CN1748939A - Anti-vibration arrangement, tool using said anti-vibration arrangement and its method for cleaning working surface - Google Patents
Anti-vibration arrangement, tool using said anti-vibration arrangement and its method for cleaning working surface Download PDFInfo
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- CN1748939A CN1748939A CN 200510067539 CN200510067539A CN1748939A CN 1748939 A CN1748939 A CN 1748939A CN 200510067539 CN200510067539 CN 200510067539 CN 200510067539 A CN200510067539 A CN 200510067539A CN 1748939 A CN1748939 A CN 1748939A
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- Prior art keywords
- liner
- vibration absorber
- center line
- supporter
- motor shaft
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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
- B24B41/00—Component parts such as frames, beds, carriages, headstocks
- B24B41/007—Weight compensation; Temperature compensation; Vibration damping
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
Abstract
The invention relates to an eccentrically rotary swinging tool (1) which comprises a shell (2), an electric motor (4) arranged on the shell, a motor shaft (11), a first annular outer pad (16) connected with a first frosted piece (8) and a second round inner pad (22) connected with a second frosted piece (9); a vibration absorber (10) transmits the energy of the electric motor (4) to pads (6 and 22) through reverse movement, thereby inertia and friction are compensated by motion. At the same time, the vibration which is transmitted to the motor shaft (11) and then to an operator of the tool is greatly reduced. Even if the operator increases the force to the eccentrically rotary swinging tool (1) in order to increase the depth of grinding or to improve the speed of the grinding, the same effect also can be obtained. To achieve the aim, cams (18a and 18b) are fixed on the motor shaft (11) and drive center lines (5 and 21) of the pads (6 and 22) to rotate 180 degrees reversely around the center line (12) of the electric motor.
Description
Affiliated technical field
The present invention relates to a kind of portable power tool field that acts on the working face surface.Particularly relate to the especially vibration absorber of sander and polishing machine of a kind of eccentric rotary oscillation class instrument.It relates to other motor machines that use same vibration absorber and the method for grinding and polishing surface of the work equally
Background technology
Well-known above mentioned eccentric rotary oscillation class instrument generally includes a floor or liner supports an abrasive body as frosted class instrument, as sand paper.Liner is connected on the motor by the suitable kind of drive, and motor is installed on the casing that has one or more handles.The kind of drive is embodied in the rotation of motor shaft driving cam.Cam is to be installed on the circular hole that is arranged in pad centers.Each o'clock on the rotation driving liner of cam, the radius of this circular trace equaled the eccentric throw of cam along the orbiting motion of a circle, and just the center line of motor shaft is to the distance at the circular hole center that is positioned at the pad centers that supports abrasive body.By allowing the center rotation of liner around circuit orbit, it can be called as compound rotation rail also can be called as " free orbit ".
The time and frequently, we can see that described orbiting motion has become the linear movement that cushion body can quicken in certain distance.This acceleration has produced rightabout reaction force.The unnecessary vibration that reaction force produces is delivered to fuselage and finally is delivered to operator's hand and arm.The amplitude of this vibration depends on the diameter dimension of track and the ratio of liner quality and machine quality.The operator of these machines generally can apply certain power or load to machine and go to accelerate operating rate and increase productivity, but tends to increase the amplitude of vibration like this.
For vibration limiting an acceptable level, it is relative less that available on the market machine, equipment and electric tool often are designed to be the diameter of working face (size of liner) and track.Yet this restriction has reduced the efficient of machine.
In order to remedy this restriction to efficient, the operator tends to machine is applied certain load to increase the frictional force on the working face.But do like this and cause vibration to strengthen further.The operator has to apply bigger power again for the vibration of eliminating this increase and goes machine by on workpiece.So, the quality of machine is actually and has increased, and vibration is that the person's of being operated hand and arm absorbed, and this can produce serious consequence to health of operator.
Even those use the people of frosted class instrument also can realize the numbness and the shouting pain of finger, arm and arm very soon once in a while.These symptoms will display after few minutes of operation, make us feeling very unhappy, and the sensation of this numbness and shouting pain also continues several hrs behind terminating operation.If the ongoing operation several hrs then will be taken several days time and recover.This vibration gives workman's the consequence that causes more serious.
The disease that the vibration of workers with long time exposure electric tool and equipment causes can make workman's retirement greatly, and this can cause high social cost.On the other hand, the employing meeting to the index of coupled vibration limiting value has significant impact to productivity and product cost.
Reason in sum clearly is that the producer of these electric tools that vibration is arranged or user wish to eliminate or reduce and be delivered to operator's vibration on one's body, thereby improves workman's safety and productivity and reduce relevant social cost.
The first method that addresses the above problem is, takes the relative liner of one or more eccentric bodies or balance weight to move in the other direction, thus balance vibration.Patent US 4,660,329, and US 4,729,194, and US 5,888,128, US 6,244,943, US6,206,771, US 2001/0003087, and DE 3922522, and EP 0303955, and EP 0455618, and WO 98/01733, this just solution that WO02/068151 disclosed.
In general, this solution can not play good effect when liner does not also touch workpiece, but significant limitation is but arranged in daily operation.Abrasive body on liner touches workpiece, and in fact load can change the quality of liner itself, thereby the ratio of liner quality and balance weight quality is also in variation.Therefore, balance weight can not be eliminated the vibration of the actual increase generation of liner quality.Load is big more, unbalance vibration is big more more in system.When load is tending towards infinitely great, liner will be stagnated and fuselage will be to equal the amplitude vibration of liner tracks radius.
The operator who is to use this type electric tool of mandatory declaration likes instrument is applied certain load to improve operating rate.By imposed load operating efficiency being significantly improved mainly is because the frictional force that liner and workpiece are asked increases.On the other hand, the increase of load makes that machine is uneven so has also increased unnecessary vibration.Deduct the diameter of this unnecessary vibration from the race way diameter of liner, what therefore it is contemplated that is that the diameter of effective working track is the race way diameter that theoretic race way diameter deducts this unnecessary vibration.
The second method that addresses the above problem is that the employing elastomeric material between machine and operator's hand, reaches the purpose of eliminating vibration thereby the kinetic energy of vibration is converted into heat energy as interface.Patent US 4,905,772, and US 5,453,577, US5,347,764, this just solution that US 2001/0011856A1, WO 03/049902 are disclosed.Yet second kind of solution do not have realistic meaning.By insert elastic component between fuselage and staff, the amplitude of this electric tool is big when holding this instrument with a firm grip more than the operator.In fact, the operator feels that very naturally the operating efficiency of machine descends, and the power that tends to Hua Gengda for the operating efficiency operator who returns to hope goes to firmly grasp it.So, the effect that adds elastic component just has been minimized, so that vibration still is delivered to operator's arm and arm.In addition, the muscle of this increase is stressed can to reduce the ability that human body self is eliminated vibration, thereby causes even more serious consequence.
Summary of the invention
Technical problem to be solved by this invention mainly provides a kind of vibration absorber and makes electric tool adapt to any working environment and keep high efficiency to overcome the problems referred to above and defective.
Another technical problem to be solved by this invention provides the amplitude that a kind of vibration absorber reduces to transmit from instrument the vibration of human body greatly, thereby reduces operator's health risk.
Another special technique problem to be solved by this invention provides a kind of cheap, maneuverable, vibration absorber of being convenient to safeguard for instrument.
Equally, the present invention also provides a kind of method that can not produce the buffing work-piece of extra vibration to the operator.
Another technical problem that the present invention solves provides a kind of portable power tool, particularly a kind of sander or polishing machine that has vibration absorber, make the user no matter roughly grind or finish grind and to keep high efficiency and productivity ratio which kind of material, no matter work as the user simultaneously and apply much load to this electric tool, can both sizable minimizing affact operator's vibration on one's body.
The technical scheme that is adopted that the present invention solves the problems of the technologies described above:
By eccentric rotary oscillation class instrument, realize by on the motor shaft rotation machine driven vibration absorber being installed as this class of polishing machine especially sander,
It is characterized in that:
A) first surface and the first pre-first directed liner are arranged
B) second surface and the second pre-second directed liner are arranged,
Abrasive body such as polished part or sand paper stick on first surface and second surface position,
And roughly align on same plane in described surface,
C) described first, second liner motion mode is to make it carry out along the track rotation around rotating shaft respectively, and the rotation of described track is an out-phase.
The liner of dull and stereotyped sand remains on predetermined direction on it.
Be the vibration absorber power compensation inertia and the frictional force of mandatory declaration has reduced the vibration that is delivered on the motor shaft.Such vibration must remain on a low level or or even compensated fully.
Thank to this design, made the function of vibration damping equipment no longer depend on the speed of rotation, the weight of machine, the type of lapped face, the radius of liner rotation and the condition of load.
Owing to cancelled the use of conventional balanced piece, made more energy can be used to grinding work.
Even in load not by mean allocation to lapped face, the vibration surplus that is delivered to the operator from electric tool also will be lower than the conventional tool that has balance weight mechanism.
The active-surface of each liner all is very smooth and is positioned at same plane.And one of them face is placed in the middle, and other face is in the periphery of this face.
In one embodiment, middle liner is circular, and peripheral liner is an annular.Certainly, liner also can be square, and four or polylith are more arranged.
A kind of mode preferably that drives the liner motion is to use the eccentric block assembly of the cam formation that comprises 180 ℃ of angles of identical, the vertical conversion of at least one pair of shape.Each cam must directly or indirectly be installed on the motor shaft.The cylindricality of each cam is identical, and the diameter of the desired just track that obtains of eccentric throw of the center line of the relative motor shaft of this cylindricality.
The external diameter of inner circular pads is slightly less than the internal diameter of outside ring liner, makes to be reserved with a minimum clearance in operating process between inside and outside liner.So, can be connected on a kind of aspirator, remove chip and dust on the workpiece as fan in the gap between liner.This is equivalent to the aperture on the conventional machines.
The embodiment of additional vibration absorber is as described in the appended claims.
According to the present invention, this is that a kind of the driving by motor shaft has the first pre-first directed liner and have the second pre-second directed liner to act on the method for workpiece equally.This method is characterised in that described first liner, and second liner rotates around second axis around first axle rotates, and this first axle and second axis overlap.
Two liners of dull and stereotyped sand keep their predetermined directions.
This in an embodiment method is possible by additional spy just:
A) use first liner of annular and second liner of circle, described second liner is the inside that is placed on first liner,
B) central axis of second liner rotates around the motor shaft center line, and
A) central axis of first liner rotates around the motor shaft center line on same direction of rotation, but departs from about 180 ℃ of the central axis of second liner.
According to the present invention, a kind of portable eccentric rotary oscillation class instrument, particularly polishing machine or sander comprise:
A) have the casing that the operator uses handle,
B) inner chamber of casing,
C) be installed in the motor in the chassis cavity and the motor shaft of longitudinal rotating shaft line is arranged,
D) at least one connects first liner of first abrasive body, with second liner that is connected second abrasive body and
E) energy transmission device from the motor shaft to the liner and as the described vibration absorber of preceding and attached claim.
This eccentric rotary oscillation class instrument can be designed to " circle sand machine ".
In order to compensate or to cancel moment of torsion, electrically powered machine can use the balance weight that directly or indirectly is connected on motor shaft or the fan, and the barycenter of balance weight is not on the motor shaft center line.
According to another embodiment, when using jockey, during the connector done as elastomeric material, eccentric rotary oscillation class instrument also can be designed as " dull and stereotyped sand ".
For fear of when liner is unloaded, rotating at a high speed, should use brake apparatus.
Brief Description Of Drawings
In conjunction with the accompanying drawings, the detailed description of the vibration absorber specific embodiment of portable power tool is made that other feature and advantage of the present invention are more obvious.In figure below:
Fig. 1 is a kind of electric tool, especially has the partial sectional view of " the circle sand machine " of vibration absorber.
Fig. 2 is the three-dimensional explosive view of the vibration absorber shown in Fig. 1.
Fig. 3 is the blast profile of the vibration absorber shown in Fig. 1.
Fig. 4 is the scaled down upward view of the device shown in Fig. 1-3.
Fig. 5 is the profile after the device assembling shown in Fig. 1-3.
Fig. 6 is the stereogram of the double cam assembly that uses in the device shown in Fig. 1-3.
Fig. 7 is the cutaway view that increases on the motor of device shown in Figure 5 behind the balance weight.
Fig. 8 is the mobile views of eight sand grains particles in operating process.
Fig. 9-the 12nd, the mobile view of four sand grains particles in operating process in addition.
Figure 13 is the upward view that four liners of second vibration absorber among the embodiment are arranged.
Figure 14 is the cutaway view that device shown in Figure 5 has increased the balance of fan piece.
Figure 15 is that device shown in Figure 1 has increased connector and shows it is the side view of " dull and stereotyped sand ".
Figure 16 is the side view that device shown in Figure 1 has increased brake apparatus.
Wherein:
1 eccentric rotary oscillation class instrument
2 casings
3 handles
4 inner chambers
5 motors
6 ball bearings
7 power switches
8 annular sand paper
9 circular sand paper
The antishock device of 10 milling tools 1
11 motor shafts
12 motor shaft center lines
13 clutch shaft bearings
13a clutch shaft bearing central point
14 clutch shaft bearing centre bores
15 clutch shaft bearing center lines
16 first (outward) liner
The 16a inner chamber
The 16b outer surface
The orientation of 16z first liner 16
17 first support members
The 17a tapered segment
The 17b annular section
Center cavity under the 17c
The cylindric center of 17d cramping body
The last center cavity of 17e
The 17f air suction opening
18 pairs of eccentric block assemblies
18a first cam
18b second cam
The 18c centre bore
The two eccentric block assembly central points of 18d
19 second bearings
19a second bearing 19 central points
The centre bore of 20 second ball bearings 19
The center line of 21 second ball bearings 19
22 second (interior) liner
The 22a outer surface
The orientation of 22z second liner 22
23 second support members (holder)
The 23a center cavity
24 little gaps
24a minimum clearance
The barycenter of 25 elements 16,17
The barycenter of 26 elements 22,23
27 straight lines perpendicular to center line 12
28 balance weights
The barycenter of 29 balance weights 28
The barycenter of 29A balance weight 28 and fan 43
30 elements 16,22,17,23, the barycenter of 13,19,18 center-of-mass systems
31 elements 16,22,17,23,13,19,18,28, the barycenter of 43 center-of-mass systems
The rotation arrow of 33 outer liners 16
The rotation arrow of 34 inner liner 22
40 ring liners, 16 orbit centres, 15 arrows
41 circular pads, 22 orbit centres, 21 arrows
42 connecting lines
43 cooling fans
44 collecting chambers
45 air and dust discharge pipe
46 first Flexible Connectors
47 second Flexible Connectors
50 first brake apparatus
51 second brake apparatus
A, b, c, d sand grains particle
E1, the e2 eccentric throw
F1, f2. power
J. eccentric throw
K, l, m. sand grains particle
Q. distance
T. circumference
F1, F2. is outer, inner surface area
K1, K2. power
P. plane
A1, A2, A3, A4. liner
B1, B2, B3, B4. liner A1, A2, A3, the surface of A4
S1, S2, S3, S4. liner A1, A2, A3, A4 center line
C1, C2, C3, C4. liner A1, A2, A3, the area of A4 center circle
R1, R2, R3, R4. liner A1, A2, A3, A4 and area C1, C2, C3, C4 track centerline
T1, T2, T3, T4. track direction of rotation arrow
D1=d2=d3=d4. track centerline R1, R2, R3, R4 is to the distance of rotation centerline M
C1 (3), C2 (3), C3 (3), C4 (3). each center circle area when (3) in the position
O1, O2, O3, O4. liner A1, A2, A3, the orientation of A4
The specific embodiment
With reference to accompanying drawing 1, disclosed a kind of eccentric rotary oscillation class instrument 1 that combines the vibration absorber of the embodiment of the invention, as sander or polishing machine.
Eccentric rotary oscillation class instrument 1 all has the casing 2 and the inner chamber 4 of band handle 3 to adorn motor 5 basically, and for example motor has motor shaft 11 and longitudinal centre line 12, and motor shaft 11 is supported by ball bearing, needle bearing or oiliness bearing.Motor 5 can not be electronic, as also can being pneumatic.Axis 12 also can be said to be motor shaft center line or rotation.Motor 5 can be worked under any speed or even very high speed.The typical scope of design of the rotating speed of motor 5 is 2000-12000 rpm.
In order to reach this target, it is inequality and separated from one another that the transmission device that comprises vibration absorber 10 makes that liner 16,22 is done.Liner 16,22 has equal quality, and preferably their work area F1, F2 also equates.The outer surface of liner 16,22 is positioned on the same plane P.
In addition, the transmission device that is driven by motor shaft 11 is configured to liner 16,22 is rotated, and can do reverse orbiting motion of stage.But, thereby reduced the vibration that is delivered on the motor shaft 11 by orbiting motion power compensation inertia and frictional force.
Orbiting motion can be paid the utmost attention to.
Specifically, transmission device and vibration absorber combine a pair of pair of eccentric block assembly 18, and this pair eccentric block assembly 18 has cam 18a, and 18b drives liner 16,22 and does orbiting motion respectively.This is further described below.
As can be seen from Figures 2 and 3, the bell support member 17 of outer liner 16 has a tapered segment 17a to link to each other with planar circular 17b, the cavity 17c below having formed.Can also have one cylindric in the middle of cramping body 17d (figure does not show) connect the center cavity 17e of annular 17b above forming one.The center cavity 17e is here formed by annulus 17b.From Fig. 2, on 3 and 5, on the supporter 17, particularly on tapered segment 17a, have an air and dust SS 17f at least as can be seen.Manage on 45 when a fan (figure does not show) is connected to, it can take dust and chip away in frosted or polishing process.
The clutch shaft bearing 13 and second bearing 19 all are ball bearing or needle bearing.The outer surface of clutch shaft bearing 13 is installed in the last center cavity 17e of annulus part 17b.And the outer surface of second bearing 19 is installed among the inner chamber 23a of cylindric cramping body 23 of inner liner 22.The central point 13a of clutch shaft bearing 13, centre bore 14 and center line 15.The central point of second bearing 19 is 19a, centre bore 20 and center line 21.
From Fig. 1-7 as can be known the primary element of vibration absorber 10 are eccentric block assemblies 18.Eccentric block assembly 18 is made up of the first cam 18a that links together and the second cam 18b.Cam 18a, the 18b shape is identical but position each other has been changed 180 ℃ in the vertical.In the centre of eccentric block assembly 18 through hole 18c is arranged, make it and motor shaft 11 be fastenedly connected.Thereby the center line of through hole 18c overlaps with rotation centerline 12.
As can be seen from Figure 6, cam 18a, 18b are actually cylindric, and they can be other shapes also, as ellipticity.Their center line is designated as 15 and 21 respectively.Cam 18a, 18b constitutes a single integral body, metal as by monoblock.Cam 18a, 18b also can be tightened together by two discrete components earlier afterwards again.With respect to the eccentric distance e 1 of center line 12, e2 also just is respectively the distance between center line 15,12 and 21,12, the race way diameter that is equal to each other (e1=e2) and equals to expect separately for cam 18a, 18b.
The outer surface of first (top) cam 18a is in the fastening centre bore 14 that is installed in clutch shaft bearing 13, and second (following) cam 18b is in the fastening centre bore 20 that is installed in second bearing 19.Knot cam 18a is transmitted in the rotation of motor shaft 11, and 18b by the slip of bearing 13 and 19, and then passes to the liner 16 and 22 that supporter 17,23 is connected separately with them again respectively.(in the embodiment of Figure 15, liner 16,22 remains at 16z in whole rotary course, the 22z direction) thereby, liner 16,22 formed eccentric orbits have been changed 180 ℃ each other.
With reference to Fig. 4 and Fig. 5 as can be known, the external diameter of inner circular liner 22 is slightly less than the internal diameter of outside ring liner 16, makes can keep a predetermined minimum clearance 24a 16,22 of liners in whole rotary manipulation process.Can be in operating process in the gap 24 of 16,22 of liners as siphoning away the chip on the workpiece and the passage of dust.This swabbing action is produced together by fan (figure does not show) and discharge pipe 45 associatings.
In operating process, liner 16,22 produces power K1 respectively, the K2 (see figure 4).Power K1, the action direction of K2 opposite (because 180 ℃ anti-phase cause is arranged) is eliminated vibration, has then passed to the operator otherwise the major part of this vibration can be delivered to the casing 2 of instrument 1.Even the operator load of instrument 1 has been increased, this vibration also can be eliminated.
With reference to Fig. 7, power f1 in the process of operation tool 1, f2 produces a little moment of torsion at point 30 places, is by liner 22,16 and put 30, supporter 17,23, the barycenter of the system that bearing 13,19 and cam pack 18 constitute.Power f1, f2 is produced by centrifugal motion, and can cause vibration.In order to eliminate this moment of torsion, can on motor shaft 11, increase a balance weight 28.Balance weight 28 can securely be directly connected on motor shaft 11 or the assembly 18, perhaps is connected to by on the cooling fan 43 of motor 4 driving cooling motors (as shown in figure 14).The barycenter 29 of balance weight 28 is not on motor rotation centerline 12.In Fig. 7, indicated its eccentric throw j.Balance weight 28 can be Any shape basically.Here usefulness is cylindric.Yet, we it should be noted that outer liner 16 adds that the quality of its supporter 17 equals the quality that inner liner 22 and its supporter 23 add balance weight 28, in order to reach the purpose of balance, being not only quality must be like this, and they also will be like this to the distance of point 31.Make whole barycenter still on point 31.
In Fig. 8, external liner 16 and inner liner 22 are described further.This will illustrate the effect of vibration absorber 10.The outer surface 16b of liner 16,22,22a is positioned on the same plane P.And supposing their area F1, F2 equates.Perhaps this requirement is not satisfied in some instances.In operating process, the center line 15 of the outer liner 16 of annular has been drawn a roundlet around the rotation centerline 12 of motor shaft 11, and has a center line 21 of 180 ℃ of conversion circular inner liner pads 22 to draw a roundlet around rotation centerline 12 equally with center line 15.These two roundlets are used arrow 40,41 indications respectively.
A connecting line 42 is center line 15,12, and 21 couple together.The distance that distance that center line is 12,15 and center line are 12,21 equates.This is to make first-selection simple in structure design, but some the time with situation under can and the condition of selection here deviate from mutually.
Suppose that arrow 16z is fixed on the outer surface 16b of outer liner 16, it has indicated predetermined direction or the location of outer liner 16 with respect to instrument 1, can be front point backward from instrument 1 such as it.Suppose that arrow 22z is fixed on the outer surface 22a of inner liner 22.It indicated equally inner liner 22 with respect to instrument 1 pre-determine direction or location, can be front point backward from instrument 1 equally such as it.In the embodiment of Figure 15, liner 16,22 remains at predetermined direction 16z in operating process, and 22z is crucial.In other words, (indicated five with (1) to (5) in Fig. 8) in all operating positions, arrow 16z, 22z are the straight lines that is parallel to predetermined vertical electric rotating machine center line 12.
Suppose eight grit particle a, b ... the position of rotation that h indicates with (1) at the outward flange of liner 16,22.Suppose the particle a on the liner 16, b, c, d separate with 90 ℃ of angles each other, and the particle e on the same liner 22, f, g, h separate with 90 ℃ of angles each other.Particle a-h moves on the roundlet of same diameter, passes through position (1)-(5) continuously, thereby the effect of polishing is arranged on processed workpiece.
In Fig. 9-12, we can see that liner 16,22 is in four coherent positions (1) respectively, (2), three particle k when (3) and (4), l, the motion of m.In this example, particle k, l, m are positioned at the inside of liner 22 and 16.Moreover particle k, l, m also are the circular motion along same diameter.
With reference to Fig. 8 to 12, it must be emphasized that, except being arranged, the liner 16 and 22 that also has the internal friction power by bearing 13 and 19 to cause respectively along the orbiting motion of circle t rotates.The rotating speed of this rotation depends on the load that sand paper 16b and 22a are subjected to respectively.In Fig. 8 to 12, indicate this rotation with arrow 33 and 34 respectively.Ring liner 16 rotates around its center line 15 all the time, and circular pads 22 is rotated around its center line 21 all the time.This rotation is hereinafter referred to as " liner rotation ".They have caused the corase grind to workpiece, and the correct grinding to workpiece has been quoted in the track road.
Is two ball bearings 13 and 19 with reference to Fig. 1-7 (comparing with Figure 14) in unique connection the between liner 16,22 and casing.Double cam assembly 18 is fastenedly connected on the motor shaft 11, makes cam 18a, and the rotating speed of 18b is identical with the rotating speed of motor shaft 11.Cam 18a, two liners 16,22 of 18b driving as discussed above.
Less relatively frictional force just drives the power that liner 16,22 rotates around their center lines 15,21 separately respectively on the steel ball of ball bearing 13,19.If instrument 1 is worked under zero load, as the operator it is held in the air, liner 16,22 is beginning rotation with motor shaft 11 same directions (seeing arrow 33 and 34), and liner 16,22 quickens finally to reach the rotating speed the same with motor shaft 11 until them.Because in this state, sand paper 16b does not have frictional force between 22a and the workpiece.
Yet in case to instrument 1 imposed load, just as sand paper 16b, 22a and surface of the work contact, and the rotating speed of liner 16,22 will sizablely reduce.Liner rotation (seeing arrow 33,34) almost stops, and can only keep a kind of very low rotating speed to roughly grind.And the rotation of this track can continue to keep, and what this moment, their were primarily carried out is the work of polishing.
From above explanation, the rotating speed and the corase grind of liner rotation depend on the load that applies as can be known for we.In contrast, the rotating speed of track rotation (can be used for eliminating vibration) depends on rotating speed of motor, and correct grinding or dull and stereotyped sand do not depend on the magnitude of load that applies.
In the course of the work, on the one hand the frictional force of the frictional force of liner 16 and load (as desktop) and liner 22 and load (as desktop) is always not the same, and having caused on the other hand, the liner of liner 16 and liner 22 rotates also different.But this performance to vibration damping has no impact, because the liner of low speed rotation not causing vibration.
The eccentric rotary oscillation class instrument of this mode of operation can be called as " circle sand machine " " sander ".
At the passed the imperial examinations at the provincial level embodiment of four liners of Figure 13.It is the same that its operation principle and Fig. 1-12 are disclosed.
Four liner A1, A2, A3, A4 do the square arrangement of symmetry.They are arranged in the center line 12 same plane on every side of motor shaft 11.All liner A1-A4 shapes are identical, and what use in the present embodiment is rectangle, particularly square.All liners all are flat, and have identical surface area B1-B4 to connect the dry sanding paper or the polishing paper of same size.Suppose sand grains particle a, b, c, d is at the exterior angle of liner.Suppose that in operating process sand grains particle a-d has coherent position (1), (2), (3), (4) or the like have only indicated position (1) and (3) on diagram.Position (3) has been changed 45 ℃ with respect to position (1) on exterior angle arrow direction indication.Liner A1-A4 and center are to represent with solid line at the border circular areas C1-C4 of a S1-S4 on position (1), are to dot on position (3).These central points comprise that the center line of liner A1-A4 all indicates with S1-S4.
The center line S1-S4 of liner A1-A4 and their central area C1-C4 does orbital motion around four center line R1-R4, continuously by the position (1) on less circle (figure does not show), (2), (3), (4) or the like.Track centerline R1-R4 is equal with the distance of the rotation centerline 12 that is positioned at liner arrangement center, i.e. d1=d2=d3=d4.
T1, T2, T3, what T4 indicated is the direction of motion of orbital motion.Among all liner A1-A4, the direction of every adjacent two liner orbital motions is opposite, liner A1 thus, and A2, A3, A4 predetermined direction 01,02 separately, 03,04 remains unchanged.Therefore, eliminated vibration.
The function that cam pack (figure does not show) and gear assembly (figure does not show) are carried out.Cam pack is similar to Fig. 6's, can comprise that two (like cylinder or column) cams connect liner A1, A3 and A2, and A4, and also these two cams all are connected on the motor shaft 11.By such cam pack and gear assembly, the rotation of motor center line 12 is delivered to four center line S1, S2, and S3, S4 rotates along arrow T1-T4 indicated direction thereby driven liner A1-A4.In this design, suppose the position that when the round C1-C4 shown in each liner A1-A4 solid line has indicated in the position (1), connects cylindric cam, and when the round C1-C4 shown in each liner A1-A4 dotted line has indicated in the position (3), connect the position of cylindric cam.
Equally in this embodiment, also can reach the purpose that reduces vibration.
Except orbital motion, thereby total has been carried out " the liner rotation " of corase grind around rotation centerline 12 rotations.
This embodiment can be designed to dull and stereotyped sand equally.
With reference to Figure 14, the cooling fan 43 of a cooling motor 4 is installed on the motor shaft 11.A balance weight 28 is positioned on the following outer surface of cooling fan 43.The barycenter 29A of cooling fan 43 and balance weight 28 is not on rotation centerline 12.Compensated imbalance in this way.
Figure 15 has disclosed the embodiment of " dull and stereotyped sand ".The embodiment of it and Fig. 1 is basic identical, and different is that it has comprised at least one first Flexible Connector 46 and at least one second Flexible Connector 47.These two connectors 46,47 can be elongated and all be to be made by elastomeric material, as rubber.First connector 46 is mounted on outer liner 16 of annular and the casing 2, and second connector 47 is mounted on circular inner liner pad 22 and the supporter 17, just between liner 22 and the casing 2.Two connectors 46,47 make liner 16,22 not rotate around their center lines 15 and 21 separately respectively.Since can not carry out this rotation, sand paper 16b and 22a can only move along roundlet t as Fig. 8 to 12 is said, shows as orbital motion.In other words be exactly, nonrigid connector 46,47 has been prevented front said " liner rotation ", but allows " track rotation ".
In Figure 16, illustrated two and can be used on brake apparatus 50,51 in round sand machine shown in Figure 1, removed to reduce the rotating speed of liner 16 and 22, particularly in instrument 1 zero load.Rotating speed can be because the effect that brake apparatus 50,51 has been simulated load by lowering.Here use brake apparatus 50,51 can be the rubber ring of various different-diameters.
Claims (34)
1. vibration absorber (10) that is used on the eccentric rotary oscillation class instrument (1), motor shaft (11) the rotation machine driven of described instrument (1) by having rotation centerline (12),
It is characterized in that:
A) has first surface (16b; B1) first liner (16; A1),
B) has second surface (22a; B2) second liner (22; A2),
First surface and second surface (16b, 22a wherein; B1, B2) in order to connecting abrasive body (8,9) respectively, and described first, second surface (16b, 22a; B1 B2) roughly is arranged on the same plane (P), and
C) in order to move described first, second liner (6,22; A1, device A2) makes described first, second liner (6,22; A1 is A2) respectively around center line (12; R1 R2) carries out track rotation out of phase.
2. according to the vibration absorber (10) of claim 1, it is characterized in that: described first liner (16) is connected to first supporter (17), and second liner (22) is connected on second supporter (23).
3. according to the vibration absorber (10) of claim 2, it is characterized in that: first liner (16) add the quality of first supporter (17) be add second supporter (23) with second liner (22) quality about equally.
4. according to the vibration absorber of claim 1,2 or 3, it is characterized in that: described first liner (16; A1) outer surface (16b; B1) and described second liner (22; A2) outer surface (22a; B2) have area identical (R1, R2).
5. according to any vibration absorber (10) of claim 1-4, it is characterized in that: described first, second liner (16,22; A1, outer surface A2) (16b, 22a; B1 is smooth and coplane B2).
6. according to any the vibration absorber (10) among the claim 2-5, it is characterized in that: it comprises that the barycenter (25) of first liner (16) of first supporter (17) and the barycenter (26) that comprises second liner (22) of second supporter (23) roughly are positioned on the straight line (27) by described rotation centerline (12).
7. according to any vibration absorber (10) of claim 1-6, it is characterized in that: the outer surface (16b) of described first liner (16) is to be center and placed in the middle the layout with rotation centerline (12), and the outer surface (22a) of second liner (22) be the periphery setting of off-centre with respect to the outer surface (16b) of first liner (16).
8. according to the vibration absorber (10) of claim 7, it is characterized in that: the outer surface (22a) of described second liner (22) roughly is circular.
9. according to the vibration absorber (10) of right 7 or 8, it is characterized in that: the outer surface (16b) of described first liner (16) roughly is an annular.
10. according to any vibration absorber (10) of claim 3-9, it is characterized in that: first supporter (17) is bell and comprises a tapered segment (17a) and an annular section (17b) that is connected on first liner (16).
11. according to any the vibration absorber (10) among the claim 3-10, it is characterized in that: when a fan was connected on the described vibration absorber (10), described first supporter (17) comprised that at least one air suction opening siphons away workpiece produces in operating process dust and chip.
12. any the vibration absorber (10) according to claim 1-11 is characterized in that: drive described liner (16,22; A1, device A2) comprise eccentric block assembly (18).
13. the vibration absorber (10) according to claim 12 is characterized in that: described eccentric block assembly (18; A1, A2) comprise at least one first cam (18a) and second cam (18b), described first cam (18a) and second cam (18b) can vertically be changed, and shape is roughly the same each other, depart from an angle each other, and had an interstitial hole (18c) to connect motor shaft (2).
14. the vibration absorber (10) according to claim 13 is characterized in that: (18a, 18b) angle has been changed about 180 ° to described first, second cam.
15. the vibration absorber (10) according to claim 13 or 14 is characterized in that: (18a 18b) is a single integral body to described first, second cam.
16. the vibration absorber (10) according to claim 15 is characterized in that: described cam (18a 18b) mainly is cylindricality, and they relatively and the eccentric throw of the center line (12) of centre bore (18c) (e1 e2) equals the diameter of the track wanted.
17. any vibration absorber (10) according to claim 9-16, it is characterized in that: the external diameter of described inner circular liner (22) is the internal diameter that is slightly less than described outside ring liner (16), make in operating process at two liners (16,22) leave predetermined gap (24) between, its minimum clearance (24a).
18. the vibration absorber (10) according to claim 17 is characterized in that: when fan is connected on the described vibration absorber (10), be the passage that siphons away dust and chip from workpiece in the gap described in the operating process (24).
19. according to any vibration absorber (10) of claim 2-18, it is characterized in that: clutch shaft bearing (13) is installed on first supporter (17), and second bearing (19) is mounted on second supporter (23).
20. according to any of claim 13-18 and the vibration absorber of claim 19 (10), it is characterized in that: (18a 18b) is installed in the inside of corresponding bearing (13,19) to each described cam.
21. any the vibration absorber according among claim 1-6 and the 10-20 is characterized in that: described first and second liners (16,22; A1 A2) mainly is rectangle or square.
22. any the vibration absorber (10) according among claim 1-6 and the 10-21 is characterized in that: four liners (A1, A2, A3 A4) has separately track central axis (R1, R2, R3, R4), and adjacent liner (A1, A2, A3 is A4) at opposite direction (T1, T2, T3 T4) does orbital motion.
23., it is characterized in that: drive described liner (16,22 according to described any the vibration absorber (10) of claim 1-22; A1, A2) Yun Dong method is in the track rotary course, described liner (16,22; A1 A2) has separately and remains on separately predetermined direction (16z, 22z substantially; 01,02) on.
24. a use has the first predetermined direction (16z; 01) first liner (16; A1) and have second a predetermined direction (22z; 02) second liner (22; A2) come the method for processing work, described liner (16,22; A1 is to drive by the motor shaft (11) that rotation centerline (12) are arranged A2), it is characterized in that: described first liner (16; A1) around first center line (12; R1) the orbiting motion and second liner (22; A2) around second center line (12; R2) orbiting motion is a different phase, vibrate thus to be compensated, and described first center line (12) and described second center line (12) can overlap.
25. method according to claim 24 is characterized in that: described liner (16,22; A1, A2) their predetermined direction (16z, 22z of maintenance in orbital motion; 01,02).
26., it is characterized in that according to claim 24 or 25 described methods:
A) use annular first liner (16) and circular second liner (22), described second liner (22) is arranged in the inner chamber of described first liner (16),
B) center line (21) of described second liner (22) rotates around described rotation centerline (12), and
C) center line (15) of described first liner (16) rotates on identical direction around described rotation centerline (12) equally, but the angle offset at 180 ° of angles is roughly arranged with respect to the center line (21) of described second liner (22).
27. an eccentric rotary oscillation class instrument (1) comprising:
A) have the casing (2) that the handle (3) that this operator uses is provided,
B) inner chamber (4) of casing (2),
C) be installed in the motor (5) of described inner chamber (4) and the motor shaft (11) of vertical rotation centerline (12) is arranged.
D) at least one connects first liner (16 of first abrasive body (8); A1) be connected second liner (22 of second abrasive body (9) with one; A2)
E) be used for transmitting energy to described liner (16,22 from described motor shaft (11); A1, transmission device A2) and vibration absorber (10), described vibration absorber (10) is according to any designs among the claim 1-23.
28. eccentric rotary oscillation class instrument according to claim 27 (1) is characterized in that: balance weight (28) is connected on the described motor shaft (11), and the barycenter (29) of balance weight (28) is not on rotation centerline (12).
29. electric tool according to claim 27 (1), it is characterized in that cooling fan (43) is connected on the described motor shaft (11), balance weight (28) is positioned on the described cooling fan (43), and the barycenter of described balance weight (28) and described cooling fan (43) is not on described rotation centerline (12).
30., it is characterized in that air and dust discharge pipe are connected to described casing (2) thereby go up being connected fan according to any eccentric rotary oscillation class instrument (1) of claim 27,28 or 29.
31. according to any eccentric rotary oscillation class instrument (1) of claim 27-30, it is characterized in that the first elasticity contiguous block (46), preferably make by rubber, be installed between described first liner (16) and the described casing (2), and the second elasticity contiguous block (47), preferably make, be installed between described second liner (22) and the described casing (2) by rubber.
32., it is characterized in that supporter (17,23) is installed between at least one described liner (16,22) and described contiguous block (46,47) and the described casing (2) according to the eccentric rotary oscillation class instrument (1) of claim 31.
33. according to any eccentric rotary oscillation class instrument (1) of claim 27-32, it is characterized in that having at least a brake apparatus (50,51) be used for reducing at least one described liner (16,22) rotating speed, at least when not having load to impose at least one described liner (16,22).
34. belt sand paper (8) and circular sand paper (9) are connected to according on claim 9-20 or any described liner (16,22) of claim 23.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ITVI20040090 ITVI20040090A1 (en) | 2004-04-16 | 2004-04-16 | ANTI-VIBRATION DEVICE FOR MOTORIZED SANDING MACHINE, AND INCORPORATING SANDING MACHINE SUCH AS DEVICE |
| ITVI2004A000090 | 2004-04-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1748939A true CN1748939A (en) | 2006-03-22 |
| CN100503164C CN100503164C (en) | 2009-06-24 |
Family
ID=34940895
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200510067539XA Expired - Fee Related CN100503164C (en) | 2004-04-16 | 2005-04-15 | Anti-vibration arrangement, tool using said anti-vibration arrangement and its method for cleaning working surface |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP1586416B1 (en) |
| CN (1) | CN100503164C (en) |
| IT (1) | ITVI20040090A1 (en) |
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2004
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Also Published As
| Publication number | Publication date |
|---|---|
| EP1586416A3 (en) | 2006-04-12 |
| EP1586416A2 (en) | 2005-10-19 |
| ITVI20040090A1 (en) | 2004-07-16 |
| CN100503164C (en) | 2009-06-24 |
| EP1586416B1 (en) | 2014-06-11 |
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Denomination of invention: Self-stress damping device Effective date of registration: 20140515 Granted publication date: 20090624 Pledgee: Bank of Communications Ltd Suzhou branch Pledgor: Baoshide Electric Tools Co., Ltd., Suzhou Registration number: 2014990000362 |
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