EP3443229B1 - Radialschmiedemaschine mit hydraulikzylinder - Google Patents

Radialschmiedemaschine mit hydraulikzylinder Download PDF

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Publication number
EP3443229B1
EP3443229B1 EP17715115.6A EP17715115A EP3443229B1 EP 3443229 B1 EP3443229 B1 EP 3443229B1 EP 17715115 A EP17715115 A EP 17715115A EP 3443229 B1 EP3443229 B1 EP 3443229B1
Authority
EP
European Patent Office
Prior art keywords
machine according
cylinder
spaces
fluid
reshaping machine
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.)
Active
Application number
EP17715115.6A
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German (de)
English (en)
French (fr)
Other versions
EP3443229A2 (de
Inventor
Karsten Busch
Paul-Josef Nieschwietz
Frederik Knauf
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.)
SMS Group GmbH
Original Assignee
SMS Group GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP3443229A2 publication Critical patent/EP3443229A2/de
Application granted granted Critical
Publication of EP3443229B1 publication Critical patent/EP3443229B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid 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
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working 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
    • F15B11/02—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
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1428—Cylinders
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • 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
    • F15B2211/7055—Linear output members having more than two chambers
    • 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
    • F15B2211/75—Control of speed of the output member
    • 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 relates to a forming machine according to claim 1.
  • DE 198 46 348 A1 describes a forging press in which hydraulic cylinders are provided as drive units for forming tools. Such hydraulic cylinders allow both a large force and a large travel distance. The provision of these properties requires a correspondingly high delivery rate of a hydraulic pump.
  • a hydraulic cylinder is generally understood to mean an actuator driven by a hydraulic, preferably liquid, fluid.
  • the fluid is preferably a hydraulic oil, as is usually used in hydraulic cylinders.
  • the cylinder of the hydraulic cylinder does not necessarily have a circular cross-section, so that the term "cylinder" in the present case relates to the function and not necessarily to a geometric shape.
  • a circular cross-section of the cylinder is preferred.
  • the cylinder can also have an elliptical cross-section. This would prevent the piston member from rotating in the cylinder.
  • any transverse forces that may occur can be better absorbed.
  • an active surface is a surface of the piston member on which the working pressure of the fluid can act in order to press the piston member in the active direction.
  • the physical effective surface does not have to run flat and perpendicular to the effective direction, but only its projected portion perpendicular to the effective direction contributes to the driving force of the piston member.
  • a cylinder space within the meaning of the invention is the entire space that the fluid fills in the cylinder depending on the position of the piston member.
  • the entire cylinder space does not necessarily have to be under the working pressure of the fluid.
  • one of the sub-spaces can also be pressure-free or essentially under atmospheric pressure. If necessary, both sub-spaces can also be under different working pressures. In the context of the invention, more than two sub-spaces that are hydraulically separated from one another can also be provided.
  • a ratio of the sizes of the two partial areas can be adapted as required.
  • a ratio in the range between 50:50 and 20:80 is appropriate for many applications.
  • a ratio of the partial areas is asymmetrical and is between 45:55 and 20:80, particularly preferably between 40:60 and 20:80. This enables a targeted application of fluid to the subspaces, for example even during a forging process.
  • a starting block is short and large in diameter. Heat loss is then low due to the surface-to-volume ratio. This means that in such a case, forging can be carried out with a low stroke frequency, but large pressing forces are required. If the starting block is reshaped to a final geometry in the course of forging, it cools down more quickly. This requires a higher stroke frequency, but the required pressing force is no longer so great because the pressed area becomes smaller.
  • the subspaces run concentrically around a central axis of the cylinder.
  • a particularly cylindrical step for separating the sub-spaces protrudes parallel to the direction of action on one of the two, piston member or cylinder.
  • the one sub-space can form a fully cylindrical space which is surrounded by the second sub-space in the form of an annular cylinder, which is also arranged offset in the effective direction with respect to the first sub-space.
  • the sub-spaces are connected to a hydraulic pump unit and a valve arrangement, the valve arrangement enabling fluid to be applied to the sub-spaces in at least two operating modes.
  • most or all of the hydraulically switching components can thereby be arranged outside the hydraulic cylinder.
  • the valve arrangement comprises a control valve with a pilot piston that can be displaced in the effective direction.
  • pilot pistons as control valves are, for example, from the aforementioned DE 198 46 348 A1 known and allow a quick and precise control of the hydraulic cylinder.
  • the pilot piston closes an outlet of the cylinder as it is advanced, which in turn leads to a pressure build-up and advance of the piston member.
  • one of the sub-spaces can be connectable to a hydraulic reservoir through the valve arrangement.
  • the hydraulic reservoir is pressureless. This ensures filling and emptying of the subchamber not acted upon by working pressure in the course of the piston movement, so that the second subchamber can be quickly charged with fluid under working pressure at any time.
  • freedom from pressure in the hydraulic reservoir means that either atmospheric pressure or a higher pressure is present in the reservoir in order to ensure rapid fluid exchange.
  • the hydraulic reservoir can in particular be designed as a pressure accumulator in the form of a hydraulic accumulator.
  • the accumulator can be implemented, for example, as a spring accumulator or in some other way. In principle, however, it is also possible for the hydraulic reservoir to be pressurized if this is necessary.
  • At least one of the partial spaces can be acted upon by the fluid by means of a valve arranged downstream of the partial space.
  • the valve When the valve is open, the fluid then flows through the subchamber or a branch without pressure, and when the valve is closed or throttled, the respective subchamber is correspondingly pressurized.
  • the hydraulic cylinder It is generally advantageous for the hydraulic cylinder to have a restoring active surface, the piston member being resettable against the direction of action by acting on the restoring active surface with the fluid. This allows a simple hydraulic return of the piston member.
  • the provision can also be implemented in other ways, depending on the requirements.
  • the present invention shows considerable advantages in the case of large hydraulic cylinders, since there is considerable effort involved in providing the hydraulic pumps and the electrical supply. Accordingly, it is advantageously provided that the entire effective area of the piston member is at least 1000 cm 2 , in particular at least 2000 cm 2 .
  • the working pressures of the fluid are chosen conventionally and are typically in the range between 200 and 500 bar.
  • Preferred maximum forces of the piston member are more than 3 MN, preferably between 5 and 30 MN or more.
  • three or more hydraulically separable sub-spaces are provided with their respective associated sub-surfaces of the piston member. This allows a further differentiation of the pressing forces and stroke speeds of the piston member.
  • the subspaces can each run concentrically to one another. A separation of the subspaces can take place in a similar way to designs with only two subspaces by means of corresponding gradations on the piston member and / or cylinder.
  • the invention relates to a forming machine for shaping a workpiece, the forming machine being designed as a radial forging machine, and wherein a tool of the radial forging machine can be subjected to a forming force by means of a hydraulic cylinder as defined in claim 1.
  • the forming force is exerted by several hydraulic cylinders so that no additional mechanical power transmission, such as a shaft, is required.
  • Such a design of the forming machine is particularly favored by the flexibility of the hydraulic cylinder defined in claim 1.
  • the forming machine is designed as a radial forging machine.
  • the radial forging machine particularly preferably comprises at least four tools that work against one another in pairs.
  • the workpiece in a first operating mode, is finished while only one of the subspaces is exposed to fluid under working pressure, whereas in a second operating mode of the forming machine, the workpiece is forged while both subspaces are exposed to fluid under working pressure. This allows the same forming machine to be used effectively for different forming processes.
  • a hydraulic cylinder as defined in claim 1 can be designed as a replacement for a conventional hydraulic cylinder in existing forming machines.
  • a variable ratio of the partial areas enables the greatest possible flexibility with regard to achievable stroke rates, which is particularly advantageous when forming temperature-critical materials.
  • By dividing the partial areas in combination with suitable forging strategies it is possible to reduce the installed power and thus save energy while at the same time achieving comparable productivity. It is also advantageous that the partial areas can also be divided up for existing systems.
  • the advantage of saving energy is even greater when using an energy storage device, for example in the form of a flywheel, which stores energy when idling and releases it when required.
  • the invention can be used independently of the forging strategy. For example, it is possible to use a conventional strategy such as that used in open die forging, which is characterized by a large feed rate without rotating the workpiece, but using four tools that act on the workpiece at the same time. When using this forging strategy, high numbers of strokes can be easily achieved. When using the invention in combination with a strategy in which two opposing tools of a radial forging machine act on the workpiece, high Stroke numbers can be realized in connection with a further optimized core forging.
  • productivity can be increased again.
  • the in Fig. 1 The hydraulic cylinder 1 shown comprises a cylinder 2 in which a piston member is guided so as to be linearly displaceable along an effective direction W.
  • the piston member 3 has a cylindrical step 3 a, which protrudes into a corresponding step of the cylinder 2. This hydraulically creates a first sub-space 4 is defined over a first partial surface 5 of an active surface of the piston member 3.
  • the first subspace essentially has the shape of a full cylinder.
  • the first subchamber 4 is hydraulically separated by the step 3a from a second subchamber 6 over a second subarea 7 of the active area of the piston member 3.
  • the second sub-space 6 essentially has the shape of an annular cylinder.
  • the partial spaces 4, 6 together form a cylinder space of the cylinder 2.
  • the effective area of the piston member 3 is the sum of the partial areas 5, 7.
  • the size of the partial spaces 4, 6 varies depending on the current position of the piston member 3 in the cylinder 2.
  • Each of the sub-spaces 4, 6 has a respective opening 4a, 6a through which a hydraulic fluid can flow into the sub-space 4, 6.
  • the openings 4a, 6a are connected via hydraulic lines 8 to a valve arrangement 9 and a hydraulic pump unit (not shown).
  • a direction of flow of the fluid when working pressure is applied by the pump unit is shown as arrow P.
  • the sub-spaces 4, 6 are hydraulically separated from one another according to the above explanations, but can be hydraulically connected to one another depending on the design of the valve arrangement 9 if necessary.
  • the valve arrangement 9 starting from the pump unit, comprises a first branch 10, a first valve 11 downstream of it and a second branch 12 downstream of it the fluid is acted upon under working pressure.
  • the second branch 12 leads on the one hand to the second subchamber 6 and on the other hand to a reservoir 13, which is through a second valve 14 between the second branch 12 and the reservoir 13 can be shut off.
  • the reservoir is filled with fluid at essentially atmospheric pressure.
  • a drain 15 of the first subchamber 4 leads back to a sump and / or an intake side of the pump unit.
  • the outlet 15 can be controllably closed by a pilot piston 16 that is drivably displaceable in the effective direction W, so that the pilot piston 16 forms a control valve of the valve arrangement 9 with the outlet 15.
  • the position of the piston member 3 in the effective direction is set via the pilot piston 16.
  • the pilot piston 16 is also hydraulically driven in the present case, but can also have an electric motor or some other drive, depending on the requirements.
  • a significantly smaller, restoring force is also applied to the piston member 3 via a restoring active surface 17 in a restoring space 18.
  • the restoring active surface 17 is also acted upon by fluid under working pressure. In contrast to the two sub-spaces, the working pressure of the fluid does not act in the effective direction, but in the opposite direction.
  • the invention now works as follows: In a first operating mode, the first valve 10 is closed and the second valve 14 is open. As a result, only the first subchamber 4 is supplied with fluid under working pressure from the pump unit. the second subchamber is connected to the reservoir 13 via the second valve. This ensures a constant filling with fluid under atmospheric pressure or a slightly higher pressure to improve a flow rate.
  • the first valve 10 is open and the second valve 14 is closed.
  • the reservoir 13 is no longer connected to the cylinder 2, and the two sub-spaces 4, 6 are hydraulically connected in parallel.
  • a simplified valve arrangement 9 without a pilot piston 16 is selected.
  • Components with the same function are provided with the same reference symbols as in the first example.
  • the piston member 3 is shown hatched in the schematic drawing.
  • a cylindrical, protruding step 2a is formed in this example as part of the cylinder 2, so that the piston member essentially has the shape of a cup. This choice of shape is independent of the design of the valve arrangement 9.
  • valve arrangement 9 has a first branch 19 which leads to the first subchamber 4.
  • a valve 20 is arranged downstream of the branch 19.
  • the second subchamber 6 and the restoring chamber 18 are charged directly with fluid and have drains 21, 22.
  • Valves 23, 24 are arranged behind the drains 21, 22, respectively.
  • one of the sub-spaces 4, 6 or the reset space 18 is acted upon with fluid under working pressure precisely when the valve 20, 23, 24 assigned to it is closed.
  • the respective valve 20, 23, 24 is opened, the fluid flows in a circle without pressure build-up. Accordingly, the three feeds P are each connected separately to carry pressure and are not connected in parallel to one another. This can be achieved, for example, by using separate hydraulic pumps.
  • the modes of operation of the hydraulic cylinder according to the second example are completely analogous to those of the first example.
  • a hydraulic cylinder 1 according to one of the types described above is designed as part of a forming machine in the form of a radial forging press (not shown).
  • the working pressure of the fluid is around 400 bar.
  • the size ratio of the two partial areas 5, 7 is approximately 50:50.
  • the forming machine comprises four tools working in pairs against one another in a cross shape, each of the tools being driven by a hydraulic cylinder 1 described above.
  • a switch is made between the operating modes in order to move the tools quickly over longer distances while no forming takes place. This can take place, for example, in the course of a workpiece feed and allows the forging process to be accelerated overall.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Forging (AREA)
EP17715115.6A 2016-04-11 2017-03-31 Radialschmiedemaschine mit hydraulikzylinder Active EP3443229B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016205973.4A DE102016205973A1 (de) 2016-04-11 2016-04-11 Hydraulikzylinder
PCT/EP2017/057708 WO2017178249A2 (de) 2016-04-11 2017-03-31 Hydraulikzylinder

Publications (2)

Publication Number Publication Date
EP3443229A2 EP3443229A2 (de) 2019-02-20
EP3443229B1 true EP3443229B1 (de) 2021-11-10

Family

ID=58464552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17715115.6A Active EP3443229B1 (de) 2016-04-11 2017-03-31 Radialschmiedemaschine mit hydraulikzylinder

Country Status (6)

Country Link
US (1) US11167338B2 (ru)
EP (1) EP3443229B1 (ru)
JP (1) JP2019516934A (ru)
CN (1) CN109072953A (ru)
DE (1) DE102016205973A1 (ru)
WO (1) WO2017178249A2 (ru)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022206855A1 (de) 2022-06-30 2024-01-04 Sms Group Gmbh Schmiedestrategie SMX

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201900012969A1 (it) * 2019-07-26 2021-01-26 Mecolpress S P A Apparecchiatura per lo stampaggio di materiali.

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US3186305A (en) * 1963-07-02 1965-06-01 Ex Cell O Corp Hydraulic actuator mechanism
DE2220180A1 (de) * 1972-04-25 1973-11-08 Geb Maier Gisela Bieber Hydraulischer zylinder ohne durchgehende kolbenstange mit gleichen vorschubund rueckzugflaechen, sowie mit schnellgangeinrichtung
PT68274A (en) * 1978-07-11 1978-08-01 A A Ribeiro De Almeida Device applicable to presses and metal bending presses to syncronize the movements of the hydraulic cylinders and control slider cross member
JPH0814212A (ja) * 1994-04-26 1996-01-16 Mitsubishi Plastics Ind Ltd マルチキャビティシリンダー
JPH08334102A (ja) * 1995-06-07 1996-12-17 Nikko Tokki Kk 増力機構及び鍛造機
DE19543876A1 (de) * 1995-11-24 1997-05-28 Rexroth Mannesmann Gmbh Verfahren und Vorrichtung zur Ansteuerung einer Hydroanlage eines Arbeitsgerätes
ATE211036T1 (de) * 1997-10-15 2002-01-15 Sms Eumuco Gmbh Hydraulisches antriebssystem für stössel von schmiedepressen oder schmiedemaschinen
US6240758B1 (en) * 1999-06-21 2001-06-05 Toyokoki Co., Ltd. Hydraulic machine
JP3782710B2 (ja) * 2001-11-02 2006-06-07 日邦興産株式会社 油圧プレス装置
JP3782725B2 (ja) * 2001-12-06 2006-06-07 カヤバ工業株式会社 油圧シリンダ
NL1025806C2 (nl) * 2004-03-25 2005-09-27 Demolition And Recycling Equip Hydraulische cilinder bijvoorbeeld voor toepassing bij een hydraulisch gereedschap.
DE102009052531A1 (de) * 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
CN201526558U (zh) * 2009-11-17 2010-07-14 姚国志 可变压变速的双缸串连液压油缸
JP2012002272A (ja) * 2010-06-16 2012-01-05 Takayoshi Numakura 油圧シリンダ及び油圧駆動装置
CN103752747A (zh) * 2014-01-16 2014-04-30 焦作市华科液压机械制造有限公司 一种机液径向锻造机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022206855A1 (de) 2022-06-30 2024-01-04 Sms Group Gmbh Schmiedestrategie SMX

Also Published As

Publication number Publication date
EP3443229A2 (de) 2019-02-20
WO2017178249A2 (de) 2017-10-19
WO2017178249A3 (de) 2017-12-14
US11167338B2 (en) 2021-11-09
DE102016205973A1 (de) 2017-10-12
US20190217373A1 (en) 2019-07-18
JP2019516934A (ja) 2019-06-20
CN109072953A (zh) 2018-12-21

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