WO2018224903A1 - Pompe à moteur hydraulique à piston flottant électromagnétique - Google Patents

Pompe à moteur hydraulique à piston flottant électromagnétique Download PDF

Info

Publication number
WO2018224903A1
WO2018224903A1 PCT/IB2018/053601 IB2018053601W WO2018224903A1 WO 2018224903 A1 WO2018224903 A1 WO 2018224903A1 IB 2018053601 W IB2018053601 W IB 2018053601W WO 2018224903 A1 WO2018224903 A1 WO 2018224903A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
magnetic
motor pump
pump according
magnetic sleeve
Prior art date
Application number
PCT/IB2018/053601
Other languages
English (en)
Inventor
Roberto PALMIERI
Michele BENINI
Original Assignee
Ceme S.P.A.
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 Ceme S.P.A. filed Critical Ceme S.P.A.
Priority to CN201880050874.4A priority Critical patent/CN110998091B/zh
Priority to EP18730124.7A priority patent/EP3635253B1/fr
Publication of WO2018224903A1 publication Critical patent/WO2018224903A1/fr

Links

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
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
    • 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
    • F04B53/001—Noise damping

Definitions

  • the present invention relates to a hydraulic, electromagnetic floating- piston motor pump, and more particularly the present invention relates to a hydraulic, electromagnetic floating-piston motor pump suitable for moving fluids such as water.
  • EP-A-1 205 663 discloses a hydraulic, electromagnetic floating-piston motor pump having the features of the preamble of claim 1 ).
  • this type of motor pump is based on the presence of a coil that cooperates with a pair of magnetic bearings: the coil is electrically powered and causes the axial movement of the floating piston or of the piston with alternating motion.
  • the known motor pumps disclosed hitherto are in any case affected by noise-related drawbacks: in fact, it is possible that in particular working conditions the floating piston, during its stroke, abuts in a more or less controlled manner on the other parts of the motor pump, thus generating acoustic waves that can also be at high frequency (and therefore in a perceived tone that is particularly annoying) or, in any case, having high sound intensity.
  • the object of the present invention is to overcome the above- mentioned drawbacks, and more particularly, the present invention relates to the implementation of a hydraulic, electromagnetic floating-piston motor pump wherein the noise level generated during normal operation (but also during possible working moments in which the stroke of the floating piston is "anomalous") is considerably reduced both in terms of acoustic volume and of sound characteristics (frequency, duration and possible resonance phenomena).
  • a further object of the present invention is that of providing a motor pump of the type which can guarantee a high level of resistance and reliability over time, which is easily manufactured and which can be made starting from minimal modifications (both of the device and of the production line), with respect to other types of motor pumps already available.
  • FIG. 1 is a schematic exploded view of the motor pump of the Applicant already part of the State of the Art and which serves as a basis for the technical improvements introduced in the present invention
  • FIG. 2 is a cross-sectional schematic view of a motor pump according to the present invention in a first operating configuration thereof;
  • Figure 3 is a cross-sectional schematic view of a motor pump according to the present invention in a second operating configuration thereof.
  • the motor pump of the present invention is generally indicated with the reference numeral 10 and basically comprises the following structural components:
  • a body 12 which is partially delimited, in its outer part, by a coil 14; - an inlet duct 44' and an outlet duct 36 opposite to the inlet duct 44' obtained in the body 12;
  • a magnetic sleeve 52 having a first end located inside the body 12 and more precisely in its part facing the inlet duct 44'.
  • the first end of the above-mentioned magnetic sleeve 52 is arranged coaxially with the sliding axis of the piston 16 so as to couple with the body 12 in its intermediate part 42 (i.e. near the terminal part 44 which defines the inlet duct 44'): at the same time, the magnetic sleeve 52 can interact functionally with the body 12 - if necessary - to increase the overall magnetic field and, therefore, in order to increase the magnetic attraction force exerted on the piston 16.
  • the motor pump of the State of the Art represented therein further comprises a pair of magnetic bearings 46, 46': these magnetic bearings are spaced apart from each other and placed between the body 12 and the coil 14 and at the same time this pair of magnetic bearings is arranged coaxially to a sliding axis 16a of the piston 16, interacting functionally with the piston 16 and / or with the magnetic sleeve 52 to increase the magnetic field and, therefore, the force of magnetic attraction exerted on the piston 16.
  • Figures 2 and 3 show a motor pump according to the invention, where the magnetic bearings 46, 46' are not visible: in any case, these two structural components (and in the same way, the coil 14, in turn not shown in Figures 2 and 3 but implicitly present in the structure of the invention, and in any case structurally and functionally able to be positioned / coupled at least with the body 12 and/or with the piston 16 according to well-known methods to a person skilled in the art dealing with designing and realizing oscillating cursor motor pumps) can be considered as optional structural features of the present invention and, if present, they are located with respect to the body 12 and/or to the sliding axis 16a of the piston 16, in the most suitable way in order to increase the magnetic interaction with the piston 16 and therefore to increase the flow and/or pressure performances of the motor pump 1 .
  • coil 14 and the pair of magnetic bearings 46, 46' can be implemented in a similar way to that shown in Figure 1 also in motor pumps having the geometric / structural arrangement of the remaining components according to the invention and more precisely according to Figures 2 and / or 3 (or they can however be implemented according to a structural and functional coupling method which is well known to a person skilled in the art dealing with designing and realizing oscillating-cursor motor pumps).
  • the noise-decreasing means will be operationally active also between the magnetic bearings 46, 46', between the magnetic sleeve 52 and between the piston 16 (and of course between the coil 14).
  • the motor pump 10 further comprises noise-decreasing means operatively active and located between the magnetic sleeve 52, the piston 16 and the body 12 (and optionally, if present, also active between the structural elements mentioned above and the magnetic bearings 46, 46'): such noise- decreasing means are suitable to prevent impacts or shocks of the piston 16 on the other parts of the motor pump 10 or, in the event that these shocks or impacts occur despite the "preventive" technical measures, they are suitable to absorb and contain - at least partly - the acoustic energy generated as a result of such shocks or impacts.
  • the noise-decreasing means mentioned above comprise at least one passive kinetic and/or acoustic absorption element 100, which is positioned at end strokes of the piston 16 and suitable to suffer an impact by the piston 16 itself: this passive kinetic and/or acoustic absorption element 100 comprises a body, preferably an annular body, made of polymeric material and still more preferably made of a material having hyperelastic behavior (therefore it can conveniently be made of natural or synthetic rubber based materials, or in any case made of materials able to absorb or dissipate the energy of the shocks/impacts of the piston 16, partially or wholly dampening the acoustic waves deriving from these phenomena).
  • this passive kinetic and/or acoustic absorption element 100 comprises a body, preferably an annular body, made of polymeric material and still more preferably made of a material having hyperelastic behavior (therefore it can conveniently be made of natural or synthetic rubber based materials, or in any case made of materials able to absorb or
  • the passive kinetic and/or acoustic absorption element 100 interposes between the piston 16 and one or more of the other structural components of the motor pump 10 at least in correspondence to an "end of stroke" reaching time of the movement of the piston 16 itself.
  • suitable "active/preventive" noise-decreasing means can also be present in the invention: these means comprise at least one active prevention assembly 200 for shocks and/or impacts which results to be active near at least one end of the piston 16 to prevent impacts or material contacts of the same with one or more of these components:
  • the active prevention assembly 200 mentioned above is suitable to exploit particular changes (or variations) of direction (and, if necessary, also of module) of the vectors resulting from the magnetic interactions between the piston 16 and the body 12 and/or between the piston 16 and the magnetic sleeve 52 and/or between the piston 16 and the optional magnetic bearings 46, 46': such magnetic interactions, which, as mention above, vary in the vector direction, occur in particular when the piston 16 crosses a certain threshold point of its stroke, defining a new balance of forces in which the attractive magnetic component along the sliding axis 16a decreases and in which, therefore, the stroke of the piston 16 is braked.
  • the suitable positioning and sizing of the active prevention assembly 200 it is therefore possible to control the end parts of the piston 16 strokes, at least near the maximum geometrical ends of strokes established by the dimensions of the body 12, so as to stop and invert the motion of the piston 16 itself before it impacts the structural components on which it has impacted - therefore "producing a sound" -.
  • the active prevention assembly 200 comprises a first interaction portion 200a formed on the piston 16, typically at one of its ends, as well as a second interaction portion 200b located near the first interaction portion 200a and always at an end of stroke of the piston 16 but which, in turn, is formed in the magnetic sleeve 52 and/or (if present) in the magnetic bearings 46, 46' and/or in the body 12.
  • the first and second interaction portions 200a, 200b mutually interact to define a vector variation of the magnetic interaction forces suitable to brake and/or slow down the piston 16.
  • the first and second interaction portions 200a, 200b can conveniently be complementary shaped, and e.g. They are geometrically interpenetrating into each other along the sliding axis 16a: this mutual complementary geometric configuration allows an interpenetration degree without contact when the piston 16 is moving, so as to be able to expose the piston 16 itself to the suitable magnetic field lines "varied in the slowing down/braking direction" but without generating mechanical contacts which, in turn, generate noise.
  • the first interaction portion 200a comprises - for instance - a cylindrical or annular protrusion (or, on the contrary, a cavity, not shown) placed on one end of the piston
  • the motor pump 10 comprises, in its basic structure, an inlet duct 44', an opposite outlet duct 36; a body 12 (partially delimited, in its outer part, by a coil 14), optionally a pair of opposite magnetic bearings 46, 46' which are spaced from each other and placed between the body 12 and the coil 14, a piston 16 which is placed inside the body 12 and flowing therein (resiliently supported by a front coil spring 20 and a rear spring 20').
  • a sealing valve and an elastic band of the piston 16 are commonly placed: the elastic band and the sealing valve cooperate with a support bearing and a rubber sealing gasket which is elastically stretched by an additional coil spring.
  • the coil spring mentioned above and, at least partially, the rubber gasket are housed inside a seat of the delivery duct whose diameter is suitable to house the assembly formed by the rubber gasket and the coil spring (generally this diameter is greater than that of the outlet duct or hole of the delivery duct).
  • a locking ring 38 with an internal thread that engages with a suitably counter-shaped part (the latter can also be threaded, depending on the needs of the more or less "reversible" connection torque) in the outer part of the container body 12 is placed on the duct 22 according to the currently known technical methods.
  • the tubular body 12 comprises a front part 40 with a larger diameter which faces the outlet duct 36, an adjacent intermediate part 42 (with a diameter smaller than that of the front part 40) which delimits the sliding axial chamber of the piston 16 and a terminal part 44 whose diameter is extremely smaller than that of the intermediate part 42 which defines the inlet duct 44'.
  • the opposite magnetic bearings 46 and 46' can be conveniently spaced from each other by the use of a spacer element and, if necessary, are adapted on the outer side surface of the intermediate part 42 of the body 12: at the same time, the coil 14 is, in turn, adapted on the body 12 so that it can include any magnetic bearings 46, 46'.
  • the coil 14 is stabilized with known technical means, which are made, e.g., of a shaped elastic ring which is coupled with a face of the coil and a shoulder (which can be seen in Figure 1 with the reference number 50) placed on the body 12 (such coupling is, e.g., located between the front part 40 and the intermediate part 42, with a smaller diameter which is coupled with the opposite face).
  • known technical means which are made, e.g., of a shaped elastic ring which is coupled with a face of the coil and a shoulder (which can be seen in Figure 1 with the reference number 50) placed on the body 12 (such coupling is, e.g., located between the front part 40 and the intermediate part 42, with a smaller diameter which is coupled with the opposite face).
  • the magnetic sleeve 52 is housed, which can typically be made of a steel having a low residual magnetic content.
  • the outer side surface of the magnetic sleeve 52 has different diameters and defines a rear area 54 which faces the duct 44' with a diameter which is equal to or slightly smaller than the inner diameter of the intermediate part 42 of the body 12 and defines a front adjacent area 56 facing the hole or outlet duct 36with a smaller diameter.
  • the areas 54 and 56 mentioned above having different diameters form a coupling shoulder 58 for the rear spring 20' and globally the first end of the magnetic sleeve 52 couples with the body 12 in the intermediate part 42 near the narrowing of the terminal part 44 which defines the inlet duct 44'.
  • the axial sliding return of the piston 16 is obtained by means of known technical means, such as, e.g., the pair of coil springs 20 and 20' previously described (these springs, therefore, cooperate with the piston 16 itself).
  • the supply of the coil 14 is obtained, e.g., by means of a conventional pair of electrical connections, e.g. of the quick-coupling type as illustrated in Figure 1 with the reference number 62.
  • the applicant has discovered, experimentally, that the motor pump of the present invention is highly efficient thanks to the presence of the magnetic sleeve 52 which, being aligned with the sliding axis of the piston 16 with one of its ends, is close to the piston and, therefore, at a shorter distance between the latter and one of the two possible magnetic sleeves 46, 46' when placed in the position reached by the piston 16 during the loading of the rear spring 20', generally near the terminal part 44 of the body 12.
  • the invention achieves different advantages.
  • noise-decreasing means both in separate terms of the "passive” or “active/preventive” elements (and, obviously, in joined and simultaneous terms) allows to maintain rather heavy-duty working conditions of the motor pump, without, however, being negatively affected by wobbling in the piston stroke and, therefore, without generating noise, shocks or "mechanical impulse” phenomena that can also damage the internal components of the motor pump itself.
  • the presence of the noise-decreasing means does not compromise the performance increase due to the interaction between the magnetic sleeve 52 and the remaining magnetically active/sensitive components of the motor pump: this means that this improved motor pump is subjected only to an increase in the magnetic attraction force exerted on the piston 16 and to that exerted on the fluid which comes out from the delivery duct 22, but it is not affected (except in predetermined "undesired" moments, i.e. in those operating moments when the piston 16 has exceeded its maximum permissible stroke point and is therefore very close to a noisy impact with other components of the motor pump itself) by the slowing down/braking magnetic effects already mentioned in other parts of the present description.
  • the magnetic sleeve 52 Thanks to the presence of the magnetic sleeve 52 it is conveniently possible to reduce the number of wires of the coil 14, with considerable production savings.
  • the motor pump manufactured according to the previous description does not imply any impediments or additional costs caused by the increased size of the coil and the related turns of wires, while the magnetic sleeve 52 can be easily obtained and installed at low cost (like the noise reduction/absorption/prevention means described so far and/or claimed below).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Abstract

L'invention concerne une pompe à moteur à piston flottant comprenant un corps délimité par une bobine, un conduit d'entrée et un conduit de sortie, un piston coulissant et un manchon magnétique coaxial à l'axe de coulissement du piston ; le manchon magnétique interagit avec la paire de paliers magnétiques pour augmenter la force d'attraction magnétique exercée sur le piston et il y a également des moyens de réduction de bruit fonctionnellement actifs et situés entre le manchon magnétique, le piston et le corps.
PCT/IB2018/053601 2017-06-05 2018-05-22 Pompe à moteur hydraulique à piston flottant électromagnétique WO2018224903A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201880050874.4A CN110998091B (zh) 2017-06-05 2018-05-22 液压、电磁式浮动活塞电动泵
EP18730124.7A EP3635253B1 (fr) 2017-06-05 2018-05-22 Pompe à moteur hydraulique à piston flottant électromagnétique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT102017000060837A IT201700060837A1 (it) 2017-06-05 2017-06-05 Motopompa idraulica elettromagnetica con pistone flottante
IT102017000060837 2017-06-05

Publications (1)

Publication Number Publication Date
WO2018224903A1 true WO2018224903A1 (fr) 2018-12-13

Family

ID=60020523

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2018/053601 WO2018224903A1 (fr) 2017-06-05 2018-05-22 Pompe à moteur hydraulique à piston flottant électromagnétique

Country Status (4)

Country Link
EP (1) EP3635253B1 (fr)
CN (1) CN110998091B (fr)
IT (1) IT201700060837A1 (fr)
WO (1) WO2018224903A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0288216A1 (fr) * 1987-04-15 1988-10-26 Eaton S.A.M. Pompe électrique à liquides
EP1365149A2 (fr) * 2002-05-23 2003-11-26 C.E.M.E. Engineering S.p.A. Moto-pumpe hydraulique électromagnétique avec piston flottant
US20080314238A1 (en) * 2007-06-19 2008-12-25 Neuner Heiko Reciprocating-piston pump for feeding a liquid
DE102008008904A1 (de) * 2008-02-13 2009-08-20 BSH Bosch und Siemens Hausgeräte GmbH Fördereinrichtung
EP2122167B1 (fr) * 2007-03-15 2011-02-23 Ceme S.p.A. Motopompe hydraulique-électromagnétique à piston flottant
US20130034459A1 (en) * 2010-03-26 2013-02-07 Thomas Magnete Gmbh Pump

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004002454B4 (de) * 2004-01-16 2006-06-29 J. Eberspächer GmbH & Co. KG Dosierpumpsystem und Verfahren zum Betreiben einer Dosierpumpe
CN202612023U (zh) * 2012-05-18 2012-12-19 宁波捷尔天电气有限公司 电磁泵
CN105756881B (zh) * 2014-12-16 2018-11-06 天纳克（苏州）排放系统有限公司 带有限位结构的柱塞泵及其应用

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0288216A1 (fr) * 1987-04-15 1988-10-26 Eaton S.A.M. Pompe électrique à liquides
EP1365149A2 (fr) * 2002-05-23 2003-11-26 C.E.M.E. Engineering S.p.A. Moto-pumpe hydraulique électromagnétique avec piston flottant
EP2122167B1 (fr) * 2007-03-15 2011-02-23 Ceme S.p.A. Motopompe hydraulique-électromagnétique à piston flottant
US20080314238A1 (en) * 2007-06-19 2008-12-25 Neuner Heiko Reciprocating-piston pump for feeding a liquid
DE102008008904A1 (de) * 2008-02-13 2009-08-20 BSH Bosch und Siemens Hausgeräte GmbH Fördereinrichtung
US20130034459A1 (en) * 2010-03-26 2013-02-07 Thomas Magnete Gmbh Pump

Also Published As

Publication number Publication date
IT201700060837A1 (it) 2018-12-05
EP3635253A1 (fr) 2020-04-15
CN110998091B (zh) 2022-04-26
EP3635253B1 (fr) 2021-07-07
CN110998091A (zh) 2020-04-10

Similar Documents

Publication Publication Date Title
JP5120419B2 (ja) 常閉型電磁弁
EP2007959B1 (fr) Dispositif de freinage et d'arret pour element mobile, en particulier une porte ou un tiroir de meuble, adaptable a une surface d'arret de l'element mobile
JP5677459B2 (ja) 液圧式車両ブレーキ装置のためのピストンポンプ
US7980368B2 (en) Damping force variable shock absorber
WO2007028076A2 (fr) Électrovanne
CN106662268B (zh) 用于电磁阀的阀衔铁和用于电磁阀的阀筒
JPH06193764A (ja) 流量制御弁
KR102096127B1 (ko) 전자기 액추에이터, 밸브 및 분사 펌프
JP2013524130A (ja) 電磁弁
EP3635253B1 (fr) Pompe à moteur hydraulique à piston flottant électromagnétique
JP6605641B2 (ja) エアサスペンションシステムの空気バルブ
JP5673189B2 (ja) 弁装置
JP2015536411A (ja) 弁装置
KR101180991B1 (ko) 유량차단 밸브
CA1193139A (fr) Pompe hydraulique bi-etagee a piston
KR102057140B1 (ko) 연료 시스템 밸브 어셈블리
JP5600844B2 (ja) 電磁弁
JP2017516957A5 (fr)
CN100467855C (zh) 燃油喷射阀
JPH11294619A (ja) 常開形パイロット式電磁弁
KR20140147176A (ko) 솔레노이드 밸브
KR20140137040A (ko) 솔레노이드 밸브
CN111207218A (zh) 一种直通常开式电磁阀
CN217976486U (zh) 电磁泵
JP2001304441A (ja) バルブ構造

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18730124

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2018730124

Country of ref document: EP

Effective date: 20200107