CN103862378A - Eccentric rotary swing type tool - Google Patents
Eccentric rotary swing type tool Download PDFInfo
- Publication number
- CN103862378A CN103862378A CN201210537262.2A CN201210537262A CN103862378A CN 103862378 A CN103862378 A CN 103862378A CN 201210537262 A CN201210537262 A CN 201210537262A CN 103862378 A CN103862378 A CN 103862378A
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- CN
- China
- Prior art keywords
- grinding disc
- disc assembly
- eccentric
- base plate
- eccentric rotary
- 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.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B23/00—Portable grinding machines, e.g. hand-guided; Accessories therefor
- B24B23/02—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor
- B24B23/03—Portable grinding machines, e.g. hand-guided; Accessories therefor with rotating grinding tools; Accessories therefor the tool being driven in a combined movement
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B24—GRINDING; POLISHING
- B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
- B24B55/00—Safety devices for grinding or polishing machines; Accessories fitted to grinding or polishing machines for keeping tools or parts of the machine in good working condition
Abstract
The invention discloses an eccentric rotary swing type tool. The eccentric rotary swing type tool comprises a shell, a motor, a transmission mechanism, a first grinding disc component, a second grinding disc component and a linkage, wherein the motor is mounted in the shell, the transmission mechanism is driven by the motor, the first and second grinding disc components are supported on the shell and are eccentrically driven by the transmission mechanism, and the linkage is mounted between the first grinding disc component and the second grinding disc component to drive the other grinding disc component to rotate in the auto-rotation of one grinding disc component. The two grinding disc components are linked through the linkage, so that even if one grinding disc component stops rotating, the other grinding disc component is also capable of driving the former to rotate in the work of the eccentric rotary swing type tool, and the grinding efficiency is improved.
Description
Technical field
The present invention relates to a kind of eccentric rotary and swing class instrument.
Background technology
Traditional eccentric rotary swings class instrument, and for example frosted class instrument, generally includes a polishing base plate.Polishing base plate is connected on motor by the suitable kind of drive, and motor is arranged on the housing with one or more handles.The kind of drive is embodied in an eccentric shaft and drives a circular polishing base plate, and it does circumference beat motion (revolution) when polishing base plate work, to rely on the eccentric drive of eccentric shaft, does rotation movement around the central shaft of polishing base plate simultaneously.Therefore, the existing revolution of polishing base plate has again rotation, makes the efficiency of instrument higher.
But polishing base plate is operated in eccentric state, when work, due to the centrifugal action of rotation, frosted class instrument has very large vibration, and this vibration has been absorbed by operator's hand and arm, and this can produce serious consequence to operator's health.Be delivered to operator's vibration with it so the producer of frosted class instrument or user wish to eliminate or reduce, thereby improve workman's safety and productivity.
Therefore, those skilled in the art have done corresponding improvement.As two contrary, inside and outside nested polishing base plate of eccentric direction are set.By this two eccentric settings, make polishing base plate under operator's pressure-acting, two relatively the grinding force of eccentric polishing base plate can cancel out each other, the amplitude of polishing base plate bias can not be delivered on machine, the vibration of machine is reduced, operate more comfortable.
But in the course of the work,, the frictional force of two polishing base plate and load is always not the same, has caused the rotational velocity of two polishing base plate different yet.Thereby the phenomenon that just there will be the partially slow or stall of one of them polishing base plate rotary speed, affects grinding efficiency.
Summary of the invention
Technical problem to be solved by this invention is: provide a kind of eccentric rotary that improves grinding efficiency to swing class instrument.
In order to address the above problem, the invention provides a kind of eccentric rotary and swing class instrument, comprise housing; Be arranged on motor in described housing and the transmission mechanism by described motor driving; Be supported on described housing by the first grinding disc assembly of described transmission mechanism eccentric drive and the second grinding disc assembly; Between described the first grinding disc assembly and the second grinding disc assembly, be provided with link gear, described link gear can make one of them grinding disc assembly time rotational drive the rotation of another one grinding disc assembly.
Disclosed eccentric rotary swings in class instrument, by link gear, two grinding disc assemblies are connected, so be arranged so that eccentric rotary swings class instrument in the course of the work, even if the phenomenon of stall appears in a grinding disc assembly rotary speed, another one grinding disc assembly also can drive this dish to rotate.Thereby improve grinding efficiency.
Preferably, described the first grinding disc assembly is the same with described the second grinding disc component speed.
Preferably, described link gear comprises and is connected to mating groove on one of them of the first grinding disc assembly and the second grinding disc assembly and is connected to the first grinding disc assembly and the counterpart of the second grinding disc assembly on another, and described counterpart matches with described mating groove.
Preferably, on described the first grinding disc assembly, be connected with interlock dish, described mating groove is arranged on described interlock dish.
Preferably, described link gear comprises some described mating groove and some counterparts that are evenly arranged on the second grinding disc assembly that are evenly arranged on interlock dish.
Preferably, described mating groove is circular trough, and described counterpart is the rolling member that can rotate around self center line.
Preferably, described mating groove is cross recess, and described counterpart is the sliding part sliding with respect to described cross recess.
Preferably, described eccentric rotary swings class instrument and comprises pressure driving mechanism, and described pressure driving mechanism comprises the gear being connected on the first grinding disc assembly or the second grinding disc assembly; The joggle piece engaging with described gear; And be movably arranged on the retainer on housing, and described retainer moves between primary importance and the second place, and in primary importance, retainer engages joggle piece is fixed with respect to housing with joggle piece, and described gear rotates with respect to joggle piece; In the second place, retainer and joggle piece disengage, and described joggle piece is moved together with described gear.Preferably, described joggle piece comprises the internal tooth coordinating with described gear and the end tooth coordinating with described retainer.
Preferably, described transmission mechanism comprises an offset assembly, described offset assembly comprises interstitial hole for connecting described main shaft, for connecting the first connecting portion of described the first grinding disc assembly and for connecting the second connecting portion of described the second grinding disc assembly, wherein said the first connecting portion and described the second connecting portion are all with respect to the center line eccentric setting of described interstitial hole.
Preferably, described pressure driving mechanism comprises and drives described the first grinding disc assembly or described the second grinding disc assembly CD-ROM drive motor around the center line rotation of self.
Preferably, described offset assembly is double-eccentric shaft, and described the first connecting portion is eccentric through-hole, and the second connecting portion is rotor journal, and the center line of described eccentric through-hole and described rotor journal is separately positioned on the both sides of the center line of described interstitial hole.
Brief description of the drawings
Below in conjunction with accompanying drawing, the present invention is done to further detailed description.
Fig. 1 is the stereogram that the eccentric rotary that discloses of the present invention swings class instrument.
The eccentric rotary that Fig. 2 discloses for Fig. 1 swings the cutaway view of class instrument.
The eccentric rotary that Fig. 3 discloses for Fig. 1 swings the three-dimensional exploded view of class instrument.
Fig. 4 is the three-dimensional exploded view of the link gear that discloses of the present invention.
The stereogram of the link gear that Fig. 5 discloses for Fig. 4.
The eccentric rotary that Fig. 6 discloses for Fig. 1 swings the cutaway view of another direction of class instrument.
Fig. 7 is the cutaway view along A-A direction in Fig. 6.
Fig. 8 is the stop button that discloses of the present invention and the schematic diagram of operating knob.
The eccentric rotary that Fig. 9 discloses for Fig. 1 swings the stereogram of class instrument other direction, has wherein removed the
One, the second mill assembly.
Figure 10 is the schematic diagram of the air flow direction that discloses of the present invention.
In figure:
30. housing 62. bell-jar 92. rotor journals
32. first grinding disc assembly 64. inner chamber 94. second bearings
34. second grinding disc assembly 66. separator 96. clutch shaft bearing centre bores
The anterior 68. gripping surface 98. clutch shaft bearing center lines of 36. housings
38. motor 70. assist handle 100. second bearing centre holes
40. housing rear portion 72. first bevel gear 102. second bearing axis
42. motor drive shaft 74. second bevel gear 104. balancing weights
44. switch 76. main shaft 106. balance weights
46. first polishing base plate 78. interstitial hole 110. link gears
Center line 112. mating grooves of 48. second polishing base plate 80. interstitial holes
50. first outer surface 82. eccentric through-hole 114. counterparts
Inner chamber 84. screw 116. interlock dishes in the middle of 52.
54. second outer surface 86. connecting axle 117. reinforcements
58. bevel gearing 88. clutch shaft bearing 118. linkage racks
60. double-eccentric shaft 90. distance piece 120. pins
122. retainer 152. accepting groove 178. elastic rings
124. joggle piece 154. circular trough 180. grooves
126. gear 156,158 first, second sliding 182. through holes
128. Connection Block groove 184. convoluted diaphragms
130. inner chamber 157. boss 186. centre bores
132. internal tooth 159. accepting groove 188. dust mouths
134. end tooth 160. stop button 190. first cavitys
135. contact-making surface 162. butting section 192. second cavitys
136. contact-making surface 163. lateral wall 194. connected entrances
138. connecting hole 164. lateral wall 196. first dust mouths
First, second 198. second dust mouths only of 140. springs 166,168
The moving portion of 142. operating knobs 200. perisporiums
144. connector 170. first contact part 202. entrances
146. rotation centerline 172. second contact part 204. through holes
148. cam pin 174. spring 300. eccentric rotaries swing
The center line 176. of 150. cam pins seals lopps instrument
Detailed description of the invention
With reference to accompanying drawing 1, the present invention has disclosed a kind of eccentric rotary and has swung class instrument 300, as sander or polishing machine etc.
Eccentric rotary swings the housing 30 that class instrument 300 comprises for supporting motor 38 (as shown in Figure 2); The transmission mechanism that is contained in the motor 38 in housing 30 and is driven by motor 38; And the grinding subassembly being connected with transmission mechanism.Grinding subassembly can comprise the first grinding disc assembly 32 and the second grinding disc assembly 34.When eccentric rotary swing class instrument 300 is done, two grinding disc assemblies 32 and 34 rotate grinding workpiece surfaces.In description of the invention, unless otherwise noted, direction term, as front, back, left, right, up and inferior, is all the direction that swings class instrument with respect to this eccentric rotary of normal use.
The power supply that eccentric rotary swings class instrument 300 is AC power, powers to motor 38 by AC power.Certainly this instrument also can adopt direct current energy to power, and swings on class instrument 300 power brick is installed at eccentric rotary, powers to motor 38 by power brick.Eccentric rotary swings class instrument 300 and also comprises switch 44, and switch 44 and motor 38 are electrically connected and are used for horse-controlling and reach 38 unlatching and stop.
As shown in Figure 2, motor can be carbon brush motor, brushless motor etc., or swings the energy source of class instrument 300 corresponding to eccentric rotary, and motor can be alternating current motor or d.c. motor.Motor 38 has motor drive shaft 42, and the power of motor drive shaft 42 being exported by transmission mechanism passes to the first grinding disc assembly 32 and the second grinding disc assembly 34, make the first grinding disc assembly 32 and the second grinding disc assembly 34 can do the motion of circumference beat, again can be around center line rotation separately.
As depicted in figs. 1 and 2, housing 30 comprises the housing rear portion 40 that housing anterior 36 and lengthwise extend.Its middle shell front portion 36 is for accommodating transmission mechanism.Housing rear portion 40 is for accommodating motor 38, and motor drive shaft 42 be arranged in parallel with the longitudinal extending axis at housing rear portion 40.Here, the longitudinal extending axis angle a at the longitudinal extending axis of housing front portion 36 and housing rear portion 40 is more than or equal to 90 degree, and angle a equals 90 degree in the present embodiment.Be convenient to eccentric rotary swing class instrument 300 works in limited space.Certainly, the longitudinal extending axis of housing front portion 36 also can parallel or coincidence with the longitudinal extending axis at housing rear portion 40.
Housing rear portion 40 is simultaneously also as operator's handle use, and in operating process, operator holds housing rear portion 40 and swings class instrument 300 with mobile eccentric rotary.On this housing rear portion 40, can be provided with encapsulate pleasant so that operator is gripped, thereby reduce fatigue.
As shown in Figures 2 and 3, the first grinding disc assembly 32 comprises that the first polishing base plate 46, the first polishing base plate 46 support smooth abrasive body (not shown), as frosted layer or sand paper.The second grinding disc assembly 34 comprises that the second polishing base plate 48, the second polishing base plate 48 support smooth abrasive body (not shown), as frosted layer or sand paper.
The first polishing base plate 46 is discoid, and it has first outer surface 50 that connects circular sand paper; The second polishing base plate 48 is annular, and it has middle inner chamber 52 and second outer surface 54 that is connected annular sand paper.The first polishing base plate 46 is placed in the inner chamber 52 of the second polishing base plate 48.
Be appreciated that the first polishing base plate also can not be arranged in the inner chamber of the second polishing base plate, and be arranged on the outside of the second polishing base plate.Like that, the shape of first, second polishing base plate can be designed to discoid or triangle, other shape such as square.
In the course of the work, workpiece produces vibration to the reaction force of first, second polishing base plate 46 and 48, can pass to operator by motor drive shaft 42, housing 30 etc.To reduce vibration in order reaching, to reduce the injury to operator, transmission mechanism makes first, second polishing base plate 46 and 48 not identical and separated from one another.First, second polishing base plate 46 and 48 preferably has equal quality, and preferably they work area also equate.First, second outer surface 52 and 54 of first, second polishing base plate 46 and 48 is in the same plane.In addition, the transmission mechanism being driven by motor drive shaft 42 is configured to and not only can makes first, second polishing base plate 46 and 48 around center line rotation separately, and can do anti-phase circumference beat motion.Beat motion by single spin-echo can power compensation inertia and frictional force, thereby reduced the vibration being delivered on motor drive shaft 42.
As shown in Figures 2 and 3, transmission mechanism is supported on the inside of housing front portion 36, and it comprises bevel gearing 58 and offset assembly etc.Bevel gearing 58 is supported on the centre position of housing front portion 36.And housing front portion 36 is extended to a bell-jar 62 at its downside, bell-jar 62 has inner chamber 64, and offset assembly is supported in the inner chamber 64 of this bell-jar 62.In bell-jar 62, be also provided with separator 66, by first, second polishing base plate 46 and 48 and transmission mechanism separate.
The gripping surface 68 of person's contact that the top of housing front portion 36 is provided with convenient operation, this gripping surface 68 can be to be made up of the plastics of good hand touch.Certainly,, for convenient operator, above housing front portion 36, be also provided with dismountable assist handle 70.
In the present embodiment, bevel gearing 58 comprises intermeshing the first bevel gear 72 and the second bevel gear 74.
Wherein the first bevel gear 72 is not fixed on motor drive shaft 42 rotatably.The second bevel gear 74 be fixedly connected on the angled main shaft 76 of motor drive shaft 42 on.This main shaft 76 is supported in housing front portion 36 by bearing.
Offset assembly comprises interstitial hole 78 for connecting main shaft 76, for connecting the first connecting portion of the first grinding disc assembly 32 and for connecting the second connecting portion of the second grinding disc assembly 34, wherein the first connecting portion and the second connecting portion are all with respect to center line 80 eccentric settings of interstitial hole.
In the present embodiment, offset assembly comprises a double-eccentric shaft 60, and interstitial hole 78 is arranged on the upper end of this double-eccentric shaft 60, for accommodating main shaft 76.By screw, double-eccentric shaft 60 is fixedly attached on main shaft 76.The center line 80 of interstitial hole overlaps with the center line of main shaft 76.
Double-eccentric shaft 60 is provided with eccentric through-hole 82 in its bottom, and this eccentric through-hole 82 has formed the first connecting portion, and its eccentric throw with respect to the center line 80 of interstitial hole is e1, namely the distance between center line 80 and the center line of eccentric through-hole of interstitial hole.The first polishing base plate 46 is arranged in this eccentric through-hole 82 by a connecting axle 86.And between connecting axle 86 and eccentric through-hole 82, be provided with a pair of clutch shaft bearing 88.
Connecting axle 86 can not relatively rotate in the interior ring that is inserted in clutch shaft bearing 88, and the outer shroud of clutch shaft bearing 88 can not relatively rotate and is contained in eccentric through-hole 82.
Between a pair of clutch shaft bearing 88, be provided with distance piece 90, this distance piece 90 is for two two bearings 88 are separated, thereby increased bearing length, extended the life-span of bearing.Clutch shaft bearing 88 and distance piece 90 are arranged on the upper end of connecting axle 86.The lower end of connecting axle 86 is provided with screwed hole, by screw 84, the first polishing base plate 46 is fixedly connected on connecting axle 86.
Double-eccentric shaft 60 is provided with rotor journal 92 in its bottom, and this rotor journal 92 has formed the second connecting portion, and its eccentric throw with respect to the center line 80 of interstitial hole is e2, namely the distance between center line 80 and the center line of rotor journal of interstitial hole.Rotor journal 92 can not relatively rotate in the interior ring that is inserted in the second bearing 94, and the outer shroud of this second bearing 94 can not relatively rotate and be contained in the second polishing base plate 48.
Clutch shaft bearing 88 and the second bearing 94 are all ball bearing or needle bearing.Clutch shaft bearing 88 comprises for the centre bore 96 of collecting company's spindle 86 and to have center line be 98.The second bearing 94 comprises that accommodating rotor journal 92 centre bores 100 and having center line is 102.The center line 98 of clutch shaft bearing 88 is parallel with the center line 80 of centre bore with the center line 102 of the second bearing 94, but lays respectively at the both sides of the center line 80 of centre bore.
The center line of clutch shaft bearing center line 98 and eccentric through-hole center line, the first polishing base plate 46 overlaps, and the center line of the second bearing axis 102 and rotor journal center line, the second polishing base plate 48 overlaps.Such design can make in the barycenter and the plane of the second polishing base plate 48 barycenter through the center line 80 of interstitial hole of the first polishing base plate 46.Preferably, the center line of rotor journal 92 and the center line of eccentric through-hole are 180 degree with respect to the center line 80 of interstitial hole and are distributed in both sides.And rotor journal 92 can equate with respect to the eccentric distance e 2 of the center line 80 of interstitial hole with respect to the eccentric distance e 1 of the center line 80 of interstitial hole and eccentric through-hole 82 also can be unequal.
The first polishing base plate 46 is arranged in eccentric through-hole 82 by clutch shaft bearing 88, and the second polishing base plate 48 is arranged on rotor journal 92 by the second bearing 94.The rotation of motor drive shaft 42 passes to double-eccentric shaft 60 by main shaft 76, drives the first polishing base plate 46 and the second polishing base plate 48 to do the motion of circumference beat, i.e. revolution by the rotation of clutch shaft bearing 88 and the second bearing 94.Thereby, the eccentric orbit phase phasic difference that the first polishing base plate 46 and the second polishing base plate 48 form 180 °.
In operating process, the first polishing base plate 46 and the second polishing base plate 48 produce respectively forced direction contrary (because having the anti-phase cause of 180 °) and eliminate vibration.The amplitude of polishing base plate bias can not be delivered on machine, the vibration of machine is reduced, operate more comfortable.
Double-eccentric shaft 60 is provided with balancing weight 104.This balancing weight 104 can be arranged on the common vibration that reduces machine of balance weight on main shaft 76 106.Balancing weight 104 and double-eccentric shaft 60 form a single entirety, metal as by monoblock.Balancing weight 104 and double-eccentric shaft 60 also can be tightened together afterwards by two discrete components again.Equally, the first connecting portion, the second connecting portion and double-eccentric shaft 60 form single entirety or are tightened together by discrete component.
Certainly, as is known to the person skilled in the art, the concrete structure of offset assembly can also have other structure, as capacity eccentric bearing or eccentric fan etc.But as long as its function and effect and the present invention are same or similar, all should be covered by protection domain of the present invention.
Clutch shaft bearing 88 and the second bearing 94 in the first polishing base plate 46 and the second polishing base plate 48 with unique connection the between housing 30.Double-eccentric shaft 60 is fastenedly connected on main shaft 76, makes the rotating speed of double-eccentric shaft 60 identical with the rotating speed of main shaft 76.Double-eccentric shaft 60 driving the first polishing base plate 46 as discussed above and the second polishing base plate 48 are done the motion of circumference beat.On the steel ball of clutch shaft bearing 88 and the second bearing 94, relatively little frictional force namely drives the first polishing base plate 46 and the second polishing base plate 48 respectively around the power of their center line 96 and 100 rotations separately, drives the center line rotation around self of the first polishing base plate 46 and the second polishing base plate 48.
Eccentric rotary swings class instrument 300 and works under zero load, as operator is held in it in the air, because in this state, be arranged between sand paper in the first polishing base plate 46 and the second polishing base plate 48 and workpiece and there is no frictional force, the first polishing base plate 46 and the second polishing base plate 48 direction same with main shaft 76 start rotation, and the first polishing base plate 46 accelerates with the second polishing base plate 48 until they finally approach the rotating speed the same with main shaft 76.
But, once eccentric rotary is swung to class instrument 300 imposed loads, namely when sand paper and surface of the work in the first polishing base plate 46 and the second polishing base plate 48 contact, reaction force suffered on the steel ball of clutch shaft bearing 88 and the second bearing 94 will strengthen, thereby the rotating speed of the rotation of the first polishing base plate 46 and the second polishing base plate 48 will sizablely reduce.The rotation of first, second polishing base plate 46 and 48 even almost stops, and can only keep the circumference beat being driven by motor drive shaft 42 to move, and can only keep revolution.
According to above explanation, our known first, second polishing base plate 46 and 48 depends on around the rotating speed of center line center line 98 and 102 rotations of clutch shaft bearing 88 and the second bearing 94 magnitude of load applying.In contrast, the eccentric swing that first, second polishing base plate 46 and 48 is driven by motor drive shaft 42 depends on the rotating speed of motor 38.But polishing base plate has revolution that motor 38 drives and the rotation around the center line center line 98 and 102 of clutch shaft bearing 88 and the second bearing 94 simultaneously, can improve the grinding efficiency of whole instrument.
In the course of the work, the frictional force of the first polishing base plate 46 and load is always not the same with the frictional force of the second polishing base plate 48 and load, has caused the rotary speed of the first polishing base plate 46 and the second polishing base plate 48 different yet.Just there will be the phenomenon that occurs the partially slow or stall of one of them rotary speed as the first polishing base plate 46 or the second polishing base plate 48 because load is excessive, thereby affected grinding efficiency.
In order to improve grinding efficiency, between the first grinding disc assembly 32 and the second grinding disc assembly 34, be provided with link gear 110, this link gear 110 can make one of them grinding disc assembly time rotational drive the rotation of another one grinding disc assembly.Thereby while making one of them polishing base plate stall, another polishing base plate drives its rotation, and then makes grinding efficiency higher.
As shown in Figure 3 and Figure 4, link gear 110 comprises and is connected to mating groove 112 on one of them of the first grinding disc assembly 32 and the second grinding disc assembly 34 and is connected to the first grinding disc assembly 32 and the counterpart 114 of the second grinding disc assembly 34 on another, and counterpart 114 matches with mating groove 112.
In the present embodiment, mating groove 112 is connected on the first grinding disc assembly 32, counterpart 114 is connected on the second grinding disc assembly 34.
And in order to increase the intensity of interlock dish 116, can reinforcement 117 be set in the centre of each mating groove 112.
In the present embodiment, mating groove 112 is 5, and the number of counterpart 114 corresponding thereto, is also 5.Certainly, mating groove and counterpart number are not corresponding also can realize creating conception of the present invention, and the number of mating groove 112 and counterpart 114 is not key, can and require design arbitrarily according to concrete structure.
Be appreciated that interlock dish 116 and linkage rack 118 can be all to have other shape, as circular, square or other polygon etc.Even without interlock dish and linkage rack are set, and mating groove and counterpart are set directly on the first grinding disc assembly 32 and the second grinding disc assembly 34.
As shown in Figure 2 and Figure 5, in the course of the work, if the first polishing base plate 46 stops because load is excessive rotating around the center line 98 of clutch shaft bearing, at this moment, the second polishing base plate 48 the center line 102 around the second bearing around in, the mating groove 112 that can coil on 116 by interlock coordinates with the counterpart 114 being arranged in the first polishing base plate 46, and then drives the first polishing base plate 46 with identical speed rotation.In like manner, if the second polishing base plate 48 stops because load is excessive rotating around the center line 102 of the second bearing, at this moment, the first polishing base plate 46 the center line 98 around clutch shaft bearing around in, can coordinate with the mating groove 112 on interlock dish 116 by the counterpart 114 being arranged in the first polishing base plate 46, and then drive the second polishing base plate 48 with identical speed rotation.
Certainly, as is known to the person skilled in the art, the concrete structure of link gear 110 can also have other structure, and if mating groove is cross recess, counterpart is sliding part sliding with respect to cross recess etc.But as long as its function and effect and the present invention are same or similar, all should be covered by protection domain of the present invention.
In foregoing description, also mention, there is one of them rotary speed partially slowly or the phenomenon of stall in the first polishing base plate 46 or the second polishing base plate 48, thereby has affected grinding efficiency because load is excessive.
In order to prevent that the phenomenon of stall from appearring rotary speed partially slowly or in the first polishing base plate 46 or the second polishing base plate 48 because load is excessive.Eccentric rotary swings class instrument 300 and comprises pressure driving mechanism.This pressure driving mechanism selectively impels at least one the center line rotation around self in the first grinding disc assembly 32 and the second grinding disc assembly 34.And this pressure driving mechanism impels the first grinding disc assembly 32 or the second grinding disc assembly 34 can be faster around the speed of the center line rotation of self, and not affected by extraneous situation, thereby improve grinding efficiency greatly.
Wherein, force driving mechanism can impel the first grinding disc assembly 32 and the second grinding disc assembly 34 respectively around self center line rotation simultaneously; Or force driving mechanism only to drive the first grinding disc assembly 32 and second grinding disc assembly 34 one of them center line rotation around self, then drive another the center line rotation around self with the speed with all wherein of the first grinding disc assembly 32 and the second grinding disc assembly 34 by link gear 110.
As shown in Figure 3 and Figure 6, force driving mechanism to drive the center line rotation of the second grinding disc assembly 34 around self.Force driving mechanism to comprise the retainer 122 that is movably arranged on housing 30, be rotatablely arranged on joggle piece 124 on housing 30, be connected to the gear 126 on the second grinding disc assembly 34, its middle gear 126 engages with joggle piece 124.Certainly,, if force the gear of driving mechanism to be arranged on the first grinding disc assembly 32, force driving mechanism to drive the center line rotation of the first grinding disc assembly 32 around self.
Eccentric rotary swings class instrument 300 and comprises Connection Block 128.Gear 126 is arranged on Connection Block 128, and the second polishing base plate 48 is connected by screw on Connection Block 128.The internal diameter of gear 126 is used for accommodating the second bearing 94.And for structure is compacter, Connection Block 128 is provided with inner chamber 130, this inner chamber 130 is for holding the structures such as interlock dish 116.Gear 126 and Connection Block 128 form a single entirety, metal as by monoblock.Gear 126 and Connection Block 128 also can be tightened together afterwards by two discrete components again.
In the present embodiment, housing 30 is provided with the chute (not shown) of accommodating retainer 122, and retainer 122 can slide in this chute between primary importance and the second place.
On the contrary, retainer 122 is positioned at the second place, contact-making surface 136 disengagements of retainer 122 and coordinating of end tooth 134, at this moment the gear 126 that joggle piece 124 is rolled thereon drives rotation, the motion that the second grinding disc assembly 34 does with aforementioned do not increase force when driving mechanism, for circumference beat motion be subject to the rotation of the center line around self of ectocine, the second grinding disc assembly 34 mainly carries out the cutting stroke that stroke is less.Equally, in the rotation process of the second grinding disc assembly 34, also can carry out relatively little cutting stroke with same speed by link gear 110, the first grinding disc assemblies 32.
Eccentric rotary swings the operating knob 142 that class instrument 300 comprises that operation retainer 122 moves.Together with this operating knob 142 is fixed by screws in connector 144 and around rotation centerline 146, be rotatably arranged on housing 30.On connector 144, be connected with cam pin 148, the center line 150 of this cam pin is with respect to rotation centerline 146 eccentric settings.When operating knob 142 is with 142 to be dynamically connected part 144 while rotating around rotation centerline 146,148 of cam pins do the motion of circumference beat around rotation centerline 146.And the end of cam pin 148 coordinates with retainer 122, thereby drive retainer 122 to move along chute along with cam pin 148 does beat motion, thereby realize the contact-making surface 136 of retainer 122 and coordinating or disengagement of end tooth 134.
As shown in Figure 7, housing 30 is provided with accepting groove 152, this accepting groove 152 comprises first, second chute 156 and 158 that roughly rounded circular trough 154 and the diametric(al) along circular trough 154 are extended, and this first, second chute 156 and 158 is symmetrical arranged and is communicated with circular trough 154.
On operating knob 142, be also provided with mobilizable stop button 160, this stop button 160 is for the rotation of control operation button 142.
As shown in Figure 8, operating knob 142 is provided with accepting groove 159, and stop button 160 is contained in this accepting groove 159 and can slides between the two positions along this accepting groove 159.In primary importance, stop button 160 allows operating knob 142 to rotate around rotation centerline; In the second place, stop button 160 stops operating knob 142 to rotate around rotation centerline.
As shown in Figure 7 and Figure 8, stop button 160 comprises selectively the butting section 162 leaning with the sidewall of first, second chute 156 and 158; And set first, second retainer 166 and 168 of first, second position.The first retainer 166 leans with the first contact part 170 on operating knob 142, and stop button 160 is positioned at primary importance; The second retainer 168 leans with the second contact part 172 on operating knob 142, and stop button 160 is positioned at the second place.
Between stop button 160 and operating knob 142, be provided with spring 174.And the bias force of spring 174 impels stop button 160 to be positioned at all the time the second place.
As shown in Fig. 6, Fig. 7 and Fig. 8, now retainer 122 engages with end tooth 134, and cam pin 148 is positioned at it bottom.But need to change being related to of retainer 122 and joggle piece 124 time, first mobile stop button 160, makes it move to primary importance with respect to the first chute 156, move to the first retainer 166 and the first contact part 170 leans; Now butting section 162 moves in circular trough 154, throws off with the sidewall of the first chute 156 and leans, and at this moment, the lateral wall 164 of stop button 160 is concordant with the lateral wall 163 of boss 157 or be positioned at the inner side of the lateral wall 163 of boss 157.Then rotary operation knob 142, rotates operating knob 142, stop button 160 together around rotation centerline 146.
Drive in the process that connector 144 rotates around rotation centerline 146 at operating knob 142, drive retainer 122 to move up in Compress Spring 140 thereby cam pin 148 does beat motion, thereby throw off and the coordinating of end tooth 134.Rotation is during to the second chute 158, and stop button 160 can, under the effect of spring force, move to the second place along the second chute 158 automatically, moves to the second retainer 168 and the second contact part 172 leans; Now butting section 162 moves in the second chute 158, and leans with the sidewall of the second chute 158, thereby stops operating knob 142 to rotate around rotation centerline, and cam pin 148 is positioned at it topmost, and retainer 122 disengagements coordinate with end tooth 134.
Equally, throw off while coordinating with end tooth 134 when retainer 122, need to change being related to of retainer 122 and joggle piece 124 time, rotary operation knob 142 make it return back to butting section 162 to move in the first chute 156 as stated above.
Be appreciated that, drive the structure of retainer 122 between first, second position to be not limited to adopt operating knob 142, stop button 160 and cam pin, it can also be designed to other structures, can between first, second position, move by direct control retainer 122 such as the forms such as screw thread are set.Or other move between the two positions as the structure such as connecting rod, cam can realize it equally.
Certainly, as will be understood by the skilled person in the art, force driving mechanism can also have other form.As force driving mechanism to comprise to drive the first grinding disc assembly or the second grinding disc assembly CD-ROM drive motor around the center line rotation of self, can realize equally the creating conception that improves stock-removing efficiency.
In above-mentioned description, mention, force driving mechanism can impel the first grinding disc assembly and the second grinding disc assembly respectively around self center line rotation simultaneously.
Here forcing driving mechanism, can be to comprise driving respectively described first, second grinding disc assembly first, second CD-ROM drive motor around the center line rotation of self.Here, first, second CD-ROM drive motor drives respectively the first grinding disc assembly and the speed of the second grinding disc assembly rotation can be the same, also can be different.
Certainly, force the structure of driving mechanism also can be similar to the pressure driving mechanism shown in Fig. 6 to Fig. 8, difference is that this pressure driving mechanism comprises the first gear being connected on the first grinding disc assembly and is connected to the second gear on the second grinding disc assembly.Thereby make to force driving mechanism can drive the center line rotation of first, second grinding disc assembly around self simultaneously.
Force driving mechanism can comprise that a joggle piece engages with first, second gear simultaneously here; Also can comprise that two joggle pieces engage with first, second gear respectively.Equally, force driving mechanism that a retainer being movably arranged on housing also can be set, for selectively suitable with the joggle piece arranging; Or it is selectively suitable with two joggle pieces that two retainers are set simultaneously.
Retainer moves between primary importance and the second place, in primary importance, retainer engages joggle piece is fixed with respect to housing with joggle piece, described first, second gear rotates with respect to joggle piece, now, the superposeed rotation of the center line around self that can not brake of the circumference beat motion of first, second grinding disc assembly, thus first, second grinding disc assembly moved a relatively large cutting stroke, improved cutting efficiency.Otherwise, in the second place, retainer and joggle piece disengage, joggle piece is moved together with first, second gear, now, the motion that first, second grinding disc assembly does is the motion of circumference beat and the rotation that is subject to the center line around self of ectocine, and first, second grinding disc assembly mainly carries out the cutting stroke that stroke is less.
The rotating speed that swings class instrument 300 in order to limit eccentric rotary is provided with braking mechanism between separator 66 and Connection Block 128.Referring to shown in Fig. 2 and Fig. 3, this braking mechanism comprises sealing ring 176 and elastic ring 178, is provided with groove 180 on the circumference of Connection Block 128 again.When installation, sealing ring 176 and elastic ring 178 are contained in this groove 180, so design can limit the rotating speed of the second polishing base plate 48, but also can play the effect of sealing, has played good dust-proof effect.In addition, owing to being provided with link gear 110, therefore, the first polishing base plate 46 is also without braking mechanism is set separately.
The second polishing base plate 48 is provided with the through hole 182 passing for double-eccentric shaft 60, in order to allow dust and dirt keep away this through hole 182, is provided with convoluted diaphragm 184 seals at the lower surface of the second polishing base plate 48.The outward flange sealing of this convoluted diaphragm 184 is fixed by screws in the second polishing base plate 48, and the centre bore 186 of convoluted diaphragm is enclosed on double-eccentric shaft 60 as sliding seal.In the time that eccentric rotary swing class instrument 300 is worked, the centre bore 186 of convoluted diaphragm 184 is followed at double-eccentric shaft 60 eccentric motions, wherein because the corrugated contours of convoluted diaphragm 184 has elasticity, can ensure in the course of the work dustproof effect.
Can find out from Fig. 9 and Figure 10, the inner chamber of bell-jar 62 is formed with dust absorption passage, is provided with the dust mouth 188 being communicated with this dust absorption passage on bell-jar 62.Dust mouth 188 is communicated with the sweep-up pipe of dust exhaust apparatus.
And be arranged on the first cavity 190 and the second cavity 192 that separator 66 on housing 30 is divided into dust absorption passage connection.Outer gas stream is flowed through after the first cavity 190, the second cavity 192 successively, flows out from dust mouth 188.
Between separator 66 and housing 30, be formed with the connected entrance 194 that is communicated with the first cavity 190 and the second cavity 192.The number of connected entrance 194 and size can arrange as required.In order to make better effects if, can there be 180 degree phase differences connected entrance 194 and dust mouth 188 in the plane that is parallel to separator.Certainly, also connected entrance 194 can be set directly on separator 66.
Again referring to Fig. 1, be positioned at the first inner polishing base plate 46 external diameter be slightly less than the internal diameter that is positioned at outside the second polishing base plate 48, make can between the first polishing base plate 46 and the second polishing base plate 48, retain a predetermined minimum clearance in whole rotation operating process.Gap between the first polishing base plate 46 and the second polishing base plate 48 can be in operating process as the entrance 202 of dust absorption passage.
In the process of work, the entrance 202 that dust forms via the first polishing base plate 46 and the second polishing base plate 48 enters to after the first cavity 190, and the through hole 204 of a part of dust in the second polishing base plate 48 directly flows out from the first dust mouth 196.And another part dust enters to after the second cavity 192 through 194 mouthfuls of the connections on separator 66 after the through hole 204 in the second polishing base plate 48, then flowed out by the second dust mouth 198.
So, air-flow is flow path the first cavity 190 and the second cavity 192 respectively, has increased the area that air flow stream is crossed, thus the parts better in cooling the first cavity 190 and the second cavity 192.The service life of instrument and the comfortableness of operation are so extended.
Certainly, as will be understood by the skilled person in the art, eccentric rotary swings class instrument 300 and only includes a polishing base plate or comprise that more polishing base plate all can play same effect.In the time that a polishing base plate is set, at this moment, in polishing base plate, can be uniformly distributed SS, for passing through of the abrasive dust that produces below polishing base plate in the time of grinding, and the first cavity and the second cavity that separator is divided into dust absorption passage connection is set on housing, increase the area that air flow stream is crossed, played better cooling effect.The service life of instrument and the comfortableness of operation are extended.
The present invention is not limited to aforementioned embodiments, and those skilled in the art also may make other and change under the enlightenment of the technology of the present invention marrow, but as long as function and the present invention of its realization are same or similar, all should be covered by protection domain of the present invention.
Claims (10)
1. eccentric rotary swings a class instrument, comprises
Housing;
Be arranged on motor in described housing and the transmission mechanism by described motor driving;
Be supported on described housing by the first grinding disc assembly of described transmission mechanism eccentric drive and the second grinding disc assembly;
It is characterized in that: between described the first grinding disc assembly and the second grinding disc assembly, be provided with link gear, described link gear can make one of them grinding disc assembly time rotational drive the rotation of another one grinding disc assembly.
2. eccentric rotary according to claim 1 swings class instrument, it is characterized in that: described the first grinding disc assembly is the same with described the second grinding disc assembly rotational velocity.
3. eccentric rotary according to claim 1 swings class instrument, it is characterized in that: described link gear comprises and be connected to mating groove on one of them of the first grinding disc assembly and the second grinding disc assembly and be connected to the first grinding disc assembly and the counterpart of the second grinding disc assembly on another, described counterpart matches with described mating groove.
4. eccentric rotary according to claim 3 swings class instrument, it is characterized in that: on described the first grinding disc assembly, be connected with interlock dish, described mating groove is arranged on described interlock dish.
5. eccentric rotary according to claim 4 swings class instrument, it is characterized in that: described link gear comprises some described mating groove and some counterparts that are evenly arranged on the second grinding disc assembly that are evenly arranged on interlock dish.
6. eccentric rotary according to claim 3 swings class instrument, it is characterized in that: described mating groove is circular trough, and described counterpart is the rolling member that can rotate around self center line.
7. eccentric rotary according to claim 3 swings class instrument, it is characterized in that: described mating groove is cross recess, and described counterpart is the sliding part sliding with respect to described cross recess.
8. eccentric rotary according to claim 1 swings class instrument, it is characterized in that: described eccentric rotary swings class instrument and comprises pressure driving mechanism, and described pressure driving mechanism comprises the gear being connected on the first grinding disc assembly or the second grinding disc assembly; The joggle piece engaging with described gear; And be movably arranged on the retainer on housing, and described retainer moves between primary importance and the second place, and in primary importance, retainer engages joggle piece is fixed with respect to housing with joggle piece, and described gear rotates with respect to joggle piece; In the second place, retainer and joggle piece disengage, and described joggle piece is moved together with described gear.
9. eccentric rotary according to claim 1 swings class instrument, it is characterized in that: described transmission mechanism comprises an offset assembly, described offset assembly comprises interstitial hole for connecting described main shaft, for connecting the first connecting portion of described the first grinding disc assembly and for connecting the second connecting portion of described the second grinding disc assembly, wherein said the first connecting portion and described the second connecting portion are all with respect to the center line eccentric setting of described interstitial hole.
10. eccentric rotary according to claim 9 swings class instrument, it is characterized in that: described offset assembly is double-eccentric shaft, described the first connecting portion is eccentric through-hole, the second connecting portion is rotor journal, and the center line of described eccentric through-hole and described rotor journal is separately positioned on the both sides of the center line of described interstitial hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210537262.2A CN103862378B (en) | 2012-12-13 | 2012-12-13 | Eccentric rotary swings class instrument |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210537262.2A CN103862378B (en) | 2012-12-13 | 2012-12-13 | Eccentric rotary swings class instrument |
Publications (2)
| Publication Number | Publication Date |
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| CN103862378A true CN103862378A (en) | 2014-06-18 |
| CN103862378B CN103862378B (en) | 2016-08-03 |
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| CN201210537262.2A Expired - Fee Related CN103862378B (en) | 2012-12-13 | 2012-12-13 | Eccentric rotary swings class instrument |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113210729A (en) * | 2021-04-19 | 2021-08-06 | 江苏东成工具科技有限公司 | Reciprocating electric tool |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB370269A (en) * | 1930-06-26 | 1932-04-07 | Mariano Castells | Improvements in grinding and polishing devices |
| US5947804A (en) * | 1998-04-27 | 1999-09-07 | Ryobi North America, Inc. | Adjustable eccentricity orbital tool |
| JP2002233941A (en) * | 2001-02-06 | 2002-08-20 | Makita Corp | Orbital sander |
| CN101633143A (en) * | 2008-07-25 | 2010-01-27 | 苏州宝时得电动工具有限公司 | Hand-held tool and application method thereof |
-
2012
- 2012-12-13 CN CN201210537262.2A patent/CN103862378B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB370269A (en) * | 1930-06-26 | 1932-04-07 | Mariano Castells | Improvements in grinding and polishing devices |
| US5947804A (en) * | 1998-04-27 | 1999-09-07 | Ryobi North America, Inc. | Adjustable eccentricity orbital tool |
| JP2002233941A (en) * | 2001-02-06 | 2002-08-20 | Makita Corp | Orbital sander |
| CN101633143A (en) * | 2008-07-25 | 2010-01-27 | 苏州宝时得电动工具有限公司 | Hand-held tool and application method thereof |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113210729A (en) * | 2021-04-19 | 2021-08-06 | 江苏东成工具科技有限公司 | Reciprocating electric tool |
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| Publication number | Publication date |
|---|---|
| CN103862378B (en) | 2016-08-03 |
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Effective date of registration: 20170426 Address after: 215123 Jiangsu Province, Suzhou City Industrial Park East Road, No. 18 Patentee after: Technology (China) Co., Ltd. Address before: 215123 Jiangsu Province, Suzhou City Industrial Park East Road, No. 18 Patentee before: Baoshide Electric Tools Co., Ltd., Suzhou |
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Granted publication date: 20160803 Termination date: 20191213 |