EP3242017A1 - Multiplicateur de pression en tant que visseuse - Google Patents

Multiplicateur de pression en tant que visseuse Download PDF

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Publication number
EP3242017A1
EP3242017A1 EP16168387.5A EP16168387A EP3242017A1 EP 3242017 A1 EP3242017 A1 EP 3242017A1 EP 16168387 A EP16168387 A EP 16168387A EP 3242017 A1 EP3242017 A1 EP 3242017A1
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EP
European Patent Office
Prior art keywords
pressure
coupling portion
hydraulic
fluid
booster
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
EP16168387.5A
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German (de)
English (en)
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EP3242017B2 (fr
EP3242017B1 (fr
Inventor
Jesper Will Iversen
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Scanwill Fluid Power ApS
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Scanwill Fluid Power ApS
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Application filed by Scanwill Fluid Power ApS filed Critical Scanwill Fluid Power ApS
Priority to DK16168387.5T priority Critical patent/DK3242017T4/da
Priority to EP16168387.5A priority patent/EP3242017B2/fr
Priority to US15/581,543 priority patent/US20170321728A1/en
Publication of EP3242017A1 publication Critical patent/EP3242017A1/fr
Application granted granted Critical
Publication of EP3242017B1 publication Critical patent/EP3242017B1/fr
Publication of EP3242017B2 publication Critical patent/EP3242017B2/fr
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Classifications

    • 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
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • 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
    • F04F13/00—Pressure exchangers

Definitions

  • the invention relates to a preferably hydraulic pressure booster according to the preamble of claim 1.
  • a device As a pressure booster, a device is referred to here, which automatically produces from a drive fluid available under low pressure, without additional external drive, a higher pressure of his output working fluid. The details of such a device will be explained in more detail later.
  • Such pressure intensifiers are used in many areas. The following application areas are not exhaustive. For example, such pressure boosters are used to generate a high pressure water jet for a cleaner using the low pressure vehicle hydraulics, or to operate a rescue shears to rescue inmates from high pressure vehicles. Even in industrial applications, such pressure intensifiers are used in a variety of forms, for example to supply clamping tools or rotating chucks with the high pressure required for clamping.
  • the clamping tools may be used in industrial manufacturing clamping tools or clamping tools used during assembly, and the rotating chuck may be part of a machine tool or, for example, a drill pipe for carrying out earth drilling.
  • the pressure intensifiers can be used individually or cascaded in series, if a particularly high Pressure is generated, which can not be achieved with the help of a single booster amplifier.
  • the pressure intensifiers known in the prior art are typically connected via high pressure hoses or hydraulic pipes to the hydraulic block, which supplies them with hydraulic fluid under low pressure and receives used hydraulic fluid.
  • the connection to the high-pressure consumer, which is supplied with the hydraulic fluid generated by the pressure intensifier, under increased pressure, is usually carried out via hydraulic hoses or tubes.
  • connection of a pressure booster with the help of high-pressure hoses or pipes to the hydraulic system supplying it and possibly also to the consumers supplied by it is problematic.
  • hydraulic hoses can age over time and then tend to leak. Hydraulic pipes can become fatigued over time, especially when exposed to oscillating loads.
  • the problem is the connection with hydraulic hoses or pipes even where several pressure intensifiers are used, for example because they are cascaded in series. This usually results very quickly space problems and the system can not be kept as compact in the end, as would actually be desirable.
  • Particularly problematic is the use of hydraulic hoses in rotating systems, where the pressure booster rotates with.
  • the invention is therefore an object of the invention to provide a pressure booster, which can be connected tube and tubeless and thereby very reliable to a hydraulic block. This object is achieved with the features of claim 1.
  • Claimed is a - usually ready to operate, only the connection to a pressure supply, a tank connection and a consumer for the higher pressure it requires - pressure booster for fluids, especially for liquids.
  • the pressure booster thus forms a ready-to-use unit for completely or partially introducing it into a hydraulic block.
  • the pressure booster consists of a cylinder block in which a pressure booster piston and a control piston move cyclically.
  • the control piston can assume different positions and thereby predefines the working cycles of the pressure intensifier piston, wherein the control piston is not actuated by a mewan forced control in the manner of a camshaft, but purely by pressure difference.
  • the pressure intensifier is in turn designed so that it, when it has reached a certain position, one Changes in the pressure conditions initiated on the control piston, so that it changes its position.
  • the pressure booster piston is preferably designed as a differential piston with two different sized, hydraulically effective piston surfaces, in any case, it forms a high-pressure working chamber and a low-pressure working space in the cylinder block.
  • the pressure booster piston is usually solid, d. H. it preferably has no through holes that connect, for example, the high pressure working space and the low pressure working space. Instead, the pressure intensifier piston usually has a constriction in the region of its circumference, which forms a gap which is located between the high-pressure working chamber and the low-pressure working chamber.
  • the cylinder block has an external connection for supplying pressurized fluid from outside, which is also called low-pressure connection - because the pressure of the fluid present here is lower than the pressure of the discharged from the pressure booster to the consumer fluid.
  • the fluid under said low pressure is intended to perform work in the pressure intensifier and possibly also serves as the basis for generating and dispensing high pressure fluid, that is, fluid which is at a higher pressure than the low pressure fluid.
  • the high-pressure fluid is discharged via an external high-pressure port as under a higher pressure working fluid to the outside to an external consumer.
  • the pressure booster has a connection for the discharge of fluid, whose working capacity is exhausted in the pressure booster.
  • This connection is in the Also referred to as tank connection, even if it does not necessarily lead to a tank in the strict sense. It should also be mentioned that the said gap usually forms part of a channel leading to the tank connection.
  • the cylinder block of the pressure intensifier is here preferably understood a solid metallic body containing all cylinder bores and channels, which are required for cooperation of the pressure booster piston and the control piston.
  • the solid metallic body has at least in the region of the control piston and the pressure booster piston everywhere cross sections in which the area occupied by the solid material in cross-section, is greater than the area occupied by the cylinder bores and the channels in the cross section ,
  • the cylinder block of the booster has a rigidly connected to him coupling portion.
  • the coupling portion is configured to be inserted into a receiving bore of a hydraulic block. He is designed so that the receiving bore encloses the coupling portion on its circumference and usually also the front side.
  • the coupling section has at least two fluid transfer regions which are fluidically separated from one another by a seal and serve for the exchange of fluid between the pressure intensifier and the hydraulic block into which it is inserted.
  • the fluid transfer areas are positioned on the coupling portion so as to be located inside the hydraulic block into which the coupling portion has been inserted, below the outer surface of the hydraulic block against which the non-hydraulic part of the hydraulic block is inserted Pressure booster rests.
  • the fluid transfer areas are at least 20 mm, more preferably at least 30 mm below the surface of the hydraulic block.
  • the pressure booster is designed so that in a fluid transfer area from the interior of the cylinder block of the pressure booster coming a channel opens, via which the pressure booster emits fluid during operation, the workable within the pressure booster working capacity is exhausted.
  • another channel opens, also coming from the interior of the cylinder block.
  • Low-pressure fluid ie fluid which drives the pressure intensifier and possibly also forms the basis for generating fluid under higher pressure and to be delivered to a consumer, is fed via this channel into the pressure intensifier.
  • the coupling portion has a third fluid transfer area for transferring the higher pressure working fluid to the hydraulic block.
  • the intensifier there is no need for any pipes or hydraulic hoses to connect the intensifier with its environment and thus make it ready for use. Instead, find an immediate one hydraulic connection between the cylinder block of the pressure booster and the hydraulic block instead.
  • At least one of the fluid transfer regions comprises an annular groove running around in the peripheral circumferential surface of the coupling section.
  • the coupling section has an external thread for screwing the coupling section into the hydraulic block.
  • the coupling portion is mechanically anchored securely in the hydraulic block.
  • the plurality of fluid transfer regions are preferably arranged between the free, to be introduced into the hydraulic block end of the coupling portion and the external thread of the coupling portion.
  • the outer diameter of the coupling portion usually tapers at the transition between the external thread and the rest of the coupling portion.
  • the cylinder block of the booster has a molded hex for attachment of a screwing tool.
  • the coupling portion of at least two parallel to the longitudinal axis of the pressure booster extending bores which extends from the free end face of the coupling portion into the region of the cylinder block of the Extend pressure booster, which is always positioned outside of the coupling portion receiving hydraulic block.
  • a hydraulic unit with a hydraulic block in which a plurality of hydraulic fluid flows through bores for connecting different hydraulic active elements (controllable or non-controllable valves and / or pumps and / or pressure equalization tank and / or more pressure booster) are formed, and at least one Pressure booster of the type according to the invention has, wherein the pressure booster has a coupling portion which is inserted into a bore in the hydraulic block and fixed there.
  • the hydraulic unit can be made particularly compact, since the pressure booster need no piping or hydraulic hoses for connection to the hydraulic block and therefore packed very close to each other can be attached to the hydraulic block.
  • the fundamental principle of the pressure booster according to the invention is to be explained, which is characterized by its particularly simple structure and therefore predestined to create a particularly compact booster, so that just working on this principle pressure booster are predestined to be equipped with the connection which forms the core of the invention.
  • 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 represented by four solid lines forming a rectangle as a box-like outline.
  • the cylinder block preferably has the outer contour of a cylinder that is rotationally symmetric 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 pressure intensifier piston preferably has a longitudinal axis that is parallel to the longitudinal axis L of the cylinder block 13.
  • 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.
  • a control piston works 3.
  • its longitudinal axis is parallel to the longitudinal axis L of the cylinder block 13.
  • the control piston and the differential piston are completely or at least predominantly arranged side by side, seen perpendicular to the longitudinal axis.
  • the pressure intensifier piston 2 shows the control piston 3 and all the necessary connection lines for better clarity in a plane projects.
  • 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 amplifier communicates via its external low-pressure connection 5 with an external low-pressure source. From this, the pressure intensifier draws lower pressure hydraulic fluid that drives it. Preferably, a portion of these under low pressure in the pressure amplifier fed hydraulic fluid is placed in the pressure booster under higher pressure and output as under higher pressure hydraulic fluid from the pressure booster to an external consumer.
  • the pressure booster has an external tank connection 6, via which it discharges at least part of the lower-pressure hydraulic fluid to the outside when this hydraulic fluid has performed its work within the pressure booster.
  • the delivery is preferably to an external tank or an external hydraulic fluid reservoir, but this is not mandatory.
  • the pressure intensifier has another connection, the so-called external high-pressure port 7.
  • the pressure intensifier Via its high-pressure connection, the pressure intensifier gives it hydraulic fluid set under a higher pressure (compared to the feeding lower pressure) Working machine, such as a rescue scissors, a clamping device or a hydraulic collet chuck.
  • a connection is external, because the pressure amplifier can be connected directly to the environment via this connection.
  • a low pressure line 8 connects to the external port 5 to the low pressure source within the cylinder block 13, a low pressure line 8 at.
  • 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 preferably existing 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, if present, to fill a newly connected, still empty high pressure consumer first 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 within the cylinder block 13 at once into a return line section 9.1, which comes from the control piston ago, and a line section 9.2, the as will be discussed later, in due course and with a corresponding, usually provided by external hydraulic circuit 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 pressure booster piston 2 moves in the direction of the black arrow in the high-pressure working chamber 11 inside.
  • the high-pressure work chamber 11 is initially filled with low-pressure fluid, ie preferably with fluid that is under the low pressure of the feed pump.
  • the pressure intensifier piston By moving the pressure intensifier piston into the high-pressure working space 11, the fluid located there is pressurized and discharged via the check valve 4.2 and the external high-pressure connection 7 to the high-pressure consumer.
  • the low-pressure working space 10 which continuously increases in the course of the working cycle, is continuously filled with low-pressure fluid, ie with fluid drawn in via the low-pressure via the external low-pressure connection 5.
  • This refilling is done via the connecting line 14.
  • the control piston 3 remains in the of Fig. 1 shown position. Although it is at its one (here the lower) end face on the low pressure line section 8.3 constantly subjected to low pressure. At the same time, however, it has been subjected to low pressure since the beginning of the power stroke at its opposite (here the upper) end side via the control line 8.5.
  • the gap 12 is also connected to the external tank port 6, that is kept pressureless. 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.
  • 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".
  • the port 5, via which the externally generated low pressure has been fed so far, is now switched 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.
  • a throttle pilot hole is still in the Fig. 1 to 4 to recognize, forming a throttle pilot hole. While the pilot control bore in the figures is symbolized by way of example schematically as a bypass throttle 24 *, in reality it is preferred that the pilot bore penetrates the right-hand hatched upper part of the control piston 3 to be recognized in the figures. It connects the region of the upper free end face of the control piston 3 with the slimming V1. In this way, the control line 8.5 is permanently connected to the slimming V1.
  • This pilot hole also has the purpose to ensure a defined position of the pressure booster piston 2 when the pressure booster has stood still for a long time.
  • pilot hole As long as the pilot hole is missing, it may happen that after a long stoppage of the pressure booster piston, the control line 8.5 has lost the pressure trapped in it by microleakages and the control piston 3 then assumes an undefined position, which makes restarting difficult.
  • the pilot hole 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, which makes it easy to restart the pressure booster.
  • the flow flowing through the pilot hole is chosen so that it is so small that it does not matter during operation. Only in longer downtime adds up the running over the pilot hole bore flow and thus shows the desired effect, as described above.
  • Fig. 6 and 7 show a concrete, physical embodiment of a pressure intensifier according to the invention.
  • FIG. 7 shows the coupling portion of the booster gem. Fig. 6 in an enlarged view.
  • the Fig. 6 shows the pressure booster 1 according to the invention in its mounted on an external hydraulic block 100 position.
  • the hydraulic block is not part of the pressure booster, but represents, for example, the hydraulic control block of a clamping device.
  • the hydraulic control block is actually a solid metal control block (no pipe sleeve o. ⁇ .) In which a plurality of hydraulic channels is formed and the z. B. also includes the actuator over which the user controls the system hydraulically.
  • the cylinder block 13 or its cylinder block element 13.1 integrally merges into a coupling section 101, i. H. a part of the circumferential surface of the cylinder block of the booster forms the coupling portion 101.
  • the coupling portion 101 has a circular cylindrical shape. Preferably, it has a reduced diameter compared to the rest of the generally likewise cylindrical cylinder block 13, ideally by at least 30%.
  • the diameter of the coupling portion 101 preferably corresponds to the core diameter of a metric thread and is reduced by a tolerance measure that allows the non-male threaded portion of the coupling portion 101 to pass through the female threaded portion of the hydraulic block 100.
  • the length of the coupling portion 101 in the direction of the longitudinal axis L of the booster 1 is preferably at least 25%, more preferably at least 30% of the total length of the cylinder block 13 of the booster 1. This ensures that the coupling portion 101 can penetrate deep enough in the hydraulic block 100, in an area that is located in the solid material of the hydraulic block, below the most planar surface of the hydraulic block 100 surrounding the bore for the introduction of the coupling portion 101.
  • the coupling section 101 is surrounded in its installed in the hydraulic block 100 at its periphery around (possibly by local channels through) solid material of the hydraulic block, seen in the radial direction has a thickness which is at least about The factor 1.5 is larger than the largest radius of the circular cylindrical cylinder block 13.
  • the fluid transfer can take place where the hydraulic block 100 has a high strength or rigidity.
  • the "low pressure" or lower pressure supplying the pressure intensifier in absolute terms, must by no means be a low pressure. Because where a very large pressure difference must be overcome, the pressure intensifier according to the invention can be used cascading, ie a subsequent pressure booster is then fed by the high pressure of the previous booster.
  • the coupling portion 101 not only provides a fluidic connection between the pressure booster 1 and the hydraulic block 100, which is supplied by the pressure booster. Rather, he keeps the pressure booster 1 also mechanically in its installation position by the weight and all forces occurring during operation due to the mass of the booster 1 predominantly or completely receives and passes on to the hydraulic block 100, z. B. the acceleration forces that occur at the pressure booster when the hydraulic block rotates or moves.
  • the coupling portion 101 is configured to be inserted and fixed in a bore of the hydraulic block 100 receiving it.
  • the coupling portion 101 is preferably provided with an external thread 102, which is screwed into a corresponding counter-thread of the coupling portion 101 receiving bore in the hydraulic block 100.
  • the coupling portion 101 is designed so that it can completely enclose the receiving bore of the hydraulic block 100 at its periphery and at its free end face.
  • two fluid transfer areas 104 and 105 are formed on the coupling portion 101. They are seen in the direction of the longitudinal axis L of the booster one behind the other and seen in the screwing of the coupling portion, if necessary, before the provided with an external thread 102 portion of the coupling portion.
  • the first fluid transfer region 104 is preferably formed on the peripheral surface of the coupling portion 101.
  • the second fluid transfer region can either also be formed on the peripheral surface of the coupling portion 101 or preferably on its free end face.
  • the pressure intensifier communicates directly with the hydraulic block 100 via these fluid transfer regions 104, 105 (and only via these). These two fluid transfer regions are hydraulically separated from one another by a seal 106.
  • the seal is preferably designed as a seal inserted with or without a support ring in a circumferential annular groove on the coupling section.
  • another seal 107 is provided which seals the lying closer to the outside fluid transfer region 104 to the outside.
  • the coupling portion 101 preferably has two bores 108 and 109 extending generally parallel to the longitudinal axis L. These extend from the free front end of the coupling portion 101 through the coupling portion into the region of the cylinder block 13 (or 13.1), which also at the hydraulic block mounted pressure booster outside the hydraulic block 100 is located.
  • the one hole 108 goes into the of the Fig. 1 to 5 shown low pressure line 8 via.
  • This bore preferably opens into the free end face of the coupling section and here constitutes the external low-pressure connection 5 (cf. Fig. 1 ) of the pressure booster.
  • the fluid transfer region 105 is located in the fluid transfer region 105, via which the pressure booster can be connected to the low-pressure feed line, which opens here in the bottom of the bore of the hydraulic block 100, which receives the coupling portion 101.
  • the fluid transfer area 105 is designed to that a fluid-conducting connection between the pressure booster and the hydraulic block can be made about him regardless of the absolute screwing or the angle of rotation, which has covered the coupling portion when screwed into the hydraulic block.
  • the other hole 109 goes into the of the Fig. 1 to 5 shown tank or reflux line 9 via. It is where it actually opens into the free end of the coupling portion 101, closed by a plug 110. It is blended with a transverse bore 111, which opens into an annular groove 112. The annular groove 112 is located in said further fluid transfer region 105. In this way, the external tank connection 6 is represented.
  • fluid transfer region 105 can alternatively be designed in accordance with how the fluid transfer region 104, that is to say can lie on the peripheral circumferential surface of the coupling section. However, such an embodiment is not preferred.
  • section of the cylinder block 13 located outside the hydraulic block 100 with a coupling section for a screwing tool, preferably in the form of an external hexagon - which, however, is not shown in the drawing.
  • the external high-pressure port 7 is located in this embodiment, preferably on the side facing away from the coupling portion 101 side of the booster 1. Here is carried out in a conventional manner a fluid-conducting connection to the high-pressure consumer.
  • FIGS. 8 and 9 show a second concrete embodiment of the pressure intensifier according to the invention.
  • the preceding statements for the first embodiment also apply here, unless otherwise described below.
  • the coupling portion is formed by the predominant part of the circumferential surface of the cylinder block 13.
  • the cylinder block 13 of the booster 1 is designed so that it can be at least 1 ⁇ 2, better 2/3 of the length that the cylinder block 13 has in the direction of its longitudinal axis L, inserted into a bore of the hydraulic block 100.
  • the cylinder block is designed so that the first and the second cylinder block element 13.1 and 13.2 can be completely inserted into the hydraulic block 100.
  • the coupling portion 101 is again designed so that it can completely enclose the receiving bore of the hydraulic block 100 at its periphery and at its free end face.
  • the diameter of the coupling portion preferably corresponds to the core diameter of a metric thread and is reduced in relation thereto by a degree of tolerance which allows the non-male threaded portion of the coupling portion to pass through the female threaded portion of the hydraulic block.
  • three fluid transfer regions 104, 105 and 113 are formed in this embodiment. They are seen in the direction of the longitudinal axis L of the booster one behind the other and seen in the screwing of the coupling portion, if necessary, before the provided with an external thread portion of the coupling portion.
  • the pressure booster 1 communicates directly to the outside, d. H. with the hydraulic block.
  • An additional hose or pipe connection for connection to the high pressure consumer is not provided here, the high pressure consumer is powered by the pressure booster 1 via the hydraulic block 100.
  • the first fluid transfer region 104 is bounded on both sides by seals 114, which are preferably cord seals inserted with or without a support ring in a peripheral annular groove on the coupling portion 101.
  • the in Fig. 8 low-pressure line section 8 opens into a transverse bore which opens on its other side into the outer surface of the cylinder block or (where present) of the second cylinder block element 13.2, within the first fluid transfer region 104.
  • the external low-pressure connection 5 is formed.
  • Preferably carries the Cylinder block 13 in this area for reasons of strength, no annular groove, but is smooth and thus unimpaired.
  • the corresponding annular groove is here instead preferably mounted in the hydraulic block 100.
  • the "tank line" shown is preferably extended by a bore extending within the cylinder block 13 into the region of the front shoulder 116 of the coupling section 101, where it discharges, into the second fluid transfer region 105.
  • the external tank connection 6 is thereby represented.
  • the second fluid transfer region is limited in the direction of the outside of the hydraulic block by a further seal 118 and thereby kept small, wherein the seal is preferably also in a circumferential annular groove of the coupling portion and the seals 114, 115 may correspond.
  • the front shoulder 116 is formed by the fact that the coupling section tapers here.
  • the tapered cylinder extension 117 of the coupling portion 101 is designed so that it can be inserted into a second, tapered portion of the here designed as a stepped bore in the hydraulic block 100 receiving bore.
  • the tapered cylinder extension 117 carries at least one, better two circumferential annular grooves in the - usually with support rings - one or two seals 119 are inserted. These one or two seals seal the third fluid transfer region 113 from the second fluid transfer region 105.
  • the third fluid transfer region is thus formed at the free end end of the coupling portion 101. In the free end, the high-pressure line opens, so that here the external high-pressure port 7 is formed.
  • Said rejuvenation of the cylinder extension 117 takes place with consideration for the high pressure present there. This preferably makes it necessary to keep the lengths to be sealed small and also to keep the surfaces exposed to the high-pressure action and thus the forces arising therefrom small.
  • a pressure intensifier cascade comprising a hydraulic block 100 and a plurality of pressure amplifiers 1 connected in series in series, characterized in that the pressure intensifiers 1 mounted side by side on the hydraulic block 100 are those according to one of the preceding claims.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Actuator (AREA)
EP16168387.5A 2016-05-04 2016-05-04 Multiplicateur de pression en tant que visseuse Active EP3242017B2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DK16168387.5T DK3242017T4 (da) 2016-05-04 2016-05-04 Trykforstærker til iskruning
EP16168387.5A EP3242017B2 (fr) 2016-05-04 2016-05-04 Multiplicateur de pression en tant que visseuse
US15/581,543 US20170321728A1 (en) 2016-05-04 2017-04-28 Pressure Intensifier for Fluids

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16168387.5A EP3242017B2 (fr) 2016-05-04 2016-05-04 Multiplicateur de pression en tant que visseuse

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EP3242017A1 true EP3242017A1 (fr) 2017-11-08
EP3242017B1 EP3242017B1 (fr) 2019-01-02
EP3242017B2 EP3242017B2 (fr) 2023-10-11

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DK (1) DK3242017T4 (fr)

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Publication number Priority date Publication date Assignee Title
ES2866888T3 (es) * 2017-10-19 2021-10-20 Pistonpower Aps Disposición de amplificador de presión hidráulica
EP3543460B1 (fr) 2018-03-19 2021-03-10 Caterpillar Global Mining Europe GmbH Système de support de blindage hydraulique et multiplicateur de pression
EP3730806B1 (fr) * 2019-04-24 2023-01-18 Piston Power s.r.o. Agencement d'actionneur hydraulique

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19633258C1 (de) * 1996-08-17 1997-08-28 Iversen Hydraulics Aps Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten
DE10158178C1 (de) * 2001-11-28 2003-07-17 Minibooster Hydraulics As Soen Hydraulischer Druckverstärker
DE10249523A1 (de) * 2002-10-23 2004-05-19 Minibooster Hydraulics A/S Druckverstärker
US20040258487A1 (en) * 2003-06-23 2004-12-23 Dbt Gmbh Hydraulic shield support
DE102006038862A1 (de) * 2006-08-18 2008-02-21 Scanwill Aps Druckübersetzer mit Doppelsitzventil
DE102007031282A1 (de) * 2007-07-05 2009-01-08 Uwe Hammer Hydraulischer Druckverstärker

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3940937A (en) * 1972-04-14 1976-03-02 Pauliukonis Richard S Intensifier
US5451145A (en) * 1993-11-05 1995-09-19 Sauter; William High pressure fluid pump transformer and method
US5669739A (en) * 1995-07-05 1997-09-23 Hl & H Timber Products (Proprietary) Limited Prestressing of mine props
US6336802B1 (en) * 1998-03-10 2002-01-08 David R. Hall Reduced mass unitary frame for ultra high-pressure high-temperature press apparatus
DE10107115B4 (de) * 2001-02-14 2004-09-30 Robert Bosch Gmbh Drucksteuerventil
DE10393780T5 (de) 2002-11-25 2005-10-27 Hartho-Hydraulic Aps Verstärkerbaueinheit
DE102009030514B4 (de) 2009-06-04 2015-09-10 Scanwill Fluid Power Aps Ausblaswerkzeug

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19633258C1 (de) * 1996-08-17 1997-08-28 Iversen Hydraulics Aps Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten
DE10158178C1 (de) * 2001-11-28 2003-07-17 Minibooster Hydraulics As Soen Hydraulischer Druckverstärker
DE10249523A1 (de) * 2002-10-23 2004-05-19 Minibooster Hydraulics A/S Druckverstärker
US20040258487A1 (en) * 2003-06-23 2004-12-23 Dbt Gmbh Hydraulic shield support
DE102006038862A1 (de) * 2006-08-18 2008-02-21 Scanwill Aps Druckübersetzer mit Doppelsitzventil
DE102007031282A1 (de) * 2007-07-05 2009-01-08 Uwe Hammer Hydraulischer Druckverstärker

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EP3242017B2 (fr) 2023-10-11
EP3242017B1 (fr) 2019-01-02
DK3242017T4 (da) 2023-12-18
US20170321728A1 (en) 2017-11-09
DK3242017T3 (en) 2019-04-23

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