WO2022000067A1 - Impact mechanism for rotary tool - Google Patents
Impact mechanism for rotary tool Download PDFInfo
- Publication number
- WO2022000067A1 WO2022000067A1 PCT/CA2020/050901 CA2020050901W WO2022000067A1 WO 2022000067 A1 WO2022000067 A1 WO 2022000067A1 CA 2020050901 W CA2020050901 W CA 2020050901W WO 2022000067 A1 WO2022000067 A1 WO 2022000067A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- anvil
- hammer
- lobes
- longitudinal axis
- face
- Prior art date
Links
- 230000007246 mechanism Effects 0.000 title claims abstract description 82
- 238000006073 displacement reaction Methods 0.000 claims description 15
- 239000000758 substrate Substances 0.000 description 5
- 238000009434 installation Methods 0.000 description 3
- 238000012360 testing method Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008520 organization Effects 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
- B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
- B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H33/00—Gearings based on repeated accumulation and delivery of energy
- F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels
Definitions
- the present invention relates to impact mechanisms impact apparatuses, and more particularly to such impact mechanisms that are efficient at producing impact torque and impact force.
- Impact apparatuses are used to forcefully turn threaded fasteners that are otherwise difficult to turn when driving threaded fasteners into a substrate. Such difficulty in turning threaded fasteners is typically encountered when driving them into a substrate such as concrete, but can be encountered in many other situations, especially in the construction industry.
- an impact apparatus is directly related to the impact torque supplied by the impact mechanism used in the impact apparatus and indirectly by the drive motor, such as a drive motor found in an electric drill.
- the entire power tool industry has sought to develop better impact apparatuses that are capable of delivering a greater amplitude of impact torque by increasing the torque of the drive motor, and by increasing the spring force of the power spring, which is typically, a coil spring.
- prior art impact apparatuses employ impact mechanisms that have a maximum distance between the anvil lobes in order to give the drive motor and the power spring as much time as possible to rotationally accelerate the hammer member. Accordingly, known prior art impact mechanisms have two diametrically opposed hammer lobes that act on two diametrically opposed anvil lobes. Although it is theoretically possible to have only one hammer lobe and one anvil lobe in order to maximize the distance, between consecutively impacted anvil lobes the unbalanced forces that would be created during use make this configuration impractical.
- the impact mechanism comprises a drive shaft defining a longitudinal axis, and operatively carrying a hammer member for rotational movement about the longitudinal axis and longitudinal movement between a forward position and a rearward position that define a longitudinal clearing displacement therebetween, and operatively carrying an anvil member for rotational movement about the longitudinal axis.
- the hammer member has first, second and third hammer lobes spaced radially around the longitudinal axis.
- the anvil member has first, second and third anvil lobes spaced radially around the longitudinal axis, to define an overall travel arc between impact faces of adjacent anvil lobes.
- a spring is operatively interconnected between the drive shaft and the hammer member for temporarily storing energy from the relative rotation of the drive shaft with respect to the hammer member and subsequently releasing stored energy to forcibly rotate the hammer member about the longitudinal axis with respect to the anvil member.
- a tool retainer is connected in torque transmitting relation to the anvil member for rotation therewith.
- the hammer member and the anvil member go through consecutive impact cycles wherein the hammer lobes are initially in lateral engagement with the anvil lobes, the hammer lobes move rearwardly with respect the longitudinal axis through the longitudinal clearing displacement to be longitudinally positioned to subsequently permit the spring to forcefully rotate the hammer past the engaged anvil lobes, and subsequently to forcefully impact the rotationally next ones of the anvil lobes, to thereby create the corresponding impact torque for the anvil member about the longitudinal axis.
- Figure 1 is a side elevational view from the front of the first illustrated embodiment of the impact mechanism according to the present invention
- Figure 2 is a perspective view from the back end of the first illustrated embodiment of the impact mechanism of Figure 1;
- Figure 3 is a back end elevational view of the first illustrated embodiment of the impact mechanism of Figure 1;
- Figure 4 is a perspective view from the front of the first illustrated embodiment of the impact mechanism of Figure 1, with a tool bit, specifically a socket, operatively engaged thereon, with the hammer member in a forward position with respect to the anvil member;
- Figure 5 is a perspective view from the front of the first illustrated embodiment of the impact mechanism of Figure 1, with the hammer member in a forward position with respect to the anvil member and just about to start an impact cycle;
- Figure 6 is a perspective view from the front of the first illustrated embodiment of the impact mechanism of Figure 1, with the hammer member in a rearward position with respect to the anvil member and having just started an impact cycle;
- Figure 7 is a perspective view from the front of the first illustrated embodiment of the impact mechanism of Figure 1 and similar to Figure 6, but with the hammer member having moved rotationally such that the hammer lobes have moved almost all the way across the anvil lobes and about be propelled forcefully to the next anvil lobes;
- Figure 8 is a front-end view of the hammer member of the second illustrated embodiment of the impact mechanism according to the present invention.
- Figure 9 is a graph showing the torque, as recorded in tests, achieved by various configurations of impact mechanisms according to the present invention and also by prior art impact mechanisms.
- Figures 1 through 9 of the drawings it will be noted that Figures 1 through 7show a first illustrated embodiment of the impact mechanism according to the present invention, Figure 8shows a second illustrated embodiment according to the impact mechanism of the present invention, and Figure 9 shows a graph showing the torque, as recorded in tests, achieved by various configurations of impact mechanisms according to the present invention and also by prior art impact mechanisms.
- FIG. 1 through 7 show a first illustrated embodiment of the impact mechanism according to the present invention, as indicated by general reference numeral 100.
- the impact mechanism 100 is part of an impact apparatus (the housing is not shown) for use with a drive motor (not specifically shown), such as the drive motor of an electric drill (not specifically shown). Any other suitable drive mechanism could be used.
- the impact mechanism 100 comprises a drive shaft 120 that engages a rotatable output, namely the chuck of the electric drill.
- the chuck-engageable back end portion 122 of the drive shaft 120 is preferably hexagonally shaped (as best seen in Figure 4), or of any other suitable shape, for secure engagement into the chuck of the electric drill for rotation therewith.
- the chuck is rotationally driven by the drive motor of the electric drill for rotation therewith about a longitudinal axis “L” about which the drive shaft 120 rotates.
- the drive shaft 120 defines the longitudinal axis “L” and operatively carries a hammer member 130 and an anvil member 140 as will be described in greater detail subsequently.
- the hammer member 130 has a first hammer lobe 131, a second hammer lobe 132, a third hammer lobe 133, and a fourth hammer lobe 134.
- the first hammer lobe 131, the second hammer lobe 132, the third hammer lobe, and the fourth hammer lobe 134 are spaced equally radially around the longitudinal axis “L”.
- the angular displacement around the longitudinal axis “L” of the centre of the first hammer lobe 131, the centre of the second hammer lobe 132, and the centre of the third hammer lobe 133, and the fourth hammer lobe 134, with respect to the adjacent hammer lobes is ninety (90) degrees.
- the ratio of the arcuate width 139b of the base137b of each hammer lobe 131,132,133,134about the longitudinal axis to the arcuate width 139t of the tip 137t of each hammer lobe 131,132,133,134 about the longitudinal axis “L” is between about 2:1 and 4:1.
- the anvil member 140 has a first anvil lobe 141, a second anvil lobe 142, a third anvil lobe 143, and a fourth anvil lobe 144.
- the first anvil lobe 141, the second anvil lobe 142, the third anvil lobe 143, and the fourth anvil lobe 144 are spaced equally radially around the longitudinal axis “L”.
- the angular displacement around the longitudinal axis “L” of the centre of the first anvil lobe 141 , the centre of the second anvil lobe 142, and the centre of the third anvil lobe 143, and the fourth anvil lobe 144, with respect to the adjacent hammer lobes is ninety (90) degrees.
- the ratio of the arcuate width 149b of the base147b of each anvil lobe141,142,143,144about the longitudinal axis“L” to the arcuate width 149t of the tip147t of each anvil lobe 141 ,142,143,144 about the longitudinal axis is between about 2:1 and 4:1.
- the drive shaft 120 defines the longitudinal axis “L” and operatively carries the hammer member 130 for rotational movement of the hammer member 130 about the longitudinal axis “L” and also for longitudinal movement of the hammer member 130 between a forward position, as is best seen in Figures 1 through 5, and a rearward position, as is best seen in Figures 6 and 7.
- the forward position and the rearward position together define a longitudinal clearing displacement “LCD” therebetween.
- the longitudinal clearing displacement “LCD” is the distance that the hammer member 130 needs to travel longitudinally rearwardly along the longitudinal axis “L” to get the hammer lobes 131, 132, 133, 134 past the anvil lobes 141, 142, 143, 144.
- the first hammer lobe 131, the second hammer lobe 132, the third hammer lobe 133, and the fourth hammer lobe 134 each impact the first anvil lobe 141, the second anvil lobe 142, the third anvil lobe 143, and the fourth anvil lobe 144. More specifically, the first hammer lobe 131 consecutively impacts the first anvil lobe 141, the second anvil lobe 142, the third anvil lobe 143, and the fourth anvil lobe 144.
- the second hammer lobe 132 consecutively impacts the second anvil lobe 142, the third anvil lobe 143, the fourth anvil lobe 144, and the first anvil lobe 141.
- the third hammer lobe 133 consecutively impacts the third anvil lobe 143, the fourth anvil lobe 144, the first anvil lobe 141, and the second anvil lobe 142.
- the fourth hammer lobe 134 consecutively impacts the fourth anvil lobe 144, the first anvil lobe 141, the second anvil lobe 142, and the third anvil lobe 143.
- a power spring 160 operatively interconnected between the drive shaft 120 and the hammer member 130 for temporarily storing energy from the relative rotation of the drive shaft 120 with respect to the hammer member 130 and subsequently releasing stored energy to forcibly rotate the hammer member 130 about the longitudinal axis “L” with respect to the anvil member 140.
- the power spring 160 provides stores potential energy to thereby provide kinetic energy for the impact forces to be transmitted from the hammer lobes 131,132,131,134 to the anvil lobes 141,142,143,144.
- the power spring 160 biases the hammer member 130 at least towards the forward longitudinal position and preferably to the forward longitudinal position.
- the hammer member 130 and the anvil member 140 go through consecutive impact cycles wherein the hammer lobes 131, 132, 133, 134 are initially in lateral engagement with the anvil lobes 141, 142, 143, 144.
- the hammer lobes 131, 132, 133, 134 move rearwardly along the longitudinal axis “L” through the longitudinal clearing displacement “LCD” to be longitudinally positioned to rotationally move past the engaged anvil lobes 141, 142, 143, 144 and subsequently to forcefully impact the rotationally next ones of the anvil lobes 141, 142, 143, 144, to thereby create the corresponding impact torque for the anvil member 140 about the longitudinal axis “L”, to thereby rotationally drive a threaded fastener.
- each of the hammer lobes 131, 132, 133, 134 has a first face 136 and a second face 138 and each of the anvil lobes 141, 142, 143, 144 has a first face 146 and a second face 148.
- the first faces 136 of the hammer lobes 131, 132, 133, 134 and the first faces 146 of the anvil lobes 141, 142, 143, 144 all face in a clockwise direction.
- the second faces 138 of the hammer lobes 131, 132, 133, 134 and the second faces 148 of the anvil lobes 141, 142, 143, 144 all face in a counterclockwise direction.
- the arcuate width 149t of the tip147t of each anvil lobel 41 , 142, 143, 144 about the longitudinal axis “L” to the arcuate distance 170 between the first face 146 of one anvil lobe, such as the first anvil lobe 141, and the second face 148 of the adjacent anvil lobe, such as the fourth anvil lobe 144, is between about 5:1 and 15:1.
- the ratio of the arcuate width 139b of the base139b of the each hammer lobe 131, 132,133, 134about the longitudinal axis “L” to the arcuate width 139t of the tip 137t of each hammer lobe 131,132,133,134 about the longitudinal axis “L” is between about 2:1 and 4:1.
- the ratio of the arcuate width 149b of the base 147b of each anvil lobe 141, 142, 143, 144 about the longitudinal axis“L” to the arcuate width 149t of the tip 147t of each anvil lobe 141, 142, 143, 144 about the longitudinal axis “L” is between about 2:1 and 4:1.
- the first faces 146 and the second faces 148 of the anvil lobes 141,142,143,144 are oriented so as to be skew with respect to the longitudinal axis “L” and the first faces 136 and the second faces 136 of the hammer lobes 131,132,133,134 are oriented so as to be skew with respect to the longitudinal axis “L”.
- the drive shaft 120 also operatively carries an anvil member 140 for rotational movement about the longitudinal axis “L”.
- a tool retainer 150 is securely connected in torque transmitting relation to the anvil member 140 for rotation therewith.
- a socket 152 is removably mounted on the tool retainer 150.
- the second is the arc of free travel of the hammer member 130, as indicated by the reference letters “FT”, about the longitudinal axis “L” when the second face 138 of each hammer lobe 131, 132, 133, 134 rotationally passes the first face 146 of the anvil lobes 141, 142, 143, 144 to the next impact with the anvil lobes 141, 142, 143, 144, whereat the first face 136 of each hammer lobe 131, 132, 133, 134 impacts the second face 148 of each anvil lobe 141, 142, 143, 144.
- each hammer lobe 131, 132, 133, 134 contacts the first face 146 of a corresponding anvil lobe 141, 142, 143, 144.
- FIG 8 shows a second illustrated embodiment of the impact mechanism according to the present invention, as indicated by general reference numeral 200.
- the second illustrated embodiment impact mechanism 200 is similar to the first illustrated embodiment impact mechanism 100, except that in the second illustrated embodiment impact mechanism 200, the hammer member230 has only a first hammer lobe 231, a second hammer lobe 232, a third hammer lobe 233, but not a fourth hammer lobe.
- the first 231, second 232, and third 233 hammer lobes are spaced equally radially around the longitudinal axis “L”.
- the angular displacement around the longitudinal axis “L” of the centre of the first hammer lobe 231, the centre of the second hammer lobe 232, and the centre of the third hammer lobe 232 with respect to the adjacent hammer lobes is one hundred twenty (120) degrees.
- the anvil member (not specifically shown) has only a first anvil lobe, a second anvil lobe, a third anvil lobe, but not a fourth anvil lobe.
- the first, second, and third anvil lobes are spaced equally radially around the longitudinal axis “L”.
- the angular displacement around the longitudinal axis “L” of the centre of the first anvil lobe, the centre of the anviL lobe, and the centre of the third anvil lobe with respect to the adjacent anvil lobes is one hundred twenty (120) degrees.
- RPM for impact mechanisms having three (3) hammer lobes on the hammer member and three (3) anvil lobes on the anvil member, having four (4) hammer lobes on the hammer member and four (4) anvil lobes on the anvil member, and five (5) hammer lobes on the hammer member and five (5) anvil lobes on the anvil member, as compared to prior art impact mechanisms that have two (2) hammer lobes on the hammer member and two (2) anvil lobes on the anvil member.
- the present invention provides an impact mechanism that is operatively engageable with the chuck of an electric drill or the like, which impact mechanism provides a high impact rotational force, which impact mechanism works from low impact forces through high impact forces, which impact mechanism is readily adjustable from low impact forces through high impact forces, which impact mechanism is accurately settable adjustable from low impact forces through high impact forces, which impact mechanism permits setting to a predetermined torque such that threaded fasteners can be properly installed in order to meet specified standards, which impact mechanism precludes threaded fasteners from being driven too far into a substrate, which impact mechanism precludes threaded fasteners from breaking during installation, all of which features are unknown in the prior art.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CA2020/050901 WO2022000067A1 (en) | 2020-06-29 | 2020-06-29 | Impact mechanism for rotary tool |
GB2301160.4A GB2612490A (en) | 2020-06-29 | 2020-06-29 | Impact mechanism for rotary tool |
EP20943423.2A EP4171881A1 (en) | 2020-06-29 | 2020-06-29 | Impact mechanism for rotary tool |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CA2020/050901 WO2022000067A1 (en) | 2020-06-29 | 2020-06-29 | Impact mechanism for rotary tool |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2022000067A1 true WO2022000067A1 (en) | 2022-01-06 |
Family
ID=79317546
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CA2020/050901 WO2022000067A1 (en) | 2020-06-29 | 2020-06-29 | Impact mechanism for rotary tool |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP4171881A1 (en) |
GB (1) | GB2612490A (en) |
WO (1) | WO2022000067A1 (en) |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3001428A (en) * | 1960-02-23 | 1961-09-26 | Master Power Corp | Rotary impact wrench |
JPH01170570U (en) * | 1988-05-20 | 1989-12-01 | ||
US5908076A (en) * | 1997-01-10 | 1999-06-01 | Power Tool Holders Incorporated | Impact tool driver |
US7588093B2 (en) * | 2007-09-05 | 2009-09-15 | Grand Gerard M | Impact mechanism |
US20140020921A1 (en) * | 2010-10-28 | 2014-01-23 | Chuan Cheong Yew | Mechanical impact mechanism for a handheld power tool |
US9272400B2 (en) * | 2012-12-12 | 2016-03-01 | Ingersoll-Rand Company | Torque-limited impact tool |
US20170259412A1 (en) * | 2014-07-31 | 2017-09-14 | Hitachi Koki Co., Ltd. | Impact tool |
US20180117745A1 (en) * | 2015-01-30 | 2018-05-03 | Hitachi Koki Co., Ltd. | Impact tool |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01170570A (en) * | 1987-12-25 | 1989-07-05 | Nippon Steel Corp | Production of oxide dispersing type steel pipe having excellent high temperature strength |
-
2020
- 2020-06-29 GB GB2301160.4A patent/GB2612490A/en active Pending
- 2020-06-29 EP EP20943423.2A patent/EP4171881A1/en active Pending
- 2020-06-29 WO PCT/CA2020/050901 patent/WO2022000067A1/en unknown
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3001428A (en) * | 1960-02-23 | 1961-09-26 | Master Power Corp | Rotary impact wrench |
JPH01170570U (en) * | 1988-05-20 | 1989-12-01 | ||
US5908076A (en) * | 1997-01-10 | 1999-06-01 | Power Tool Holders Incorporated | Impact tool driver |
US7588093B2 (en) * | 2007-09-05 | 2009-09-15 | Grand Gerard M | Impact mechanism |
US20140020921A1 (en) * | 2010-10-28 | 2014-01-23 | Chuan Cheong Yew | Mechanical impact mechanism for a handheld power tool |
US9272400B2 (en) * | 2012-12-12 | 2016-03-01 | Ingersoll-Rand Company | Torque-limited impact tool |
US20170259412A1 (en) * | 2014-07-31 | 2017-09-14 | Hitachi Koki Co., Ltd. | Impact tool |
US20180117745A1 (en) * | 2015-01-30 | 2018-05-03 | Hitachi Koki Co., Ltd. | Impact tool |
Also Published As
Publication number | Publication date |
---|---|
GB202301160D0 (en) | 2023-03-15 |
GB2612490A (en) | 2023-05-03 |
EP4171881A1 (en) | 2023-05-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10569394B2 (en) | Rotary impact device | |
US20240082997A1 (en) | Impact wrench having dynamically tuned drive components and method thereof | |
CN100491079C (en) | Principal axis lock devices for screwdrivers | |
CN101743375B (en) | For the epicyclic train of electric tool, rotary power tool and wireless transfer gear train | |
US9555532B2 (en) | Rotary impact tool | |
CN105658379A (en) | Impact tool | |
US20120118596A1 (en) | Impact tool | |
US20230226670A1 (en) | Screw Gun with Additional Trigger | |
US3606931A (en) | Rotary impact motor | |
WO2022000067A1 (en) | Impact mechanism for rotary tool | |
US6581697B1 (en) | Power impact tool torque apparatus | |
JP4013782B2 (en) | Rotating hammer tool | |
EP2132005B1 (en) | Rotary percussion mechanism | |
EP3577317A1 (en) | Fastener installation system and method | |
US3666023A (en) | Rotational impact tool | |
US8857066B2 (en) | Power saw including an impact mechanism | |
JP3767475B2 (en) | Impact tools | |
JP6156785B2 (en) | Impact tool | |
US20230013688A1 (en) | Impact tool with tapered anvil wing design | |
DE1478877A1 (en) | Impact tightening wrench | |
CA3098780A1 (en) | Impact apparatus and impact mechanism with variable pitch spring | |
EP0149874B1 (en) | An impact wrench | |
US20210101466A1 (en) | Method of applying a engageable mechanism for supplying both intermittent impulses and smooth rotary motion as needed so that they may be applied within a vehicle's powertrain and a System for managing a Rotary Impact Powertrain in a vehicle and an apparatus for supplying both intermittent impulses and smooth rotary motion as needed so that they may be applied within a vehicle's powertrain | |
JP3492789B2 (en) | Electric shock tool | |
JP2001088049A (en) | Impact tool |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 20943423 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 202301160 Country of ref document: GB Kind code of ref document: A Free format text: PCT FILING DATE = 20200629 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 2020943423 Country of ref document: EP Effective date: 20230130 |
|
ENP | Entry into the national phase |
Ref document number: 2020943423 Country of ref document: EP Effective date: 20230130 |