EP0828942A1 - Machine-outil hydropneumatique - Google Patents

Machine-outil hydropneumatique

Info

Publication number
EP0828942A1
EP0828942A1 EP97920528A EP97920528A EP0828942A1 EP 0828942 A1 EP0828942 A1 EP 0828942A1 EP 97920528 A EP97920528 A EP 97920528A EP 97920528 A EP97920528 A EP 97920528A EP 0828942 A1 EP0828942 A1 EP 0828942A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
space
machine tool
tool according
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
EP97920528A
Other languages
German (de)
English (en)
Other versions
EP0828942B1 (fr
Inventor
Viktor Malina
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tox Pressotechnik GmbH and Co KG
Original Assignee
Tox Pressotechnik GmbH and Co KG
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 Tox Pressotechnik GmbH and Co KG filed Critical Tox Pressotechnik GmbH and Co KG
Publication of EP0828942A1 publication Critical patent/EP0828942A1/fr
Application granted granted Critical
Publication of EP0828942B1 publication Critical patent/EP0828942B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/076—Combined pneumatic-hydraulic systems with pneumatic drive or displacement and speed control or stopping by hydraulic braking
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention is based on a hydropneumatic machine tool according to the preamble of the main claim.
  • a known tool machine of the generic type (DE-P 43 01 983)
  • the working stroke of the working piston is braked to the bottom of the corresponding pneumatic working space by impacting the step of the largest diameter serving the rapid traverse, namely the drive piston, on the
  • a damping disc on the drive piston surface, which, however, causes only a slight damping.
  • Such generic machine tools are in themselves fast-working and energy-saving pneumatic systems in which a hydraulic system is integrated, by means of which a power stroke with a very high actuating force can be achieved after the desired forward stroke in the working direction.
  • a hydraulic system is integrated, by means of which a power stroke with a very high actuating force can be achieved after the desired forward stroke in the working direction.
  • the pressure is converted using the hydraulics.
  • hydraulic chambers in addition to pneumatic chambers move in the piston stroke direction, with the not inconsiderable problem of sealing from one to the other. Air entering the hydraulic fluid leads to undesirable compressibility of the oil; Oil leaking from the hydraulic part can lead to malfunctions.
  • the machine tool according to the invention with the characterizing features of the main claim has the advantage over the fact that more or less damping is achievable after the throttle point cross section, in particular towards the end of the working stroke, whereby this cross section can be adapted to the masses at the throttle point.
  • the hydraulic fluid with which the rest of the hydropneumatic pressure intensifier works can be used for this damping.
  • the seals, which are of high quality anyway, between the pneumatic space and the hydraulic space also serve to seal the annular space, so that an additional, complex seal is not required.
  • the invention can be implemented in a very simple manner and very effectively and while overcoming the prejudice of the specialist world on such machine tools. It is known to dampen the end position of the working piston hydraulically or pneumatically in the case of working cylinders, but this is not a step piston with the problems mentioned above.
  • the stepped piston displaces at least towards the end of the return stroke and for braking its return stroke movement liquid from the annulus through a restriction.
  • both the forward and the return of the stepped piston and thus the lower dead center area and the upper dead center area of the tool are damped during the stroke movement, the additional piston collar arranged on the stepped piston for damping the working stroke with its annular surface facing away from the ring surface used during the working stroke Return stroke damping causes.
  • the annular space has at least one of its end sections a taper corresponding to the diameter of the piston collar, into which the piston collar is immersed toward the end of the stroke, the volume of liquid enclosed in this as a brake chamber being displaced by the throttle point.
  • the stroke movement is braked or damped only towards the end of the stroke of the working stroke or return stroke.
  • the entire stroke movement can also be braked by the piston collar sealing more or less to the cylinder wall or the annular spaces located on both sides of the piston collar being connected to one another via a throttle channel.
  • the annular space can be connected to the working space during the working stroke and / or return stroke.
  • the hydraulic fluid can get from the annulus to the work area without throttling, unless braking is to take place.
  • the refilling of hydraulic oil via the extra refill devices provided for this purpose also has an effect on the hydraulic damping.
  • the annular space can also be completely separate from the working space and be located at a different location on the stepped piston, for example in the region of the piston rod.
  • that clearance between the piston collar and the annular space wall serves as the throttle point. In the case of a taper in the end sections of the annular space, the damping naturally only acts in these areas.
  • a relief channel branches off from the brake chamber, in which a control element for controlling the flow through the flow is present.
  • the relief channel can open into the annular space again.
  • the relief channel can also lead from one brake chamber to the other, the brake chambers being activated alternately and two control elements can also be arranged in the relief channel, one for one and the other for the other brake chamber, which are then alternately effective.
  • a bypass channel connecting the braking space to the storage space with a check valve blocking the storage space.
  • a bypass bypasses the point at which the plunger separates the working space and the storage space from one another in order to thereby quickly fill up the working space during the rapid stroke.
  • a rapid refilling of the working space is achieved at the beginning of the rapid stroke in the working stroke direction, specifically via the braking space.
  • a bypass channel connecting the annular space to the work space with a check valve blocking the work space.
  • This bypass channel advantageously runs in the working piston.
  • a pressure equalization is achieved via the check valve when the stepped piston moves away from its end position, i.e. before the start of the return stroke.
  • a short-circuit channel connecting the annular space to the working space is arranged in the working piston, the mouth of which is provided on the surface of the piston collar and which is at least partially closed towards the end of the working stroke by the taper in the annular space.
  • This short-circuit duct also serves as an overflow bore for volume compensation when the stepped piston moves away from its starting position, that is to say at the beginning of the working stroke.
  • the storage space is arranged in a storage cylinder and is delimited by a storage piston which is subjected to low pressure (pneumatic or spring) on the side facing away from the storage space in order to generate a storage pressure.
  • low pressure pneumatic or spring
  • the central axis of the storage cylinder is arranged parallel but at a distance from that of the working piston and wherein the storage space and working space are accommodated within a common machine housing.
  • a coil spring is used to generate low pressure. This has the advantage that the hydraulic oil is always under a low pressure sufficient for venting the hydraulic area.
  • the accumulator is normally switched off during the return stroke, with the disadvantage that none then Bleeding the hydraulic area can be made.
  • a control rod protruding outside the storage cylinder is arranged on the storage piston, with a longitudinal channel leading to the storage space, the end of which faces away from the storage space opens into a control space which is closed to the outside but is visible from the outside.
  • control room is arranged in a transparent control bush attached to the end of the control rod.
  • This control socket can be made of glass or plastic. In any case, it is very easy for the operator of the machine tool to determine an oil shortage.
  • control room can be vented to the outside via a venting device.
  • This ventilation device can advantageously be a bore which is conceivable as a continuation of the longitudinal channel through the control room.
  • that hydraulic connection between the storage space and the working space is formed as a transverse bore arranged in the machine housing, which is accessible from outside the machine housing and can be used for oil refilling. Depending on the position of the machine tool, this hole can also be used for ventilation.
  • the plunger is arranged coaxially with the working piston and can be actuated via a pneumatic piston against the force of a return spring. Especially when the storage space is not arranged around the plunger but at a distance and parallel to it, the working cylinder receiving the pneumatic piston of the plunger can be shortened, which means that the length of the machine tool can be shortened .
  • the pressure generator has a storage space which is arranged coaxially with the plunger, the common longitudinal axis being arranged parallel to that of the stepped piston, with a pressure channel connecting the pressure generator to the working space, after the end of the working stroke and corresponding afterflow of liquid the pressure channel is blocked by the plunger from the storage space into the working space, after which a high pressure can be generated in the working space when the plunger is lifted further.
  • a high pressure can be generated in the working space when the plunger is lifted further.
  • Figure 1 shows the first embodiment in longitudinal section.
  • Fig. 2 shows a variant of the first embodiment as
  • Embodiment also as a section
  • Fig. 4 shows the second embodiment
  • Fig. 5 shows the third embodiment as a detail.
  • All three exemplary embodiments work as stroke-controlled machine tools, each with a hydropneumatic pressure intensifier.
  • a pressure intensifier compressed air is used for a rapid traverse, namely the approach of the tool to the workpiece, whereas for the actual operation, a hydraulic high pressure is generated via a piston, which is also driven by compressed air, by means of which the tool is actuated.
  • a stepped piston 1 is present, the individual steps of which are formed by a working piston 2, a drive piston 3 and a piston rod 4.
  • the working piston 2 works in a working cylinder 5, which is part of the machine housing 6 and to which is connected a cylinder tube 7, in which the drive piston 3 works and on which a cylinder head 8 is arranged on the side facing away from the working cylinder 5, in its central bore the piston rod 4 is mounted.
  • the drive piston 3 is in a known manner on both sides by compressed air acted upon, causing a rapid traverse of this stepped piston in both stroke directions.
  • a plunger 9 is shown in the upper part of the machine tool, which plunger can be driven by a pneumatic piston 1 1 and which is shown in half in the drawing in two different diameters, each diameter of course causing a different oil displacement per lifting unit.
  • the pneumatic piston 11 works in a cylinder tube 12 which is placed on the machine housing 6 and is closed by a cylinder head 13.
  • the compressed air for actuating the pneumatic piston 11 is also supplied via this cylinder head 13, the adjustment taking place against a restoring force, which can be compressed air, for example, or can be a helical spring.
  • the plunger 9 dips with its free end into a space 14 which is connected to a working space 16 located below an annular seal 15, so that the plunger 9 separates the space 14 in front of the space 16 during its stroke movement and penetrates the annular seal 15 and correspondingly to it Cross-sectional area generates a corresponding hydraulic high pressure in the work space 16.
  • the space 14 is connected via a transverse bore 17 running in the housing 6 to a storage space 18 which is essentially arranged in a pneumatic cylinder 19 and is delimited at the top by a storage piston 21.
  • the storage piston 21 is loaded in the direction of the storage space 18 by a helical spring 22, which is supported on the side facing away from the storage piston 21 on a cylinder head 23 of the pneumatic cylinder 19.
  • a control rod 24, which penetrates outside the cylinder head 23 and penetrates it, is arranged on the accumulator piston, in which there is a control bore 25 which penetrates the entire control rod in the longitudinal direction and opens into a control chamber 26.
  • the control room 26 is in front all arranged in a screw nipple 27 made of transparent material such as plastic or glass, in order to be able to recognize from the outside whether air is in
  • Ventilation can be carried out via a ventilation bore 28.
  • a transparent protective tube 29 is placed coaxially around the control rod 24 on the cylinder head 23.
  • a piston collar 31 is arranged and there is an annular groove 32 in the working cylinder 5, which forms an annular space 33 towards the working piston 2 and has tapers 34 at its two ends, which corresponds to the diameter of the piston collar 31, such as it is shown on an enlarged scale in Fig. 2.
  • the piston collar 31 dips into this taper 34 towards the end of its forward stroke or its return stroke, it delimits a brake chamber designated here by 35.
  • the volume of fluid enclosed in this brake chamber is displaced via a throttle point, as is explained in detail for FIG. 2.
  • a bypass 40 which is only shown in dashed lines, can be arranged between the working space 16 and the storage space 17, 18, in which only a flow through a non-return valve in the direction of the working space 16 is possible, whereas the flow from the working space 16 to the storage space 17, 18 is locked.
  • the pressure generator having the plunger 109 is arranged parallel to the axis of the stepped piston 1, the storage space 118 is arranged coaxially to the plunger 109.
  • the "harmful space" of the working space is enlarged as a result, this has the advantage that the pressure generator is arranged next to the working cylinder to save space.
  • the working piston 102 has a head part 36 which is connected by screws 37 to the rest of the working piston 102 and in which bypass channels 38 and 39 are arranged, which separate the respective brake chamber 35 with the working chamber 116 (In Fig. 1 the work space 16) connect.
  • Check valves 41 are arranged in these bypass channels 38, 39 in the region of the mouth towards the working space 116, which only allow a flow in the direction of the braking space 35.
  • the working piston 102 assumes its upper starting position, that is, the position before the rapid stroke begins.
  • hydraulic oil can flow in from the working chamber 1 16 into the braking chamber via the bypass duct 38 or the check valve 41 arranged there, so that there is no obstruction of the drive.
  • the piston collar 31 is then swung out of the taper 34, a hydraulic connection is created between the annular space 33 and the working chamber 116, so that the piston collar 31 is freely movable.
  • the plunger 109 then driven plunges through the ring seal 115 into the Working space 1 16 and actuates the working piston 102 via a corresponding hydraulic high pressure.
  • the effect of the hydropneumatic pressure intensifier results from the cross-sectional difference between the plunger 109 with a relatively small cross-section and the working piston 102 with a relatively large cross-section.
  • a brake chamber 35 is formed there.
  • the bypass duct 39 branches off from this brake chamber 35, the connection to the working chamber 116 is blocked in this stroke direction by the check valve 41.
  • a relief channel 42 and 43 branches off from the brake spaces 35 and open into the annular space 33.
  • a throttle valve 44 is arranged in each of these relief channels. As soon as a corresponding pressure is created in the brake chambers 35 due to the piston collar 33, the trapped hydraulic fluid is displaced back into the annular space 33 via the relief channel 32 during the upper end stroke and via the relief channel 43 during the lower end stroke and in each case via the throttle valve 44. Because of this throttling effect, the remaining stroke of the working piston 102 is damped corresponding to the throttle cross section.
  • the throttle valve 44 is adjustable in cross section, so that this braking or damping effect can be adapted to the respective tool or its function.
  • Short-circuit channel 45 can be achieved, the mouth of which is arranged towards the annular space 33 on the lateral surface of the piston collar 31 and is only locked after a specific plunging stroke of this piston collar 31 into the taper 34. Since this short-circuit bore 35 is independent of the brake chamber 35, it has no influence on the braking, but has the advantage that when the working piston 102 is moved out of the illustrated top dead center position, rapid volume compensation between the annular space 33 and the working space 116 can take place at this rapid traverse.
  • a further variant of this first embodiment is shown, which largely corresponds to that of Fig. 2 and only has the difference that there is an annular gap between the piston collar 31 and the taper 34, through which the desired, but unchangeable throttling effect occurs , in that stroke movement hydraulic fluid is displaced into the annular space 33 from the brake chamber 35.
  • the variant shown here works like that from FIG. 2, particularly as far as the short-circuit channel 45 is concerned.
  • the braking device according to the invention is moved into the region of the piston rod 104.
  • the remaining parts such as the working piston 2, the plunger 9 and the drive piston 3 essentially correspond to the variant of the first exemplary embodiment, which is shown in FIG. 1. This also applies to their function.
  • the storage space 218, on the other hand, is arranged here in its central axis transverse to the axis of the stepped piston 201, but this has no influence on the function of this second exemplary embodiment.
  • the piston rod 104 here has a piston collar 46 which can be moved back and forth in an annular space 47 of the cylinder tube 107 is and limited in the respective stroke end positions by tapering 48 of the annular space 47 brake chambers 49.
  • These brake chambers 49 each have relief channels 51, which can be connected to one another, for example, but in which a throttle element is arranged.
  • the advantage of this second exemplary embodiment is above all that the area of the working piston with its changing hydraulic high pressures is not affected and that such a damping device can be fitted to a machine tool in a kind of modular system, only the cylinder tube 107 or the piston rod 104 correspondingly is designed differently.
  • the braking or damping device acts over the entire stroke of the stepped piston 301.
  • the working piston 302 is radially sealed off from its working cylinder 305 by ring seals 52, so that the resulting annular space 53 acts as a braking chamber , as soon as the hydraulic fluid present in this annular space 53 is throttled via a control channel 54 and a corresponding device.
  • the machine tool otherwise works as described for the first embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Abstract

L'invention a pour objet une machine-outil fonctionnant au moyen d'un multiplicateur de pression hydropneumatique, dont le piston à gradin (1) est freiné hydrauliquement, en particulier vers la fin de sa course, du fait que le fluide hydraulique est déplacé, via un point d'étranglement, à partir d'un espace de freinage (35) qui se forme durant la course du piston.
EP97920528A 1996-03-19 1997-03-19 Machine-outil hydropneumatique Expired - Lifetime EP0828942B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19610726 1996-03-19
DE19610726 1996-03-19
PCT/DE1997/000559 WO1997035114A1 (fr) 1996-03-19 1997-03-19 Machine-outil hydropneumatique

Publications (2)

Publication Number Publication Date
EP0828942A1 true EP0828942A1 (fr) 1998-03-18
EP0828942B1 EP0828942B1 (fr) 2000-08-09

Family

ID=7788718

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97920528A Expired - Lifetime EP0828942B1 (fr) 1996-03-19 1997-03-19 Machine-outil hydropneumatique

Country Status (4)

Country Link
US (1) US5943862A (fr)
EP (1) EP0828942B1 (fr)
DE (2) DE19780220D2 (fr)
WO (1) WO1997035114A1 (fr)

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EP0828942B1 (fr) 2000-08-09
US5943862A (en) 1999-08-31
DE59702132D1 (de) 2000-09-14
DE19780220D2 (de) 1998-03-19
WO1997035114A1 (fr) 1997-09-25

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