EP2540452A1 - Mécanisme de percussion pneumatique avec volumes d'amortisseur pneumatique séparés - Google Patents

Mécanisme de percussion pneumatique avec volumes d'amortisseur pneumatique séparés Download PDF

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Publication number
EP2540452A1
EP2540452A1 EP12003954A EP12003954A EP2540452A1 EP 2540452 A1 EP2540452 A1 EP 2540452A1 EP 12003954 A EP12003954 A EP 12003954A EP 12003954 A EP12003954 A EP 12003954A EP 2540452 A1 EP2540452 A1 EP 2540452A1
Authority
EP
European Patent Office
Prior art keywords
air spring
drive
air
piston
air chamber
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.)
Withdrawn
Application number
EP12003954A
Other languages
German (de)
English (en)
Inventor
Helmut Braun
Philip Overfeld
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.)
Wacker Neuson Produktion GmbH and Co KG
Original Assignee
Wacker Neuson Produktion 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 Wacker Neuson Produktion GmbH and Co KG filed Critical Wacker Neuson Produktion GmbH and Co KG
Publication of EP2540452A1 publication Critical patent/EP2540452A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0023—Pistons

Definitions

  • the invention relates according to claim 1, a Lucasfedertschwerk that can be used, for example, in a departure, impact and / or hammer drill.
  • air spring impact devices in break-away, impact and / or hammer drills is well known.
  • a drive piston is driven by a suitable drive, e.g. from an operated by an electric motor crank mechanism, offset in an oscillating axial movement.
  • the oscillating axial movement can then be converted into a pushing movement of a tool, for example a chisel.
  • a striking piston is arranged between the drive piston and the tool.
  • the drive piston and the percussion piston can be sealed against each other and against a striking mechanism housing with the aid of seals, for example with gap seals, so that an air spring can form at high relative speeds between the drive piston and the percussion piston due to the trapped air volume.
  • the oscillating axial movement of the drive piston can be transmitted by the air spring on the percussion piston, so that the percussion piston can act on a provided for example on the tool impact device.
  • the drive piston is accelerated by the drive, for example, from an extreme position (top dead center of the drive piston) facing away from the percussion piston in the direction of the percussion piston, the air volume trapped between drive piston and percussion piston can be compressed and an air spring can be formed. About the compressed air spring, a thrust of the drive piston is transmitted to the percussion piston, so that it can act for example, arranged on the tool impactor or an anvil and transmits the pulse to the tool.
  • the percussion piston can be set in a return movement in the direction of the drive piston.
  • the return movement of the percussion piston can be additionally reinforced by a return movement of the drive piston when the drive piston is moved by the drive from an extreme, the percussion piston facing position (bottom dead center of the drive piston) in the direction of its top dead center.
  • a negative pressure in the trapped between the drive piston and percussion piston air volume can arise and thereby form a stretched air spring, which can exert a suction effect on the percussion piston and strengthen its return movement.
  • the speed, with which the percussion piston is moved in the direction of the drive piston, and also the distance that he travels, depend on the one hand on recoil and on the other hand on the suction effect of the air spring.
  • the impact energy with which the percussion piston can act on the tool in the further impact cycle is determined by the velocity of the percussion piston at impact and by its mass.
  • the speed of the percussion piston upon impact in turn depends on the speed of the percussion piston during the return movement (racket return speed) and on the time of the maximum air spring compression since the percussion piston in the further percussion cycle is accelerated by the drive piston by means of the compressed air spring over the distance traveled in the return movement can.
  • the racket return speed is therefore determinative of the achievable impact energy.
  • the racket return speed depends on the energy absorption capacity of the substrate or rock to be processed. If the substrate to be processed consumes little energy, the percussion piston rebounds at a high reverse speed. Such substrates are marked with a high recoil number. If, on the other hand, the underground absorbs a lot of energy, the percussion piston rebounds at a low reverse speed. Such substrates are marked with a low recoil number. In extreme cases, the percussion piston can remain on the tool without being pushed back.
  • the racket return speed depends on the negative pressure of the air spring when sucking the racket.
  • This negative pressure is critical in a weak or non-existent recoil, for example, on a background with a low recoil number.
  • the negative pressure in the air spring and thus the remindsaugkraft depend greatly on the geometry of the air spring from, for example, the piston stroke, the surface and the length of the air spring.
  • the invention is therefore an object of the invention to provide an air spring impact that provides improved impact energy for the treatment of substrates with different recoil numbers.
  • An air spring impact mechanism has an axially reciprocable, drivable by a drive drive element, an axially reciprocable striker for striking a tool and acting between the drive element and the impact element or arranged air spring device, wherein a movement of the drive element on the Impact element is transferable by the air spring device.
  • the air spring device has a first air chamber adjoining the drive element and a second air chamber adjoining the first air chamber and the striking element, wherein an axially reciprocable separating element is arranged between the first and the second air chamber.
  • a mobility of the separating element relative to the drive element is bounded on one side by a coupling device such that a predetermined maximum distance between the separating element and the drive element can not be exceeded.
  • the drive may include a motor, such as an electric or an internal combustion engine.
  • the drive torque generated by the drive can be transmitted in a known manner, for example via a crank mechanism or a wobble gear to the drive element and put this in an axial oscillation movement.
  • the axial oscillatory movement of the drive element can be transmitted by the air spring device to the striking element, so that this is also set in an axial oscillation movement.
  • the axial oscillatory movement of the impact element can be used to impact the impact element on the tool, for example on an impact device or an anvil provided at one end of the tool.
  • the drive element Upon movement of the drive element from top dead center toward bottom dead center, for example, when the striking element is stationary, it moves more slowly than the drive element or moves toward the drive element, in the air spring device and in particular in the first and second air chambers build up, through which the trapped air volume is compressed.
  • a largely uniform compression of the trapped air volume of the first and second air chamber is made possible by the axially reciprocable separating element, which is axially movable relative to both the drive element and relative to the striking element in this subsection of thenamszyklusseses.
  • the trapped in the first and second air chambers air volumes can thus act together as a combined, uniform air spring and transmit a thrust of the drive element to the striking element.
  • the striking element can thereby be moved in the direction of the tool and in particular in the direction of a point of impact on the tool or the impact device.
  • the impact member may be repelled by a recoil of the tool and be placed in a movement from the impact point in the direction of the drive element.
  • the drive element may be in this moment still in a movement in the direction of its bottom dead center, have reached this or have already been forced by the drive in a movement to its top dead center.
  • the first air chamber can expand because of the separating element that can still be moved freely relative to the drive element and to the striking element. Due to the expansion of the predetermined maximum distance between the drive element and the separating element can be achieved.
  • the coupling device can couple the separating element with the drive element.
  • the mobility of the separating element relative to the drive element can be limited on one side and a further expansion of the air volume located in the first air chamber can be prevented.
  • essentially ambient pressure can prevail in the first air chamber.
  • the air volume located in the second air chamber is not limited, can form by the return movement of the separating element in the second air chamber, a sucking air spring, which can be transmitted to the striking element by the suction, the movement of the separating element.
  • the striking element is therefore sucked back by the air spring formed in the second air chamber in the direction of its top dead center.
  • the coupling device has a blocking element coupled to the separating element.
  • the blocking element may have a projection, a nose, a blocking body, a locking disk or the like and be coupled to the separating element, for example, by a coupling rod or by a wire rope.
  • the mobility of the separating element relative to the drive element can be limited in this embodiment by a one-sided positive engagement of the locking element with the drive element.
  • This positive connection can be achieved for example by placing the mounting plate or Aufsetzklotzes on the drive element when the predetermined maximum distance between the separating element and the drive element is reached. The placement may cause a further movement apart of the separating element and the drive element and thus an enlargement of the first air chamber is prevented even in a further, acting on the separating element and / or the drive element in each case opposite train.
  • the form fit only acts on one side, since, for example, a movement toward one another of the separating element and of the drive element is not effected or must be due to the positive connection.
  • the drive element and / or the blocking element can be designed in this embodiment such that the one-sided positive locking is favored.
  • the drive element may have a surface on which the stop element designed as a stopper can seat, or a recess which corresponds to the shape of the stopper element.
  • the volume of the second air chamber may be substantially less than the volume of the first air chamber in a rest state of the air spring impact mechanism, for example, when the drive is stopped. Since the air volumes of the first and second air chambers during a Schlagzyklusses change due to the relative movements between the drive element, impact element and separating element, the volume can be considered at rest. For example, in the resting state, the impact element may be at the theoretical impact point, for example with support on the impact device, and the beater may be at bottom dead center. Furthermore, in the idle state, substantially ambient pressure prevails in the first and second air chambers.
  • the volume of the first air chamber may be substantially two or three times as large as that of the second air chamber.
  • this order of magnitude is to be understood as an example, other embodiments may be possible depending on the geometry of the air chambers, mass of the drive and the percussion piston, nature of the tool and nature of the substrates to be processed.
  • the second air chamber has a small volume, it can be particularly effective in the above-described second phase with coupling of the separating element to the drive element.
  • a strong suction can form, so that a high racket return speed can be achieved and thus a blow with high impact energy can be prepared.
  • the advantages of a short air spring when sucking back the striking element can be combined with those of a long air spring in the impact preparation and in a strong recoil.
  • a powerful suckback possible in decompression of the air springs, for example in the second phase described above, whereas in compression of the air springs effective transmission of the thrust and thus a higher single impact energy and high tolerance to different strong rebounds and thus a protection of the operator and the Air striker having working device is achieved.
  • lower vibrations are achieved by the joint action of the air springs in the first and the second air chamber.
  • there is a lower maximum pressure in the two air chambers in the air spring compression the lower operating temperatures caused and the seals less loaded. Consequently, lower air losses occur, for example, in the event of a leak in one of the air chambers.
  • the blocking element is arranged on the side of the drive element which is opposite to the separating element.
  • the separating element can be guided, for example, in a guide cylinder for axially guiding the drive element and / or the striking element.
  • the separating element may be formed by a cutting disc which is substantially tightly fitted in the guide cylinder and which is arranged between the drive element and the striking element. The separating disk substantially separates the first and second air chambers from each other.
  • the drive element can be arranged within a hollow cylinder.
  • the separating element can be formed by a bottom of the hollow cylinder and the blocking element have a projection arranged in the interior of the hollow cylinder.
  • the coupling of the separating element ie the bottom of the hollow cylinder, may be formed with the arranged in the interior of the hollow cylinder blocking element by a conversion of the hollow cylinder. This allows a robust connection of the blocking element with the separating element.
  • a movement of the drive element takes place completely in the interior of the hollow cylinder.
  • the hollow cylinder itself is axially movable relative to the drive element.
  • the mobility of the hollow cylinder relative to the drive element is limited on one side by the blocking element.
  • the projection can prevent a disengagement of the drive element and the hollow cylinder by a one-sided positive locking.
  • a second air spring in a push phase, in which the drive element is moved by the drive in the direction of the impact element, in the first air chamber, a first air spring and in the second air chamber, a second air spring may be formed.
  • a thrust of the drive element via the first air spring is transmitted to the separating element and from the separating element via the second air spring on the striking element.
  • a thrust of the drive element in the direction of the striking element is in this case transmitted by the joint effect of the two air springs on the striking element.
  • a train of the drive element in a traction phase in which the drive element is moved away from the impact element by the drive, a train of the drive element can be transmitted to the separating element via the coupling device and to the striking element from the separating element via the second air spring.
  • the coupling device which couples the separating element with the drive element on one side. The movement of the drive element can therefore be effectively transmitted to the striker via the comparatively short second air spring.
  • a working device has a pipe impact mechanism, a hollow piston impact mechanism or a hollow impact impactor according to one of the preceding claims.
  • the air springs formed in the first and second air chambers act together, while in a decompression, the expansion of the air spring formed in the first air chamber is limited by the one-sided coupling of the separating element with the drive element.
  • Fig. 1 schematically shows an air spring impact mechanism in which a drive torque of a drive motor (not shown) via a crank mechanism 1 on a guided in a guide cylinder 2, axially reciprocable drive piston 3 is transferable.
  • the crank mechanism 1 may, for example, have an eccentric disk which can be driven by a motor shaft and has a connecting rod fastened thereto. Due to the transmission of the drive torque, the drive piston 3 can be displaced into an axial oscillation movement between a top dead center located in the direction of the crank drive 1 and a bottom dead center of the drive piston 3 located in the opposite direction.
  • the axial oscillation movement of the drive piston 3 can be transmitted by an air spring device to a percussion piston 4 also guided in the guide cylinder 2, so that the latter also performs an axial oscillation movement.
  • a tool 5 such as a chisel or a drill can be acted upon, which can be used for example for processing a substrate.
  • the air spring device has in the in Fig. 1 shown embodiment, a first air chamber 6a and a second air chamber 6b.
  • the first air chamber 6a adjoins a front end face of the drive piston 3, while the second air chamber is adjacent to a rear end face of the percussion piston 4.
  • Both air chambers 6a, 6b are adjacent to each other separated by an axially movable in the guide cylinder blade 7.
  • a predetermined maximum distance M between the drive piston 3 and the cutting disc 7 is limited.
  • a mobility of the blade 7 relative to the drive piston 3 is therefore limited on one side, since the blade 7 in the in Fig. 1 shown position can not be moved away from the drive piston 3.
  • Fig. 1 shows the embodiment in a pulling phase in which the drive piston 3 by the crank mechanism 1 moves away from the percussion piston 4, so moved upwards becomes.
  • a train transmitted to the drive piston 3 by the crank drive 1 is transmitted to the separation plate 7 via the blocking body 9 forming the one-sided positive engagement with the drive piston 3 and the coupling rod 8 connected thereto.
  • the air volume trapped in the first air chamber 6a therefore no longer acts as an air spring.
  • the transmitted to the blade 7 train can lead to an expansion of the air volume located in the second air chamber 6 b, which forms a suction and thus an air spring in the second air chamber 6 b.
  • the train can be transferred to the percussion piston 4 and move it in the direction of the drive piston 3 upwards.
  • the train can be effectively transmitted to the percussion piston 4. It forms the negative pressure quickly even with low piston stroke. Consequently, even with a small transmitted from the tool 5 to the percussion piston 4 recoil the percussion piston 4 can be effectively moved in the direction of the drive piston 3.
  • Fig. 2 shows the air spring impact mechanism Fig. 1 in a pushing phase, in which the drive piston 3 is pushed by the crank mechanism 1 in the direction of the percussion piston.
  • the unilateral positive connection of the locking element 9 with the drive piston 3 in this case does not act or is released, so that the drive piston 3 can be moved freely in the direction of the cutting disc 7 and the percussion piston 4.
  • the air volume located in the two air chambers 6a, 6b is compressed and the thrust is transmitted to the percussion piston 4.
  • the drive piston 3 is arranged axially movable within a hollow cylinder 10.
  • the hollow cylinder 10 is in turn likewise arranged axially movable in the guide cylinder 2.
  • the drive piston 3 is therefore relatively movable to the hollow cylinder 10.
  • this relative mobility is limited on one side by stops 11a, 11b serving as stops, which are arranged inside the hollow cylinder 10.
  • the projections 11a, 11b may also be formed uniformly as a ring.
  • the first air chamber 6a Within the hollow cylinder 10, between a bottom of the hollow cylinder 10 and the drive piston 3 is the first air chamber 6a, which is separated by the bottom of the hollow cylinder 10 from the located between the bottom of the hollow cylinder 10 and the percussion piston 4 second air chamber 6b.
  • the bottom of the hollow cylinder 10 thus forms a separating element between the first air chamber 6a and the second air chamber 6b.
  • the projections 11a, 11b limit the mobility of the bottom of the hollow cylinder 10 to the drive piston 3 in such a way that here also a predetermined maximum distance between the bottom of the hollow cylinder 10 and the drive piston 3 can not be exceeded.
  • the maximum distance between the drive piston 3 and the bottom of the hollow cylinder 10 has not yet been reached.
  • the air chambers 6a and 6b may still prevail overpressure.
  • essentially ambient pressure can prevail in the first and second air chambers 6a, 6b.
  • the projections 11a, 11b can then form with the drive piston 3 unilaterally acting form-fitting, through which the movement of the drive piston 3 can be transmitted to the hollow cylinder 10.
  • the second air chamber 6 b can then be formed by decompression of the trapped air volume, a short air spring through which the movement of the drive piston 3 is effectively transferred to the percussion piston 4.
  • Fig. 4 corresponds in large part to in Fig. 1 shown.
  • a tension element 12 such as a wire rope coupled to the drive piston 3.
  • the tension element 12 limits in this embodiment, on one side, the mobility of the cutting disk 7 relative to the drive piston 3, whereby the drive piston 3 is coupled to the cutting disc 7 in the shown portion of theabsoluszyklusses.
  • this coupling does not exist, so that the cutting disc 7 is movable relative to the drive piston 3 on both sides.
  • a further embodiment is shown in the form of a hollow bat impactor.
  • the percussion piston 4 is formed in this embodiment as a hollow piston in which the drive piston 3 and the drive piston 3, for example, by the tension element 12 coupled cutting disc 7 are embedded.
  • the cutting disc 7 is on one side coupled by the tension member 12 with the drive piston 3 such that transmitted by the crank mechanism 1 on the drive piston 3 train is transmitted through the tension member 12 on the cutting disc 7.
  • the train can then be transmitted to the percussion piston 4 by the second air spring forming in the second air chamber 6b by decompression.
  • the coupling can be solved.
  • the cutting disk 7 can then be moved relative to the drive piston on both sides and the air springs formed in the two air chambers 6a and 6b can cooperate.
  • Fig. 6 shows a further embodiment in the form of a hollow Schläger impact.
  • the drive piston 3 is designed as a hollow piston, in which the cutting disc 7 and the percussion piston 4 are embedded. Also in this embodiment, the cutting disc 7 is coupled to the drive piston 3 by the tension member 12 such that a mobility of the cutting disc 7 is limited relative to the drive piston 3 on one side.
  • the air spring means can be an effective suction effect of a short air spring (the second air spring formed in the second air chamber 6b by decompression second air spring) with a good absorption effect and thrust transmission of a long air spring (common effect of formed in the first and second air chambers 6a, 6b air springs) be combined.
  • This design allows a powerful suckback regardless of a recoil number of a machined underground.
  • the resulting air spring impactor is more tolerant of various substrates and especially for use on surfaces with a low recoil number.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP12003954A 2011-06-27 2012-05-21 Mécanisme de percussion pneumatique avec volumes d'amortisseur pneumatique séparés Withdrawn EP2540452A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011105600A DE102011105600A1 (de) 2011-06-27 2011-06-27 Luftfederschlagwerk mit geteiltem Luftfedervolumen

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EP2540452A1 true EP2540452A1 (fr) 2013-01-02

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EP12003954A Withdrawn EP2540452A1 (fr) 2011-06-27 2012-05-21 Mécanisme de percussion pneumatique avec volumes d'amortisseur pneumatique séparés

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DE (2) DE202011110340U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110573305A (zh) * 2017-05-05 2019-12-13 费希尔厂有限责任两合公司 安装工具
US10816910B2 (en) 2016-03-03 2020-10-27 Asml Netherlands B.V. Vibration isolator, lithographic apparatus and device manufacturing method

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109875520B (zh) * 2019-04-15 2022-03-22 遵义市红花岗区人民医院 神经科用检查器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3304916A1 (de) * 1983-02-12 1984-08-16 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
DE3717694A1 (de) * 1987-05-26 1988-12-08 Bosch Gmbh Robert Bohrhammer

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3304916A1 (de) * 1983-02-12 1984-08-16 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
DE3717694A1 (de) * 1987-05-26 1988-12-08 Bosch Gmbh Robert Bohrhammer

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10816910B2 (en) 2016-03-03 2020-10-27 Asml Netherlands B.V. Vibration isolator, lithographic apparatus and device manufacturing method
CN110573305A (zh) * 2017-05-05 2019-12-13 费希尔厂有限责任两合公司 安装工具

Also Published As

Publication number Publication date
DE202011110340U1 (de) 2013-09-12
DE102011105600A1 (de) 2012-12-27

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