CN1792563A - Drive mechanism for a power tool - Google Patents

Drive mechanism for a power tool Download PDF

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Publication number
CN1792563A
CN1792563A CN200510135808.1A CN200510135808A CN1792563A CN 1792563 A CN1792563 A CN 1792563A CN 200510135808 A CN200510135808 A CN 200510135808A CN 1792563 A CN1792563 A CN 1792563A
Authority
CN
China
Prior art keywords
housing
driving mechanism
reciprocating motion
ferrule
motor
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.)
Pending
Application number
CN200510135808.1A
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Chinese (zh)
Inventor
克劳斯-迪特尔·阿里希
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Black and Decker Inc
Original Assignee
Black and Decker Inc
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 Black and Decker Inc filed Critical Black and Decker Inc
Publication of CN1792563A publication Critical patent/CN1792563A/en
Pending legal-status Critical Current

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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
    • B25D11/005—Arrangements for adjusting the stroke of the impulse member or for stopping the impact action when the tool is lifted from the working surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—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
    • 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
    • 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
    • B25D16/00—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
    • B25D16/006—Mode changers; Mechanisms connected thereto
    • 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
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/26—Lubricating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/008—Cooling means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/02—Construction of casings, bodies or handles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • 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
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Landscapes

  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Surgical Instruments (AREA)
  • Dry Shavers And Clippers (AREA)
  • Drilling And Boring (AREA)
  • Valve Device For Special Equipments (AREA)
  • Cutting Tools, Boring Holders, And Turrets (AREA)
  • Gripping On Spindles (AREA)
  • Braking Systems And Boosters (AREA)
  • Turning (AREA)
  • Debugging And Monitoring (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Electrophonic Musical Instruments (AREA)
  • Road Repair (AREA)
  • Stored Programmes (AREA)
  • Automatic Tool Replacement In Machine Tools (AREA)

Abstract

A driving mechanism for a hammer drill comprises a hollow piston (558) having a cylindrical bearing which is suitable for receiving a crank pin so that the hollow piston (558) reciprocates in a main shaft (548). Multiple longitudinal ridges (559) are formed on the outer surface of the hollow piston to reduce the contact surface area between the hollow piston (558) and the main shaft (548), and multiple grooves (561) are formed in the gaps between the ridges. The grooves (561) are suitable for maintain lubricant (558) so as to reduce the friction contact therebetween.

Description

The driving mechanism that is used for power tool
Technical field
The present invention relates to be used for the driving mechanism of power tool and the power tool of this mechanism is housed.The present invention specifically but be not ad hoc to relate to the driving mechanism that is used for hammer drill and the hammer drill that this mechanism is housed.
Background technology
Hammer drill is usually can be at the power tool of three kinds of mode of operation works.Hammer drill has cutter head, and it can be operated under hammering pattern, rotary mode and hammering rotation integrated mode.For hammering and hammering rotation integrated mode, because piston is used to produce positice ground effect and rams to affact, this is ramed and the reciprocating motion of piston can be converted into the hammering action, therefore rotatablely moving of tool motor output shaft need be converted into the reciprocating motion of piston.
A kind of mechanism that is used for rotatablely moving of the output shaft of motor is converted into the hammering action is described in GB1343206.With reference to Figure 21 of the cross-sectional view of the driving mechanism that GB1343206 is shown, Figure 22 of partial cross sectional view of the driving mechanism of Figure 21 is shown, and illustrate along Figure 23 of the cross-sectional view of the line V-V of Figure 22, electric hammer 101 has the motor shell 102 that has CD-ROM drive motor and gear unit (not shown).Hollow cylinder guide sleeve 107 has knife rest 108, and it keeps the impacting body 110 and the cylindrical shaft 111 of piston shape slidably, the described impact of receipts from cup-shaped ram 113 that be coupling.
Piston 114 is slidably disposed on the inside of cup-shaped ram 113, and ram is slidably mounted in the guide sleeve 107.Piston 114 comprises bar 120, and it is driven by motor so that piston head 116 moves back and forth in cup-shaped ram 113.This makes positice ground effect produce in the front portion of piston head 116, institute so that ram 113 under positice ground effect, move back and forth.The reciprocating motion of ram 113 is passed to bump axon 111 and impacting body 110, to cause the hammering action that is delivered to the cutter head (not shown).
With reference to Figure 22 and 23, the outer surface of ram 113 comprises a plurality of planes 128 and a plurality of part cylindrical surface 129.Part cylindrical surface 129 engages with the inner cylindrical surface of guide sleeve 107 slidably.Plane 128 does not engage with the inner cylindrical surface of guide sleeve 107, and reduces the contact area between ram 113 and guide sleeve 107 effectively.This reduces in the friction between ram 113 and guide sleeve 107, to improve the efficient of driving mechanism.
The driving mechanism of GB1343206 has following shortcoming, promptly the gap between the inner cylindrical surface of plane 128 and guide sleeve 107 is bigger, and except reducing contact area and perhaps help the air-flow of driving mechanism the inside of GB1343206, to the function of driving mechanism without any effect.
Summary of the invention
Preferred embodiment of the present invention is intended to overcome the above-mentioned shortcoming of prior art.
According to an aspect of the present invention, provide a kind of driving mechanism that is used for power tool, described power tool has housing and motor, and this motor is arranged in the housing and has the output shaft of the operation element that is used for actuation tool, and this driving mechanism comprises:
The slidably mode with described relatively housing of being suitable for is installed to the reciprocating motion element in the ferrule element, described reciprocating motion element is suitable for responding the rotation of output shaft to move back and forth with respect to described ferrule element, wherein said reciprocating motion element and/or ferrule element comprise a plurality of complementary protuberance that form in its surface, described a plurality of projection be suitable for slidably with move back and forth element and/or ferrule element in another engage, reducing the contact area between described reciprocating motion element and the described ferrule element, and wherein said projection is suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
By on reciprocating motion element and/or ferrule element, a plurality of projections being set, and described projection be suitable for slidably with move back and forth element and ferrule element in another engage, described projection is suitable for keeping lubricant between reciprocating motion element and ferrule element, and this provides the advantage that reduces moving back and forth the CONTACT WITH FRICTION between element and the sleeve.This has reduced the energy consumption of motor, and prolongs the battery life of battery-powered tools.
Particularly, have been found that driving mechanism the startup stage during require more substantial electric energy.Supply easily by the lubricant that projection kept, the startup stage hollow core piston and main shaft between the reducing and reduce significantly of CONTACT WITH FRICTION by the employed total electric weight of driving mechanism, therefore help extending battery life.
In a preferred embodiment, described ferrule element is a hollow cylinder basically, and described a plurality of projection comprises a plurality of vertical oncus that form on reciprocating motion element external peripheral surface, and described oncus limits the groove of a plurality of convex curve shapes, wherein these grooves define than the smaller cylinder of external peripheral surface diameter that moves back and forth element, so these grooves are suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
In another preferred embodiment, described reciprocating motion element is a hollow cylinder basically, and described a plurality of projection comprises a plurality of vertical oncus that form on the inner circumferential surface of ferrule element, and described oncus limits the groove of a plurality of convex curve shapes, wherein these grooves define the cylinder more bigger than the inner circumferential surface diameter of ferrule element, so these grooves are suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
Among two kinds of embodiment any one all has following advantage, promptly the degree of depth of the groove between oncus is superficial, and no matter hammer drill be in be operation or stop, can both keeping the lubricant of the normal viscosity of enough deals, to lubricate in the motion that moves back and forth between element and the ferrule element.This means lubricant the startup stage and its whole normal operating period between all be available, thereby reduce wearing and tearing and power consumption.
Moving back and forth element can be to have the hollow piston of raming that slidably is installed in wherein, wherein rams to be suitable for the operation element transmission collision to instrument as the reciprocating result of described hollow piston.
Ferrule element can be a main shaft, and it is suitable for responding the rotation of motor output shaft to rotate with respect to hollow piston, so that the operation element of instrument in use rotates.
According to another aspect of the present invention, provide a kind of power tool, it comprises housing, be arranged in the housing and have the motor of the output shaft that is used to activate this tool work element, and according to above-described driving mechanism.
In a preferred embodiment, this power tool is a hammer drill.
Description of drawings
With way of example rather than with the meaning of any restriction the preferred embodiments of the present invention are described below with reference to the accompanying drawings, wherein:
Fig. 1 is the partial cut-away perspective view of the driving mechanism of hammer drill prior art;
Fig. 2 is the viewgraph of cross-section of the driving mechanism of Fig. 1;
Fig. 3 is the perspective view of the hammer drill of first embodiment of the invention;
Fig. 4 is the hammer drill side viewgraph of cross-section of Fig. 3;
Fig. 5 is the Zoom Side viewgraph of cross-section of the hammer drill part of Fig. 4;
Fig. 6 is that the piston drive mechanism part of Fig. 3 is excised perspective view by the part of position, back at it;
Fig. 7 is 1/4th parts excision perspective views that move back and forth the piston drive mechanism part of circulation time Fig. 3 that advance from position shown in Figure 6;
Fig. 8 advances half cycles to its part excision perspective view of the piston drive mechanism part of Fig. 3 during forward position from position shown in Figure 6;
Fig. 9 is the side viewgraph of cross-section that is used for the hammer piston driving mechanism of second embodiment of the invention;
Figure 10 is the enlarged cross-sectional view along the A-A line intercepting of Fig. 9;
Figure 11 is the side viewgraph of cross-section of the hammer drill part of third embodiment of the invention;
Figure 12 is that for clarity sake some parts with this transmission mechanism remove along the viewgraph of cross-section of the B-B line intercepting of Figure 11;
Figure 13 is the viewgraph of cross-section along the C-C line intercepting of Figure 12;
Figure 14 is the side viewgraph of cross-section of the hammer drill of fourth embodiment of the invention;
Figure 15 a is the perspective view that the right side half clam shell of two parts transmission housing of the hammer drill of fifth embodiment of the invention is seen from the outside;
Figure 15 b is the side view in the half clam shell outside of Figure 15 a;
Figure 15 c is the perspective view of the half clam shell inboard of Figure 15 a;
Figure 15 d is the side view of the half clam shell inboard of Figure 15 a;
Figure 15 e is the front view of half clam shell of Figure 15 a;
Figure 15 f is the viewgraph of cross-section along the A-A line intercepting of Figure 15 d;
Figure 15 g is the viewgraph of cross-section along the B-B line intercepting of Figure 15 d;
Figure 15 h is the viewgraph of cross-section along the F-F line intercepting of Figure 15 b;
Figure 16 a is the perspective view of seeing from the outside corresponding to a left side half clam shell of the right side half clam shell of Figure 15 a to Figure 15 h;
Figure 16 b is the side view in the half clam shell outside of Figure 16 a;
Figure 16 c is the perspective view of the half clam shell inboard of Figure 16 a;
Figure 16 d is the side view of the half clam shell inboard of Figure 16 a;
Figure 16 e is the front view of half clam shell of Figure 16 a;
Figure 16 f is the viewgraph of cross-section along the A-A line of Figure 16 d;
Figure 16 g is the viewgraph of cross-section along the B-B line intercepting of Figure 16 d;
Figure 16 h is the viewgraph of cross-section along the F-F line intercepting of Figure 16 d;
Figure 17 is the inboard perspective view that amplifies of half clam shell of Figure 16;
Figure 18 is the part excision top view of the hammer drill part that combines of half clam shell with Figure 15 and Figure 16;
Figure 19 is the part excision perspective view of the hammer drill part of Figure 18;
Figure 20 is the viewgraph of cross-section of this piston drive mechanism opposite side;
Figure 21 is the viewgraph of cross-section of prior art piston drive mechanism;
Figure 22 is the partial cross-sectional view that the piston drive mechanism of Figure 21 amplifies;
Figure 23 is the viewgraph of cross-section along the V-V line of Figure 22;
Figure 24 a is the viewgraph of cross-section of the hammer drill hollow piston of sixth embodiment of the invention;
Figure 24 b is the side perspective view of the hollow piston of Figure 24 a;
Figure 24 c is the top view of the hollow piston of Figure 24 a;
Figure 24 d is the front view of the hollow piston of Figure 24 a;
Figure 25 is the rearview of piston drive mechanism that includes the hollow piston of Figure 24 a to Figure 24 d that is installed on the main shaft;
Figure 26 is the rear view of the piston drive mechanism of Figure 25;
Figure 27 is the side view of the hammer drill of seventh embodiment of the invention; And
Figure 28 is the hammer drill side viewgraph of cross-section of Figure 27.
The specific embodiment
With reference to figure 3, be that the hammer drill of power comprises tool housing 22 and is used for fixing the dop 24 of drill bit (not shown) with the battery.This tool housing 22 is formed with handle 26, and this handle has the trigger 28 that is used to start this hammer drill.Battery pack 30 is connected in the bottom of this tool housing 22 removably.Model selection knob 32 is set, is used for selecting between a hammering pattern, a rotary mode and the hammering rotation integrated mode in the drill bit operation.
With reference to figure 4, motor 34 is arranged in this tool housing 22 and has rotating output shaft 36.Pinion 38 is formed on the end of this output shaft 36, and this pinion 38 meshes with first driven wheel 40 of rotary drive mechanism and second driven wheel 42 of hammering driving mechanism.
This rotary drive mechanism is described below.First bevel gear 44 is driven by first driven wheel 40.This first bevel gear 44 and 46 engagements of second bevel gear.This second bevel gear 46 is installed on the main shaft 48.The rotation of second bevel gear 46 passes to this main shaft 48 via the clutch mechanism that comprises overload spring 88.This main shaft 48 is installed around its longitudinal axis rotation by spherical ball bearing race 49.The drill bit (not shown) can insert in this dop 24 and be connected in the front end 50 of this main shaft 48.When hammer drill 20 is in rotary mode or hammering rotation integrated mode, this main shaft 48 and drill bit rotation.This clutch mechanism prevents that excessive torque from passing to motor 34 from drill bit and main shaft 48.
The hammering driving mechanism will be described below.The pinion 38 of motor output shaft 36 and the engagement of second driven wheel 42 make the rotation of this second driven wheel 42 cause the rotation of crank disc 52.Crank-pin 54 is driven and slidably engages the cylindrical bearing 56 that is arranged on hollow piston 58 ends by this crank disc 52.This hollow piston 58 slidably is installed in the main shaft 48, makes the rotation of this crank disc 52 cause the reciprocating motion of the hollow piston 58 in this main shaft 48.Ram and 60 slidably be arranged in the hollow piston 58.Just as well known for one of skill in the art, as the result that mattress 93 expands and shrinks, the reciprocating motion of this hollow piston 58 causes rams 60 with these hollow piston 58 reciprocating motions.When this hammer drill during with the operation of hammering pattern or hammering rotation integrated mode, 60 the reciprocating motion of raming causes to ram 60 impacts hit pieces 62, and hit piece is delivered to impact the drill bit (not shown) in the dop 24 again.
Mode shift mechanism comprises first and second drive sleeve 64,66, it optionally is connected in relative this first bevel gear 44 and crank disc 52 with this first and second driven wheel 40,42 respectively, so that the user can be selected between a hammering pattern, a rotary mode or hammering rotation integrated mode.This mode shift mechanism is the theme of UK Patent Application 0428215.8.
Transmission mechanism comprises rotary drive mechanism, hammering driving mechanism and mode shift mechanism.This transmission mechanism is arranged on transmission housing 80 the insides.This transmission housing 80 also supports motor 34.This transmission housing is made of half clam shell of two durable plastic material or cast metal, and this two and half clam shell pushes O shape ring 82 between them.This O shape is encircled 82 seal casinghousings 80, enters this transmission housing and damages the moving component of this transmission mechanism to prevent dust and foul.
This transmission housing 80 slidably is installed on the closed slide (not shown) of tool housing 22 the insides, and is rested on the tool housing 22 by first and second shock-absorbing springs 84 and 86 that are arranged on its rear end.Therefore this transmission housing 80 can be with respect to little amount of these tool housing 22 motions, to pass to user's vibration in this hammer drill 20 operating periods minimizing.This first and second shock-absorbing spring 84 and 86 spring constant are chosen as, when this hammer drill 20 uses under normal operating condition, this transmission housing 80 slide into its forward and backward between the limit of sports record roughly in the middle of point.This point is an equalization point, equals to be placed on this hammer drill 20 on the workpiece and to be leaned against on this tool housing 22 and the power backward that produces on this transmission housing 80 by the user at this biasing force forward of putting this shock-absorbing spring 84 and 86.
With reference to figure 5, will describe the hammering driving mechanism in detail below.Crank-pin 54 comprises the cylindrical link member 68 that is rigidly connected to part ball bearing 70.This part ball bearing 70 is slidably to be arranged in the cup shaped recess 72 that is formed in this crank disc 52 with rotatable mode.This cup shaped recess 72 has roughly hemisphere portion 72b of top cylindrical part 72a and bottom.This top cylindrical part 72a and lower hemispherical part 72b have same maximum gauge, and this maximum gauge is a bit larger tham the maximum gauge of part ball bearing 70.As a result, this part ball bearing 70 can be easy to insert in this cup shaped recess.This crank-pin 54 can pivot, rotate and slide vertically with respect to this crank disc, and this part ball bearing still remains in the scope of this cup shaped recess 72 simultaneously.
This cylindrical link member 68 slidably is arranged in the cylindrical bearing 56 that is formed in these hollow piston 58 ends.Force of sliding friction in this cup shaped recess 72 is a bit larger tham the force of sliding friction in this cylindrical bearing 56.Therefore, when this part ball bearing swung back and forth in this cup shaped recess, this cylindrical link member 68 slided up and down in this cylindrical bearing 56.Cylindrical shaft ring 74 is around the cylindrical link member 68 of this crank-pin 54, and can be against the lower position of these part ball bearing 70 upper surfaces with slide between the upper position of these cylindrical bearing 56 downsides.This axle collar spare 74 is a kind of prevent means, and it limits the motion of this part ball bearing 70 towards this cylindrical bearing 56, makes this crank-pin 54 and its part ball bearing 70 can not break away from fully and the engaging of this cup shaped recess 72.This cylindrical collar 74 can be installed on this crank-pin 54 after forming this crank disc 52 and crank-pin 54 assemblies.
With reference to figure 6 to Fig. 8, when this crank disc 52 along counter-clockwise direction when stand up position shown in Figure 6 rotates to position shown in Figure 7, can see that crank-pin 54 pushes away this hollow piston 58 forward and to lopsidedness.Because crank-pin 54 tilts, this cylindrical link member 68 in this cylindrical bearing 56 to lower slider.Because crank disc 52 rotates to the position of Fig. 8 from the position of Fig. 7, shift this hollow piston 58 onto its most forward position, this crank-pin 54 is in upright position again, and the cylindrical link member 68 of this crank-pin 54 upwards slides in this cylindrical bearing 56.Can see,, can prevent that this crank-pin 54 from moving too far and the engaging of disengaging and this crank disc 52 in this cylindrical bearing by this axle collar spare 74 last side engagement with downside and this part ball bearing 70 of this cylindrical bearing 56.Therefore, do not need interference engagement to engage with this crank disc, simplified the assembling of this driving mechanism so greatly to keep this crank-pin.
The hammer drill of second embodiment of the invention is shown in Fig. 9 and Figure 10, and the parts identical with the embodiment of Fig. 3 to Fig. 8 are with same but increase by 100 Reference numeral and represent.
Crank-pin 154 has the structure same with the embodiment of Fig. 3 to Fig. 8.But in the embodiment of Fig. 9 and Figure 10, this axle collar spare 176 is helical springs.Pad 178 is arranged between this axle collar helical spring 176 and this cylindrical bearing 156.This axle collar helical spring 176 has additional advantage, and promptly it is biased into the part ball bearing 170 of this crank-pin 154 with the cup shaped recess 172 of this crank disc 152 and engages, so this part ball bearing even can not partly break away from this crank disc 152.
The hammer drill of third embodiment of the invention is shown in Figure 11 to Figure 13, with the embodiment common means of Fig. 3 to Fig. 8 with same but increase by 200 Reference numeral and represent.
This transmission housing 280 is made of half clam shell of two durable plastic material or cast metal material.This two and half clam shell is clipped in O shape ring 282 between them and pushes this O shape ring.This transmission housing 280 is supported by first and second shock-absorbing springs 284 and 286 in its back-end.This transmission housing 280 also is installed on the parallel orbit (not shown) that is arranged on these tool housing 222 the insides, makes that this transmission housing 280 can be along the direction of these main shaft 248 longitudinal axis with respect to these tool housing 222 front and back little distance of sliding.
Shock-absorbing spring 284 and 286 spring constant are chosen to, when this hammer drill uses under normal operating condition, make this transmission housing 280 slide into its forward and backward between the limit of sports record roughly in the middle of point.This point is an equalization point, and the biasing force forward in this shock-absorbing spring 284 on this aspect and 286 equals to be placed on this hammer drill 220 on the workpiece and to be leaned against on this tool housing 222 and the power backward that produces on this transmission housing 280 by the user.
The front end of this transmission housing 280 has local tapering part 290 roughly, and it is resisted against and is formed on corresponding local tapering part 292 on this tool housing 222.This part tapering part 290 and 292 and the longitudinal axis of this main shaft 248 form an about angle of 15 °.The interface that is formed by this part tapering part 290 and 292 forms a retainer, and when this hammer drill 220 was in the inoperation state, this transmission housing 280 rested on this tool housing 222 at this retainer place.When this hammer drill 220 uses under normal operating condition, a gap appears between the surface of this part tapering part 290 and 292, this gap helps to reduce axially and oscillation crosswise, otherwise these vibration meetings directly pass to the user who holds this hammer drill 220 from the tool heads (not shown).Certainly, when this transmission housing overcomes the bias voltage of this shock-absorbing spring 284,286 when mobile backward, this gap can increase slightly.This help to reduce when the user applies bigger pressure forward to this hammer drill 220, to increase axially and oscillation crosswise.But this gap is enough little, and this hammer drill 220 and transmission housing 280 always can suitably be controlled by the interface between this part tapering part 290 and 292 by the user, and this interface keeps this transmission housing 280 and 222 alignment of this tool housing.
The hammer drill of fourth embodiment of the invention is shown in Figure 14, and the parts identical with the embodiment of Fig. 3 to Fig. 8 are with same but increase by 300 Reference numeral and represent.
This hammer drill 320 has tool housing 322.In this embodiment, this transmission housing 380 is made of three housing parts.The first roughly L shaped housing parts 380a holds the transmission mechanism except that the front end 348a of first and second gears 340,342 and main shaft 348.The bottom of this first housing parts 380a is installed on the second housing parts 380b, and the O shape ring 382a that wins is stuck between these two parts, enters to prevent dust and foul.This second housing parts 380b remains on the bottom of this transmission mechanism the inside of this first housing parts 380a and holds this first and two gear 340,342.This second housing parts 380b has motor delivery outlet 390, motor output shaft 336 is entered in this transmission housing the inside, and make pinion 338 can drive first and second gears 340,342 of this transmission mechanism.The 3rd housing parts 380c is installed in the front end of this first housing parts 380a, makes the 2nd O shape ring 382b be stuck between these two parts to prevent that dust and foul from entering.The 3rd housing parts 380c remains on first housing parts 380a the inside with the front portion of this transmission mechanism and holds the front end 348a of main shaft.
This first roughly L shaped housing parts 380a makes transmission mechanism can be assembled in this first housing parts 380a the inside from its two ends fully.For example hollow piston and spindle assemblies can insert the front end of this first drive shell body portion 380a, this first housing parts 380a can rotate 90 ° then, and each gear and mode shift mechanism can and fall into correct position by the bottom insertion, and this main shaft 348 and hollow piston 358 are engaged.This second and the 3rd drive shell body portion 380b and 380c can be installed on this first drive shell body portion 380a then, so that cover the openend of this first drive shell body portion 380a.
This first drive shell body portion 380a can be as the standard stand (the hammering driving mechanism, rotary drive mechanism and the mode shift mechanism that comprise standard) of some kinds of power tools, and the second and the 3rd drive shell body portion 380b and 380c can change, with motor and the main shaft that adapts to different size.
The hammer drill of fifth embodiment of the invention has the transmission housing that is shown in Figure 15 to Figure 20, and the parts identical with the embodiment of Fig. 3 to Fig. 8 are with same but increase by 400 Reference numeral and represent.
With reference to Figure 15 and Figure 16, the transmission housing is made of the right side half clam shell 421a and left half clam shell 421b, and this right side half clam shell 421a and left half clam shell 421b are formed with injection moulding by senior strong plastics.Each half clam shell 421a, 421b have a plurality of screwed hole 423a, the 423b that is suitable for admitting the screw (not shown) respectively, make half clam shell 421a, 421b to combine, and seal the transmission housing of this transmission mechanism with formation.
This two housing sections is suitable for keeping all members of this transmission mechanism, and various recesses are molded on half clam shell so that provide support for these members.For example, the shape of the first driven wheel recess 427a, 427b is made and is suitable for supporting this first driven wheel 40.Motor support part 425a and 425b are suitable for supporting and local top of sealing this motor 34.
This transmission housing slidably is installed on the pair of guide rails (not shown) in this tool housing 22.Because the inside and user that this transmission housing is arranged on this tool housing 22 can't see, therefore can be with this transmission housing of senior strong constructed in plastic material.Such material is because its unengaging color and quality are unsuitable for being used for the outside of power tool usually.Senior strong plastics have vibration and the noise damping property better than metal usually.The ribs (not shown) can be molded in the plastics to strengthen the intensity of this transmission housing.
With reference to Figure 15 to Figure 20, each half clam shell 421a and 421b comprise overflow ducts 429a and the 429b that forms.This half clam shell also comprises corresponding ball distance ring support recesses 431a and 431b, and it is suitable for keeping ball distance ring 49, with supports main shaft 48.
Specifically referring to figs. 18 to Figure 20, this half clam shell 421a and 421b cooperate the first transmission shell chamber 433 and the second transmission shell chamber 435 that is arranged on ball distance ring 499 either sides with formation.This first transmission shell chamber 433 and the second transmission shell chamber 435 interconnect by passage 429a and 429b.The rear end of this hollow piston 458, cylindrical bearing 456, crank-pin 454 and crank disc 452 all are arranged in this first transmission shell chamber 433.The major part of this main shaft 448 and overload spring 458 are arranged in this second transmission shell chamber 435.The part of the main shaft 448 in this second transmission shell chamber has the passage 448a of circumference array.This passage 448a makes this second transmission shell chamber 435 and can be communicated with between the main shaft chamber 448b of these main shaft 448 the insides and this hollow piston 458 and 460 fronts of raming.
In the hammering pattern, this hollow piston 458 causes reciprocating motion by this crank disc 452.When this hollow piston 458 moved in this first transmission shell chamber 433, because the arrival of this hollow piston reduces the volume of this first transmission shell chamber, thereby the air pressure in this first transmission shell chamber 433 increased.Simultaneously, this hollow piston 458 and ram and 460 shift out this main shaft 448.Because this hollow piston and the volume that makes this main shaft chamber that leaves of raming increase, thereby this causes that the air pressure among the 448b of this main shaft chamber reduces.This second transmission shell chamber 435 is communicated with main shaft chamber 448b through passage 448a, and therefore the air pressure in the second transmission shell chamber 435 also reduces.This air pressure difference is balanced owing to air flows to into this second transmission shell chamber 435 and this main shaft chamber 448b by overflow ducts 429a and 429b from the first transmission shell chamber 433.
On the contrary, when this hollow piston 458 entered this main shaft 448, because the volume of this first transmission shell chamber 433 is owing to leaving of this hollow piston increases, therefore the air pressure of the first transmission shell chamber 433 reduced.Simultaneously, because the volume of this main shaft chamber is owing to this hollow piston and the arrival of raming reduce, this causes that the air pressure among the 448b of main shaft chamber increases.As mentioned above, this second transmission shell chamber 435 is communicated with main shaft chamber 448b via passage 448a, so the air pressure in this second transmission shell chamber 435 also increases.This first transmission shell chamber 433 is balanced this air pressure difference because air refluxes into from this second transmission shell chamber 435 and main shaft chamber 448b by this overflow ducts 429a and 429b.
As the result that the air among overflow ducts 429a and the 429b moves back and forth and circulates, during hollow piston 58 moved back and forth, the compression of air was eliminated, or significantly reduces.Therefore the hammering driving mechanism can do work owing to the air that compression retains or off-energy hardly.The efficient of motor and the battery life of hammer drill have been increased like this.
The hammer drill of sixth embodiment of the invention has the hammering driving mechanism that is shown in Figure 24 to Figure 26, and the parts identical with the embodiment of Fig. 3 to Fig. 8 are with same but increase by 500 Reference numeral and represent.
With reference to Figure 24 to Figure 26, hollow piston 558 comprises cylindrical bearing 556, and it is suitable for holding crank-pin 554 and moves back and forth in main shaft 548 the insides so that cause this hollow piston 558.The (not shown) of raming slidably is arranged on this hollow piston 558 the insides, because the air spring effect that these hollow piston 558 the insides produce makes this ram and produces the hammering action.A plurality of vertical oncus 559 are formed on the external peripheral surface of hollow piston 558 of substantial cylindrical, and are long-pending with the contact surface between the main shaft 548 that reduces this hollow piston 558 and substantial cylindrical.The groove 561 of a plurality of convex curve shapes is formed in the gap between this oncus.This groove 561 defines the diameter slightly little cylinder of a diameter than these hollow piston 558 external peripheral surfaces.Therefore, this groove 561 is enough shallow, to hold the lubricant of normal viscosity during the whole normal running of this hammering driving mechanism.
This hollow piston 558 slidably is arranged on this main shaft 548 the insides.The rotation of crank disc 552 makes this crank-pin 554 act on cylindrical bearing 556, makes this hollow piston 558 move back and forth in these main shaft 548 the insides.This main shaft 548 also can be around these hollow piston 568 rotations.Be formed on the inner surface that vertical oncus 559 on these hollow piston 558 outer surfaces slidably engages this main shaft 548.Can see that the contact area between this hollow piston 558 and this main shaft 548 reduces owing to this oncus 559 only engages with the inner surface of this main shaft 548.Be retained in the friction that the lubricant 563 in this groove 561 reduces between this main shaft 548 and this hollow piston 558.Air also can pass through between this hollow piston 558 and this main shaft through the space that is formed by groove 561, has therefore strengthened the cooling of this transmission mechanism.Air by this groove also helps the air pressure in balanced this first and second transmissions shell chamber 433,435 of having discussed in the 5th embodiment.
Hammer drill with seventh embodiment of the invention of motor cooling system is shown in Figure 27 and Figure 28, and the parts identical with the embodiment of Fig. 3 to Fig. 8 are with same but increase by 600 Reference numeral and represent.
Hammer drill 620 comprises tool housing 622, wherein forms a plurality of passages 669.This passage 669 is suitable for admitting the cold air from this hammer drill outside, perhaps hot-air is discharged from this hammer drill the inside.
With reference to Figure 28, the position of motor cooling fan (not shown) between the commutator (not shown) of the magnet exciting coil (not shown) on these motor 634 tops and bottom is arranged on the axis of this motor 634.Transmission housing 680 with above-mentioned two parts or three part types is sealed this transmission mechanism substantially.
Drive by this motor at this power tool this cooling fan of operating period.This cooling fan axially sucks air and passes this motor and radially discharge this air by the hole 675 in the shell 677 that is formed on this motor 634.This cooling fan aligns vertically with this hole 675, makes that air ratio is easier to radially discharge.This make air by be formed on these housing 622 tops, in the side of this housing 622 and the passage 669 between this housing 622 and this battery pack 630 suck.This cold air flows through with the path of passing through this housing 622 shown in the cold air arrow 671.Cold air still flows in the inside of this tool housing 622 around the outside of this transmission housing 680, makes air by this sealed transmission mechanism, enters to prevent foul.
A plurality of motors hole 635 is formed in the shell 677 of this motor 634, so that cold air can enter this motor to cool off this motor.Because the position of this cooling fan, cold air is inhaled into by the magnet exciting coil of this motor and motor commutator, makes each member be downward through this magnet exciting coil and the air that upwards flows through this commutator cools off separately.Hot-air is by being discharged by the preceding passage 669 of this shell front by the flow path shown in the hot-air arrow 673.Should align vertically with the hole 675 in these motor 634 shells 677 by preceding passage 669.Hot-air also can be discharged by the back passage 699 that is arranged between this tool housing 622 and the detachable battery group 630.
Describe embodiment with way of example rather than with any limited significance above it will be understood by those of skill in the art that, and in not breaking away from the scope of the present invention that is defined by the claims, can carry out various changes and modification.

Claims (11)

1. driving mechanism that is used for power tool, described power tool has housing and motor, and this motor is arranged in the housing and has the output shaft of the operation element that is used for actuation tool, and this driving mechanism comprises:
The slidably mode with described relatively housing of being suitable for is installed to the reciprocating motion element in the ferrule element, described reciprocating motion element is suitable for responding the rotation of output shaft to move back and forth with respect to described ferrule element, wherein said reciprocating motion element and/or ferrule element comprise a plurality of corresponding projections that form in its surface, described a plurality of projection be suitable for slidably with move back and forth element and/or ferrule element in another engage, reducing the contact area between described reciprocating motion element and described ferrule element, and wherein said projection is suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
2. mechanism as claimed in claim 1, wherein said ferrule element is upward hollow columniform, and described a plurality of projection comprises a plurality of vertical oncus that form on the external peripheral surface that moves back and forth element, and described oncus limits the groove of a plurality of convex curve shapes, wherein these grooves define than the little cylinder of external peripheral surface diameter that moves back and forth element, so these grooves are suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
3. mechanism as claimed in claim 1, wherein said reciprocating motion element is upward hollow columniform, and described a plurality of projection comprises a plurality of vertical oncus that form on the inner circumferential surface of ferrule element, and described oncus limits the groove of a plurality of convex curve shapes, wherein these grooves define the cylinder bigger than ferrule element inner circumferential surface diameter, so these grooves are suitable for keeping lubricant between described reciprocating motion element and described ferrule element.
4. each described mechanism in the claim as described above, wherein said reciprocating motion element is to have the hollow piston of raming that slidably is installed in wherein, and wherein this is ramed and is suitable for the operation element transmission bump to instrument as the reciprocating result of described hollow piston.
5. mechanism as claimed in claim 4, wherein ferrule element is a main shaft, described ferrule element is suitable for responding the rotation of motor output shaft to rotate with respect to hollow piston, so that the operation element of instrument rotates in use.
6. power tool comprises housing, is arranged in the housing and has the motor of the output shaft that is used to activate this tool work element, and according to each described driving mechanism in the aforementioned claim 1 to 3.
7. driving mechanism as claimed in claim 6, wherein this power tool is a hammer drill.
8. power tool comprises housing, is arranged in the housing and has the motor of the output shaft that is used to activate this tool work element, and according to each described driving mechanism in the aforementioned claim 4.
9. driving mechanism as claimed in claim 8, wherein this power tool is a hammer drill.
10. power tool comprises housing, is arranged in the housing and has the motor of the output shaft that is used to activate this tool work element, and according to each described driving mechanism in the aforementioned claim 5.
11. driving mechanism as claimed in claim 10, wherein this power tool is a hammer drill.
CN200510135808.1A 2004-12-23 2005-12-23 Drive mechanism for a power tool Pending CN1792563A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0428210.9 2004-12-23
GBGB0428210.9A GB0428210D0 (en) 2004-12-23 2004-12-23 Mode change mechanism
GB0510937.6 2005-05-27

Publications (1)

Publication Number Publication Date
CN1792563A true CN1792563A (en) 2006-06-28

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ID=34113148

Family Applications (8)

Application Number Title Priority Date Filing Date
CNB2005101358151A Expired - Fee Related CN100406208C (en) 2004-12-23 2005-12-23 Cooling mechanism for a power tool
CNB2005101358293A Expired - Fee Related CN100515687C (en) 2004-12-23 2005-12-23 Power tool
CNB2005101358236A Expired - Fee Related CN100434240C (en) 2004-12-23 2005-12-23 Power tool housing
CN200510135808.1A Pending CN1792563A (en) 2004-12-23 2005-12-23 Drive mechanism for a power tool
CNB2005101358166A Expired - Fee Related CN100423908C (en) 2004-12-23 2005-12-23 Drive mechanism for a power tool
CN200510135809.6A Pending CN1792565A (en) 2004-12-23 2005-12-23 Power tool housing
CN200510135824.0A Pending CN1792567A (en) 2004-12-23 2005-12-23 Power tool housing
CNB2005101358170A Expired - Fee Related CN100450726C (en) 2004-12-23 2005-12-23 Power tool housing

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Application Number Title Priority Date Filing Date
CNB2005101358151A Expired - Fee Related CN100406208C (en) 2004-12-23 2005-12-23 Cooling mechanism for a power tool
CNB2005101358293A Expired - Fee Related CN100515687C (en) 2004-12-23 2005-12-23 Power tool
CNB2005101358236A Expired - Fee Related CN100434240C (en) 2004-12-23 2005-12-23 Power tool housing

Family Applications After (4)

Application Number Title Priority Date Filing Date
CNB2005101358166A Expired - Fee Related CN100423908C (en) 2004-12-23 2005-12-23 Drive mechanism for a power tool
CN200510135809.6A Pending CN1792565A (en) 2004-12-23 2005-12-23 Power tool housing
CN200510135824.0A Pending CN1792567A (en) 2004-12-23 2005-12-23 Power tool housing
CNB2005101358170A Expired - Fee Related CN100450726C (en) 2004-12-23 2005-12-23 Power tool housing

Country Status (4)

Country Link
CN (8) CN100406208C (en)
AT (2) ATE416889T1 (en)
DE (2) DE602005011562D1 (en)
GB (9) GB0428210D0 (en)

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DE602005010037D1 (en) 2008-11-13
GB0510930D0 (en) 2005-07-06
CN100406208C (en) 2008-07-30
GB0510936D0 (en) 2005-07-06
GB0510934D0 (en) 2005-07-06
CN1792567A (en) 2006-06-28
GB0510940D0 (en) 2005-07-06
ATE409554T1 (en) 2008-10-15
CN100450726C (en) 2009-01-14
GB2421700A (en) 2006-07-05
GB2421460A (en) 2006-06-28
CN100515687C (en) 2009-07-22
CN1792565A (en) 2006-06-28
CN100434240C (en) 2008-11-19
CN1807027A (en) 2006-07-26
GB2421459A (en) 2006-06-28
CN1792566A (en) 2006-06-28
GB2421461A (en) 2006-06-28
CN1792562A (en) 2006-06-28
GB2421462A (en) 2006-06-28
ATE416889T1 (en) 2008-12-15
CN100423908C (en) 2008-10-08
GB0510933D0 (en) 2005-07-06
GB0428210D0 (en) 2005-01-26
CN1792564A (en) 2006-06-28
GB2421464A (en) 2006-06-28
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CN1807026A (en) 2006-07-26
GB0510935D0 (en) 2005-07-06
GB0510932D0 (en) 2005-07-06
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GB0510937D0 (en) 2005-07-06

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