EP1903217A1 - Hydropneumatischer Dämpfer für die Dämpfung der Schläge einer Pumpeinrichtung - Google Patents

Hydropneumatischer Dämpfer für die Dämpfung der Schläge einer Pumpeinrichtung Download PDF

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Publication number
EP1903217A1
EP1903217A1 EP20060425648 EP06425648A EP1903217A1 EP 1903217 A1 EP1903217 A1 EP 1903217A1 EP 20060425648 EP20060425648 EP 20060425648 EP 06425648 A EP06425648 A EP 06425648A EP 1903217 A1 EP1903217 A1 EP 1903217A1
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EP
European Patent Office
Prior art keywords
membrane
damper
hydropneumatic damper
hydropneumatic
previous
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EP20060425648
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English (en)
French (fr)
Inventor
Giovanni Zanardi
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SAIP Srl
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SAIP Srl
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Publication date
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Priority to EP20060425648 priority Critical patent/EP1903217A1/de
Publication of EP1903217A1 publication Critical patent/EP1903217A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration

Definitions

  • the present invention relates to a hydropneumatic damper for damping pressure pulsations in fluid pumping plants, and in particular to a damper to be mounted in line with the main piping.
  • Hydropneumatic dampers which are hydropneumatic accumulators being used for damping pulsations, are devices which are capable of storing and releasing pressure energy in hydraulic circuits by utilizing the compressibility of a gas contained therein. They are widely used, for instance, in the food industry, chemical industry and pharmaceutical industry and are also used for hydraulic applications such as, for example, in the hydraulic circuits of machine tools.
  • a hydropneumatic damper generally comprises a metallic chamber arranged in fluid communication with the plant piping. In the chamber there is mounted a membrane separating the plant fluid from an inert gas, usually nitrogen, which is in the chamber of the damper at a suitable pressure and occupies the whole internal volume thereof.
  • an inert gas usually nitrogen
  • the membrane When the pressure in the plant exceeds the pressure of the gas contained in the damper, the membrane is displaced thus reducing the volume which is occupied by the gas and consequently the gas pressure increases until it balances the pressure of the fluid. When the pressure in the plant decreases, the membrane is displaced in the opposite direction and the gas expands until it balances the new pressure of the fluid. The membrane displacement thus allows to accumulate fluid when the pressure in the plant increases and to release fluid when the pressure in the plant decreases.
  • Dampers are generally immediately downstream of the pumps on the main piping line of the plant and are usually mounted perpendicularly to the main piping, on a secondary piping which is in fluid communication with the main one.
  • patent EP 0078721 discloses a hydropneumatic damper consisting of a container divided into two chambers which are isolated one from the other by means of a diaphragm. One chamber is connected to a hydraulic plant through a duct, while the other chamber is connected to a gas reservoir.
  • known hydropneumatic dampers do not allow to completely damp the pressure pulsations in the plants, and in particular to obtain pulsation values at the output from the damper which are lower than 0,5% of the input pulsations.
  • Object of the present invention is thus to provide a hydropneumatic damper which is free from such drawbacks. Said object is achieved by means of a hydropneumatic damper arranged in line with the main piping and provided with one or more membranes having a substantially flat shape.
  • a first important advantage of this damper is that it allows to obtain output pulsation values down to 0,05% of the input pulsation.
  • a second significant advantage of this damper is that it allows to obtain high velocities of response to the input pulsations.
  • Another advantage of the present damper is that it allows a remarkable ease of cleaning and maintenance without the need to be disassembled, thanks to the flat shape of the elastic membranes being used and to the type of fixing of the latter to the damper chamber.
  • Figures 1 and 2 show a first embodiment of a pneumatic damper 1 according to the present invention, which comprises a duct 2 provided at each of its ends with a flange 3 suitable for fluid-tight connection of damper 1 to the piping (not shown) of the pumping plant line.
  • the duct 2 of damper 1 is further provided in its mantle with one or more openings 4 around which one or more corresponding hollow containers 5 are hermetically fixed.
  • damper 1 is provided with two openings 4 and two corresponding hollow containers 5, diametrically opposite with respect to the axis of duct 2.
  • duct 2 may have more than two ends suitable to receive or distribute the fluid of the plant in more directions.
  • Each container 5 defines in its inside a chamber 6 hermetically closed by an elastic membrane 7 which separates chamber 6 from the central part of duct 2.
  • the elastic membrane 7 has a substantially flat disc shape and is secured along its perimeter to container 5 at the zone of connection of container 5 to duct 2.
  • Each chamber 6 contains an inert gas, usually nitrogen, as well as a dividing baffle 8 limiting the deformation of membrane 7 towards the inside of chamber 6.
  • membrane 7 contributes to balancing the pressure of the fluid, in fact, because of the effect of the deformation, internal stresses arise in the membrane which oppose the deformation by trying to bring the membrane back to the non-deformed condition, that is by contrasting the increase in pressure of the fluid in duct 2.
  • membrane 7 is deformed in the opposite direction and the gas expands until it balances the new pressure of the fluid, thus reducing the internal volume of the central part of duct 2.
  • the deformation of membrane 7 thus allows to vary the volume of the central part of duct 2 according to the pumping pressure of the fluid, that is to accumulate fluid as the plant pressure increases and to release fluid as the plant pressure decreases.
  • the deformation of membrane 7 is limited in the direction of gas compression, that is from the axis of duct 2 towards chamber 6, by means of the dividing baffle 8.
  • the dividing baffle 8 is provided with a central hole 9 wherein a perforated element may be fixed, such as for example a grid, a net or a perforated sheet, which allows the gas contained in chamber 6 to go through it and to apply a pressure on membrane 7.
  • a perforated element may be fixed, such as for example a grid, a net or a perforated sheet, which allows the gas contained in chamber 6 to go through it and to apply a pressure on membrane 7.
  • the deformation of membrane 7 is limited in the direction of gas expansion, that is from chamber 6 towards the axis of duct 2, by means of a second perforated baffle 10 having a convex shape facing the axis of duct 2.
  • the baffle 10 is perforated in order to allow the fluid pumped in duct 2 to easily flow therethrough and to apply a pressure on membrane 7, and the size of the holes in baffle 10 is suitable for preventing the stagnation of fluid between baffle 10 and membrane 7 especially in case of very dense fluids such as, for example, greases, paints, rubbers in the fluid state, etc. In this way, the duct 2 of damper 1 according to the present invention can be cleaned, for example after each cycle, directly in line without disassembling any component thereof. Furthermore, the size of the holes of baffle 10 has to be suitable for preventing excessive deformations of membrane 7 as it pushes on baffle 10 due to the effect of the pressure of the gas contained in chamber 6, i.e. when the pressure in duct 2 decreases.
  • the baffle 10 may be a grid, a net or a perforated sheet, made e.g. of a metallic material, a polymeric material, PTFE, PVDF and other materials compatible with the pumped fluid.
  • baffle 10 has to be firmly fixed so as to not be damaged when membrane 7 pushes thereon, for example when the plant internal pressure is low and membrane 7 is pushed towards duct 2 by the gas contained in chamber 6.
  • baffle 10 can be fixed to the perimeter of opening 4 by welding and/or stiffened by means of a suitable frame connecting baffles 10 one to another and keeping fixed the mutual distances.
  • the damper 1 according to the present invention is arranged in line with the plant piping.
  • the entire surface of membrane 7 is arranged directly in contact with the fluid flowing in duct 2 and in the main line piping during the operation, and in this way it is possible to achieve high damping velocities of the pressure pulsations.
  • mounting the membrane dampers in branch configuration with respect to the line piping which is typical of the prior-art dampers, involves the use of side ducts and fittings which generate eddies and pressure drops thus altering and delaying the pressure signal reaching the membrane or bag.
  • membrane 7 contributes to increase the damping velocity of damper 1; in fact, as membrane 7 is substantially flat and is firmly fixed to the damper along the perimeter of container 5, a variation in the pressure of the fluid flow induces on membrane 7 a displacement which involves immediately the whole surface of the membrane itself and which is immediately transmitted to the gas contained in chamber 6.
  • the flatness of membrane 7 makes the response of damper 1 very sensitive and quick to high-frequency, small-amplitude pulsations.
  • membranes 7 having a slightly wavy, sinusoidal or concave section, whereby it is possible to achieve a higher volume of fluid accumulation. Therefore, slightly wavy or differently shaped membranes are particularly suitable for damping large amplitude pulsations.
  • membrane 7 exhibits a damping characteristic which can be suitably selected by adjusting the mounting tension thereof and using suitable materials, such as e.g. PTFE.
  • the membrane 7 can be entirely made of PTFE, however, as this material does not have optimal gas barrier properties, it is preferred to use a membrane consisting of a PTFE layer suitable for the contact with fluids which is coupled, e.g. in a vulcanization step, with a layer of butyl rubber or other elastomers.
  • membrane 7 Other materials suitable for manufacturing membrane 7 can be fluororubbers, EPDM, NBR, depending on the fluid being worked.
  • the pulsations transmitted by the membrane are mainly damped by suitably adjusting the pressure of the gas which is contained in each chamber 6.
  • the pressurized gas in chamber 6 behaves as a hydraulic damper activated by the action of membrane 7.
  • Suitable values of gas pressure in chamber 6 are comprised between 80% and 97% of the pumping pressure of the fluid, and preferably between 90% and 95%.
  • damper 1 may be provided with a number of containers 5 and respective membranes 7, whereby in this case it is possible to obtain a higher damping action. Furthermore, by connecting the chambers 6 one to another by means of channels 11, which are for example formed in the thickness of duct 2, the gas pressure in chambers 6 is homogeneous and it is thus possible to achieve a uniform behaviour of membranes 7.
  • the damper 1 allows to achieve extremely low output pulsation values, which are equal to e.g. 0,05% of the input pulsation.
  • Figure 3 shows a second embodiment of the above illustrated double-chamber damper 1, which comprises a second membrane 12 within each chamber 6, which is fluid-tightly fixed to the hollow container 5 in a way similar to the first membrane 7.
  • This embodiment is particularly suitable for plants in which no accumulation of the fluid being worked must occur, e.g. for food and pharmaceutical plants.
  • no dividing baffle 10 is present between the flat membrane 7 and duct 2 so that there are no cavities or recesses where the fluid being worked may stop.
  • the internal surfaces of duct 2 usually have a very low roughness, e.g. lower than 0,2 ⁇ m, in order to avoid the adhesion of the fluid being worked.
  • the volume comprised between the second membrane 12 and the first membrane 7 contains an incompressible fluid 13, which is suitable for contacting the fluid passing through duct 2 in case of failure of the first membrane 7.
  • the gas contained in chamber 6 would be mixed with the fluid being transported in duct 2 and this could be detrimental to the quality of the fluid itself and also to the main line piping.
  • the hole of the dividing baffle 8 it is not necessary to arrange a perforated element, since when membrane 7 is pressed towards the dividing baffle 8, it cannot be pushed through the hole because it is supported by the incompressible fluid contained between the two membranes 7, 12.
  • chamber 6 is provided with a second dividing baffle 14 which is arranged between membrane 12 and container 5, and which is provided with a hole for the passage of the gas contained in chamber 6.
  • the membrane 12 may be provided with an anti-extrusion element (12a) which is suitable to engage the edge of the hole of the dividing baffle 14 thus preventing membrane 12 from exiting through said hole. In this last case, it is not necessary that the hole is provided with a perforated element for limiting the displacement of membrane 12.
  • Materials suitable for manufacturing membrane 12 are e.g. elastomers such as EPDM, fluororubbers and/or NBR.
  • the chamber 6 may also have shapes which are different from the dome shape shown in Figure 3, such as for example a dome shape with one or more cylindrical expansions. Further, it is possible to replace or combine chamber 6 with one or more accumulators of the prior art.
  • FIG. 4 shows a third embodiment of damper 1 according to the present invention, which comprises a heating and/or cooling system.
  • a heating and/or cooling system can for example allow to maintain a desired viscosity value in the fluid being transported in duct 2, and thus allows to keep in the fluid state substances which can solidify inside duct 2, such as e.g. waxes.
  • the heating and/or cooling system may for example consist of a hydraulic circuit which is provided with a delivery pipe 15 and a return pipe 16, and with passageways 17 formed in the structure of damper 1 wherein a suitable heating/cooling fluid circulates.
  • the heating system may be carried out in other ways, e.g. by means of electrical resistances.
  • membranes 7, 12 may, for example, be metallic membranes.
  • damper 1 may be provided with manometers or pressure sensors being mounted, for example, on container 5 in order to keep the operating state of the device under control and to detect possible failures of membranes 7, 12.
  • dampers 1 according to the present invention may vary depending on the application they are intended for.
  • the volumetric capacities of the single chambers 6 of a single damper 1 may be different from each other in order to obtain an optimal pulsation damping response.
  • damper 1 it is possible to apply to damper 1 according to the present invention a pressure control system capable of keeping constant the ratio between the pressure in each chamber 6 and the plant internal pressure, which may undergo variations during the operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Pipe Accessories (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP20060425648 2006-09-22 2006-09-22 Hydropneumatischer Dämpfer für die Dämpfung der Schläge einer Pumpeinrichtung Withdrawn EP1903217A1 (de)

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Application Number Priority Date Filing Date Title
EP20060425648 EP1903217A1 (de) 2006-09-22 2006-09-22 Hydropneumatischer Dämpfer für die Dämpfung der Schläge einer Pumpeinrichtung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20060425648 EP1903217A1 (de) 2006-09-22 2006-09-22 Hydropneumatischer Dämpfer für die Dämpfung der Schläge einer Pumpeinrichtung

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EP1903217A1 true EP1903217A1 (de) 2008-03-26

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111637037A (zh) * 2020-05-30 2020-09-08 上海大隆机器厂有限公司 一种往复式压缩机装置中的脉动缓冲器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1108551A (en) * 1964-05-26 1968-04-03 Power Aux Ies Ltd Improvements in or relating to pressure accumulators for hydraulic liquid
GB1245717A (en) * 1969-02-01 1971-09-08 Teves Gmbh Alfred Accumulator for hydraulic systems
US3853147A (en) * 1973-01-08 1974-12-10 Airco Inc Respirator flow curve modifier
US4312382A (en) * 1979-03-14 1982-01-26 Firma J. Wagner Gmbh Pressure peak compensator for pulsating streams of liquid
EP0078721A1 (de) 1981-10-30 1983-05-11 DOSAPRO MILTON ROY, SociÀ©té dite: Hydropneumatischer Dämpfer
WO1994001680A1 (de) * 1992-07-09 1994-01-20 Hydac Technology Gmbh Mehrmembranenspeicher
WO2004071929A1 (en) * 2003-02-14 2004-08-26 Hultdin System Ab Damping device
US20050139277A1 (en) 2002-04-10 2005-06-30 Herbert Baltes Hydraulic accumulator, in particular a membrane accumulator

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1108551A (en) * 1964-05-26 1968-04-03 Power Aux Ies Ltd Improvements in or relating to pressure accumulators for hydraulic liquid
GB1245717A (en) * 1969-02-01 1971-09-08 Teves Gmbh Alfred Accumulator for hydraulic systems
US3853147A (en) * 1973-01-08 1974-12-10 Airco Inc Respirator flow curve modifier
US4312382A (en) * 1979-03-14 1982-01-26 Firma J. Wagner Gmbh Pressure peak compensator for pulsating streams of liquid
EP0078721A1 (de) 1981-10-30 1983-05-11 DOSAPRO MILTON ROY, SociÀ©té dite: Hydropneumatischer Dämpfer
WO1994001680A1 (de) * 1992-07-09 1994-01-20 Hydac Technology Gmbh Mehrmembranenspeicher
US20050139277A1 (en) 2002-04-10 2005-06-30 Herbert Baltes Hydraulic accumulator, in particular a membrane accumulator
WO2004071929A1 (en) * 2003-02-14 2004-08-26 Hultdin System Ab Damping device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111637037A (zh) * 2020-05-30 2020-09-08 上海大隆机器厂有限公司 一种往复式压缩机装置中的脉动缓冲器

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