EP3034889A1 - Multiplicateur de pression doté de douille de serrage - Google Patents

Multiplicateur de pression doté de douille de serrage Download PDF

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Publication number
EP3034889A1
EP3034889A1 EP14198888.1A EP14198888A EP3034889A1 EP 3034889 A1 EP3034889 A1 EP 3034889A1 EP 14198888 A EP14198888 A EP 14198888A EP 3034889 A1 EP3034889 A1 EP 3034889A1
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EP
European Patent Office
Prior art keywords
cylinder block
pressure
clamping sleeve
piston
block elements
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
EP14198888.1A
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German (de)
English (en)
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EP3034889B1 (fr
Inventor
Jesper Will Iversen
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Scanwill Fluid Power ApS
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Scanwill ApS
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Priority to EP14198888.1A priority Critical patent/EP3034889B1/fr
Publication of EP3034889A1 publication Critical patent/EP3034889A1/fr
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Publication of EP3034889B1 publication Critical patent/EP3034889B1/fr
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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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Definitions

  • the invention relates to a preferably hydraulic pressure booster according to the preamble of claim 1.
  • Such pressure intensifiers typically consist of two or more solid cylinder block elements that are joined together to form a cylinder block. Due to the often several hundred or z. T. more than a thousand bar internal pressures, the cylinder block elements must be braced against each other by means of several screws, which penetrate through the cylinder block elements in the direction parallel to the longitudinal axis. These screws, which are usually designed as expansion bolts, take up valuable space in the interior of the cylinder block elements, which is no longer available for the execution of work spaces for the one or more pressure booster piston and the control piston and also hinders the realization of the connecting lines. This is the effort in the way to create the smallest possible pressure booster with the same performance and optionally also to reduce the weight of the predominantly made of solid metal parts booster.
  • pressure booster is referred to in the context of the invention, a device that automatically under a higher pressure The fluid to be dispensed is generated by means of a lower pressure fluid without external energy being applied to increase the pressure other than through the lower pressure fluid.
  • a pressure booster is particularly suitable for hydraulic fluids.
  • the higher pressure fluid may be the same fluid as the lower pressure fluid, or these two fluids may be different, such as when a high pressure steel water is to be generated for sewer cleaning with the aid of on-board low pressure hydraulics.
  • the pressure booster comprises a cylinder block which is composed of a plurality of disk-like or block-like, and usually completely solid cylinder block elements except for the holes which provide the hydraulic connecting lines and the cylinder chambers or other functional spaces.
  • a pressure booster piston and a spool cyclically reciprocate.
  • the pressure booster piston which is generally designed as a differential piston or stepped piston, forms in the cylinder block at least one high-pressure working space and at least one low-pressure working chamber.
  • the control piston controls the movement of the pressure intensifier piston in direct dependence on the position of the pressure intensifier piston. As a rule, the control piston is actuated solely by the fluid in the cylinder block.
  • the cylinder block has at least one external low-pressure port and at least one external high-pressure port and usually at least one external tank port or unpressurised port, each one (usually the only) interface of the pressure intensifier form the environment outside of its cylinder block.
  • the pressure intensifier according to the invention is designed so that at least the majority of the bias, with which the cylinder block elements are biased against each other, is applied by the clamping sleeve, so that in the interior of the cylinder block only slimmer or shorter and / or less the cylinder block elements gegenradapressende screws must be provided.
  • the pressure intensifier is designed so that no additional screws are installed parallel to the clamping sleeve, which are connected to the generation of the voltage with which the cylinder block elements are held against each other, involved. It should be noted that any existing short and / or small screws that are not involved in pressing the cylinder block elements against each other, but only hold any local attachments, are irrelevant, so do not disturb the invention.
  • the pressure booster according to the invention is designed so that the clamping sleeve has no separate screws, but even a thread, with the aid of which the voltage is generated, with which the cylinder block elements are pressed against each other.
  • the thread is preferably an internal thread. This ideally does not extend over the entire length of the clamping sleeve, which has this in the direction of its longitudinal axis, but at least over 25% of this length, better at least 50%.
  • the usable length of a thread designed as an M60 thread should preferably be at least 15 mm.
  • the clamping sleeve has a radially inwardly projecting in the direction of its central longitudinal axis, preferably designed as a circumferentially self-contained annular shoulder retaining projection.
  • a first, preferably thread-free cylinder block element on its outer circumference can be positively applied.
  • the retaining projection of the clamping sleeve thereby forms a re-bearing, against which a second cylinder block element can be biased by means of the clamping sleeve. This makes it possible to provide only one of the cylinder block elements with an expensive external thread.
  • the retaining projection preferably has a centering bevel, ie a bevel, which forms a surface which is inclined so that the cylinder block element abutting against it in a to the central longitudinal axis concentric position is forced. This automatically leads to the correct positioning of the bearing against the retaining element of the clamping sleeve cylinder block element.
  • the pressure intensifier according to the invention has a cylinder block of at least three cylinder block elements, which are arranged in the clamping sleeve along its longitudinal axis one behind the other and biased against each other.
  • the cylinder block element (s) held between two other cylinder block elements in each case are not themselves directly connected to the clamping sleeve, but rather have clearance therefrom and are held only by the adjacent cylinder block elements. This eliminates the need for precision machining of the peripheral surface of the cylinder block or sandwich-mounted components.
  • the pressure booster is preferably designed such that the maximum outer diameter of three cylinder block elements differ, ideally such that the maximum outer diameters of the cylinder block elements arranged directly coaxially one behind the other along the pressure booster longitudinal axis are gradually increased one step at a time. This facilitates the insertion and positive locking of the cylinder block in the clamping sleeve.
  • the high pressure working space is preferably fully formed in a cylinder block member, while the low pressure working space is also preferably completely formed in another cylinder block member. It is particularly advantageous if the low-pressure working space and / or the high-pressure working space is in each case formed by a bore which completely penetrates the relevant cylinder block element. In this way, the Inner peripheral surfaces, which serve as sliding surfaces for the respective piston, work particularly well with the necessary precision.
  • the bore receiving the control piston is formed jointly by all the cylinder block elements.
  • a cylinder block element is suitably completely penetrated by a bore, which is involved in the formation of the control piston receiving bore.
  • the pressure intensifier for fluids is particularly preferred to configure the pressure intensifier for fluids in such a way that all the fluid lines required for the operation of the pressure intensifier are formed between the pressure intensifier piston and the control piston in the cylinder block elements accommodated by the clamping sleeve and / or the pressure intensifier is designed such that the external high-pressure port is connected the one end face of the cylinder block elements received by the clamping sleeve is arranged, while the external low-pressure connection is arranged on the other end face of the cylinder block elements accommodated by the clamping sleeve.
  • This offers a particularly good space utilization and also facilitates the execution of external connections that do not interfere with each other.
  • the said cylinder block element bears a thread corresponding to the thread of the clamping sleeve only along part of its axial length, which preferably corresponds at most to 60% of its total axial length.
  • the correct spatial positioning of the cylinder block members relative to each other is made by pass means acting directly between the cylinder block members.
  • the passage means are preferably formed in the form of pins and corresponding pin receiving bores on and in the cylinder block elements.
  • the clamping sleeve is equipped with a holding projection for torque-tight, positive coupling of a screwing tool.
  • the design of the holding projection in the form of at least two diametrically opposite flat surfaces or grooves on the circumference of the clamping sleeve is particularly favorable. This allows the collet to be securely gripped and tightened, usually with just the torque or tightening angle required to produce the required preload of the cylinder block members relative to one another.
  • the retaining projection serving for tightening the clamping sleeve is formed exclusively in a portion of the clamping sleeve, which is outside the power flow during operation of the booster, which is generated by the bias of the cylinder block elements by means of the clamping sleeve in this.
  • clamping sleeve and / or the respective cylinder block element may be particularly favorable to design the clamping sleeve and / or the respective cylinder block element in such a way that the clamping sleeve has clearance at its inner circumference in the region radially below its holding projection relative to the cylinder block element located there, so that the (fixed) tightening of the clamping sleeve in the region of Holding section inevitably occurring elastic deformations of the clamping sleeve do not affect the underlying cylinder block element.
  • the clamping sleeve is designed to be thin-walled in the radial direction at least in the region over which the said force flow required for bracing the cylinder block elements runs.
  • "thin-walled” is to be considered if the wall thickness DW and the inside diameter D of the clamping sleeve have the following relationship: W ⁇ 0.2 D, better yet W ⁇ 0.1 D.
  • the cylinder block can be optimally counteracted during the tightening of the clamping sleeve or fixed in a counter holding device.
  • At least one of the cylinder block elements may have a bore in a region disposed within the collet, forming a fluid conduit over part of its length, the bore terminating in the preferably threaded circumferential surface of the cylinder block member, and sealing the mouth by a closure member.
  • clamping sleeve according to the invention can be used not only for single-acting pressure booster, the succession always alternately perform a power stroke and a charge cycle, but also for double-acting pressure booster load and work simultaneously in each cycle.
  • a pressure intensifier for fluids is claimed with a cylinder block of at least two cylinder block elements, which is characterized in that the cylinder block elements are arranged in a clamping sleeve and the clamping sleeve holds the cylinder block elements together or, preferably, braced against each other.
  • FIG. 1 shows the developed in a single plane hydraulic circuit diagram and the conditions during a working stroke of the pressure intensifier piston.
  • FIG. 2 shows the same developed in a single plane hydraulic circuit diagram and the conditions at a time when the pressure intensifier piston has reached its top dead center after a power stroke.
  • FIG. 3 shows the same in a plane developed hydraulic circuit diagram and the conditions during a charge cycle of the pressure intensifier piston.
  • FIG. 4 shows based on the FIG. 1 the conditions in normal operation, in which is generated using a correspondingly wired external switching valve fluid, which is output under high pressure.
  • FIG. 5 shows based on the FIG. 1 the conditions in the switching operation, in which the high-pressure consumer is depressurized using the appropriately switched, external switching valve back through the pressure booster or even emptied.
  • FIG. 6 shows a central longitudinal section through an actual embodiment of the pressure intensifier according to the invention.
  • FIG. 7 shows a perspective oblique view of an actual embodiment of the pressure intensifier according to the invention.
  • FIG. 8 shows another central longitudinal section in another plane by the already FIG. 6 underlying actual embodiment of the pressure intensifier according to the invention.
  • FIG. 9 shows a detailed view of a variant of the control piston 3, in the neck.
  • the fundamental principle of the pressure intensifier according to the invention is to explain, which is characterized by its particularly simple structure and therefore predestined to create a particularly compact pressure booster, so that just working on this principle pressure booster are predestined to with the to be combined according to the invention and thereby achieve the aspired, particularly compact pressure booster.
  • the Fig. 1 shows the pressure booster 1, which is completely formed in a metal, preferably steel cylinder block 13 which is cut here and therefore initially only schematically shown as a box-like outline.
  • the cylinder block preferably has the outer contour of a cylinder which is rotationally symmetrical about the longitudinal axis L.
  • the cylinder block 13 consists of at least two and ideally three separate, ie separable from each other, materially not interconnected cylinder block elements.
  • the plurality of cylinder block elements are mutually positively fixed relative to each other in a defined position, for example using not illustrated here dowel pins.
  • This pressure booster piston 2 is typically designed as a differential piston with two different sized, effective in the opposite direction effective hydraulic active surfaces and then consists of a low-pressure piston N with a large diameter and a high-pressure piston H with a small diameter fixed to each other are connected by a piston stem S.
  • the low-pressure piston N forms a low-pressure working chamber 10 in the cylinder block
  • the high-pressure piston H forms a high-pressure working chamber 11 in the cylinder block.
  • a gap 12 is formed, whose function will be explained later.
  • the gear ratio i. H. the factor by which the supplied low pressure can be increased depends on the diameter ratio DN / DH of the low pressure piston N and the high pressure piston H.
  • control piston 3 operates in the cylinder block 13.
  • Fig. 1 shows the pressure booster piston 2, the control piston 3 and all the connection lines required for the operation of a better overview in a plane projected.
  • said components are not all in one plane, because such an arrangement would make only extremely bad use of the cross-section of the cylinder block Fig. 1 Drawn plane, the piston and the connecting lines would crowd, while in a longitudinal axis also included cutting plane perpendicular to this no piston and almost no connection lines would be found.
  • the pressure intensifier communicates via an external connection 5 with an external low-pressure source and via an external connection 6 with an external tank or hydraulic fluid reservoir.
  • the pressure intensifier communicates via a further external port 7 with an external high pressure consumer, such as a hydraulically actuated tensioner or rescue scissors, just to name a few examples.
  • the external terminals 5 to 7 may be formed on one or distributed on both end sides of the booster. Preferably, they are formed together on a single end face of the pressure intensifier, so that the pressure booster can be installed in an overall system so that it is accessible after installation only from one end side. This "unpretentiousness" with regard to the installation situation makes it more universally applicable.
  • the pressure booster should, however, be designed such that none of the external connections, via which the pressure booster communicates with the environment, discharge into the area of its circumferential jacket. Why this is an important aspect will be understood later in this description.
  • a low-pressure line 8 connects to the external connection 5 to the low-pressure source.
  • the low pressure line 8 branches soon. It branches into a low-pressure line section 8.1, which serves primarily to feed the high-pressure working space with fresh low-pressure fluid, and moreover also serves to supply the control piston 3 with low pressure via the low-pressure line section 8.4.
  • the low pressure line section 8.2 leads past the high pressure working space directly into the line leading to the high pressure consumer.
  • the low pressure line section 8.2 is used to initially fill a newly connected, still empty high pressure consumer with low pressure fluid and the air from the u. U. initially empty lines of high pressure consumer to displace, so that then can be started with the high pressure generation.
  • a tank or return line 9 branches immediately into a return line section 9.1, which comes from the control piston ago, and a line section 9.2, which, as will be discussed later, in due course and with appropriate, i. d. R. externally accomplished hydraulic wiring of the pressure booster as a control line for the controllable check valve 4.3 is used.
  • a connecting line 14 is provided from the control piston to the pressure booster piston, whose function will be explained later in more detail.
  • control piston 3 is to say that this control piston 3 is also designed as a differential piston.
  • the gap 12 is also connected to the tank, that is held without pressure. This is necessary to be able to dissipate any leakage which possibly flows from the high-pressure working chamber and / or from the low-pressure working space into the intermediate space 12, so that no disturbing counterpressure can build up in this intermediate space, because possibly hydraulic fluid is trapped.
  • pilot line 24 * goes off, with the chamber or slimming V1 of the control piston is in fluid communication, which is alternately switched without pressure or subjected to low pressure.
  • This pilot line 24 * is characterized in that it allows only a very small pressure flow.
  • the purpose and operation of the pilot control line corresponds to that of the pilot control bore 24, the later or in connection with the Fig. 9 be discussed.
  • the pilot line at least locally forms a nozzle or aperture which forms a diameter between 0.1 mm and 1 mm, more preferably between 0.1 mm and 0.75 mm, depending on the level of pressure, for which the pressure booster is designed.
  • the presence of the nozzle or aperture indicates Fig. 1 the symbol for the bottleneck drawing.
  • the pilot control line can also have the said, small diameter over its entire length.
  • FIG. 2 shows the top dead center, ie the moment in which the pressure booster piston 2 had stopped in its movement and the direction of movement changes, shows the Fig. 3 the charge cycle, during which the pressure booster piston 2 again penetrates deeper into the low-pressure working space.
  • control piston works without a spring.
  • the otherwise necessary application of the closing force of a spring is replaced by the constant admission of a front side with the low pressure. This contributes to the achievement of the goal to build smaller the pressure booster, since the space required for the placement of the most replaceable subsequently replaceable spring required space is eliminated.
  • This line serves to relax the high pressure consumer at the appropriate time.
  • the pressure intensifier according to the invention is operated with a preferably externally mounted changeover valve 25.
  • the switching valve 25 is switched so that the already based on the FIGS. 1 to 3 discussed operation takes place, is generated in the high-pressure fluid, see. Fig. 4 ,
  • the switching valve 25 is switched to the position as the FIG. 5 shows. Basically, nothing happens except that the external connections 5 and 6 are "reversed". Of the Terminal 5, via which previously the externally generated low pressure was fed, is now depressurized and thus corresponds to the tank or. Return connection. The previously operated as a tank or return port external port 6 is now, z. B. via the external low-pressure feed pump 26, subjected to low pressure and thus even to the low-pressure connection. This has the consequence that the line section 9.2 is no longer depressurized, but now low pressure leads.
  • clamping sleeve as a central aspect of the invention
  • FIG. 6 shows a central longitudinal section along the longitudinal axis L by a pressure booster in real version, no longer shown schematically.
  • the pressure intensifier consists of a cylinder block 13 which, in this preferred exemplary embodiment, is composed of three cylinder block elements 13.1, 13.2 and 13.3, each of which is preferably designed as a circular cylinder section.
  • Each of the cylinder block elements is preferably designed as a solid metal block, in which a number of holes are subsequently introduced, which form the working piston and the control piston receiving cylinder chambers, and these working ready connecting lines including the spaces in which the check valves are installed.
  • the cylinder block elements are arranged in alignment in the direction along the longitudinal axis L in a row. They lie against each other with their ideally planely executed faces. How to use the Fig. 6 sees, the individual cylinder block elements are sealed at their usually ground end surfaces, with which they collide, by additional sealing elements 20.
  • These sealing elements 20 are preferably cord seals or so-called O-rings, which are preferably accommodated in a groove in the end face of a cylinder block element and bear against the end face of an adjacent cylinder block element with their part originally protruding from the groove.
  • the thus assembled cylinder block 13 is received by a clamping sleeve 15.
  • This clamping sleeve 15 is formed in the present embodiment as in its interior from one end face to the other continuously hollow tube.
  • This tube is expediently provided with an internal thread at least along one third of its length in the direction of the longitudinal axis L, but preferably over the predominant length. How to be good in the Fig. 6 can recognize, the clear inner diameter of acting as a clamping sleeve 15 tube is reduced at one end and forms a preferably circumferentially closed therein retaining projection 17 from.
  • the central cylinder block element 13.2 preferably has a maximum outer diameter which is smaller than the smallest diameter of the internal thread in the clamping sleeve 15. In this way, the second cylinder block element 13.2 during assembly easily through the inner, clear cross-section of the clamping sleeve glide without getting stuck there.
  • the first cylinder block element 13.1 preferably has a portion having the same maximum outer diameter as the second cylinder block element 13.2.
  • the first cylinder block element 13. 1 preferably forms a shoulder which forms a retaining projection 18 of this cylinder block element.
  • this retaining projection 18 of the cylinder block element which is usually completely self-contained in the circumferential direction, is matched to the retaining projection 17 of the clamping sleeve.
  • the clamping sleeve 15 Since the clamping sleeve 15 is thin-walled, it preferably assumes the function of a so-called expansion screw - the clamping sleeve 15 presses the cylinder block elements with considerable elastic bias against each other and is thereby stretched even elastic. Due to the pressure pulsation during operation, the cylinder block is pushed apart as a whole in the direction of the longitudinal axis L in both directions. As a result, a swelling load for the clamping sleeve 15 would arise in and of itself. Due to the fact that the clamping sleeve 15 is designed as an expansion sleeve, this swelling stress but kept away from the clamping sleeve 15 or reduced.
  • the clamping sleeve 15 while receiving the cylinder block 13, better still at least 75%, but still the cylinder block 13 at least on one side, better still in the region of both end faces, on the clamping sleeve 15th protrudes.
  • This is advantageous for the assembly, because in this way can in the area in which the cylinder block 13 protrudes freely on the clamping sleeve 15, each set a holding tool to hold the cylinder block against rotation while the clamping sleeve 15 on the cylinder block is screwed to produce the necessary bias.
  • this holding projection is formed, on which a screwing can be applied directly to the clamping sleeve.
  • this holding projection consists of at least two diametrically opposite flat surfaces 21.
  • radial or oblique bores are also made in the cylinder block from its peripheral jacket in order to produce the necessary connecting lines.
  • these holes are closed later, where they open out into the peripheral shell of the cylinder block, before the relevant cylinder block element is installed in the clamping sleeve.
  • the peripheral skirt of the cylinder block is therefore only drilled for manufacturing purposes, the openings located there have no function later.
  • FIG. 6 For a better overview, the reference to is still short Fig. 1 manufacture.
  • the Fig. 6 In the cutting plane, which the Fig. 6 is represented by the drawing Pressure booster piston 2 and the low-pressure working chamber 10 and the high-pressure working chamber 11 and the gap 12. Good to see how the high-pressure working chamber 11 is completed by the check valve 4.2 to the high pressure consumer. Good to see is also the control line 8.5, which is connected via a check valve 4.1 with the low pressure line section 8.1 in conjunction, via which the high-pressure working space is filled during charging cycle with low-pressure fluid.
  • the low-pressure piston N is provided on its front side facing the high-pressure working space with at least one spacer member 22, which prevents the low-pressure piston N over the entire surface on the shoulder between the high-pressure working space and the low-pressure working space and in this way the line laid, which makes the gap 12 depressurized, because it connects him to the tank level.
  • control line 8.5 has been introduced into the cylinder block element 13.1.
  • a bore perpendicular to the longitudinal axis L from the outer shell of the first cylinder block member 13.1 has been driven transversely through this until cutting in the direction parallel to the longitudinal axis L extending threaded bore receiving the check valve 4.1.
  • the second cylinder block element 13.2 is completely penetrated by the bore forming the low-pressure working chamber 10 and the intermediate space 12. In this way, the inner surface of this hole is the easiest to work.
  • the first cylinder block element 13.1. If you look closely you put In that regard, it is clear that the bore forming the high-pressure working chamber also completely penetrates the first cylinder block element 13.1 in the direction parallel to the longitudinal axis. Thus, the surface of the high-pressure work space can be processed very well. What is also to be seen is the fact that this bore has been enlarged and threaded in a subsequent manufacturing step where no high-pressure piston H is moving in it in order to insert the non-return valve 4.2 and to intersect with the Control line 8.5 to form.
  • the low-pressure line section 8.1 also completely penetrates the second cylinder block element 13.2 in the direction of the longitudinal axis. The same applies with respect to this low-pressure line section 8.1 for the third cylinder block element 13.3.
  • FIG. 8 shows a section through the already of the FIGS. 6 and 7 described real pressure translators in another level.
  • the control piston 3 which is constructed slightly different than the control piston 3, in the context of FIGS. 1 to 3 has been shown, in addition to further details.
  • control piston 3 consists of a control sleeve 3.1 and a relatively movable held in the control sleeve damping piston 3.2.
  • This spool is received by a hole, which, as already in the FIGS. 1 to 3 shown, is formed by several cylinder block elements and that in this case of the cylinder block elements 13.1 to 13.3 together.
  • FIG. 9 shows the spool 3 in the position and at the time of work, including the FIG. 3 its control piston 3 shows.
  • the control line 8.5 is at this time no pressure, so that in FIG. 9 shown upper end face of the control piston 3 is not under pressure.
  • the FIG. 9 shown lower annular end face of the control piston 3 via the line 8.3 of the low pressure, so that the control piston 3 is held in its uppermost position.
  • the control sleeve 3.1 has a slimming V1, ie a wormed and thus reduced in diameter portion in the of FIG. 9 shown moment, the connecting line 14 and the return line section 9.2 connects to each other, so that the low-pressure working chamber 10 is depressurized.
  • pilot hole 24 which goes through the wall of the control sleeve 3.1 inwardly toward the central bore and the control line 8.5 permanently connects with the slimming V1.
  • This pilot hole 24 has the purpose then also to ensure a defined position of the pressure booster piston 2 when the pressure booster has stood still for a long time. As long as the pilot hole 24 is missing, it may happen that after prolonged stoppage of the pressure booster piston, the control line 8.5 has lost the pressure trapped in it by microleakages and then the control piston 3 then assumes an undefined position, which makes restarting difficult.
  • the pilot hole 24 has the purpose to always ensure that the control line 8.5 is still correctly pressurized even after a long time and therefore forces the control piston 3 in a defined position, the restart of the Pressure intensifier easily possible.
  • the bore forms, at least locally, a nozzle or orifice which has a diameter between 0.1 mm and 1 mm, preferably between 0.1 mm and 0.75 mm, depending on the level of pressure for which the pressure booster is designed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP14198888.1A 2014-12-18 2014-12-18 Multiplicateur de pression doté de douille de serrage Active EP3034889B1 (fr)

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EP14198888.1A EP3034889B1 (fr) 2014-12-18 2014-12-18 Multiplicateur de pression doté de douille de serrage

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EP14198888.1A EP3034889B1 (fr) 2014-12-18 2014-12-18 Multiplicateur de pression doté de douille de serrage

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EP3034889A1 true EP3034889A1 (fr) 2016-06-22
EP3034889B1 EP3034889B1 (fr) 2018-09-12

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109185240A (zh) * 2018-11-16 2019-01-11 美钻深海能源科技研发（上海）有限公司 储能式自泄压增压结构及控制方法
CN109964047A (zh) * 2016-11-04 2019-07-02 活塞动力有限责任公司 具有压力放大器的液压致动器
CN112879379A (zh) * 2021-02-01 2021-06-01 中国航发沈阳发动机研究所 一种高效三腔液压缸及其作动方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2931218A (en) * 1957-05-23 1960-04-05 Gen Dynamics Corp Controlled actuator
US3676022A (en) * 1970-11-25 1972-07-11 Richard S Pauliukonis Pneumatic/hydraulic pressure actuated positive displacement pump
US3848414A (en) * 1972-02-29 1974-11-19 Assa Ab Pressure converter
WO1995013478A1 (fr) * 1993-11-09 1995-05-18 Valavaara Viljo K Cylindre de compression a deux etages
DE19633258C1 (de) * 1996-08-17 1997-08-28 Iversen Hydraulics Aps Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten
DE102006038862A1 (de) * 2006-08-18 2008-02-21 Scanwill Aps Druckübersetzer mit Doppelsitzventil

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2931218A (en) * 1957-05-23 1960-04-05 Gen Dynamics Corp Controlled actuator
US3676022A (en) * 1970-11-25 1972-07-11 Richard S Pauliukonis Pneumatic/hydraulic pressure actuated positive displacement pump
US3848414A (en) * 1972-02-29 1974-11-19 Assa Ab Pressure converter
WO1995013478A1 (fr) * 1993-11-09 1995-05-18 Valavaara Viljo K Cylindre de compression a deux etages
DE19633258C1 (de) * 1996-08-17 1997-08-28 Iversen Hydraulics Aps Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten
DE102006038862A1 (de) * 2006-08-18 2008-02-21 Scanwill Aps Druckübersetzer mit Doppelsitzventil

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109964047A (zh) * 2016-11-04 2019-07-02 活塞动力有限责任公司 具有压力放大器的液压致动器
CN109185240A (zh) * 2018-11-16 2019-01-11 美钻深海能源科技研发（上海）有限公司 储能式自泄压增压结构及控制方法
CN109185240B (zh) * 2018-11-16 2023-09-26 美钻深海能源科技研发（上海）有限公司 储能式自泄压增压结构及控制方法
CN112879379A (zh) * 2021-02-01 2021-06-01 中国航发沈阳发动机研究所 一种高效三腔液压缸及其作动方法

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