EP2678562B1 - Druckregelnde hubkolbenpumpe mit magnetischem antrieb - Google Patents

Druckregelnde hubkolbenpumpe mit magnetischem antrieb Download PDF

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Publication number
EP2678562B1
EP2678562B1 EP12707233.8A EP12707233A EP2678562B1 EP 2678562 B1 EP2678562 B1 EP 2678562B1 EP 12707233 A EP12707233 A EP 12707233A EP 2678562 B1 EP2678562 B1 EP 2678562B1
Authority
EP
European Patent Office
Prior art keywords
piston
spring
outlet
reciprocating
pump
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.)
Not-in-force
Application number
EP12707233.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2678562A1 (de
Inventor
Olaf OHLIGSCHLÄGER
Axel MÜLLER
Thomas Rolland
Stefan Quast
René Schulz
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.)
Thomas Magnete GmbH
Original Assignee
Thomas Magnete GmbH
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 Thomas Magnete GmbH filed Critical Thomas Magnete GmbH
Publication of EP2678562A1 publication Critical patent/EP2678562A1/de
Application granted granted Critical
Publication of EP2678562B1 publication Critical patent/EP2678562B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B51/00—Testing machines, pumps, or pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons

Definitions

  • the invention relates to a driven by magnets reciprocating pump and a method for adjusting a reciprocating pump.
  • devices known as metering pumps or linearly driven pumps are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective rights, DE 40 35 835 A1 .
  • DE 10 2008 013 441 B4 or DE 298 21 022 U1 are known, for example by the protective
  • DE 35 04 789 A1 describes a reciprocating pump with an electromagnetic drive, in which an anchor is connected to a connected thereto, designed as a Kobenstange piston due to the excitation of a coil from an outlet away, wherein when moving from the outlet fort a return spring against the armature and a Spring abutment is supported, is tensioned.
  • the return spring displaces the actuator formed from the armature and the piston rod against an outlet nozzle which forms an adjustable end stop for the actuator within the housing of the pump.
  • the pump has a suction-side first, referred to as suction chamber and a second displacement chamber, referred to as anchor space displacement, which are connected by a fluid-conducting channel and provided therein check valve and radial bores such that a preferred flow from the first to the second displacer allows is.
  • a check valve in a transition region between an inlet and the first Displacer arranged.
  • the return spring in this case has a bias sufficient to displace the actuator when de-energized against the outlet and eject the entire volume of the second displacement chamber.
  • the effective force of the return spring is further enhanced by the fact that the inlet side end face of the piston facing the first displacement chamber is subjected to fluid there and thus pressed in the direction of the outlet.
  • the task for this invention is not to generate a predetermined flow, but a predetermined pressure at the outlet of the pump and to adjust the flow independently depending on the needs of the connected consumer. Since the inlet pressure is known and approximately constant, the generation of a predetermined pressure difference between outlet and inlet is expedient.
  • Automatic pressure-regulating pumps are known as rotary pumps in the field of oil hydraulics, either as valve-controlled variable displacement pumps, for example “Bosch Rexroth A10VOxDR / 5" or as variable displacement pumps whose effective displacement is changed directly from the pressure to be regulated, for example " Bosch Rexroth PV7-2X / ... ".
  • the rotary pumps are widely used, but in the present application considerably too large and too expensive.
  • a pressure control can also be achieved by combining a known metering pump with a pressure relief valve, which is connected to the line between the pump and the consumer, but this leads to a higher construction cost, the risk of vibration and possibly a significant temperature influence on the pressure control.
  • a driven by a magnet reciprocating pump with the indicated means is designed so that it promotes only necessary for maintaining the required pressure fluid flow. It is used to the fact that the pressure generated counteracts the movement of the delivery piston and brings the movement of the piston to a stop when exceeding the limit set by the force balance on the piston. As a result, the piston covers only a partial stroke, the size of the partial stroke depends directly on the pressure built up and indirectly on the fluid requirement of the consumer.
  • the force of the return spring is used for promotion and force balance.
  • the piston stroke after switching on the magnet is only used to pump fluid from the first displacement chamber in the second displacement chamber and to tension the return spring.
  • the force of the return spring is not affected by the aforementioned disturbances supply voltage and temperature, but is essentially dependent on the spring bias of the return spring and the piston stroke.
  • the bias of the return spring can only be adjusted with unreasonable effort or risks to the function, it is advisable to let act another spring on the piston, the bias can be set much easier. It is irrelevant for this invention, whether this additional spring, the so-called correction spring acts in the same direction on the piston as the return spring, or the return spring counteracts, as long as only the effects of both springs from the stroke of the piston are dependent, and Case of the opposite effect, the force of the return spring is greater than the force of the correction spring.
  • the return spring or the spring group consisting of restoring spring and correction spring produce by their spring rigidity a small, but measurable and possibly usable influence of the stroke on the pressure at the outlet.
  • the partial lift at the end of the funding phase mainly affects the pressure.
  • the described pressure control can be realized with different known designs of reciprocating pumps, as long as only the promotion of the fluid in the return phase of the working cycle, ie when the magnet is switched off.
  • the reciprocating pump will typically include two valves, which may be an inlet valve and an overflow valve between the displacers, or an overflow valve and an exhaust valve.
  • the reciprocating pump includes an inlet valve and an overflow valve, and the piston is slidably and dynamically sealingly supported in the cone. Since the return spring is supported in the cone, it is advantageous not to adjust the bias of the return spring, but to adjust the bias of an additional correction spring by means of a sliding sleeve. After moving the bushing must be secured, this can be achieved by a sufficient interference fit or by welding, soldering, gluing or caulking.
  • the reciprocating pump includes an overflow valve and an exhaust valve, and the piston is slidably and sealingly mounted in the yoke. Since the cone does not contain a sliding bearing for the piston in this case, it is possible without risk to adjust the bias of the return spring by means of a displaceable spring bearing. In this case, then the stop bushing inside the spring bearing, which represents the inlet-side stop for the piston, must be adjusted to their correct size, without further moving the spring bearing. Both the spring bearing and the stop bushing must be secured after adjustment so that they do not move further during operation of the pump. This can serve a sufficient interference fit, welding, soldering, gluing or caulking.
  • the spring bearing seal s the pump to the outside, therefore, a completely impermeable seal to the cone is required, to the welding, soldering and gluing methods can be used, or it can be used an elastomeric seal.
  • the setting of the return spring can also be realized by storing the return spring on one side or both sides on shims, which are selected according to the needs of a suitable test operation of the pump or a subassembly and then used.
  • shims which are selected according to the needs of a suitable test operation of the pump or a subassembly and then used.
  • this solution is considered less advantageous because the test described can not be summarized with the final test of the pump after its preparation.
  • this pump In some applications of this pump is required that after stopping the pump, the fluid slowly back into the reservoir, which is connected to the inlet side, flows back.
  • a targeted leakage is provided in the two valves, which is so large that a sufficient drain after stopping the pump, but is so small that the delivery function is not affected in normal operation.
  • the sealing gap of the dynamic seal between the piston and the piston bearing is designed.
  • the piston of the pump is provided with an outlet side sealing stop disc, the effective sealing surface results in the required residual pressure in cooperation with the force of the return spring.
  • a uniform discharge pressure of the pump is required, which is not or only slightly exceeded when freezing the fluid after stopping the pump.
  • a pressure variable compensating volume is divided from the second displacement chamber, which is integrated in an advantageous embodiment in the pump housing and therefore requires little additional space.
  • the variable compensating volume is limited by a tubular elastic membrane, on the side facing away from the working fluid side of the membrane is a closed gas volume. Fluid dampers as such are known, but not in the interaction described herein with pressure-regulating reciprocating pumps.
  • the reciprocating pump according to this invention is characterized by a very small size and low manufacturing costs compared to known pumps similar function. Because of its robustness, it can also be used under adverse environmental conditions in a wide temperature range. It is particularly suitable for large series applications in vehicle construction, for example for the supply of systems for injection of additive or fuel in the exhaust system of internal combustion engines. Also, liquids that freeze within the specified environmental conditions for the application can be pumped with this pump when thawed.
  • Fig. 1 shows a first example of a reciprocating pump 1, which is driven by a magnet consisting of a magnet housing 2, a coil 3, a yoke 4, a cone 5 and an armature 6. Between the armature 6 and the cone 5 is the primary air gap at which the axial magnetic force is built up. The secondary air gap between the yoke 4 and the armature 6 builds up only a negligible axial magnetic force, it serves only to conduct the magnetic flux.
  • the armature 6 is connected to the piston 7 of the pump 1, and both are pressed by a return spring 8 in an initial position.
  • the piston 7 and the armature 6 are additionally acted upon by a correction spring 22 designed as a correction means with a stroke-dependent force.
  • the magnet is cyclically supplied by a non-illustrated electrical control with the working voltage, by the switching on and off of this working voltage, the duty cycle of the pump first
  • the piston 7 is mounted in a bore of the cone 5, piston 7 and cone 5 form with their sliding cylindrical surfaces a sliding bearing 20 which is designed so narrow that it simultaneously fulfills the function of a dynamic seal with a sealing gap 21.
  • the interior of the pump 1 is divided into two displacement chambers: the first displacement chamber 25 is connected via an inlet valve 14 with an inlet 13 of the pump 1; the second displacement chamber 26 is connected to an outlet 19 of the pump 1 when the piston 7 is not in the non-magnetic and pressureless rest position.
  • the two displacement chambers 25, 26 are interconnected by the channel 28, which may for example run in the interior of the piston 7, and which contains an overflow valve 9, which preferably only a fluid flow from the first displacement chamber 25 to the second displacement chamber 26 permits.
  • the overflow valve 9 is advantageously designed as a ball check valve, consisting of a ball 10, a valve spring 12 and a sealing seat 11, the Part of the piston 7 is.
  • the sealing seat 11 is in this case provided with a groove or a survey which is dimensioned so that a defined leakage current can flow.
  • the inlet valve 14 is designed as a cone check valve, it consists of a valve cone 15, a valve spring 16 and a sealing seat 17, which is part of the cone 5.
  • the outlet 19 is formed on the yoke 4 and contains the correction spring 22, which is vespannt between a setting sleeve 23 and the stop plate 24.
  • valve cone 15 of the inlet valve contains in Fig. 1 not shown in detail, the valve cone 15 passing through hole with a small diameter, as in Fig. 3 is shown as a bore 18, so that a defined leakage, which causes a limited outflow of the fluid to the inlet 13, is achieved.
  • the dynamic seal 20 between the piston 7 and the bearing in the cone 5 has a leakage, which depends on the gap height in the camp. This gap height is adjusted to the leakage requirement in the application.
  • Fig. 1 also describes the integration of a fluid damper in the reciprocating pump 1.
  • a membrane 27 divides the second displacement chamber 26, the side facing away from the fluid side of the membrane 27 is acted upon by a gas which is located in a closed space.
  • the function of the pump 1 according to Fig. 1 can best be described in chronological order: in the resting state, which is due to very low pressure on the patient Outlet 19 of the pump 1 and characterized by a de-energized state of the solenoid 3, the return spring 8 presses the piston 7 to the exhaust side stop in the yoke 4.
  • the solenoid coil 3 is energized, builds up at the primary air gap between the armature 6 and the cone 5, a magnetic force which is greater than the sum of the spring forces of the return spring 8 and the correction spring 22.
  • the first displacement chamber 25 decreases, the pressure therein rises above the pressure of the inlet 13.
  • the pressure in the outlet 19 increases until the pressure limit value predetermined by the forces of the springs 8 and 22 and the effective area of the piston 7 is reached. If this pressure limit is reached, the movement of the piston 7 comes to a standstill, because there is none Power surplus more in the direction of movement. If further fluid is removed by the consumer in this situation, then the springs 8 and 22 press the piston 7 accordingly, the pressure changes only slightly. The pump 1 remains in this situation until a new electrical drive signal is sent to the magnet.
  • FIG Fig. 2 An alternative exemplary embodiment of a reciprocating pump 101 is shown in FIG Fig. 2 shown.
  • the same or incremented by 100 reference numerals as in Fig. 1 denote the same or structurally comparable parts that are no longer introduced separately.
  • an outlet valve 130 is provided in the outlet 19 which, in cooperation with the piston 7 and an overflow valve 109, ensures the pump function.
  • the outlet valve 130 consists of a ball 131, a sealing seat 132 and a spring 135.
  • the outlet valve 130 according to FIG Fig. 2 has a sealing seat 132, which is provided with a suitable groove or a suitable elevation, to allow a leakage current.
  • a correction spring 22 is in the embodiment according to Fig. 2 not provided, but an adjustable spring bearing 129 is provided which allows adjustment of the biasing force of the return spring 8.
  • the adjustable spring bearing 129 and the inlet 13 are formed as a member that can be fixed in the cone 5.
  • Within the inlet 13 is a stop bushing 136 which limits the stroke of the armature 6.
  • the piston 7 is different from Fig. 1 in the execution according to Fig. 2 mounted in a corresponding hole in the yoke 4, so that the outer periphery of the piston 7 and the bore in the yoke 4 together form a sliding bearing 120 with a sliding seal 121.
  • the dynamic seal 120 between the piston 7 and the bearing in the yoke 4 has a leakage, which depends on the gap height in the bearing 120. This gap height is adjusted to the leakage requirement in the application.
  • the pressure in the outlet 19 increases until the pressure limit predetermined by the force of the return spring 8 and the effective area of the piston 7 is reached. If this pressure limit is reached, the movement of the piston 7 comes to a standstill, because there is no excess of force in the direction of movement. If further fluid is removed by the consumer in this situation, then the spring 8 presses the piston 7 accordingly, the pressure changes only slightly. The pump remains in this situation until a new electrical drive signal is issued to the magnet.
  • Fig. 3 describes an embodiment of a reciprocating pump 201, with respect to the reciprocating pump 1 off Fig. 1 and whose function is only slightly modified, so that the same or the incremented by 200 Reference numerals as in Fig. 1 mean the same or structurally comparable parts that are no longer introduced separately.
  • the reciprocating pump 201 has a stop disc 224, which prevents the fluid 19 from flowing to the outlet 19 by sealing the displacement chamber 26 against the outlet 19 after stopping the pump 201, and maintains a low minimum pressure in the line connected to the outlet 19 the force of the return spring 8 and the effective sealing surface of the stop plate 224 results.
  • the channel 28 is connected through a bore 233 with the second displacement chamber 26.
  • valve plug 15 having valve member 215 is a dashed line
  • valve member 215 axially passing through the leakage hole 18 is shown.
  • the pump 101 is now energized cyclically and pressure builds up in the pressure vessel. This pressure is compared with a target value, and from the deviation of the pressure from the target value, a correction value for the adjustment of the spring bias of the return spring 8 is calculated. According to this correction value, the spring bearing 129 of the return spring 8 is moved.
  • the spring bearing 129 is taken with a press fit in the cone 5 of the magnet, so it can be moved with high force, but then remains in operation of the pump 101 in its position. If the design of the interference fit requires it, the spring bearing 129 is secured after adjustment. After adjustment and securing of the spring bearing 129, the stop bushing 136 is set to its correct degree, without moving the spring bearing 129 further. Also, the socket 136 is secured if necessary.
  • the pump 1, 201 an additional correction spring 22, so that the spring preload of the return spring 8 need not be adjusted.
  • the adjusting sleeve 23 is displaced instead of a spring bearing of the return spring 8, which forms the spring bearing of the correction spring 22.
  • this adjusting bushing 23 is gripped in an interference fit, in this case in the component outlet 19. If required according to the design, the adjusting bush 23 is secured after the adjustment.
EP12707233.8A 2011-02-25 2012-02-27 Druckregelnde hubkolbenpumpe mit magnetischem antrieb Not-in-force EP2678562B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011012322A DE102011012322A1 (de) 2011-02-25 2011-02-25 Druckregelnde Hubkolbenpumpe
PCT/EP2012/000837 WO2012113579A1 (de) 2011-02-25 2012-02-27 Druckregelnde hubkolbenpumpe mit magnetischem antrieb

Publications (2)

Publication Number Publication Date
EP2678562A1 EP2678562A1 (de) 2014-01-01
EP2678562B1 true EP2678562B1 (de) 2016-11-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12707233.8A Not-in-force EP2678562B1 (de) 2011-02-25 2012-02-27 Druckregelnde hubkolbenpumpe mit magnetischem antrieb

Country Status (6)

Country Link
US (1) US9359999B2 (ru)
EP (1) EP2678562B1 (ru)
CN (1) CN103392071A (ru)
DE (1) DE102011012322A1 (ru)
RU (1) RU2553887C2 (ru)
WO (1) WO2012113579A1 (ru)

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DE102012020274B4 (de) * 2012-10-17 2018-10-31 Thomas Magnete Gmbh Elektromagnetisch angetriebene Hubkolbenpumpe mit Dämpfungselement
DE102013006234B4 (de) 2013-04-11 2018-10-25 Thomas Magnete Gmbh Pumpenaggregat mit zwei Hubkolbenpumpen und einer elektrischen Ansteuerung
CN105464917B (zh) * 2014-09-12 2018-03-13 浙江福爱电子有限公司 一种电磁泵
DE102015004868A1 (de) * 2015-04-13 2016-10-13 Bernd Niethammer Pumpe für ein SCR-System in Fahrzeugen
DE102015010505A1 (de) * 2015-08-12 2017-02-16 Thomas Magnete Gmbh Vorrichtung zur Mischung und Förderung von Fluiden
CN105546311A (zh) * 2016-01-15 2016-05-04 徐华萍 漂浮机油直压泵
TR201813341T1 (tr) * 2016-03-18 2018-11-21 Forbes Marshall Private Ltd Bir kontrol valfi tertibatı.
RU2660744C1 (ru) * 2016-07-08 2018-07-09 Федеральное государственное бюджетное образовательное учреждение высшего образования "Казанский государственный аграрный университет" (ФГБОУ ВО Казанский ГАУ) Поршневой насос
RU169289U1 (ru) * 2016-07-15 2017-03-14 Закрытое акционерное общество "Инженерно-Технический Центр" Поршневой насос с электромагнитным приводом
GB2554401B (en) * 2016-09-26 2019-01-23 Dyson Technology Ltd Cleaning appliance
CN107387476B (zh) * 2017-09-08 2019-09-06 上海航天控制技术研究所 一种抗振型直动式球形溢流阀
FR3078114B1 (fr) * 2018-02-16 2020-02-21 Sauermann Industrie Pompe a piston oscillant comprenant un element de structure monobloc presentant un premier et un second corps tubulaires creux

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Also Published As

Publication number Publication date
CN103392071A (zh) 2013-11-13
RU2013143045A (ru) 2015-03-27
WO2012113579A1 (de) 2012-08-30
RU2553887C2 (ru) 2015-06-20
DE102011012322A1 (de) 2012-08-30
EP2678562A1 (de) 2014-01-01
US20130343921A1 (en) 2013-12-26
US9359999B2 (en) 2016-06-07

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