US20050247462A1 - Hand machine tool with a hammer mechanism - Google Patents
Hand machine tool with a hammer mechanism Download PDFInfo
- Publication number
- US20050247462A1 US20050247462A1 US11/120,355 US12035505A US2005247462A1 US 20050247462 A1 US20050247462 A1 US 20050247462A1 US 12035505 A US12035505 A US 12035505A US 2005247462 A1 US2005247462 A1 US 2005247462A1
- Authority
- US
- United States
- Prior art keywords
- hammer
- spring mechanism
- tool
- machine tool
- hand 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.)
- Abandoned
Links
- 230000006835 compression Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 11
- 229910000639 Spring steel Inorganic materials 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
Images
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
- B25D11/12—Means for driving the impulse member comprising a crank mechanism
- B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
-
- 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
- B25D11/12—Means for driving the impulse member comprising a crank mechanism
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D2216/0007—Details of percussion or rotation modes
- B25D2216/0015—Tools having a percussion-only mode
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2216/00—Details of portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit
- B25D2216/0007—Details of percussion or rotation modes
- B25D2216/0023—Tools having a percussion-and-rotation mode
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/185—Pressure equalising means between sealed chambers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/371—Use of springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/371—Use of springs
- B25D2250/375—Fluid springs
Definitions
- the present invention relates to a hand machine tool—preferably a hammer drill and/or slide hammer—equipped with a hammer mechanism, which has a hammer that moves axially back and forth in a guide tube; a spring mechanism is provided, which exerts a force on the hammer and can set the hammer into a movement toward a tool that can be inserted into the hand machine tool.
- a hand machine tool preferably a hammer drill and/or slide hammer
- a compression hammer mechanism of this kind which executes repeating hammering movements and is intended for an electro-pneumatic hammer drill and/or slide hammer of the kind known from DE 198 10 088 C1, is comprised of an eccentric drive unit, a piston, and a hammer. These three elements serve to convert a rotating motion into a hammering motion.
- the axial back-and-forth motion of the hammer in a guide tube occurs in the following way: the piston, which the eccentric drive unit moves forward, compresses the air cushion between the piston and the hammer, thus causing the hammer to fly freely toward the tool inserted in the machine.
- the hammer imparts its hammering energy to the tool and from it, receives an impetus in the backward direction.
- the eccentric drive unit also moves the piston backward, which produces a certain vacuum in the air cushion between the piston and the hammer.
- the piston moves the piston backward, which produces a certain vacuum in the air cushion between the piston and the hammer.
- the piston reaches its reversal point but the hammer is still flying toward the piston, the air cushion between the two is compressed, generating a compression, which, with a renewed forward motion of the piston, then causes the hammer to fly at an even higher speed in the forward direction toward the tool.
- a compression hammer mechanism of this kind the piston and the hammer move with the same frequency.
- a high individual hammering energy at a low hammering frequency is not possible with a hammer mechanism of this kind.
- an eccentric drive unit sets an angle made of spring steel into an oscillating motion and this spring steel piece drives the hammer forward toward the tool or toward an intermediate anvil provided between the tool and hammer.
- the recoil energy of the hammer is stored in the spring buckle and released again during forward motion as in a pneumatic hammer mechanism.
- the object of the present invention is to disclose a hammer mechanism of the type mentioned at the beginning, which can be implemented with the simplest possible technical means and is able to generate a high individual hammering energy at a low hammering frequency.
- a suitable drive unit for the hammer produces a frictional engagement with the hammer after an impact has been imparted, moves it counter to the force of the spring mechanism, and then releases the frictional engagement again as soon as the hammer has reached a certain position in its movement counter to the force of the spring mechanism.
- An advantageous spring mechanism is comprised of a pressure reservoir that is filled with a compressible medium and situated in the guide tube, on the side of the hammer oriented away from the tool.
- the pressure reservoir can be filled with a gas, for example air, or also a fluid.
- a pump can be provided, which supplies compressible medium to the pressure reservoir to compensate for leakage losses.
- the pumping capacity of this pump can be very low because it only needs to compensate for leakage losses in the pressure reservoir.
- Such a pump which does not take up much space or weigh much, can be integrated into the hand machine tool.
- Another advantageous spring mechanism can be comprised of one or more compression springs and/or tension springs that are supported against the hammer on the one hand and against a shoulder that is stationary in the movement direction of the hammer on the other hand.
- FIG. 1 shows a longitudinal section through a hammer drill and/or slide hammer equipped with a hammer mechanism and a spring mechanism embodied in the form of a pressure reservoir and
- FIG. 2 shows a longitudinal section through a hammer drill and/or slide hammer equipped with a hammer mechanism and a spring mechanism embodied in the form of compression/tension springs.
- FIG. 1 shows a longitudinal section through a hand machine tool equipped with a hammer mechanism.
- this hand machine tool is a hammer drill and/or slide hammer.
- the schematic depiction of the hand machine tool shows only the hammer mechanism, which is the subject of the present invention. All other functional units usually provided in a hand machine tool are not shown.
- the hammer mechanism is comprised in an intrinsically known way of a hammer 1 that is supported so that it can move in a reciprocating fashion in a guide tube 2 .
- a tool 3 for example a drill bit or chisel, is inserted into a tool socket of the hand machine tool. If the hammer 1 flies forward toward the tool 3 , then the hammer 1 imparts its hammering impetus to the tool 3 . Between the tool 3 and the hammer 1 , it is also possible for an intermediate anvil (not shown here) to be provided in the guide tube 2 , which transmits the hammering impetus from the hammer 1 to the tool 3 .
- this spring mechanism is a pressure reservoir 4 , which is filled with a compressible medium and is situated in the guide tube 2 on the side of the hammer 1 oriented away from the tool.
- the pressure reservoir 4 is delimited by the side wall of the guide tube 2 , the hammer 1 sliding in the guide tube, and a back wall 5 of the guide tube 2 at its end oriented away from the tool 3 .
- a seal 6 is inserted between the hammer 1 and the side wall of the guide tube 2 and prevents the compressible medium from escaping from the pressure reservoir 4 .
- the compressible medium can be a fluid or a gas.
- the pressure reservoir 4 is filled with air.
- the pressure reservoir 4 is connected to a pump 7 that can supply compressible medium to the pressure reservoir 4 in order to compensate for leakage losses. Since it is only necessary to compensate for leakage losses of the compressible medium, it is sufficient to provide a small pump 7 with a low pumping capacity, which can easily be accommodated in the hand machine tool because of its low weight and small volume.
- the hammer mechanism has a drive unit, which, after each impact with the tool 3 , sets the hammer 1 into a motion counter to the force of the spring mechanism, thus stressing the spring mechanism.
- the aforementioned drive unit is designed so that after the stressing of the spring mechanism, it abruptly releases the hammer 1 again so that, driven by the spring mechanism, the hammer 1 flies toward the tool. Because the spring mechanism is stressed not only by the recoil force of the hammer 1 , but also actively by the separate drive unit, which exerts a very high stress on it, a very powerful hammering force is imparted to the hammer 1 upon release of the spring mechanism. Consequently, a very high individual hammering energy can be generated, even at a relatively low hammering frequency.
- the above-described drive unit is embodied as follows:
- the side of the hammer 1 oriented away from the tool 3 is attached to a rod 8 , which extends in the direction of the longitudinal axis of the guide tube 2 and passes through the back wall 5 of the guide tube 2 .
- a seal 9 between the rod 8 and the guide opening in the rear wall 5 of the guide tube 2 prevents compressible medium from escaping from the pressure reservoir 4 .
- the rod 8 ends in the vicinity of a driving gear 10 , which is rotatable around an axis that extends perpendicular to the longitudinal axis of the guide tube 2 .
- the shaft 11 of a motor not shown, sets the driving gear into rotation, e.g. by means of a parallel shaft gearing (not shown in the drawing).
- a pin 13 is provided, which protrudes from the driving gear 10 perpendicular to the plane of the drawing.
- the end of the rod 8 oriented toward the driving gear 10 is embodied in the form of a hook 14 so that when the driving gear 10 rotates, the pin 13 can travel into the hook 14 . If the hammer 1 is moving backward after striking the tool, then the rod with the hook 14 slides toward the driving gear 10 .
- the pin 13 of the rotating driving gear 10 slides into the hook 14 and carries the rod 8 with the hammer 1 toward the driving gear 10 —clockwise in the exemplary embodiment—so that the hammer 1 moves toward the back wall 5 of the guide tube 2 , thus causing the medium in the pressure reservoir 4 to be compressed. This results in a sharp increase in the pressure on the hammer 1 toward the tool 3 .
- the driving gear 10 has completed a half rotation and the pin 13 has thus reached a position 13 ′, which is the furthest from the guide tube 2 , then the pin 13 slides back out of the hook 14 again. At this moment, the hammer 1 is released and can move toward the tool 3 to strike it again, driven by the pressure in the pressure reservoir 4 .
- the rotation speed of the driving gear 10 must be set so that whenever the hammer 1 is traveling backward after an impact, the hook 14 at the end of the rod 8 is situated directly over the pin 13 of the driving gear 10 .
- FIG. 2 shows a schematic cross section through a hand machine tool in which the spring mechanism is not comprised of a pressure reservoir as in the exemplary embodiment of FIG. 1 , but instead, one or more tension and/or compression springs are used. Aside from the spring mechanism, all other functional elements are the same as in the previously described exemplary embodiment of FIG. 1 and are also provided with the same reference numerals in FIG. 2 as in FIG. 1 .
- the chamber of the guide tube 2 between the hammer 1 and the back wall 5 of the guide tube contains a compression spring 15 , which rests against the back wall 5 of the guide tube 2 at one end and against the hammer 1 at the other.
- this compression spring 15 or in addition to it, it is also possible to provide a tension spring 16 on the side of the hammer 1 oriented toward the tool 3 . This tension spring is connected to the hammer 1 at one end and is connected to a shoulder of the guide tube 2 at the other.
Abstract
A hand machine tool is equipped with a hammer mechanism, which has a hammer (1) that moves axially back and forth in a guide tube (2); a spring mechanism (4) is provided, which exerts a force on the hammer (1) and can set the hammer (1) into a movement toward a tool (3) that can be inserted into the hand machine tool. The hammer mechanism produces a very high individual hammering energy at a relatively low hammering frequency by virtue of the fact that after each impact, the hammer (1) is set into a motion counter to the force of the spring mechanism (4) in order to stress this spring mechanism and after the stressing of the spring mechanism (4), the hammer (1) is abruptly released again so that it flies toward the tool (3).
Description
- The present invention relates to a hand machine tool—preferably a hammer drill and/or slide hammer—equipped with a hammer mechanism, which has a hammer that moves axially back and forth in a guide tube; a spring mechanism is provided, which exerts a force on the hammer and can set the hammer into a movement toward a tool that can be inserted into the hand machine tool.
- A compression hammer mechanism of this kind, which executes repeating hammering movements and is intended for an electro-pneumatic hammer drill and/or slide hammer of the kind known from DE 198 10 088 C1, is comprised of an eccentric drive unit, a piston, and a hammer. These three elements serve to convert a rotating motion into a hammering motion. The axial back-and-forth motion of the hammer in a guide tube occurs in the following way: the piston, which the eccentric drive unit moves forward, compresses the air cushion between the piston and the hammer, thus causing the hammer to fly freely toward the tool inserted in the machine. The hammer imparts its hammering energy to the tool and from it, receives an impetus in the backward direction. At the same time, the eccentric drive unit also moves the piston backward, which produces a certain vacuum in the air cushion between the piston and the hammer. The moment the piston reaches its reversal point but the hammer is still flying toward the piston, the air cushion between the two is compressed, generating a compression, which, with a renewed forward motion of the piston, then causes the hammer to fly at an even higher speed in the forward direction toward the tool. In a compression hammer mechanism of this kind, the piston and the hammer move with the same frequency. A high individual hammering energy at a low hammering frequency is not possible with a hammer mechanism of this kind. The same is true for a so-called spring buckle hammer mechanism of the kind known from EP 544 865 B1. In it, an eccentric drive unit sets an angle made of spring steel into an oscillating motion and this spring steel piece drives the hammer forward toward the tool or toward an intermediate anvil provided between the tool and hammer. The recoil energy of the hammer is stored in the spring buckle and released again during forward motion as in a pneumatic hammer mechanism.
- The object of the present invention is to disclose a hammer mechanism of the type mentioned at the beginning, which can be implemented with the simplest possible technical means and is able to generate a high individual hammering energy at a low hammering frequency.
- The stated object is attained with the characteristics of
claim 1 in that means are provided, which set the hammer into a motion counter to the force of the spring mechanism after each impact in order to place this spring mechanism under stress; after the spring mechanism has been stressed, the means abruptly release the hammer again so that, driven by the spring mechanism, the hammer flies toward the tool. Because the hammer is actively moved counter to the force of the spring mechanism after each impact, a very powerful energy is imparted to the hammer after it is subsequently released for a new impact. - A suitable drive unit for the hammer produces a frictional engagement with the hammer after an impact has been imparted, moves it counter to the force of the spring mechanism, and then releases the frictional engagement again as soon as the hammer has reached a certain position in its movement counter to the force of the spring mechanism.
- An advantageous spring mechanism is comprised of a pressure reservoir that is filled with a compressible medium and situated in the guide tube, on the side of the hammer oriented away from the tool. The pressure reservoir can be filled with a gas, for example air, or also a fluid. The compressible medium—gas or fluid—remains in the pressure reservoir on a constant basis and only certain leakage losses from the pressure reservoir need be compensated for. To that end, a pump can be provided, which supplies compressible medium to the pressure reservoir to compensate for leakage losses. The pumping capacity of this pump can be very low because it only needs to compensate for leakage losses in the pressure reservoir. Such a pump, which does not take up much space or weigh much, can be integrated into the hand machine tool.
- Another advantageous spring mechanism can be comprised of one or more compression springs and/or tension springs that are supported against the hammer on the one hand and against a shoulder that is stationary in the movement direction of the hammer on the other hand.
-
FIG. 1 shows a longitudinal section through a hammer drill and/or slide hammer equipped with a hammer mechanism and a spring mechanism embodied in the form of a pressure reservoir and -
FIG. 2 shows a longitudinal section through a hammer drill and/or slide hammer equipped with a hammer mechanism and a spring mechanism embodied in the form of compression/tension springs. -
FIG. 1 shows a longitudinal section through a hand machine tool equipped with a hammer mechanism. For example, this hand machine tool is a hammer drill and/or slide hammer. The schematic depiction of the hand machine tool shows only the hammer mechanism, which is the subject of the present invention. All other functional units usually provided in a hand machine tool are not shown. - The hammer mechanism is comprised in an intrinsically known way of a
hammer 1 that is supported so that it can move in a reciprocating fashion in aguide tube 2. A tool 3, for example a drill bit or chisel, is inserted into a tool socket of the hand machine tool. If thehammer 1 flies forward toward the tool 3, then thehammer 1 imparts its hammering impetus to the tool 3. Between the tool 3 and thehammer 1, it is also possible for an intermediate anvil (not shown here) to be provided in theguide tube 2, which transmits the hammering impetus from thehammer 1 to the tool 3. - The forward motion of the
hammer 1 toward the tool 3 inserted into the hand machine tool is generated by a spring mechanism whose force is directed toward thehammer 1 in the direction of the forward motion. In the exemplary embodiment depicted inFIG. 1 , this spring mechanism is a pressure reservoir 4, which is filled with a compressible medium and is situated in theguide tube 2 on the side of thehammer 1 oriented away from the tool. The pressure reservoir 4 is delimited by the side wall of theguide tube 2, thehammer 1 sliding in the guide tube, and aback wall 5 of theguide tube 2 at its end oriented away from the tool 3. Aseal 6 is inserted between thehammer 1 and the side wall of theguide tube 2 and prevents the compressible medium from escaping from the pressure reservoir 4. - The compressible medium can be a fluid or a gas. Preferably, the pressure reservoir 4 is filled with air. In order to compensate for leakage losses from the pressure reservoir 4, the pressure reservoir 4 is connected to a
pump 7 that can supply compressible medium to the pressure reservoir 4 in order to compensate for leakage losses. Since it is only necessary to compensate for leakage losses of the compressible medium, it is sufficient to provide asmall pump 7 with a low pumping capacity, which can easily be accommodated in the hand machine tool because of its low weight and small volume. - The hammer mechanism has a drive unit, which, after each impact with the tool 3, sets the
hammer 1 into a motion counter to the force of the spring mechanism, thus stressing the spring mechanism. The aforementioned drive unit is designed so that after the stressing of the spring mechanism, it abruptly releases thehammer 1 again so that, driven by the spring mechanism, thehammer 1 flies toward the tool. Because the spring mechanism is stressed not only by the recoil force of thehammer 1, but also actively by the separate drive unit, which exerts a very high stress on it, a very powerful hammering force is imparted to thehammer 1 upon release of the spring mechanism. Consequently, a very high individual hammering energy can be generated, even at a relatively low hammering frequency. - In the exemplary embodiment shown in
FIG. 1 , the above-described drive unit is embodied as follows: - The side of the
hammer 1 oriented away from the tool 3 is attached to arod 8, which extends in the direction of the longitudinal axis of theguide tube 2 and passes through theback wall 5 of theguide tube 2. Aseal 9 between therod 8 and the guide opening in therear wall 5 of theguide tube 2 prevents compressible medium from escaping from the pressure reservoir 4. Outside the pressure reservoir 4, therod 8 ends in the vicinity of adriving gear 10, which is rotatable around an axis that extends perpendicular to the longitudinal axis of theguide tube 2. Theshaft 11 of a motor, not shown, sets the driving gear into rotation, e.g. by means of a parallel shaft gearing (not shown in the drawing). On thedriving gear 10, offset from therotation axis 12 of the driving gear, apin 13 is provided, which protrudes from thedriving gear 10 perpendicular to the plane of the drawing. The end of therod 8 oriented toward thedriving gear 10 is embodied in the form of ahook 14 so that when thedriving gear 10 rotates, thepin 13 can travel into thehook 14. If thehammer 1 is moving backward after striking the tool, then the rod with thehook 14 slides toward thedriving gear 10. Thepin 13 of the rotatingdriving gear 10 slides into thehook 14 and carries therod 8 with thehammer 1 toward thedriving gear 10—clockwise in the exemplary embodiment—so that thehammer 1 moves toward theback wall 5 of theguide tube 2, thus causing the medium in the pressure reservoir 4 to be compressed. This results in a sharp increase in the pressure on thehammer 1 toward the tool 3. As soon as thedriving gear 10 has completed a half rotation and thepin 13 has thus reached aposition 13′, which is the furthest from theguide tube 2, then thepin 13 slides back out of thehook 14 again. At this moment, thehammer 1 is released and can move toward the tool 3 to strike it again, driven by the pressure in the pressure reservoir 4. The rotation speed of thedriving gear 10 must be set so that whenever thehammer 1 is traveling backward after an impact, thehook 14 at the end of therod 8 is situated directly over thepin 13 of thedriving gear 10. - In lieu of the drive mechanism described above, which pulls the
hammer 1 by means of therod 8 counter to the force of the spring mechanism, it is also possible to provide a drive mechanism that pushes thehammer 1 counter to the force of the spring mechanism. In that case, the drive mechanism would have to be situated on the side of thehammer 1 oriented toward the tool. By contrast with the drive unit for thehammer 1 described above by way of example, it is possible to use any other mechanism that moves thehammer 1 counter to the force of the spring mechanism after each individual impact in order to stress the spring mechanism. -
FIG. 2 shows a schematic cross section through a hand machine tool in which the spring mechanism is not comprised of a pressure reservoir as in the exemplary embodiment ofFIG. 1 , but instead, one or more tension and/or compression springs are used. Aside from the spring mechanism, all other functional elements are the same as in the previously described exemplary embodiment ofFIG. 1 and are also provided with the same reference numerals inFIG. 2 as inFIG. 1 . - As shown in
FIG. 2 , the chamber of theguide tube 2 between thehammer 1 and theback wall 5 of the guide tube contains acompression spring 15, which rests against theback wall 5 of theguide tube 2 at one end and against thehammer 1 at the other. Alternatively to thiscompression spring 15 or in addition to it, it is also possible to provide atension spring 16 on the side of thehammer 1 oriented toward the tool 3. This tension spring is connected to thehammer 1 at one end and is connected to a shoulder of theguide tube 2 at the other. Instead of only onecompression spring 15 and/ortension spring 16, it is also possible for several compression and/or tension springs to be used, which impart the required hammering force to thehammer 1.
Claims (5)
1. A hand machine tool—preferably a hammer drill and/or slide hammer—equipped with a hammer mechanism, which has a hammer (1) that moves axially back and forth in a guide tube (2); a spring mechanism (4, 15, 16) is provided, which exerts a force on the hammer (1) and can set the hammer (1) into a movement toward a tool (3) that can be inserted into the hand machine tool, wherein means (8, 10, 13, 14) are provided, which set the hammer (1) into a motion counter to the force of the spring mechanism (4, 15, 16) after each impact in order to stress this spring mechanism and, after the stressing of the spring mechanism (4, 15, 16), these means (8, 10, 13, 14) abruptly release the hammer (1) again so that, driven by the spring mechanism (4, 15, 16), it flies toward the tool (3).
2. The hand machine tool as recited in claim 1 ,
wherein the means (8, 10, 13, 14) are comprised of a drive mechanism that produces a frictional engagement with the hammer (1) after an impact has been imparted, moves it counter to the force of the spring mechanism (4, 15, 16), and then releases the frictional engagement again as soon as the hammer (1) has reached a certain position in its movement counter to the force of the spring mechanism (4, 15, 16).
3. The hand machine tool as recited in claim 1 ,
wherein the spring mechanism (4, 15, 16) is comprised of a pressure reservoir (4), which is filled with a compressible medium and is situated in the guide tube (2) on the side of the hammer (1) oriented away from the tool (3).
4. The hand machine tool as recited in claim 3 ,
wherein a pump (7) is able to supply compressible medium to the pressure reservoir (4).
5. The hand machine tool as recited in claim 1 ,
wherein the spring mechanism (14, 15) is comprised of one or more compression springs (15) and/or tension springs (16), which is/are supported against the hammer (1) on the one hand and against a shoulder (5, 17) that is stationary in the movement direction of the hammer (1) on the other hand.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004022623.7 | 2004-05-07 | ||
DE102004022623A DE102004022623A1 (en) | 2004-05-07 | 2004-05-07 | Hand tool with a striking mechanism |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050247462A1 true US20050247462A1 (en) | 2005-11-10 |
Family
ID=34684124
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/120,355 Abandoned US20050247462A1 (en) | 2004-05-07 | 2005-05-03 | Hand machine tool with a hammer mechanism |
Country Status (5)
Country | Link |
---|---|
US (1) | US20050247462A1 (en) |
CN (1) | CN1693034A (en) |
DE (1) | DE102004022623A1 (en) |
FR (1) | FR2869825A1 (en) |
GB (1) | GB2413777A (en) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7198116B1 (en) * | 2005-10-25 | 2007-04-03 | Xiaojun Chen | Wholly air-controlled impact mechanism for high-speed energy-accumulating pneumatic wrench |
US20090020299A1 (en) * | 2007-07-19 | 2009-01-22 | Hilti Aktiengesellschaft | Hand-held power tool with a pneumatic percussion mechanism |
US20110150590A1 (en) * | 2009-12-18 | 2011-06-23 | Buchner David J | Installation System for Ceiling Mounted Items |
US20130277077A1 (en) * | 2012-04-19 | 2013-10-24 | Hilti Aktiengesellschaft | Machine tool |
CN104227666A (en) * | 2013-06-20 | 2014-12-24 | 苏州宝时得电动工具有限公司 | Electric hammer |
JP2015517342A (en) * | 2010-12-29 | 2015-06-22 | オルトー テクノロジース エル エル シーOrtho Technologies,Llc | Electric motor driven instrument for applying orthopedic impact |
US10420567B2 (en) | 2010-12-29 | 2019-09-24 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
US11076903B2 (en) | 2016-08-31 | 2021-08-03 | DePuy Synthes Products, Inc. | Orthopedic device delivering a controlled, repeatable impact |
US11134962B2 (en) | 2016-08-31 | 2021-10-05 | DePuy Synthes Products, Inc. | Orthopedic impacting device having a launched mass delivering a controlled, repeatable and reversible impacting force |
US11579344B2 (en) | 2012-09-17 | 2023-02-14 | Government Of The United States Of America, As Represented By The Secretary Of Commerce | Metallic grating |
SE2230406A1 (en) * | 2022-12-09 | 2024-03-12 | Atlas Copco Ind Technique Ab | Hand-held percussive tool |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010029918A1 (en) * | 2010-06-10 | 2011-12-15 | Hilti Aktiengesellschaft | machine tool |
CN101949260B (en) * | 2010-07-22 | 2013-07-24 | 浙江师范大学 | Auxiliary hammer mechanism of percussive hammer capable of releasing after storing energy and energy-storage type percussive hammer |
WO2012024843A1 (en) * | 2010-08-27 | 2012-03-01 | Bosch Power Tools (China) Co., Ltd. | Striking mechanism |
CN110340852B (en) * | 2019-08-13 | 2024-02-27 | 油特机械工具(大连)有限公司 | High-precision long-life rechargeable point punching gun |
CN112296947A (en) * | 2020-02-27 | 2021-02-02 | 杨新军 | Slider striking formula electric impact drill |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1464824A (en) * | 1922-03-22 | 1923-08-14 | Electric Hammer Company | Electric hammer |
USRE20365E (en) * | 1937-05-18 | Portable power hammer | ||
US2145760A (en) * | 1936-07-24 | 1939-01-31 | Milwaukee Electric Tool Corp | Electric hammer |
US2501542A (en) * | 1947-10-15 | 1950-03-21 | Harold S Sheldon | Hammer tool |
US2655921A (en) * | 1951-07-09 | 1953-10-20 | Edward J Haboush | Vibratory tool for operating bone sets, bone chisels, and bone nail drivers |
US2905034A (en) * | 1958-04-18 | 1959-09-22 | Ralph M Turner | Reciprocatory impact hand tool |
US3599731A (en) * | 1969-12-01 | 1971-08-17 | Del Guy Inc | Drilling apparatus |
US3887018A (en) * | 1974-01-25 | 1975-06-03 | Murray L Jayne | Fluid driven hammers |
US4030556A (en) * | 1975-09-22 | 1977-06-21 | Phillips Raymond J | Miniature impact tool |
US4567951A (en) * | 1983-02-12 | 1986-02-04 | Robert Bosch Gmbh | Hammer drill |
US5117923A (en) * | 1989-01-11 | 1992-06-02 | Sulzer Brothers Limited | Hydraulic jackhammer |
US6116352A (en) * | 1998-03-10 | 2000-09-12 | Robert Bosch Gmbh | Drilling and/or percussion power tool |
US6523622B1 (en) * | 1998-09-23 | 2003-02-25 | Wacker Construction Equipment Ag | Pneumatic percussion power tool with pneumatic returning spring |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1124527A (en) * | 1966-05-19 | 1968-08-21 | Sonomotive Engineers Ltd | Improvements in or relating to percussive tools and machines |
DE2346519A1 (en) * | 1972-09-18 | 1974-04-11 | Technology Inc Const | HYDRAULICALLY OPERATED IMPACT DEVICE |
DE3428333C1 (en) * | 1984-08-01 | 1986-03-13 | Byrne, Rodger J., 4005 Meerbusch | Electric tacker |
-
2004
- 2004-05-07 DE DE102004022623A patent/DE102004022623A1/en not_active Withdrawn
-
2005
- 2005-05-03 FR FR0551153A patent/FR2869825A1/en not_active Withdrawn
- 2005-05-03 US US11/120,355 patent/US20050247462A1/en not_active Abandoned
- 2005-05-05 GB GB0509188A patent/GB2413777A/en not_active Withdrawn
- 2005-05-08 CN CNA2005100712774A patent/CN1693034A/en active Pending
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USRE20365E (en) * | 1937-05-18 | Portable power hammer | ||
US1464824A (en) * | 1922-03-22 | 1923-08-14 | Electric Hammer Company | Electric hammer |
US2145760A (en) * | 1936-07-24 | 1939-01-31 | Milwaukee Electric Tool Corp | Electric hammer |
US2501542A (en) * | 1947-10-15 | 1950-03-21 | Harold S Sheldon | Hammer tool |
US2655921A (en) * | 1951-07-09 | 1953-10-20 | Edward J Haboush | Vibratory tool for operating bone sets, bone chisels, and bone nail drivers |
US2905034A (en) * | 1958-04-18 | 1959-09-22 | Ralph M Turner | Reciprocatory impact hand tool |
US3599731A (en) * | 1969-12-01 | 1971-08-17 | Del Guy Inc | Drilling apparatus |
US3887018A (en) * | 1974-01-25 | 1975-06-03 | Murray L Jayne | Fluid driven hammers |
US4030556A (en) * | 1975-09-22 | 1977-06-21 | Phillips Raymond J | Miniature impact tool |
US4567951A (en) * | 1983-02-12 | 1986-02-04 | Robert Bosch Gmbh | Hammer drill |
US5117923A (en) * | 1989-01-11 | 1992-06-02 | Sulzer Brothers Limited | Hydraulic jackhammer |
US6116352A (en) * | 1998-03-10 | 2000-09-12 | Robert Bosch Gmbh | Drilling and/or percussion power tool |
US6523622B1 (en) * | 1998-09-23 | 2003-02-25 | Wacker Construction Equipment Ag | Pneumatic percussion power tool with pneumatic returning spring |
Cited By (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070089890A1 (en) * | 2005-10-25 | 2007-04-26 | Xiaojun Chen | Wholly air-controlled impact mechanism for high-speed energy-accumulating pneumatic wrench |
US7198116B1 (en) * | 2005-10-25 | 2007-04-03 | Xiaojun Chen | Wholly air-controlled impact mechanism for high-speed energy-accumulating pneumatic wrench |
EP2017038B1 (en) * | 2007-07-19 | 2016-03-09 | HILTI Aktiengesellschaft | Hand tool machine with pneumatic striking mechanism |
US20090020299A1 (en) * | 2007-07-19 | 2009-01-22 | Hilti Aktiengesellschaft | Hand-held power tool with a pneumatic percussion mechanism |
US8267189B2 (en) * | 2007-07-19 | 2012-09-18 | Hilti Aktiengesellschaft | Hand-held power tool with a pneumatic percussion mechanism |
US20110150590A1 (en) * | 2009-12-18 | 2011-06-23 | Buchner David J | Installation System for Ceiling Mounted Items |
US9931721B2 (en) * | 2009-12-18 | 2018-04-03 | Accelerated Fastening, LLC | Installation system for ceiling mounted items |
USRE47963E1 (en) | 2010-12-29 | 2020-04-28 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
USRE48387E1 (en) | 2010-12-29 | 2021-01-12 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
EP2846723A4 (en) * | 2010-12-29 | 2016-04-13 | Ortho Technologies Llc | Electric motor driven tool for orthopedic impacting |
EP3162314A1 (en) * | 2010-12-29 | 2017-05-03 | Medical Enterprises, LLC | Electric motor driven tool for orthopedic impacting |
JP2018020183A (en) * | 2010-12-29 | 2018-02-08 | メディカル エンタープライゼス, エルエルシー | Electric motor driven tool for orthopedic impacting |
USRE49666E1 (en) | 2010-12-29 | 2023-09-26 | Depuy Synthes Products, Inc | Electric motor driven tool for orthopedic impacting |
US10420567B2 (en) | 2010-12-29 | 2019-09-24 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
US11076867B2 (en) | 2010-12-29 | 2021-08-03 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
USRE47997E1 (en) | 2010-12-29 | 2020-05-19 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
USRE48184E1 (en) | 2010-12-29 | 2020-09-01 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
USRE48251E1 (en) | 2010-12-29 | 2020-10-13 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
JP2015517342A (en) * | 2010-12-29 | 2015-06-22 | オルトー テクノロジース エル エル シーOrtho Technologies,Llc | Electric motor driven instrument for applying orthopedic impact |
USRE48388E1 (en) | 2010-12-29 | 2021-01-12 | DePuy Synthes Products, Inc. | Electric motor driven tool for orthopedic impacting |
US20130277077A1 (en) * | 2012-04-19 | 2013-10-24 | Hilti Aktiengesellschaft | Machine tool |
US11579344B2 (en) | 2012-09-17 | 2023-02-14 | Government Of The United States Of America, As Represented By The Secretary Of Commerce | Metallic grating |
US11733439B2 (en) | 2012-09-17 | 2023-08-22 | Government Of The United States Of America. As Represented By The Secretary Of Commerce | Process for making a metallic grating |
CN104227666A (en) * | 2013-06-20 | 2014-12-24 | 苏州宝时得电动工具有限公司 | Electric hammer |
US11076903B2 (en) | 2016-08-31 | 2021-08-03 | DePuy Synthes Products, Inc. | Orthopedic device delivering a controlled, repeatable impact |
US11083512B2 (en) | 2016-08-31 | 2021-08-10 | DePuy Synthes Products, Inc. | Orthopedic device delivering a controlled, repeatable impact |
US11134962B2 (en) | 2016-08-31 | 2021-10-05 | DePuy Synthes Products, Inc. | Orthopedic impacting device having a launched mass delivering a controlled, repeatable and reversible impacting force |
US11696770B2 (en) | 2016-08-31 | 2023-07-11 | Depuy Synthes Products, Inc | Orthopedic impacting device having a launched mass delivering a controlled, repeatable and reversible impacting force |
SE2230406A1 (en) * | 2022-12-09 | 2024-03-12 | Atlas Copco Ind Technique Ab | Hand-held percussive tool |
SE545906C2 (en) * | 2022-12-09 | 2024-03-12 | Atlas Copco Ind Technique Ab | Hand-held percussive tool |
Also Published As
Publication number | Publication date |
---|---|
GB2413777A (en) | 2005-11-09 |
CN1693034A (en) | 2005-11-09 |
DE102004022623A1 (en) | 2005-12-08 |
GB0509188D0 (en) | 2005-06-15 |
FR2869825A1 (en) | 2005-11-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20050247462A1 (en) | Hand machine tool with a hammer mechanism | |
JP5130207B2 (en) | Blowing device with electric force type linear drive | |
US7252157B2 (en) | Power tool | |
US9044848B2 (en) | Impact tool having a vibration reducing member | |
US8267189B2 (en) | Hand-held power tool with a pneumatic percussion mechanism | |
RU2482957C2 (en) | Hand-held machine | |
JPS59156678A (en) | Boring hammer | |
US20100012337A1 (en) | Percussive mechanism of an electric hand-held machine tool | |
US20160271779A1 (en) | Handheld Machine Tool | |
US4102410A (en) | Resilient work-coupled impact device | |
CN101104261A (en) | Vibration reduction apparatus for power tool and power tool incorporating such apparatus | |
JP5551461B2 (en) | Pneumatic striking mechanism | |
JP5100171B2 (en) | Impact type work tool | |
EP1872912A3 (en) | Beat piece support structure for a hammer drill | |
CN109070325B (en) | Hand-held power tool | |
US9498874B2 (en) | Hammer drill | |
EP1980371B1 (en) | Impact tool | |
US1841781A (en) | Blow striking implement | |
CN101795824A (en) | Recoilless hammer | |
US8096369B2 (en) | Striking mechanism for a handheld electric power tool | |
EP3603892B1 (en) | Hammer drill | |
US1842302A (en) | Mechanically actuated reciprocating tool | |
US20110308829A1 (en) | Nail gun | |
US1127535A (en) | Impact-machine. | |
US1183846A (en) | Rock-drill. |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MEIXNER, GERHARD;HENKE, THILO;LENNARTZ, JUERGEN;REEL/FRAME:016315/0146;SIGNING DATES FROM 20050421 TO 20050426 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |