CN103625995B - Can the identical tension formula cable drum device of flexible take-up - Google Patents
Can the identical tension formula cable drum device of flexible take-up Download PDFInfo
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- CN103625995B CN103625995B CN201310683805.6A CN201310683805A CN103625995B CN 103625995 B CN103625995 B CN 103625995B CN 201310683805 A CN201310683805 A CN 201310683805A CN 103625995 B CN103625995 B CN 103625995B
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Abstract
The present invention relates to cable and draw over to one's side equipment, particularly relate to a kind of can the identical tension formula cable drum device of flexible take-up, this device comprises reel, reel is connected with speed regulation device by its drum shaft, speed regulation device comprises casing and is located at the planetary differential transmission device in casing, described planetary differential transmission device comprises the input shaft rotating and be assemblied on casing, speed governing axle and pinion carrier, stop mechanism is provided with between speed governing axle and casing, stop mechanism comprises pivoting friction dish and mobile friction disc, the side of mobile friction disc is top-loaded with Compress Spring, in addition, mobile frictional disc drive is connected with regulating mechanism, regulating mechanism comprises adjustment seat and platen, spin-endedly in drum shaft be equipped with free gear, free gear is also connected with driving lever, planetary differential transmission device is in transmission connection by its pinion carrier and drum shaft.This identical tension formula cable drum device of flexible take-up can solve the problem of existing cable drum device damage cable.
Description
Technical field
The present invention relates to cable and draw over to one's side equipment, particularly relate to a kind of can the identical tension formula cable drum device of flexible take-up.
Background technology
Cable drum device, as the term suggests, be mainly used for the folding and unfolding to cable.It is widely used in as mobile device provides electrical source of power, controls power supply or control signal.
Current cable drum device mainly comprises reel and sliding mechanism, wherein sliding mechanism many employings friction clutch, fluid coupling, magnetic coupling, stalling torque motor etc., and it is located in reel.
When using, reel is mounted on the mobile apparatus and walks about with mobile device.When take-up, all make the cable rolling linear velocity of reel be greater than the speed of travel of mobile device, rely on sliding mechanism to keep reel cable rolling linear velocity consistent with the walking line speed of mobile device, thus one side tensioning cable, prevent cable to be pulled off on the other hand, make the reliable take-up of reel.
By describing the cable drum device of known, current employing said structure above in the course of the work, in order to keep cable to be reliably wound on reel, cable all maintains larger tension force all the time, and this just exacerbates the wearing and tearing of cable, shortens service life.Therefore, the problem that current cable drum device also exists damage cable, shortens cable service life.
Summary of the invention
The object of the present invention is to provide a kind of can the identical tension formula cable drum device of flexible take-up, to solve the problem of existing cable drum device damage cable.
In order to solve the problem, of the present invention can flexible take-up identical tension formula cable drum device by the following technical solutions: can the identical tension formula cable drum device of flexible take-up, comprise reel, described reel is connected with speed regulation device by its drum shaft, described speed regulation device comprises casing and is located at the planetary differential transmission device in casing, described planetary differential transmission device comprises the input shaft rotating and be assemblied on casing, speed governing axle and pinion carrier, input shaft, the pivot center conllinear of speed governing axle and pinion carrier and parallel with drum shaft, stop mechanism is provided with between speed governing axle and casing, stop mechanism comprises the pivoting friction dish that is fixedly assemblied on speed governing axle and movably rotates the mobile friction disc be assemblied on speed governing axle vertically, the side of mobile friction disc pivoting friction dish is dorsad top-loaded with Compress Spring, in addition, mobile frictional disc drive is connected with for ordering about its regulating mechanism moved axially along speed governing axle, regulating mechanism comprises and is fixed on adjustment seat on casing and is enclosed within adjustment seat and forms the platen of screw-nut body with adjustment seat, in the drum shaft of reel, spin-ended being equipped with can along its axially movable free gear, it is movable to make the driving lever of its tooth mesh set when reel works and on platen in drum shaft that free gear is also connected with for ordering about it, planetary differential transmission device is in transmission connection by its pinion carrier and drum shaft.
Described pinion carrier and reel synchrodrive link together.
Described pinion carrier and reel co-rotating transmission link together.
The spool of reel and pinion carrier are respectively provided with gear, and pinion carrier and reel are by together with being in transmission connection in the same way synchronous with the transition gear that described gear engages simultaneously.
Casing is also equipped with the driving handle rotated for ordering about platen, Compress Spring top is contained between platen and mobile friction disc.
Described driving handle is in transmission connection by gear and platen.
Described driving lever to be assemblied on casing by a rotating shaft and to form seesaw structure.
The inner of driving lever is connected with driver plate by connecting rod, and driving lever orders about free gear along drum shaft activity by driver plate.
Described planetary differential transmission device also comprises and rotates the tween drive shaft that is assemblied in pinion carrier, and tween drive shaft is parallel to each other with input shaft and be connected by gear transmission, and adjusting shaft is also in transmission connection by gear and tween drive shaft.
Because this reel of identical tension formula cable drum device of flexible take-up can be connected with speed regulation device, planetary differential transmission device is provided with in the casing of described speed regulation device, and input shaft, the pivot center conllinear of speed governing axle and pinion carrier, stop mechanism is provided with between speed governing axle and casing, planetary differential transmission device is in transmission connection by its pinion carrier and reel, therefore, when in use, propulsive effort suffered by reel can be distributed by planetary differential transmission device, thus make reel only provide required less pulling force to cable, the automatic speed changing of transmission device is relied on to complete automatic adjustment to power needed for take-up, realize flexible take-up, in addition, free gear in drum shaft coordinates with Compress Spring and platen and in reel take-up process, can also automatically regulate its tension force along with the change of outside barrel diameter, as can be seen here, this identical tension formula cable drum device of flexible take-up can solve the problem of existing cable drum device damage cable.
Accompanying drawing explanation
Fig. 1 is can the schematic diagram of embodiment of identical tension formula cable drum device of flexible take-up;
Fig. 2 is can the constitution diagram of embodiment when cable is vertical of identical tension formula cable drum device of flexible take-up;
Fig. 3 the embodiment of identical tension formula cable drum device of flexible take-up can tighten up the reeling condition figure of rear cable;
Fig. 4 is can the embodiment schematic diagram after a period of time of identical tension formula cable drum device of flexible take-up;
Fig. 5 is can the free gear of embodiment of identical tension formula cable drum device of flexible take-up constitution diagram when being separated with platen;
Fig. 6 is the schematic diagram that the access point of power supply cable is positioned at the initial point of cable drum device forced stroke;
Fig. 7 is the schematic diagram that the access point of power supply cable is positioned at the mid point of cable drum device forced stroke.
Detailed description of the invention
Can the embodiment of identical tension formula cable drum device of flexible take-up, Fig. 1 is the schematic diagram of cable drum of the present invention.It comprises casing 1,2K-H(WW) type positive sign planetary differential transmission device 2, planet carrier gear 3, electrical motor 4, worm-gear speed reducer 5, transition gear 6, drum shaft gear 7, current colector rotate slide plate 8, current colector fixes slide plate 9, the power lead 10 of mobile device self, free gear 11, driver plate 12, connecting rod 13, rotating shaft 14, driving lever 15, reel 16, power supply cable 17, mobile friction disc 18, Compress Spring 19, adjustment seat 20, platen 21, driving handle 22, bearing 23, handle gear 24, pivoting friction dish 25.Add in casing 1 and have lubricating oil, ensure that in casing 1, each rotatable parts are in all the time by lubricating status.
2K-H(WW) type positive sign planetary differential transmission device 2 is made up of input shaft I, sun wheel a and b, satellite gear d and g, pinion carrier H, output shaft II (adjusting shaft).The number of teeth of sun wheel a and b, satellite gear d and g is respectively Z
a, Z
b, Z
d, Z
g, the rotating speed that electrical motor 4 produces and moment are by being delivered to input shaft I after worm-gear speed reducer 5, and the rotating speed of input shaft I is n
irevolutions per second, moment is M
inewton millimetre.The rotating speed of input shaft I and moment are distributed to output shaft II and pinion carrier H by planetary differential transmission device 2.The rotating speed of output shaft II is n
iIrevolutions per second, moment is M
iInewton millimetre; The rotating speed of pinion carrier H is n
hrevolutions per second, moment is M
hnewton millimetre.The rotating speed of pinion carrier H and moment are by passing to output shaft III (drum shaft) after gear 3, transition gear 6, gear 7, and the rotating speed of output shaft III is n
iIIrevolutions per second, moment M
iIInewton millimetre.The right-hand member of output shaft III is installed with reel 16, left end is installed with current colector and rotates slide plate 8, and free gear 11 is arranged on the centre of output shaft III.Free gear 11 can rotate with output shaft III, also can horizontally slip on output shaft III.Reel 16 is winding and the storage device of power supply cable 17, and power supply cable 17 adopts single Multi-layer Store mode.When output shaft III rotates, just band movable reel 16 and current colector rotate together with slide plate 8 and rotate, power supply cable 17 is by after reel 16, through hole through axle III central authorities rotates slide plate 8 with current colector and is connected, power lead 10 and the current colector of mobile device self are fixed slide plate 9 and are connected, and achieve the power supply of fixing power supply to mobile device.Pivoting friction dish 25 rotates with output shaft II, and the end face pin of mobile friction disc 18 inserts in the end-face hole of adjustment seat 20, can not rotate.The periphery of adjustment seat 20 has screw thread, and the endoporus of platen 21 has screw thread, is connected with adjustment seat 20 by screw thread.Between mobile friction disc 18 and platen 21, Compress Spring 19 is installed.When output shaft III rotates, also drive free gear 11 to rotate together, thus drive platen 21 to rotate.When platen 21 rotates, meeting is transverse shifting simultaneously, loosens or compresses Compress Spring 19, can change the friction force between mobile friction disc 18 and pivoting friction dish 25 friction disc pair, thus the resisting moment that change output shaft II is subject to.When platen 21 rotates, fixed handle gear 24 and driving handle 22 can be with to dally.
Its principle of work is such:
Select the number of teeth of planet carrier gear 3, drum shaft gear 7, and make its number of teeth equal, then the rotating speed of pinion carrier H equals the rotating speed n of output shaft III
iII, namely
N
h=n
iIIformula (A)
Select 2K-H(WW) Z in type positive sign planetary differential transmission device 2
a, Z
b, Z
d, Z
gthe number of teeth, make the PARAMETER ALPHA=Z of this planetary differential transmission device
dz
b/ Z
az
g=0.5.Then the rotating speed of input shaft I, output shaft II and pinion carrier H, moment meet following relational expression:
N
i-0.5n
iI-0.5n
h=0 formula (B)
M
i=-2M
iI=-2M
hformula (C)
Formula (A) is substituted into formula (B), obtains:
N
i-0.5n
iI-0.5n
iII=0 formula (D)
From formula (B), when input shaft I can not transmission time, the rotating speed of pinion carrier H and output shaft II is equal, turn to contrary, and therefore pinion carrier H is to the transmitting ratio n of output shaft II
h-II=1.From formula (C), when electrical motor 4 rotates, its output torque is when worm-gear speed reducer 5 amplifies backward input shaft I input torque, and moment is averagely allocated to output shaft II and pinion carrier H by input shaft I, therefore the active moment that is subject to of output shaft II and pinion carrier H is equal all the time, i.e. M
iI=M
h.
If the inside and outside radius of mobile friction disc 18, pivoting friction dish 25 is respectively R
1, R
2millimeter, friction coefficient is μ
1, friction face number is Z, and the elasticity modulus of Compress Spring 19 is κ
1newton/millimeter, amount of compression are L millimeter, then rotation, mobile friction disc are to the resisting moment M of output shaft II
iI' available following formula expression:
M
iI'=μ
1z κ
1lR
vnewton millimetre formula (E)
Wherein R
vfor equivalent friction radius of facing, unit: millimeter, its value is:
R
v=2(R
2 3-R
1 3)/[3(R
2 2-R
1 2)] formula (F)
If the nominal diameter of screw thread is d1 millimeter on adjustment seat 20 periphery, moment coefficient is κ
2, then the moment T that rotating platen 21 needs can express with following formula:
T=κ
2κ
1ld
1newton millimetre formula (G)
So resisting moment M of being subject to of output shaft II
iI' with the ratio m rotating the moment T that platen 21 needs be:
M=M
iI'/T=μ
1zR
v/ κ
2d
1formula (H)
The material of friction disc adopts hardened steel, μ
1value be between 0.05 ~ 0.1, adjustment seat 20 is the precision machined surface having lubrication with the screw thread pair of platen 21, κ
2value desirable 0.1, select quantity and the parameter R of friction face number Z
1, R
2, d
1size, and above each parameter is substituted into formula (H), can M be made
iI' be the multiple of T.Through checking computations, m value is more reasonable between being in 20 ~ 40.
Minimum tension during reel take-up suffered by power supply cable 17 is the gravity of the free overhang length part of cable, as shown in Figure 2, consider that cable must be wound around closely on reel, need to be added to cable initial tension, so the minimum tension suffered by cable is above two power sums, represent with N, unit: newton.Namely, during real work, the pendulous tank after cable tightens up is greater than its free overhang length, tightens up the reeling condition of rear cable as shown in Figure 3.
When the equipment that is movably walking is in the reference position of action stroke, cable drum is also in incipient state as shown in Figure 6, now adjusts cable pendulous tank, makes tension force suffered by cable be N newton.Use R
cylinderthe outer radius of a circle that contacts with cable of millimeter expression reel, uses d
2millimeter represents the diameter of power supply cable 17, then the resisting moment M that is subject to of reel
at the beginning of cylinder' be:
M
at the beginning of cylinder'=NR
just=N(R
cylinder+ d
2/ 2) Newton millimetre formula (I)
In reference position as shown in Figure 6, if the amount of compression of spring 19 is L
justmillimeter, according to formula (G), the moment T that rotating platen 21 needs is just: T
just=κ
2κ
1l
justd
1newton millimetre.If the number of teeth of free gear 11 and platen 21 is respectively Z
11, Z
21, and Z
21=Z
11, then free gear 11 is to the transmitting ratio n of platen 21
11-21for: n
11-21=Z
21/ Z
11=1, the resisting moment that therefore free gear 11 is subject to is:
M
at the beginning of 11'=T
just/ n
11-21=κ
2κ
1l
justd
1newton millimetre formula (K)
Ignore various loss due to friction, then output shaft III is subject to resisting moment and is:
M
at the beginning of III'=M
at the beginning of cylinder'+M
at the beginning of 11'=N(R
cylinder+ d
2/ 2)+κ
2κ
1l
justd
1formula (L)
M
at the beginning of III' unit be Newton millimetre.
Because the number of teeth of planet carrier gear 3, drum shaft gear 7 is equal, ignore loss due to friction, then the resisting moment that output shaft III is subject to will pass to pinion carrier H by equivalence.Therefore the resisting moment M that is subject to of pinion carrier H
at the beginning of H' be:
M
at the beginning of H'=M
at the beginning of III'=N(R
cylinder+ d
2/ 2)+κ
2κ
1l is d just
1formula (M)
M
at the beginning of H' unit be Newton millimetre
According to formula (H), the resisting moment that now output shaft II is subject to is:
M
at the beginning of II'=mT
just=m κ
2κ
1l
justd
1newton millimetre formula (N)
Make formula (M) equal with formula (N), then:
L
just=N(R
cylinder+ d
2/ 2)/[(m-1) κ
2κ
1d
1] formula (O)
In formula (O), because m value is between 20 ~ 40, therefore when replacing (m-1) with m, when namely ignoring the resisting moment of platen 21 pairs of output shafts III, the error of L value just, between 2.5% ~ 5%, affect very little, therefore formula (O) can be reduced to:
L
just=N(R
cylinder+ d
2/ 2)/(m κ
2κ
1d
1) formula (P)
In sum, when cable stretch be N newton, the initial compression amount of Compress Spring 19 is L
just=N(R
cylinder+ d
2/ 2)/(m κ
2κ
1d
1) millimeter time, the resisting moment that output shaft II and pinion carrier H are subject to is equal, if now electrical power, then the active moment that is subject to of the output shaft II of cable drum and pinion carrier H is also equal.
Equipment of supposing to be movably walking walked forward t second from reference position, and reel 16 is t second with rotating speed n revolutions per second of continuous take-up work, as shown in Figure 4.Because the power supply cable 17 on cable drum of the present invention adopts single Multi-layer Store mode on reel 16, so when reel 16 take-up, the increase speed of cable winding radius is d
2millimeter/turn.Then after t second, cable winding radius increases to:
R
t=R
cylinder+ d
2/ 2+ntd
2formula (Q)
R
tunit be millimeter.
If tension force when now power supply cable 17 rolls tightly is still N, then the resisting moment that reel is subject to is:
M
cylinder t'=NR
t=N(R
cylinder+ d
2/ 2+ntd
2) Newton millimetre formula (R)
Similarly, ignore platen 21 to the loss due to friction in the resisting moment impact of output shaft III and messenger chain, then the resisting moment that pinion carrier H is subject to is:
M
ht'=M
cylinder t'=NR
t=N(R
cylinder+ d
2/ 2+ntd
2) Newton millimetre formula (S)
If between adjustment seat 20 and platen 21, the pitch of screw thread pair is p millimeter, and makes:
P=Nd
2/ (m κ
2κ
1d
1) formula (T)
Because the transmitting ratio n of free gear 11 to platen 21
11-21=Z
21/ Z
11=1, therefore after t second, the distance that platen 21 is moved to the left is ntp millimeter, the total compression amount L of Compress Spring 19
tfor: L
t=L
just+ ntp, L
tunit be millimeter.According to formula (G), the moment that rotating platen 21 needs is T
t=κ
2κ
1l
td
1newton millimetre, according to formula (H), the friction moment of friction disc pair, namely friction disc pair to the resisting moment of output shaft II is:
M
iI t'=mT
t=m κ
2κ
1l
td
1=m κ
2κ
1d
1(L
just+ ntp) Newton millimetre formula (U)
Formula (P) and formula (T) are substituted into formula (U), obtain:
M
iI t'=N (R
cylinder+ d
2/ 2+ntd
2) Newton millimetre formula (V)
Comparison expression (S) and formula (V) find, M
ht'=M
iI t'.Namely, after determining the pitch p of screw thread pair by formula (T), after reel 16 is with speed n revolutions per second of continuous rotation t second, when the tension force when power supply cable 17 rolls tightly is still for N, the resisting moment of pinion carrier H and output shaft II is still equal.Conversely, after determining the pitch p of screw thread pair by formula (T), after reel 16 is with speed n revolutions per second of continuous rotation t second, when the resisting moment that pinion carrier H and output shaft II are subject to is equal, the pulling force that power supply cable 17 is subject to is still N newton.
The principle of work of Here it is constant-tension cable reel of the present invention.
As can be seen from formula (T), the tension force N newton that the pitch p of screw thread pair and cable need and cable size d
2millimeter is directly related, and that is, cable drum of the present invention is the special constant-tension cable reel of the power supply cable of a certain model specification.
Its working process collecting cable is such:
First the initial compression amount of holddown spring 19 is adjusted.When the reference position of equipment at shift motion, cable drum is also in incipient state.Reel 16 is pierced in one end of power supply cable 17, then couples together through rotating slide plate 8 with current colector after the through hole of output shaft III, then cable overhang will as shown in Figure 2.Now, as shown in Figure 5, the driving lever 15 of cable drum of the present invention is pushed the left side, driving lever 15 will rotate around axle 14, drivening rod 13, thus driver plate 12 is moved right, and driven gear 11 slides to the right, depart from engage with platen 21.Rotating drive handle 22, just band fixed handle gear 24 rotates together, thus drives platen 21 to rotate, holddown spring 19.Under the effect of holddown spring pressure, pivoting friction dish and mobile friction disc produce resisting moment by the rotation of output shaft II.For the power supply cable 17 of certain model specification specific, when cable stretch is N Newtonian time, the empty millimeter of due pendulous tank L can be calculated, as shown in Figure 6.First rotary actuation handle 22 loosens the pressure of Compress Spring 19 completely, and then opposite spin driving handle 22 compresses Compress Spring 19 a little, then uses hand rotating drum 16, makes its pendulous tank be greater than L
empty mm, then decontrol reel 16 again, reel 16 will rotate backward.If when reel 16 is slack, the pendulous tank of cable equals L
empty mmthen the initial compression amount of Compress Spring 19 has just been adjusted.The principle of such adjustment is as follows: when electrical motor 4 is not energized, input shaft I can not rotate under the self-locking action of worm-gear speed reducer 5, so when rotating drum 16, output shaft III will drive output shaft II to rotate by drum shaft gear 7, transition gear 6, planet carrier gear 3, pinion carrier H.Because from the transmitting ratio n of drum shaft gear 7 to output shaft II
7-II=1, so the moment that output shaft III is subject to equals the moment that output shaft II is subject to, i.e. M
iII=M
iI, meet the condition that formula (O) is set up.Therefore, if the amount of compression of Compress Spring 19 is greater than L
justmillimeter, then the resisting moment of output shaft II is greater than M
at the beginning of II', after so loosening reel 16, cable overhang length must be greater than L
emptymillimeter, cable stretch must be greater than N newton; Otherwise, if the amount of compression of Compress Spring 19 is less than L
justmillimeter, then the resisting moment of output shaft II is less than M
at the beginning of II', after so loosening reel 16, cable overhang length must be less than L
emptymillimeter, cable stretch must be less than N newton.In a word, repeatedly adjust several times by the above adjustment mode, cable stretch must be adjusted to and equal N newton, now the amount of compression of Compress Spring is just initial compression amount L
justmillimeter.
After the initial compression amount of Compress Spring 19 is adjusted, driving lever 15 is pushed the right, free gear 11 is engaged with platen 21, and cable drum just can have been started working.In order to make the reliable take-up of cable drum, should when the reference position shown in Fig. 6, the model specification of choose reasonable electrical motor 4, worm-gear speed reducer 5, when supposing that output shaft II does not rotate, the convoluting speed of reel 16 is allowed to be greater than slightly the moving velocity V of mobile device, like this, along with the increase of cable winding radius, the convoluting speed of reel 16 must increase gradually, ensure that cable drum all the time can reliably take-up.At n
iIwhen=0, the rotating speed of output shaft III is with n
iII is fixedrevolutions per second represent.
Reference position shown in Fig. 6, when mobile device walk forward with speed V, electrical motor 4 electric rotation time, the active moment that input shaft I distributes to output shaft II and pinion carrier H is equal, and the resisting moment that pinion carrier H and output shaft II are subject to is also equal, so output shaft II and pinion carrier H will rotate, according to formula (D), the rotating speed n of output shaft III
iIIn must be less than
iII is fixed, when the rotating speed of output shaft III drops to the rotating speed being less than and tightening up cable needs, the cable of tension will be relaxed, the resisting moment of cable to pinion carrier H diminishes, and gear 11 is when driving platen 21 rotate and be moved to the left, after any t second, friction disc secondary to the resisting moment of output shaft II be all constantly equal to roll tightly cable time the pinion carrier H resisting moment that is subject to, therefore, when the cable strained is relaxed, the resisting moment that pinion carrier H is subject to is less than the resisting moment that output shaft II is subject to, so, the output torque of motor also can reduce, pinion carrier H can only be driven to rotate, the rotating speed of pinion carrier H will be elevated to n
iIIfixed.In brief, after the cable of tension is relaxed, rotating speed under the lock torque effect of friction disc pair is reduced to zero by output shaft II, and the rotating speed of output shaft III will be elevated to n
iIIfixed, accelerate take-up.When after t second, cable is tightened up, and cable stretch reaches again N Newtonian time, the resisting moment that pinion carrier H is subject to equals again the resisting moment that friction disc is applied to output shaft II, the take-up speed of reel 16 can reduce again, repeats above-mentioned take-up process, the terminal until mobile device is walked.
The flexible take-up process of Here it is constant-tension cable reel of the present invention.
Cable drum of the present invention has two kinds of mode of operation.First kind of way is the end points of access point at mobile device shift motion of power supply cable 17.As shown in Figure 6.In this case, when mobile device moves from right to left, cable packed up by cable drum.After adjusting the initial compression amount of Compress Spring 19 as previously mentioned, cable drum is just along with the flexible take-up of mobile identical tension of equipment.When mobile device moves from left to right, reel 16 rotates backward under cable tension, and cable released by cable drum.Now, electrical motor 4 is without the need to power supply, and input shaft I can not rotate under the self-locking action of worm-gear speed reducer 5, n
i=0.Because the thrust that platen 21 loosens Compress Spring 19 is taken in rotating backward of reel 16 to, so the tension force suffered by cable is still definite value.Therefore output shaft III drives output shaft II rotation, the rotating speed of output shaft II equals the rotating speed of output shaft III, and cable drum can release cable.When mobile device stops midway, electrical motor 4 dead electricity, can not rotate under the self-locking action of input shaft I worm-gear speed reducer 5, the stopping of equipment also can not make cable pull reel 16 to rotate backward, output shaft II also can not rotate under the brake action of friction moment, therefore, reel 16 can not rotate, and the cable of winding can not be released automatically.Namely in this mode of operation, during take-up, flexible take-up; During cable laying, output shaft II rotating speed is equal with output shaft III rotating speed, and cable drum is with identical tension N newton cable laying; When equipment stops, under the brake action of friction disc, the cable of winding can not be released automatically.
The second way is the mid point of access point at equipment moving stroke of power supply cable 17, as shown in Figure 7.In this case, no matter equipment whichaway moves, and cable drum is always subject to allowing it rotate counterclockwise collects the active moment of cable, and only when equipment stops mobile, electrical motor 4 just understands dead electricity, and cable drum just can quit work.When equipment is in right endpoint as shown in Figure 7, after adjusting the initial compression amount of Compress Spring 19 as previously mentioned, cable drum just can be started working.During take-up, normal take-up as previously mentioned; During cable laying, cable tension makes reel 16 rotate backward, and the rotating speed of input shaft I and direction are all constant, therefore according to formula (D), output shaft II faster rotational speed, because cable tension is definite value always, when cable is applied to the moment direction of reel 16 and collects cable too, so the moment of input shaft I, output shaft II, output shaft III still meets formula (C).Namely in this mode of operation, during take-up, flexible take-up; During cable laying, output shaft II is accelerated to rotate, and cable drum is with identical tension N newton cable laying; When equipment stops, under the brake action of friction disc, the cable of winding can not be released automatically.
Claims (9)
1. can the identical tension formula cable drum device of flexible take-up, comprise reel, described reel is connected with speed regulation device by its drum shaft, it is characterized in that, described speed regulation device comprises casing and is located at the planetary differential transmission device in casing, described planetary differential transmission device comprises the input shaft rotating and be assemblied on casing, speed governing axle and pinion carrier, input shaft, the pivot center conllinear of speed governing axle and pinion carrier and parallel with drum shaft, stop mechanism is provided with between speed governing axle and casing, stop mechanism comprises the pivoting friction dish that is fixedly assemblied on speed governing axle and movably rotates the mobile friction disc be assemblied on speed governing axle vertically, the side of mobile friction disc pivoting friction dish is dorsad top-loaded with Compress Spring, in addition, mobile frictional disc drive is connected with for ordering about its regulating mechanism moved axially along speed governing axle, regulating mechanism comprises and is fixed on adjustment seat on casing and is enclosed within adjustment seat and forms the platen of screw-nut body with adjustment seat, in the drum shaft of reel, spin-ended being equipped with can along its axially movable free gear, it is movable to make the driving lever of its tooth mesh set when reel works and on platen in drum shaft that free gear is also connected with for ordering about it, planetary differential transmission device is in transmission connection by its pinion carrier and drum shaft.
2. according to claim 1 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, described pinion carrier and reel synchrodrive link together.
3. according to claim 2 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, described pinion carrier and reel co-rotating transmission link together.
4. according to claim 3 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, the spool of reel and pinion carrier are respectively provided with gear, and pinion carrier and reel are by together with being in transmission connection in the same way synchronous with the transition gear that described gear engages simultaneously.
5. according to claim 1 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, casing is also equipped with the driving handle rotated for ordering about platen, Compress Spring top is contained between platen and mobile friction disc.
6. according to claim 5 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, described driving handle is in transmission connection by gear and platen.
7. according to claim 1 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, described driving lever to be assemblied on casing by a rotating shaft and to form seesaw structure.
8. according to claim 7 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, the inner of driving lever is connected with driver plate by connecting rod, and driving lever orders about free gear along drum shaft activity by driver plate.
9. according to any one of claim 1-8 can the identical tension formula cable drum device of flexible take-up, it is characterized in that, described planetary differential transmission device also comprises the tween drive shaft rotating and be assemblied in pinion carrier, tween drive shaft is parallel to each other with input shaft and be connected by gear transmission, and adjusting shaft is also in transmission connection by gear and tween drive shaft.
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| CN201310683805.6A CN103625995B (en) | 2013-12-13 | 2013-12-13 | Can the identical tension formula cable drum device of flexible take-up |
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| CN201310683805.6A CN103625995B (en) | 2013-12-13 | 2013-12-13 | Can the identical tension formula cable drum device of flexible take-up |
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| CN104828729B (en) * | 2015-05-12 | 2017-08-29 | 中南大学 | Tension maintaining device |
| CN106516915A (en) * | 2015-09-13 | 2017-03-22 | 沧州华海风电设备科技技术开发有限公司 | Force adjusting and outputting machine |
| CN106966238B (en) * | 2017-04-04 | 2018-08-31 | 诸暨市鼎鼎商务服务有限公司 | A kind of bridge equipment |
| CN107128748B (en) * | 2017-04-04 | 2018-07-24 | 苏州交通工程集团有限公司 | A kind of bridge equipment |
| CN107043049B (en) * | 2017-06-14 | 2018-12-28 | 佛山佛塑科技集团股份有限公司 | The winding/unwinding device of tubing |
| CN110077918A (en) * | 2019-05-30 | 2019-08-02 | 晋中学院 | A kind of control system according to shuttle car speed closed loop folding and unfolding cable |
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| SU1650566A1 (en) * | 1987-11-24 | 1991-05-23 | Производственное объединение "Уралмаш" | Drawworks |
| JPH10167677A (en) * | 1996-12-06 | 1998-06-23 | Komatsu Ltd | Winch device |
| CN2331642Y (en) * | 1998-04-14 | 1999-08-04 | 莫魁 | Stepless speed regulating small-sized winch for mine |
| CN2565559Y (en) * | 2002-08-19 | 2003-08-13 | 自贡金锐硬质合金工模具有限公司 | Wire collecting machine having friction on-off speed regulating device |
| CN102241372A (en) * | 2010-05-13 | 2011-11-16 | 韩方云 | Transmission mechanism of electric hoist |
| CN202609846U (en) * | 2012-05-04 | 2012-12-19 | 宝鸡石油机械有限责任公司 | Integrated winch of reducer casing |
| CN203173725U (en) * | 2013-04-18 | 2013-09-04 | 洛阳涧光石化设备有限公司 | Planetary speed-changing drilling rig winch for hydraulic decoking device |
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