EP0802328A1 - Bélier-aspirateur - Google Patents

Bélier-aspirateur Download PDF

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Publication number
EP0802328A1
EP0802328A1 EP96119475A EP96119475A EP0802328A1 EP 0802328 A1 EP0802328 A1 EP 0802328A1 EP 96119475 A EP96119475 A EP 96119475A EP 96119475 A EP96119475 A EP 96119475A EP 0802328 A1 EP0802328 A1 EP 0802328A1
Authority
EP
European Patent Office
Prior art keywords
valve
jack
water
pressure
bellows
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96119475A
Other languages
German (de)
English (en)
Other versions
EP0802328B1 (fr
Inventor
Karl Obermoser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SIEBHOLZ, DIETMAR
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AU16354/97A priority Critical patent/AU708806B2/en
Priority to NZ331397A priority patent/NZ331397A/xx
Priority to PCT/EP1997/001908 priority patent/WO1997040277A1/fr
Priority to US09/142,312 priority patent/US6234764B1/en
Priority to PL97329346A priority patent/PL182664B1/pl
Priority to CN97192909A priority patent/CN1081758C/zh
Priority to CA002249263A priority patent/CA2249263C/fr
Priority to AU26380/97A priority patent/AU2638097A/en
Priority to IL12589397A priority patent/IL125893A/en
Priority to KR10-1998-0708318A priority patent/KR100383489B1/ko
Priority to RU98120702A priority patent/RU2159361C2/ru
Priority to JP53770097A priority patent/JP3853847B2/ja
Priority to CZ983322A priority patent/CZ332298A3/cs
Priority to IDP971312A priority patent/ID16633A/id
Publication of EP0802328A1 publication Critical patent/EP0802328A1/fr
Application granted granted Critical
Publication of EP0802328B1 publication Critical patent/EP0802328B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F7/00—Pumps displacing fluids by using inertia thereof, e.g. by generating vibrations therein
    • F04F7/02—Hydraulic rams

Definitions

  • the invention relates to a hydraulic jack for converting small amounts of water under high pressure into large amounts of water under low pressure.
  • Such jacks are also referred to as suction rams.
  • Ram is a ram that can be used to convert large amounts of water under low pressure to small amounts of water under high pressure.
  • the jack of the invention can do both, i.e. it can be used to increase pressure or flow.
  • Suction rams have been known at least since 1905 ("Inertial machines as a possibility of hydraulic-mechanical energy conversion", lecture by Ivan Cyphelly, Fegawerk / Switzerland, held at the IHP of the RWTH Aachen, Prof. Backé, June 21, 1991). They use a ram valve, which, like the hydraulic rams with a water pipe and a natural slope, is closed suddenly due to the hydrodynamic pressure drop caused by the water flow through the valve.
  • suction rams In known suction rams (e.g. German patent N 804 288, 1949, or in the still-built suction ram from Fegawert SA Le Locie / Switzerland), when the ram valve is closed, the kinetic energy of the flowing water in the motive water pipe is destroyed because the motive water is stopped becomes. In order to keep this loss as small as possible, the suction ram of the Fegawerk has a hose with an extremely large cross-section as a motive water line, which also prevents high speeds of the motive water.
  • the ram valve is exposed to a particularly high load due to the sudden stopping of the propellant water column, which is even higher in known suction rams than in conventional hydraulic rams, in which the pressure on the valve is only dammed up by the stopping of the propellant water column to convey in a wind kettle.
  • This high load on the jack valve has an unfavorable effect on the service life of the known suction ram.
  • shock lifter described in the unpublished (EPC Art. 54 (3)) German patent application DE 19520343, according to which the shock lifter valve is not formed as a check valve, as in the aforementioned prior art, which is kept open by spring force and by the motive water flow is closed, but as a valve held closed by spring force and opened by the motive water pressure. It is further provided according to the invention to cyclically actuate the jack valve in cooperation with a pressure storage element, likewise acted upon by the propellant, in the manner of an oscillating circuit. Due to its design, this suction ram can work to increase both pressure and volume flow.
  • the driving water pressure in this jack is absorbed by the pressure-adjustable element of a pressure storage element before the opening of the jack valve, it is ensured that the driving water does not stop abruptly during operation of the jack, but can be supplied continuously to it, which means that the jack valve compared to the prior art is significantly relieved, which benefits the lifespan of the jack as a whole.
  • FIGS. 1 and 2 of the drawing show:
  • Fig. 1 is a schematic representation of a first embodiment
  • Fig. 2 shows a second embodiment of the jack described in the unpublished DE 19520343.
  • the hydraulic ram shown in FIGS. 1 and 2 generally comprises, in a conventional manner, a motive water pipe 1, a delivery water pipe 2, a ram valve 3 and a bottom valve 4 for sucking in delivery water.
  • the ram outlet 9 is located at the end of the conveying water line 2.
  • the ram valve 3 consists of a piston 3a and a return spring 3b which prestresses the piston 3a against a valve seat 6.
  • the jack valve 3 is held closed by a spring.
  • the motive water line 1 is not only connected to the pressure side of the jack valve 3 as in the prior art, but also to a spring accumulator 5.
  • the pressure accumulator element 5 is formed as a spring accumulator in the embodiments of the jack shown in FIGS. 1 and 2.
  • the spring accumulator 5 has its own housing 5c, which communicates with the motive water line 1 upstream of the jack valve 3.
  • a piston 5a which is biased by a spring 5b and forms the pressure-adjustable member of the pressure accumulator element.
  • the piston 3a, the return spring 3b and the valve seat of the jack valve 3 are in the embodiment of the jack shown in Fig. 1 also housed in a separate, separate from the housing 5c housing 3c, so that the jack valve 3 and the spring 5 exclusively via the motive water are in operative connection with each other.
  • the elements of the spring accumulator 5 and the jack valve 3 are housed in a common housing 10 and mechanically coupled to one another: the piston 5a of the spring accumulator 5 is arranged at the upper end of the coupled piston-spring system, and the pressure spring 5b connects the piston 5a with the piston 3a of the jack valve 3 underneath, the restoring spring 3b of which extends in the downward direction and is fixed to a stationary abutment 11 in the housing 10.
  • the lower end of the housing is immersed in the pumped water and is closed by the bottom valve 4.
  • the driving water line opens into the housing 10 at the level of the storage spring 5b, while the feed water line branches off from the housing at the level of the lower end of the closing spring 3b.
  • the closing spring 3b and the pressure spring 5b are tension springs in this embodiment of the suction ram of FIG. 2.
  • shock jack shown in Figures 1 and 2 operates as follows:
  • the motive water flows through the motive water line 1 and tensions the pressure accumulator spring 5b via the motive water pressure acting on the piston 5a (pressure accumulator phase) until the pressure on the surface of the jack valve piston 3a minus the surface of the valve seat 6 overcomes the force of the return or jack valve closing spring 3b .
  • the jack valve 3 opens abruptly, since when the opening begins, the motive water pressure acts on the surface of the entire jack valve piston 3a.
  • the storage spring 5b now relaxes (relaxation phase) by accelerating the water mass in the delivery line 2 via a stroke movement of the piston 5a, as a result of which the pressure in this line drops until the force of the closing spring 3b overcomes the pressure on the entire surface of the jack valve piston 3a and the jack valve closes.
  • the further flowing water in the delivery line 2 sucks water out of the bottom valve 4 until the water flow comes to a standstill due to the counterpressure caused by the delivery head. Thereupon, further relaxation and pressure storage phases take place cyclically.
  • the jack shown in FIG. 2 cycles through pressure accumulation and relaxation phases.
  • the pressure accumulator piston 5a in the shock lifter of FIG. 2 partially assumes its reversing function due to its spring coupling to the shock lifter valve piston 3a. That is, the motive water tensions the pressure accumulator spring 5b via the motive water pressure acting on the piston 5a (pressure accumulator phase) until the pressure on its surface minus the surface of the valve seat 6 overcomes the force of the return or lift valve closing spring 3b.
  • the jack valve 3 opens abruptly, since when the opening begins, the motive water pressure acts on the surface of the entire pressure accumulator piston 5a.
  • the pressure accumulator spring 5b now relaxes (relaxation phase) by accelerating the water mass in the delivery line 2 by means of a stroke movement of the piston 5a, as a result of which the pressure in this line drops until the force of the closing spring 3b releases the pressure on the entire surface of the pressure accumulator piston 3a overcomes and closes the jack valve.
  • the further flowing water in the delivery line 2 sucks water out of the bottom valve 4 until the water flow comes to a standstill due to the counterpressure caused by the delivery head. Thereupon, further relaxation and pressure storage phases take place cyclically.
  • an air-filled hose 8 is additionally arranged in a free space of the housing 10 above the piston 3b, which buffers the pulsating movements of the jack valve piston 3b and the water in the delivery line 2, thereby ensuring a relatively quiet mass flow at the jack outlet 9.
  • other known buffering means can also be used.
  • the object of the present invention is to provide a hydraulic jack, which ensures high efficiency and a long service life with a compact structure, and can be operated to increase both pressure and volume flow.
  • the hydraulic jack according to the invention is constructed in principle as shown in FIGS. 1 and 2 and explained above.
  • a special feature of the jack according to the invention is a mechanical coupling of the valve seat of the jack valve with the valve seat of the bottom valve in such a way that the kinetic energy that occurs when one valve closes is transmitted to the other valve to open its valve member.
  • this achieves an energetically favorable operation.
  • Another advantage is that the harmful distance between the two valves, which is a problem in the prior art, because the kinetic energy of the water cannot be used in this connecting section and can lead to cavitation on the latter when it is closed, is optimally short can be held.
  • this ensures a compact construction of the jack that the jack valve and the bottom valve are arranged in the immediate vicinity and axially.
  • the compact structure benefits from a design of the pressure accumulator in the form of a bellows, which carries the valve member of the jack valve at one end.
  • the arrangement of the return spring for the valve element of the jack valve within the pressure accumulator bellows also has an impact on the compact design.
  • the compact structure benefits from the formation of the return spring for the bottom valve in the form of a bellows, which is arranged in the pump in such a way that it is penetrated by the pumped water.
  • FIG. 3 of the drawing shows a longitudinal sectional view through a preferred embodiment of the jack according to the invention. Parts that are functionally the same as in FIGS. 1 and 2 are designated in FIG. 3 with the same reference numbers.
  • the jack shown in FIG. 3 has a generally tubular housing 20 with a cylindrical jacket 21 which is closed by a bottom 22 at one end, which is lower in FIG. 3, and at its other end, in FIG. 3 upper end, is closed by a cover 23.
  • the interior of the tubular housing 20 is axially divided by a partition 24 into a sub-chamber 24 with a larger volume and a sub-chamber 26 with a smaller volume.
  • the bottom 22 of the housing 20 is formed in two parts in the embodiment shown and comprises a ring 27, the outer circumference of which corresponds to the outer circumference of the jacket 21, and the eccentric inner circumference of which has an internal thread into which a sealing plug 28 with an external thread is screwed.
  • a sealing plug 28 with an external thread is screwed.
  • an annular groove is formed on the outer circumference of the sealing plug 28, in which an O-ring 29 sits, which is supported on the inner circumference of the ring 27.
  • a driving water line is connected to an inlet pipe 30 which passes through a hole in the cover 23 and a corresponding hole in the partition 24. At least with the partition 24, the inlet pipe 30 is tightly connected.
  • a tubular valve seat support 31 is inserted in a sealed manner, which has an annular part 4a projecting into the smaller partial chamber 26 and, with its outside facing the cover 23, forms a valve seat 4b of the bottom valve 4, which also has a return spring 4c, which is formed as a bellows, with one end of the valve member 4b is fixedly connected, and the other end is fixedly connected to a pipe connection 32 which penetrates a hole in the cover 23, firmly connected to it and connected to a delivery line, not shown.
  • a valve seat 6 is formed in the form of a conical surface, which tapers in the direction of the valve seat 4a of the bottom valve 4 and interacts to cooperate with a complementary spherical surface on the valve member 3a of the jack valve 3, which also in the form of a Circular disk is formed, which is fixedly connected to the one end in FIG. 3 of a bellows 5, which, as explained below, forms the pressure accumulator of the jack and with the other end firmly to the inner surface of the sealing plug 28 in the bottom of the housing 20 connected is.
  • a return spring 3b is supported on the inside of the annular ram valve member 3, the other end of which is supported on the upper end of a support tube 33, the other end of which is in a bore in the Sealing plug 28 is inserted and firmly connected to this.
  • the support tube 33 is penetrated radially by bores 34 which on the one hand open into the interior of the tube 33 and on the other hand into the interior enclosed by the bellows 5.
  • the valve body 3a of the jack valve 3 has a central bore, which is penetrated by a cylindrical body 35, which projects with its end facing the bottom valve 4 into the interior enclosed by the valve seat support 31, and which is widened at the other end in a flange-like manner, this flange-like end part serves to attach the valve body 3 to the bellows 5.
  • a mounting body for the return spring 3b is formed, which is encompassed by this spring.
  • This body and the flange end of the cylindrical body 35 and this itself is completely penetrated by a capillary bore, which is extended in a capillary tube 36 which extends into the bottom region of the holding tube 33.
  • the casing of the housing 20 is preferably perforated at several points in the region of the smaller partial chamber 26, and metal sieves 37 and 38 are seated in these openings.
  • the pressure in the sub-chamber 25 acts when the lift valve 3 is open on the interior of the bellows 4c, which forms the return spring for the bottom valve 4, which is still closed at this time, and the conveying water present in this interior, and accelerates this, thereby reducing the pressure continues to drop until it falls below the value at which the return spring 3b presses the valve body 3 again against its valve seat and thereby closes the jack valve, the pressure in the sub-chamber 25 being built up again.
  • the kinetic energy transmitted by the closing of the jack valve 3 to the associated valve seat 6 is transmitted via the valve seat support 31 to the valve seat 4a of the bottom valve 4, and this valve opens this valve.
  • the kinetic energy imparted to the pumped water is consumed by the pumped water sucking in water from the environment through the now open bottom valve 4 - the valve body 4b is lifted off the valve seat 4a - against the gravity of the pumped water.
  • the bottom valve 4 is kept open by a slight negative pressure in the bellows 4c. As soon as the energy contained in the pumped water is used up, the bottom valve 4 is closed again by the spring force inherent in the bellows 4c.
  • the kinetic energy of this closing process is transmitted by an elastic impact via the valve seat carrier 31 to the valve seat 6 of the jack valve 3 and from there to the valve member 3a of the jack valve 3, thereby opening the latter.
  • the delivery water that has just stopped swings back slightly due to the elasticity of the bellows 4c and generates a small setting shock that supports the opening of the jack valve.
  • the closing energy of the respective valve is advantageously used to open the other valve.
  • This advantage cannot be achieved with conventionally constructed jacks because the valve seats of the two valves in question (the bottom valve is a reset valve!) Are designed separately from one another, so that kinetic energy cannot be transmitted from one valve to the other. Rather, the kinetic energy released when closing is destroyed by damping, for example in the sealing rubber of the valve. Such damping is conventionally required to prevent the so-called bouncing of the respective valve member on the valve seat. This bouncing does not occur in the valves designed according to the invention, which are connected to one another via the valve seat or are made of the same material, because the kinetic energy is introduced from the closing valve into the other valve in order to trigger or support its opening.
  • a flow is applied to a valve member, and after the flow, the flow runs radially apart between the valve member and the valve seat.
  • the flow in the valves designed according to the invention with a common valve seat runs radially inwards between the valve members and the associated seats and then axially away from the respective valve. This is the only way to have a common valve seat.
  • Another advantage of the coupling of the valve seats of the two valves according to the invention is that the distance between the two valves can be kept negligibly short.
  • the above-described jack according to the invention can also be operated as a normal ram. For this it is only necessary to provide an additional spring, which causes the bottom valve 4 to be open in the rest position.
  • the operation of this modified jack is as follows:
  • the conveying water is accelerated due to its natural gradient, and it emerges through the open bottom valve 4 via the pipe connection 32 until a hydrodynamic negative pressure between the valve member 4b and the valve seat 4a and a dynamic pressure in the bellows 4c cause the bottom valve 4 to close.
  • the jack valve 3 opens, and the kinetic energy of the pumped water loads the spring accumulator (bellows 5), whereby the jack valve 3 closes again and the process begins again, as explained above.
  • the spring accumulator (bellows 5) is already loaded (i.e.
  • the bottom valve 4 does not close when the pumped water has come to a standstill, but only after the excess energy from the spring accumulator has accelerated the pumped water in the opposite manner or backwards Has. After the shock valve 3 has been closed, the delivery water then sucks in water through the bottom valve 4 until the direction of flow reverses. This means that if no pressurized water is required, the consumption of the pumped water is reduced to a minimum.
  • the purpose of the capillary tube 36 or the capillary opening in the valve member is that the pressure inside the bellows 5 becomes equal to the mean pressure in the bellows 4c or in the delivery line. This ensures that the pressure difference between motive water and pumped water at which the jack valve opens is independent of the head. As a result, the load on the external motive water pump is always the same, regardless of whether the jack is used to pump large amounts of surface water or small amounts of water from a great depth.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Vehicle Body Suspensions (AREA)
  • Pipe Accessories (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Glass Compositions (AREA)
  • Surgical Instruments (AREA)
  • Switches With Compound Operations (AREA)
  • Braking Systems And Boosters (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve Device For Special Equipments (AREA)
EP96119475A 1996-04-19 1996-12-04 Bélier-aspirateur Expired - Lifetime EP0802328B1 (fr)

Priority Applications (14)

Application Number Priority Date Filing Date Title
AU16354/97A AU708806B2 (en) 1996-04-19 1997-03-14 Hydraulic ram pump
RU98120702A RU2159361C2 (ru) 1996-12-04 1997-04-16 Гидравлический плунжерный насос
US09/142,312 US6234764B1 (en) 1996-04-19 1997-04-16 Hydraulic ram pump
PL97329346A PL182664B1 (pl) 1996-04-19 1997-04-16 Pompa nurnikowa hydrauliczna
CN97192909A CN1081758C (zh) 1996-04-19 1997-04-16 液压水锤泵
CA002249263A CA2249263C (fr) 1996-04-19 1997-04-16 Pompe hydraulique de type belier
AU26380/97A AU2638097A (en) 1996-04-19 1997-04-16 Hydraulic ram pump
IL12589397A IL125893A (en) 1996-04-19 1997-04-16 Hydraulic ram pump
NZ331397A NZ331397A (en) 1996-04-19 1997-04-16 Hydraulic ram pump with closing energy of one valve used to open another valve
PCT/EP1997/001908 WO1997040277A1 (fr) 1996-04-19 1997-04-16 Pompe hydraulique de type belier
JP53770097A JP3853847B2 (ja) 1996-04-19 1997-04-16 水圧ラムポンプ
CZ983322A CZ332298A3 (cs) 1996-04-19 1997-04-16 Hydraulické plunžrové čerpadlo
KR10-1998-0708318A KR100383489B1 (ko) 1996-04-19 1997-04-16 수압 램 펌프
IDP971312A ID16633A (id) 1996-04-19 1997-04-21 Pompa pelantak hidrolik

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19615689 1996-04-19
DE19615689A DE19615689A1 (de) 1996-04-19 1996-04-19 Hydraulische Saugwidder-Trägheitspumpe

Publications (2)

Publication Number Publication Date
EP0802328A1 true EP0802328A1 (fr) 1997-10-22
EP0802328B1 EP0802328B1 (fr) 2001-07-18

Family

ID=7791876

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96119475A Expired - Lifetime EP0802328B1 (fr) 1996-04-19 1996-12-04 Bélier-aspirateur

Country Status (7)

Country Link
EP (1) EP0802328B1 (fr)
KR (1) KR100383489B1 (fr)
AT (1) ATE203307T1 (fr)
BR (1) BR9708769A (fr)
DE (2) DE19615689A1 (fr)
ES (1) ES2160758T3 (fr)
GR (1) GR3036876T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022218974A1 (fr) * 2021-04-14 2022-10-20 Thermofluidics Ltd. Ensembles extrémités d'entrée pour pompes à bélier hydraulique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100412134B1 (ko) * 2001-06-27 2003-12-31 주식회사 하이닉스반도체 넓은 범위의 전원전압에서 동작하는 데이터 출력 버퍼 및이를 이용하는 반도체 메모리 장치

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE804288C (de) * 1949-06-28 1951-04-19 Wilhelm Raub Unterbrecherpumpe
FR2589900A1 (fr) * 1985-09-10 1987-05-15 Cyphelly Ivan J Dispositif d'exhaure avec belier-aspirateur.

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE628113C (de) * 1934-10-31 1936-03-30 Harry Sauveur Dipl Ing Fluessigkeitspumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE804288C (de) * 1949-06-28 1951-04-19 Wilhelm Raub Unterbrecherpumpe
FR2589900A1 (fr) * 1985-09-10 1987-05-15 Cyphelly Ivan J Dispositif d'exhaure avec belier-aspirateur.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022218974A1 (fr) * 2021-04-14 2022-10-20 Thermofluidics Ltd. Ensembles extrémités d'entrée pour pompes à bélier hydraulique
GB2620319A (en) * 2021-04-14 2024-01-03 Thermofluidics Ltd Inlet end assemblies for hydraulic ram pumps

Also Published As

Publication number Publication date
KR100383489B1 (ko) 2003-06-18
GR3036876T3 (en) 2002-01-31
DE59607317D1 (de) 2001-08-23
ES2160758T3 (es) 2001-11-16
ATE203307T1 (de) 2001-08-15
DE19615689A1 (de) 1997-10-23
EP0802328B1 (fr) 2001-07-18
BR9708769A (pt) 1999-08-03
KR20000005524A (ko) 2000-01-25

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