (10, 17) is arranged in an upper region.
8. A system according to claim 7, characterized in that the gas volume (10, 17) of the storage container (8, 15) is fluidically connected to the second pressure chamber (24, 33) of the volume changing device (105, 106).
9. A system according to any one of the preceding claims, characterized in that the piston pump is designed as a piston diaphragm pump (101) with a pump working chamber (2) and a pump conveyance chamber (4) which is fluidically separated therefrom and operatively connected thereto, wherein the first conveyance fluid connection (6a) and the second conveyance fluid connection (13a) are arranged on the pump conveyance chamber (4) and the at least one damping fluid connection (20a, 29a) is arranged on the pump working chamber (2).

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