WO2015000129A1 - Dispositif d'impact et machine-outil pour opération d'impact - Google Patents

Dispositif d'impact et machine-outil pour opération d'impact Download PDF

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Publication number
WO2015000129A1
WO2015000129A1 PCT/CN2013/078653 CN2013078653W WO2015000129A1 WO 2015000129 A1 WO2015000129 A1 WO 2015000129A1 CN 2013078653 W CN2013078653 W CN 2013078653W WO 2015000129 A1 WO2015000129 A1 WO 2015000129A1
Authority
WO
WIPO (PCT)
Prior art keywords
impact
force
hammer
reciprocating
cylindrical piston
Prior art date
Application number
PCT/CN2013/078653
Other languages
English (en)
Chinese (zh)
Inventor
陈振宇
Original Assignee
Chen Zhenyu
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 Chen Zhenyu filed Critical Chen Zhenyu
Priority to PCT/CN2013/078653 priority Critical patent/WO2015000129A1/fr
Publication of WO2015000129A1 publication Critical patent/WO2015000129A1/fr

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Classifications

    • 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
    • B25D11/062—Means for driving the impulse member comprising a wobbling mechanism, swash plate
    • 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
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force
    • 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
    • B25D2217/0015—Anvils
    • 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
    • B25D2217/0019—Guide-sleeves

Definitions

  • This invention relates to an impact device, and more particularly to an impact device for performing an impact operation and a power tool provided with the impact device, particularly a hand-held power tool such as a hand-held hammer drill or a hammer. Background technique
  • an impact device for impacting a workpiece is generally comprised of an element called anvil or horn that can be axially displaced to the guide member.
  • the guiding member is generally fixed relative to the entire machine tool without relative movement in the impact direction, and includes a driving motor on the driving side, and the rotation of the driving motor is converted into the reciprocating motion of the piston by the reciprocating conversion mechanism
  • An impact hammer (Hammer) is arranged between the piston and the anvil or the horn, and a sealed air spring can be formed between the impact hammer and the piston, so that the piston can drive the impact hammer to generate a reciprocating hammering motion.
  • the impact hammer is impacted in the impact device against the anvil or horn in the direction of impact operation.
  • the impact energy is transmitted through the anvil or the horn to the end of the driving side of the tool holder that is in contact with the tool holder, and the impact energy is transmitted to the object to be processed through the tool.
  • the impact reaction force can be transmitted through the above-mentioned guide member.
  • a guide for anvil or horn is disclosed in the patent document EP 1910039 B1, which attempts to increase the life of the impact device by using a plurality of materials of different hardness on the main body under a reasonable manufacturing economy.
  • the value of the rebound force of the tool is very large, and the duration is very short, even if the driving side portion of the main body is absorbed by an elastic body such as rubber as described therein.
  • Most of the energy is transmitted to the outside of the machine tool, causing the operator to feel the vibration of the reaction force during use, low use comfort and safety.
  • similar problems exist in the patent document DE 10 2010 03 0026 A1.
  • a return spring and an elastic body that absorbs a reaction force are simultaneously provided, but the synthesis of the cartridge does not have a good effect or even worse.
  • the reaction force is not completely absorbed by the elastic element and partially transmitted to the outside of the machine.
  • the operator has to press the machine tool hard to make the punch The vibrational sensation produced by the counterforce is enhanced.
  • an impact device for performing an impact operation which includes a power drive output. a portion, an impact portion, an impact transmitting portion, and a guiding portion, the power driving output portion is powered and has a reciprocating portion that outputs a reciprocating motion to cause the impact portion to reciprocate in an impact working direction Moving, and applying a first force to the impact transmitting portion to perform an impacting operation on the processing object, the guiding portion guiding at least the reciprocating portion and the impact transmitting portion, the punching
  • the striking device further includes a biasing portion associated with the reciprocating portion, such that the reciprocating portion applies a second force to the impact transmitting portion directly or through the guiding portion, the second action The force is the same as the first force direction.
  • the maximum value and the minimum value of the second force respectively correspond to when the reciprocating portion reciprocates
  • the distance between the impact transmitting portions is the smallest and largest.
  • the second action changes periodically.
  • the second action has a first value and a second value respectively corresponding to before and after the first force is applied, the first value being greater than the second value.
  • the biasing portion includes a first magnet respectively connected to the reciprocating portion, and a second magnet connected to the impact transmitting portion or the guiding portion, and the first magnet and the second magnet The same magnetic poles of the magnets are arranged opposite each other to form the second force.
  • the reciprocating portion includes a cylindrical piston
  • the impact portion includes an impact hammer
  • the impact hammer An air spring disposed in the cylindrical piston and capable of being formed or disconnected according to an operating state or a non-working state, the first magnet being disposed on the cylindrical piston;
  • the impact transmission The portion includes a cutter, and an anvil or horn connected to the cutter, the second magnet being disposed on the anvil or horn; or
  • the reciprocating portion includes a cylindrical piston, the impact portion includes an impact hammer, the first magnet is disposed on the cylindrical piston; the impact transmitting portion includes a cutter, and is coupled to the cutter An anvil or horn; the guiding portion includes an outer sleeve and an inner sleeve, the inner sleeve being sleeved in the outer sleeve in a movable manner relative to the outer sleeve in an impact working direction, the anvil Iron or horn is sleeved in the outer sleeve in a manner movable relative to the outer sleeve in an impact working direction and can push the inner sleeve to move in an impact working direction, the cylindrical piston and the The impact hammer is sleeved in the inner sleeve in a movable manner relative to the inner sleeve in the direction of the impact work, and is provided between the cylindrical piston and the impact hammer according to the working state or An air spring that can be
  • the biasing portion includes an elastic member that is disposed to reciprocate with the reciprocating motion at least The moving portion, and the impact transmitting portion or the guiding portion abut against each other to form the second force.
  • the reciprocating portion includes a cylindrical piston
  • the impact portion includes an impact hammer
  • the impact hammer An air spring disposed in the cylindrical piston and capable of being formed or disconnected according to an operating state or a non-working state
  • the impact transmitting portion including a cutter, and an anvil iron connected to the cutter or a horn, one end of the elastic member abutting against the cylindrical piston in the reciprocating motion, and the other end of which is connected to the anvil or horn;
  • the reciprocating portion includes a cylindrical piston
  • the impact portion includes an impact hammer
  • the impact transmitting portion includes a cutter, and an anvil or horn connected to the cutter
  • the guiding portion including an outer sleeve and An inner sleeve, the inner sleeve being sleeved in the outer sleeve relative to the outer sleeve in a direction of impact operation, the anvil or horn being capable of rushing relative to the
  • the impact transmitting portion is further provided to be capable of rotational motion with the impact working direction as an axis.
  • the machine tool is optionally a hand-held power tool provided with a battery unit for supplying electrical energy to the power drive output portion and/or Or an external power connector.
  • the second force is greater than the operator when the impact transmitting portion and the guiding portion abut against the direction of the impacting operation.
  • Operating pressure applied to the hand-held power tool, and the operating pressure is greater than a minimum operating pressure required to maintain the power tool in an operating state such that the impact transmitting portion is in an operational state One position of the working direction does not contact the guide portion in the direction of the impact work.
  • the impact device of the present invention can provide a high restoring force and transmit it to a part such as an anvil or a horn that moves with the cutter in the guiding structure, thereby achieving a larger passage before the first empty hammer occurs.
  • the purpose of the resetting force is to return to the non-working (no-load) position to avoid the occurrence of the first empty hammer, thus completely improving the anti-air hammer capability of the impact device, especially for normal impact work.
  • Non-operator's willingness to switch, such as sudden breakage of the object to be processed The trend of the empty hammer generated by the working state is effectively avoided, improving the safety and the service life of the components.
  • the impact device of the present invention has a structure capable of effectively absorbing the impact reaction force, thereby fully absorbing the reaction force without being transmitted to the operator holding position outside the machine tool, thereby effectively reducing the tool machine.
  • the vibration transmitted by the body during work improves the comfort and safety of use.
  • Figure 1 is a partial side cross-sectional view showing a first embodiment of a machine tool having an impact device according to the present invention.
  • Figure 2 is a partial side cross-sectional view of a second embodiment of a machine tool having an impact device in accordance with the present invention.
  • Fig. 3 is a view showing the assembly of parts such as a pressure ring and a sleeve in the second embodiment shown in Fig. 2.
  • Figure 4 is a partial side cross-sectional view of a third embodiment of a machine tool having an impact device in accordance with the present invention.
  • Figure 5 is a partial side schematic cross-sectional view of a fourth embodiment of a machine tool having an impact device according to the present invention. detailed description
  • battery refers to all rechargeable or non-rechargeable battery cells, battery packs, etc.
  • part refers to a part or element that constitutes a single component or structure. Or, it refers to one or more structures, components, devices or devices that constitute the whole described.
  • up, down, front, back, inner, eve, horizontal, vertical, etc. mentioned herein are described with respect to the impact device, machine tool or its components shown in the various figures. They are relative concepts, so it is possible to make corresponding changes depending on their location and usage. Therefore, these or other orientation terms should not be interpreted as restrictive terms.
  • the present invention improves the design by innovatively optimizing, and provides an impact device that can be applied to a machine tool for impact work, thereby bringing about, for example, effectively avoiding empty hammers, absorbing shock reaction forces, and comprehensively reducing Numerous technical effects such as vibration, extended component life, and improved operator comfort.
  • an impact device basically comprises a power driving output portion, an impact portion, an impact transmitting portion, a guiding portion and a biasing portion.
  • FIG. 1 to FIG. The present invention will be described in detail by four specific embodiments.
  • Fig. 1 in which only a partial side cross-sectional view of a first embodiment of applying the impact device of the present invention to a machine tool is schematically illustrated.
  • the electric hammer 100 of this embodiment is a specific application of the present invention to a hand-held power tool which can have relatively lightweight features.
  • the impact device is disposed inside the hammer 100, and its components and its structure will be described below.
  • the power drive output portion of the impact device specifically includes a motor and a cylindrical piston
  • the former is used to provide driving power for the entire hammer 100
  • the outer output is reciprocated by the latter, that is, when the hammer
  • the cylindrical piston is used as the power drive.
  • the reciprocating portion in the exit portion reciprocates.
  • the gear la provided on the motor shaft cooperates with the reduction gear 3a fitted on the transmission shaft 2a to transmit the rotational energy of the motor to the transmission shaft 2a for rotation.
  • the guide tube 4a is arranged in parallel with the drive shaft 2a, and a hole is opened at the front end of the guide tube 4a for insertion of the cutter 5a, and an anvil iron 6a and a cylindrical piston 7a are arranged in the inside of the guide tube 4a from the side of the cutter 5a.
  • the impact hammer 8a is provided as a shock portion in the impact device in the cylindrical piston 7a, and a rotary pin 21a rotatable in the vertical direction of the guide tube 4a is provided behind the cylindrical piston 7a, the swing lever 14a One end passes through the rotating pin 21a, and the other end is annularly connected to a rotating body 13a having a raceway having a certain angle with the guide pipe, and the rotating body 13a is coupled with the drive shaft 2a for rotation, and the rotating body 13a and the swinging bar
  • the raceway formed by 14a has a plurality of balls 15a, so that the rotational motion of the motor in the above-described power drive output portion can be converted into the swing of the swing link 14a along the guide tube 4a, and then the swing rod 14a drives the cylinder by the rotary pin 21a.
  • the piston 7a reciprocates.
  • the guide tube 4a further includes a ring disk 18a which is fixed in the guide tube 4a by the snap ring 22a.
  • the anvil iron 6a can be moved within a section of the guide tube 4a in the axial direction (i.e., the direction of the impact operation), that is, such a configuration sets the electric hammer 100 to be unloaded (non-working) and in an operating state.
  • the range of movement of the lower impact transmitting portion When the operator presses the hammer 100 to apply force to the object to be processed, the cutter 5a together with the anvil iron 6a serves as an impact transmitting portion which moves in the axial direction of the guide tube 4a to the vicinity of the ring disk 18a.
  • the impact end 81a of the hammer 8a is also moved by the anvil iron 6a and toward the power drive output portion, and the annular seal port 82a of the impact hammer 8a will pass over the vent hole 71a of the cylindrical piston 7a, thereby
  • the air spring 20a is formed between the impact hammer 8a and the cylindrical piston 7a (which is formed or disconnected according to the working state or the non-working state), and the cylindrical piston 7a can drive the impact hammer 8a to the anvil iron 6a.
  • the cutter 5a performs a hammering operation, that is, an impact force (ie, a first force) is applied to the workpiece by the impact transmitting portion; when the cutter 5a does not abut the workpiece, the anvil iron 6a and the cutter 5a are at
  • the front end of the guide tube 4a is embedded with a 0-shaped cymbal 19a in the ring disk 18a to catch the impact end 81a of the impact hammer 8a, so that the impact hammer 8a is stopped at the front end of the cylindrical piston 7a, at which time the impact hammer
  • the upper annular seal port 82a is located near the cutter 5a of the vent hole 71a.
  • the side that is, the air spring 20a is kept in the off state, so that the hammer 100 is stabilized in a non-working (i.e., no-load, no hammer) state. Thereafter, when the operator presses the hammer against the object to be processed, the anvil 6a is moved. The movement will push the impact end 81a away from the 0-type ⁇ 19a to the right, that is, the air spring 20a is simultaneously formed and brought into an operating state.
  • Elastic pads 61a, 62a are provided on both sides of the anvil iron 6a to reduce the rigid contact with the guide tube 4a and the ring disk 18a, and two bearings 10a, 11a are provided outside the guide tube to be connected to the hammer base.
  • an axial external spur 9a is arranged outside the guiding tube, which cooperates with the output shaft upper gear 12a for realizing the rotational movement of the guiding tube 4a together with the cutter 5, so that the electric hammer 100 can be equipped with a hammer and can be drilled ( That is, the impact transmission part performs the rotary motion of the impact work direction as the axis:).
  • annular magnet 16a is further mounted on the side of the anvil iron 6a adjacent to the impact hammer 8a, and an annular magnet 17a is provided at the outer edge of the nozzle of the cylindrical piston 7a.
  • These annular magnets 16a, 17a are coaxial in the direction of the guide tube 4a and the same magnetic poles are opposite. Arranged, they together constitute the biasing portion in the present embodiment to provide a biasing force by the repulsive force generated between the above-mentioned magnets, which is the same as the impact force applied to the object to be processed in the impact operation Directions, the terms "repulsive force” and “biasing force” as used hereinafter, and “second force” appearing elsewhere in the text have the same meaning.
  • a material such as stainless steel which does not affect the magnetic properties of the above magnet can be used.
  • the operator applies a thrust (ie, an operating pressure) to the hammer in the direction in which the tool impacts the work, and the repulsive force between the ring magnets 16a, 17a is opposite to the thrust direction, and the cylindrical piston 7a moves to the reciprocating motion.
  • the above repulsive force is maximum when the front end of the motion (ie, the tool direction), and the repulsive force is the smallest at the last end of the reciprocating motion (ie, the direction of the power drive output portion).
  • the characteristic and magnitude of the repulsive force can be changed by, for example, adjusting the properties of the magnet, and the thrust of the operator can be balanced by its equivalent stress.
  • the reaction force rebounded by the cutter 5a will be transmitted to the magnetic spring between the ring magnets 16a, 17a through the anvil iron 6a and absorbed.
  • the effect of reducing the vibration of the hammer is achieved.
  • the magnetic spring is non-contact type and has a large compression stroke, a relatively small stiffness coefficient can be used, thereby obtaining a good vibration damping effect.
  • the non-contact of the magnet is employed in the present embodiment, the technical solution for carrying out the invention under the premise of the guaranteed life is provided.
  • the above-mentioned repulsive force between the ring magnets 16a, 17a may be periodically alternated, which is in a very large range during the impact of the impact hammer 8a, so when the repulsive force is greater than the thrust of the operator, At this time, the object to be processed is destroyed, and under the action of a large repulsive force, the anvil iron 6a and the cutter 5a return to the front end of the guide tube 4a with a large acceleration, so that the first empty hammer can be effectively avoided. The occurrence of the next impact of the hammer.
  • the equivalent force can be adjusted widely, so that the electric hammer 100 has better user adaptability, and the repulsive force generated by the magnet at a close distance is relatively large. Therefore, a very effective anti-air hammer effect can be obtained. In this way, the number of times the hammer can occur in the life cycle can be fundamentally reduced, and the service life of the machine tool can be effectively improved.
  • the electric hammer 200 of the second embodiment is a specific implementation of the present invention on a relatively lightweight electric hammer in which an elastic member is used in the power drive output portion and impact of the impact device.
  • the biasing force is transmitted between the transmitting portions, and such elastic members can adopt various spring members such as a spiral compression spring, and thus such components are standard parts that are easy to purchase, thus providing a particularly low-cost solution. It can make the present invention have a very significant cost advantage while ensuring the effects of the present invention.
  • the present embodiment differs in the following aspects.
  • the inner cutter end of the guide pipe 4a has a sleeve 23b fitted to the guide pipe 4a, and a pin 33b penetrating the guide pipe 4a is attached to the end of the sleeve 23b, in the guide pipe 4a.
  • the outer peripheral fixing clasp 34b prevents the detachment of the pin 33b
  • the anvil iron 24b is mounted inside the sleeve 23b and is movable in the axial direction
  • the inside of the sleeve 23b and the inside of the guide tube 4a are mounted to be axially movable along the guide tube 4a.
  • Pressure ring 25b is provided to be axially movable along the guide tube 4a.
  • an elongated groove 231b is formed in the sleeve 23b.
  • Long pin 26b runs through The pressure ring 25b, the sleeve 23b and the anvil iron 24b connect the pressure ring 25b and the anvil iron 24b, and can simultaneously move axially with respect to the sleeve 23b and the guide tube 4a.
  • a hole is formed in the guide tube 4a and the lock ball 28b is placed, and a collar 29b is disposed outside the guide tube 4a to prevent the lock ball 28b from coming out.
  • an elongated blind groove 251b is formed in the pressure ring 25b shown in Fig. 3, and cooperates with the lock ball 28b to restrict the movement range of the anvil iron 24b and the pressure ring 25b inside the guide pipe 4a.
  • a thrust bearing 30b and a friction ring 31b are disposed on a side of the pressure ring 25b close to the cylindrical piston, one side of the friction ring 31b is in contact with the thrust shaft 730b, and the other side thereof is connected to the compression spring 32b. One end and the other end are in contact with the end of the cylindrical piston 7a.
  • the purpose of providing the thrust bearing 30b is that when the hammer 200 is in the hammered and drilled working state, the compression spring 32b can be thereby made in the case where the above-mentioned pressure ring 25b will rotate and the cylindrical piston 7a does not rotate together. Does not suffer from circumferential torsion.
  • the biasing portion in the impact device is constructed by providing a lower cost elastic member, and the elastic member provides a mechanical force as the biasing force, and the effect thereof is the same as in the first embodiment.
  • the magnetic repulsive force formed by a pair of magnets is similar, and therefore is not limited to the length and will not be described again.
  • FIG. 4 a third embodiment of the machine tool according to the present invention will be specifically described with reference to Fig. 4, and a partial side sectional view of the third embodiment is schematically shown in Fig. 4.
  • an impact device according to the present invention is provided inside the electric hammer 300 of the present embodiment, and the electric hammer is a concrete implementation of the present invention on a heavy-duty electric hammer.
  • the basic structure, working principle, and the like of the hammer and the impact device therein will be described below.
  • the power drive output portion of the impact device in the electric hammer 300 specifically includes a motor and a cylindrical piston, the former is used to provide driving power to the entire hammer 300, and the latter is outputted to reciprocate outwardly, that is, When the hammer 300 is in the operating state, the cylindrical piston reciprocates as a reciprocating portion in the power drive output portion.
  • a lower portion of the fixing pin 2c is fixedly coupled to the base of the electric hammer 300, and the first gear 3c is sleeved on the fixing pin 2c through the blind hole 31c thereon and can be fixed around the fixing pin 2c.
  • the pin 2c is rotated, and the first gear 3c is driven by a gear lc provided on the motor shaft.
  • a cylindrical protrusion offset from the center of rotation is fixed to the first gear 3c. 4c, the circular motion of the columnar projection 4c is achieved by the driving of the gear lc.
  • an integrated gear having two gears for achieving two-stage deceleration, that is, one-stage deceleration is realized by the large circumferential tooth portion of the gear lc and the gear 5c, and a small tooth protruding through the middle of the gear 5c
  • the part cooperates with the gear 16c sleeved on the outer guiding tube 6c to realize the second-stage deceleration, and the purpose of using the deceleration is to make the electric hammer 300 have the function of hammering and drilling, and the rotation speed thereof is not very large due to the two-stage deceleration.
  • the gear 5c has a shaft 51c which is sleeved in a hole in the casing of the hammer 300 (not shown) and can be added to the bearing to reduce wear.
  • the outer guide tube 6c is arranged perpendicularly to the motor shaft in the axial direction, and is provided at one end thereof with a cutter sleeve 7c which passes through the outer guide tube 6c and is inserted into the cutter sleeve 7c, and is arranged circumferentially in the outer guide tube 6c.
  • the retaining ring 1 1c serves to prevent the pin 10c from coming out, thereby achieving the connection of the outer guide tube 6c and the tool sleeve 7c.
  • an inner sleeve 8c is provided along the inner side of the outer guiding tube 6c and axially movable, and a snap ring 85c is arranged in the cutter end of the inner sleeve 8c.
  • the faces 93c are in contact with each other, and the other end of the anvil iron 9c is inserted into the tool bushing 7c and abuts against the end face of the cutter 23c. As shown in FIG.
  • a cylindrical section 92c is provided at an end of the anvil iron 9c near the impact hammer to ensure that the horn 9c can be held at the center position and the right end thereof does not detach from the hole of the inner sleeve of the guide portion, so
  • the cylindrical section 92c is configured to be guided and radially supported by the guiding portion at all in the working position or the inoperative position.
  • FIG. 4 Also shown in Fig. 4 is an extension section 63c on the right side of the outer guide tube 6c. Since the cylindrical piston 20c is sleeved in the inner sleeve 8c and protrudes on the right side of the inner sleeve 8c, the extension portion thereof is further It is in contact with and guided by the rightmost extension section 63c of the outer guide tube 6c, so that the cylindrical piston 20c can be better supported by the extension section 63c, especially when the cylindrical piston 20c reciprocates.
  • the length to the far right so that it is sleeved by the inner sleeve 8c is the shortest.
  • the outer guide tube 6c has an axially open oblong groove 61c, and the outer portion of the outer guide tube is provided with sleeves 12c, 13c, and a circular hole is formed in the sleeve 12c, and the pin 14c passes through The circular hole, the oblong groove 61c is inserted into the blind hole of the inner sleeve 8c, and a snap ring 15c is disposed outside the sleeve 12c to prevent the pin 14c from coming loose.
  • bearings 17c, 18c are provided as supports for the outer guide tube 6c to support their ability to perform a rotational motion.
  • An impact hammer 19c is disposed in the inner sleeve 8c, and a cylindrical piston 20c is disposed at the other end of the inner sleeve 8c.
  • Type 0 ⁇ 191 c, 201 c and 91c may be respectively disposed along the outer circumferential directions of the impact hammer 19c, the cylindrical piston 20c, and the anvil iron 9c.
  • the cylindrical piston 20c is connected to the eccentric cylindrical projection 4c of the first gear 3c via the joint 4c, so that the cylindrical piston 20c can be reciprocated by the eccentric cylindrical projection 4c.
  • the inner sleeve 8c On the inner sleeve 8c, there is an opening 86c between the cylindrical piston 20c and the impact hammer 19c, and a through hole 62c is formed in the outer guide tube, and the anvil iron 9c is pressed by the cutter 23c to the long circular groove 61c side. At this time, the opening 86c and the through hole 62c are not centered, and the sleeve 13c closes the flow of the through hole 62c with the outside air, so that an air spring 21c is formed between the cylindrical piston 20c and the impact hammer 19c, that is, I entered the working state and carried out the impact work.
  • the cutter 23c leaves the processing object, the cutter 23c, the anvil iron 9c and the inner sleeve 8c move to the pin 14c at the tool end of the long circular groove 61c (ie, the impact working direction), at which time the through hole 62c is aligned with the opening 86c. And the sleeve 13c does not block the through hole 62c, so that the air spring 21c is broken, that is, it enters a non-working (idle) state.
  • An annular magnet 24c is disposed on a side of the inner sleeve 8c adjacent to the power drive output portion, and a ring magnet 25c is disposed on a corresponding side of the cylindrical piston 20c.
  • the ring magnets 24c, 25c are mutually in operation Without contact, they are arranged coaxially and the same magnetic poles are arranged opposite each other, which together constitute the biasing portion in the present embodiment, so as to provide a biasing force by the repulsive force generated between the above-mentioned magnets, the direction of the biasing force and the impact operation
  • the direction of the impact force applied to the object to be processed is the same.
  • the operator applies a thrust to the hammer in the direction in which the tool strikes, and the repulsive force between the ring magnets 24c, 25c is opposite to the thrust, and the cylindrical piston 20c moves to the foremost end of the reciprocating motion (ie, In the tool direction), the above repulsive force is the largest; at the last end of the reciprocating motion (ie, the direction of the power drive output portion), the above repulsive force is the smallest.
  • the equivalent force of the above repulsive force is balanced with the thrust applied by the operator to the electric hammer 300, the steady operation state is entered.
  • the present invention by adjusting the properties of the ring magnets 24c, 25c (i.e., the characteristics and magnitude of the repulsive force), under the action of the operator's thrust, when entering a stable working state, , through with anvil iron 9c
  • the pin 14c of the inner sleeve 8c that is in contact does not come into contact with the extreme position of the long circular groove 61c on the side close to the cylindrical piston 20c.
  • the reaction force bounced back by the cutter 23c will be transmitted to the magnetic spring between the ring magnets 24c, 25c through the anvil iron 9c and the inner sleeve 8c, thereby reducing the vibration of the hammer.
  • the magnetic spring is non-contact and has a relatively small stiffness coefficient, a good damping effect of 4 ⁇ can be obtained, and the non-contact of the magnet also provides a reliable guarantee for the service life of the entire hammer.
  • the repulsive force between the above-mentioned ring magnets 24c, 25c may be periodically alternated, the magnet repulsive force during the impact of the impact hammer 19c is in a very large range, so when the repulsive force is larger than the operator's In the case of thrust, if the object to be processed is broken at this time, the anvil iron 9c, the inner sleeve 8c, the cutter 23c, and the like return to the front end of the guide tube 4c with a large acceleration of 4 ⁇ under a large repulsive force, thereby The first occurrence of the empty hammer is effectively avoided, which fundamentally reduces the occurrence of the empty hammer in the life cycle of the electric hammer, and effectively improves the service life of the machine tool.
  • FIG. 5 a fourth embodiment in which the impact device of the present invention is applied to a machine tool is shown in FIG. 5, since the embodiment has many identical or similar structures to the aforementioned third embodiment, Or the structure will be described or omitted, or will not be marked in FIG.
  • the electric hammer 400 in the fourth embodiment is a specific implementation of the present invention on a heavy-duty electric hammer in which an elastic member is used in the power driving output portion and the impact transmitting portion of the impact device.
  • the biasing force is transmitted therebetween, and such elastic members can employ various types of spring members such as a spiral compression spring, whereby a particularly low-cost solution can be realized and the present invention has a cost advantage.
  • the present embodiment is different from the third embodiment in that a thrust bearing 26d and a spacer 27d are mounted on a side of the inner sleeve 8c close to the power drive output portion (including the motor and the cylindrical piston 20c), and An annular groove 202d is disposed at the outer edge of the cylindrical piston 20c, and a compression spring 28d is disposed between the spacer 27d and the annular groove 202d.
  • the purpose of providing the thrust bearing 26d is that when the hammer 400 is required to have the hammer drill function, the inner sleeve 8d will rotate and the cylindrical piston 20d will not rotate, and the thrust piston 26d can be used to prevent the piston 20d from bearing the circumference. The role of torsion.
  • the machine tool provided by the present invention for performing an impact operation may be a hand-held type, and of course, the impact device provided by the present invention for performing an impact operation may be applied to other non-handheld devices.
  • the above various technical advantages of the present invention can also be exerted on the machine tool.
  • the application examples may be desktop machine tools, or heavy machinery rather than operator hand operations.
  • a battery unit for example, a lithium ion battery or the like
  • a battery unit may be provided on the power tools to which the present invention is applied to supply power to the power drive output portion of the impact device, or may be separately or combined with the power tools.
  • An external power interface is provided to supply power to or to charge the power drive output portion.
  • the power drive output portion of the impact device of the present invention is not limited to the above-described manner of reciprocating the output after the gear is driven by the rotary electric machine, and for example, a linear reciprocating motor, an alternating current drive solenoid, a magnet, etc. The way to provide drive power and direct output reciprocating motion.
  • the biasing force provided by the biasing portion of the impact device of the present invention may be set as follows: the maximum value corresponds to the reciprocating motion. The distance between the portion when the reciprocating motion is performed and the impact transmitting portion is the smallest, and the minimum value thereof corresponds to when the distance between the two is the maximum.
  • the above-mentioned biasing force can also be set to have characteristics that change periodically. For example, when the repulsive force mode is provided by the magnet, the parameter variation law of the biasing force can be changed according to the magnetic field characteristics formed by the magnet, and it is obvious that these magnets are used.
  • the biasing force provided by the biasing portion may have a different value within the range of its value, wherein those values corresponding to the impact force applied to the processing object may be greater than those corresponding to the impact force applied to the processing object Those values after the last, In this way, there is a relatively large biasing force before each impact hammer hammers the impact transmitting portion, that is, a higher restoring force can be provided to improve the prevention of the occurrence of the empty hammer.
  • the impact transmitting portion can be placed in a "suspended" state, ie, the operation at this time.
  • the pressure can ensure that it is in the working state, and such a state can cause the impact transmitting portion to "suspend" without abutting against the guiding portion in the impact direction and staying at a position in the direction of the impacting operation, thereby Better vibration isolation and vibration absorption.
  • Additional reciprocating parts acting on the impact transmitting portion or acting on the impact transmitting portion through the guiding portion can serve as a provider of biasing force to the biasing portion, one of which is beneficial to additionally provide another eccentric disk plus Additional reciprocating parts are applied to the impact transmitting portion, and a suitable reciprocating distance can be designed as needed to adjust the characteristics and magnitude of the biasing force provided.
  • the "impact transmission part" of the biasing force as long as it can be moved relative to the machine tool following the tool, it can be used as the biasing force of the biasing force because it can transmit the biasing force to the tool.
  • the pressure ring mentioned in the above second embodiment is fixed and moved together with the anvil, so that the biasing force it receives can be finally transmitted to the cutter, so such a structure
  • the type is also included in the broader sense of the range of the impact transfer portion.
  • the aforementioned second force (or referred to as biasing force, repulsive force, etc.) can also be applied to the impact transmitting portion through the guiding portion, so that the desired effect expected by the present invention can also be achieved.
  • the tool receives the biasing force provided by the spring directly in the embodiment, or if the tool sleeve can be moved axially with the tool in the embodiment, it can also be used as part of the impact transmitting portion to receive the biasing force.
  • the object of the invention can likewise be achieved.
  • the cylindrical piston or the like in the above embodiment may be made of any suitable material such as a polymer material to avoid the influence of the magnetic field generated by the aforementioned magnet.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Abstract

La présente invention concerne un dispositif d'impact et une machine-outil pour une opération d'impact, le dispositif d'impact comportant : une partie de sortie de commande mécanique, une partie d'impact, une partie de transfert d'impact et une partie de guidage; la partie de sortie de commande mécanique fournit une puissance mécanique ou présente une partie à mouvement alternatif; la partie à mouvement alternatif produit un mouvement alternatif de sorte que la partie d'impact effectue un mouvement de va-et-vient dans la direction de l'opération d'impact, et applique une première force d'actionnement à la partie de transfert d'impact pour effectuer une opération d'impact sur un objet à traiter; et la partie de guidage guide au moins la partie à mouvement alternatif et la partie de transfert d'impact. Le dispositif d'impact comporte également une partie inclinée associée à la partie à mouvement alternatif, la partie inclinée étant configurée pour permettre à la partie à mouvement alternatif de guider d'appliquer directement ou à travers la partie de guidage une seconde force d'actionnement à la partie de transfert d'impact, la seconde force d'actionnement et la première force d'actionnement étant dans la même direction. La présente invention peut améliorer la capacité d'interdire un impact raté, par absorption la force antagoniste des impacts, améliorant ainsi la durée de vie utile et le confort.
PCT/CN2013/078653 2013-07-02 2013-07-02 Dispositif d'impact et machine-outil pour opération d'impact WO2015000129A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2013/078653 WO2015000129A1 (fr) 2013-07-02 2013-07-02 Dispositif d'impact et machine-outil pour opération d'impact

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Application Number Priority Date Filing Date Title
PCT/CN2013/078653 WO2015000129A1 (fr) 2013-07-02 2013-07-02 Dispositif d'impact et machine-outil pour opération d'impact

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3822030A1 (fr) * 2019-11-15 2021-05-19 Hilti Aktiengesellschaft Marteau perforateur et/ou burin avec agencement de mécanisme de percussion
US12115637B2 (en) 2019-11-15 2024-10-15 Hilti Aktiengesellschaft Impact mechanism arrangement

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191406196A (en) * 1913-03-29 1915-06-10 Hermann Jost A Mechanical Percussion Tool.
US20090065226A1 (en) * 2007-09-12 2009-03-12 Hilti Aktiengesellschaft Hand-held power tool with air spring percussion mechanism, linear motor, and control process
CN101797745A (zh) * 2009-01-21 2010-08-11 喜利得股份公司 冲击工具和手持式工具机
CN103331735A (zh) * 2013-07-02 2013-10-02 陈振宇 用于进行冲击作业的冲击装置以及工具机
CN203390895U (zh) * 2013-07-02 2014-01-15 陈振宇 用于进行冲击作业的冲击装置以及工具机

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191406196A (en) * 1913-03-29 1915-06-10 Hermann Jost A Mechanical Percussion Tool.
US20090065226A1 (en) * 2007-09-12 2009-03-12 Hilti Aktiengesellschaft Hand-held power tool with air spring percussion mechanism, linear motor, and control process
CN101797745A (zh) * 2009-01-21 2010-08-11 喜利得股份公司 冲击工具和手持式工具机
CN103331735A (zh) * 2013-07-02 2013-10-02 陈振宇 用于进行冲击作业的冲击装置以及工具机
CN203390895U (zh) * 2013-07-02 2014-01-15 陈振宇 用于进行冲击作业的冲击装置以及工具机

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3822030A1 (fr) * 2019-11-15 2021-05-19 Hilti Aktiengesellschaft Marteau perforateur et/ou burin avec agencement de mécanisme de percussion
WO2021094213A1 (fr) * 2019-11-15 2021-05-20 Hilti Aktiengesellschaft Ensemble mécanisme de percussion
CN114450128A (zh) * 2019-11-15 2022-05-06 喜利得股份公司 冲击机构布置
US12115637B2 (en) 2019-11-15 2024-10-15 Hilti Aktiengesellschaft Impact mechanism arrangement

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