CN209307533U - A kind of carding machine transmission system and carding machine - Google Patents
A kind of carding machine transmission system and carding machine Download PDFInfo
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- CN209307533U CN209307533U CN201821942627.9U CN201821942627U CN209307533U CN 209307533 U CN209307533 U CN 209307533U CN 201821942627 U CN201821942627 U CN 201821942627U CN 209307533 U CN209307533 U CN 209307533U
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Abstract
The utility model discloses a kind of carding machine transmission system and carding machines, comprising: cylinder section transmission mechanism, deck portion transmission mechanism doffer's section transmission mechanism, cross apron web-collecting system transmission mechanism and pressure roller section transmission mechanism.It is driven between cover board and cylinder using retarder, guarantees to have ensured the synchronism between cover board and cylinder while rate request.Retarder can improve the operation strategies and economic value of machine, while using clutch, greatly improve the efficiency of removable cover cleaning according to the requirement shift speed change of different material.The body structure of retarder has the advantages that cotton not easy to pollute and convenient for lubrication.Doffer part uses double-sided synchronous belt, effectively simplifies transmission system, while ensuring the accuracy of transmission ratio, and cross apron web-collecting system enables the automatic shaping of machine, and the soft readjustment of pressure roller substantially increases shaping quality.
Description
Technical field
This disclosure relates to field of mechanical technique, more particularly to a kind of carding machine transmission system and carding machine.
Background technique
Transmission system connects each part of machine, conveys power to each part, is the core in carding machine design
Part.Carding process to it is each combing work package speed have higher requirements, its needle of the carding roller of auxiliary work to difference and
Difference between the two speed ratio can all have a huge impact carding effect, and since carding machine uses enclosed construction,
It must assure that synchronization with waste of raw materials phenomenon, its transmission system of each comb unit to prevent from blocking up greatly.Therefore, raw material
Characteristic proposes very high requirement to carding machine transmission system transmission ratio, also, each combing segment need to guarantee the connection of its transmission
Property, this just gives the design of combing machine for fur transmission system, and more stringent requirements are proposed.
It is continued to develop recently as electrical technology and new carding technology continuously emerges, the transmission system of carding machine occurs
Great variety.At this stage, Carding Machine Imported has mostly used multi-cell drive mode, i.e., each comb unit is equipped with individual motor
It drives；Simultaneously for the requirement of transmission system synchronism and cost the considerations of, domestic carding machine uses Belt Driven by Double Motor at this stage
Mode.Two kinds of transmission modes have the characteristics that respective, with the rapid development of textile industry, how to design and a kind of are both able to satisfy
Synchronism requirement, while also ensuring that the carding machine transmission system of cost advantage seems especially urgent, therefore to the biography of carding machine
It is a far-reaching project that dynamic system, which carries out improvement design research,.
Through retrieving, the carding machine transmission system existing to domestic and international market is commented as follows:
Domestic first generation high-production card A186 type is driven using single motor, electronic using a motor for being driven
Power is first reached cylinder by machine, then drives to other combing work packages by cylinder by machine driven system, passes through belt, chain
And gear ensures the correct speed ratio of each carding element suitable of full machine, when work, starts motor, and each carding element, which will synchronize, reaches requirement
Running speed.This kind of drive reduces the use of motor, and the low and programming Control workload of electrical equipment investment is small, to machine
The requirement of device part processing precision is low therefore at low cost, while ensure that the net synchronization capability of full machine, in the case where machine power-off,
Also the problem of can be avoided the asynchronous stopping because of cylinder inertia caused by different substantially reduces to have a power failure suddenly and causes machine
The probability that the problems such as blocking and waste of raw materials occurs.But the disadvantages of this solution is that transmission efficiency is low, Yi Fare.Single motor transmission
For mode since its transmission ratio is big, drive line is long, and required driving member is also more among it, this just considerably increases transmission system
Complexity, and one transmission link of every increase can all cause energy loss, so that entire drive line transmission efficiency
It substantially reduces, when system worked well can cause fever phenomenon, be easy to cause failure problems.
Domestic third generation high-production card such as FA201 type transmission system is mainly made of two main motors, a drive line
Road is to drive to cylinder, licker-in and cover board by constant speed motor (on third generation high-production card, to change speed, lid for convenience
Plate transmission is driven using independent small size motor)；Another drive line be driven to by variable-speed motor doffer, pattern doffing roller and
Upper and lower roll.In addition safely cleaning roller need to be driven with a small size motor, which can also be used in transmission and copy grinding roller.It is this
Kind of drive synchronism is good, and transmission efficiency is higher, stable transmission.Under the premise of guaranteeing linkage, still there is above-mentioned single electricity
The good advantage of the synchronism of machine transmission, but be driven compared to single motor, actuated element is reduced, and plays the work of simplified transmission system
With raising machine drive efficiency and stability.Product cost increases, but greatly reduce production of machinery, installation, operation and
The workload of maintenance.
The DK3 type carding machine of one enterprise, Switzerland production uses three three-phase motors, and the special three-phase motor of First passes through skin
V belt translation cylinder licker-in and cover board, second is double-contact and swashs motor, and using chain drive feed roll motor, third platform is double touchings
Point shunt wound dynamo, transmission doffer, pattern doffing roller and circle component, second identical as third platform motor performance, is all continuously to become
The motor of speed, rear two motors are manipulated by an electronic controller, make to carry out simultaneously to cotton with shaping.When sliver exporting speed changes
The multiple of drawing-off remains constant, and the number for changing sliver does not need change gear, greatly reduces the workload of maintenance.Tin
The start and stop of woods are also synchronous with the movement of raw material, therefore there is no need to connect sliver head again when driving again.
By above-mentioned analysis as it can be seen that domestic third generation high-production card can satisfy synchronism requirement but substantially due to lid
Plate is driven using separate electrical motor, and synchronism can not ensure between cover board and cylinder, while domestic third generation high-production card is adopted
It is single area's cover board combing (there was only a cover board above cylinder) and transmission system described in the utility model is based on double
The Design of Transmission System of area's cover board combing；One enterprise, Switzerland production DK3 type carding machine due on each transmission parts using
Separate electrical motor transmission need to just be able to achieve synchronism requirement using automatically controlled, and higher cost is more demanding to control system, at present technology
It is grasped by a small amount of foreign corporation.Carding machine is not belonging to precision machinery simultaneously, and production precision is not very high, camera bed equally use control
System effect processed is bad.
Utility model content
In order to solve the deficiencies in the prior art, embodiment of the disclosure provides a kind of carding machine transmission system, can
The good transmission effect of synchronizing property of each unit to carding machine.
To achieve the goals above, the application uses following technical scheme:
A kind of carding machine transmission system, comprising: cylinder section transmission mechanism, deck portion transmission mechanism, doffer part pass
Motivation structure, cross apron web-collecting system transmission mechanism and pressure roller section transmission mechanism；
Cylinder section transmission mechanism, by power transmission to cylinder, is changed by duplex tensioning wheel and is driven by cylinder motor
Direction drives to licker-in；
In the deck portion transmission mechanism, cylinder drives to removable cover transmission shaft by belt；
Doffer's section transmission mechanism reaches pressure roller transmission shaft by synchronous pulley by doffer's motor；
In the pressure roller section transmission mechanism pressure roller transmission shaft by two-sided synchronous toothed belt drive to cross apron web-collecting system,
Pattern doffing roller, bottom roll, topping roll and doffer；
The cross apron web-collecting system transmission mechanism drives cross apron web-collecting system movement.
Further technical solution, cylinder section transmission mechanism are flat-belt drive mechanism, including cylinder main shaft, thorn
Roller main shaft and reducer input shaft, the component for needing to be driven have cylinder roller, cover board and licker-in.
Further technical solution, the cylinder motor are mounted on the mainframe of cylinder lower end, are passed through by electrical machine belt pulley
At cylinder flat-belt drive to the big belt wheel of cylinder belt wheel, during which by duplex tensioning pulley and tensioning pulley, tensioning pulley can
With up and down adjustment, duplex tensioning pulley can be biserial belt wheel with left and right adjusting, it has, and there are two effects, first is that as licker-in
The driving wheel of transmission transmits torque to licker-in belt wheel by licker-in flat belt, and two are responsible for adjusting tensioning, pass through two tensioning wheels
While act on, link between cylinder, licker-in and cylinder motor
Further technical solution, the cylinder belt wheel is biserial belt wheel, but pulley diameters are not identical, on cylinder belt wheel
Retarder belt wheel on small pulley and cover board retarder transmits power by cover board flat belt, and final torque passes through cover board retarder
Removable cover sprocket wheel is driven to, realizes the rotary motion of removable cover.
Further technical solution, the deck portion transmission mechanism include retarder, cover board transmission shaft and cover plate chain
Wheel, removable cover, which is bolted, to be fixed on chain, and cover board sprocket wheel is fixed on cover board transmission shaft, between cylinder and cover board
It is provided with retarder；
Cover board transmission shaft is axis III, and for the output shaft after speed change in deceleration, the component which needs to be driven is removable cover
Plate.
The retarder uses closed box structure, and four axis are shared in cabinet, and reducer input shaft is axis I, pacifies thereon
It equipped with sliding duplicate gear, can be engaged with the gear for being mounted on II both ends of axis, realize double speed shift, while II interlude of axis is processed
At worm screw, clutch helical gear engaged transmission on worm screw and axis III is preceding when clutch engagement of the clutch helical gear not with rear end
The power of end transmitting makes clutch helical gear dally on axis III, and manual operation lid can be realized by the handle of III other end of axis
Plate passes through axis III conversely, the powered belt moving axis III of front end transmitting rotates when the clutch engagement of clutch helical gear and rear end
On worm screw engaged with helical gear on cover board transmission shaft realize torque be transferred at removable cover sprocket wheel, finally realize removable cover
Rotary motion.
Further technical solution, the sliding duplicate gear and clutch move on axis to be realized by shift fork；
In retarder, axis I is equipped with retarder belt wheel, and the torque passed over from cylinder small pulley rotates axis I,
Sliding duplicate gear is also mounted on axis I, is moved axially on axis I by shift fork impetus, is rolled by the circular cone at axis both ends
Sub- bearing and the shaft shoulder realize positioning；One two gear engaged with sliding duplicate gear is installed respectively at the both ends of axis II, it
Connect with axis using flat key, the axis between two gears is processed to worm screw, to the conveying power of reducer shaft III, passes through the device
Retarder is set to realize folk art term throw-over.
Further technical solution, cover board are provided with manual operation device, and the deceleration is realized by mechanical clutch
The switching of device primary speed-down and double reduction makes clutch separation, using level-one gear on worm retarder that is, in manual operation
Transmission；Conversely, being driven in removable cover work using second-stage worm gear reduction unit；
The mechanical clutch is made of gear with clutch and clutch, by the tooth engagement in the two and disconnects control
System, through axle sleeve empty set on axis III, clutch is connect with axis III by flat key gear with clutch, and shift fork swings can be with
The engagement and disconnection between gear and clutch with clutch are controlled, when the two engagement, the receiving of axis III is transmitted by front end axis
Torque, retarder is double reduction at this time；Otherwise when the two disconnects, gear with clutch dallies on axis III, passes through at this time
Handle transmission, retarder are first stage decelerator, and clutch is limited by the spacing ball being fixed on axis, and spacing ball is existed by spring
The radial of axis moves back and forth, and the right end of axis III is worm screw, drives to removable cover transmission shaft.
Further technical solution, sliding duplicate gear realize by clutch shifter and move on axis that selector fork is pacified
It is that fulcrum realizes movement of the shifting slide gear on axis with axis III, retarder uses box sealing on axis III.
Further technical solution, doffer's running part refer to all parts by doffer's motor as power source,
Including cross apron web-collecting system, pressure roller part, three roller stripping parts and doffer part, which includes 4 routes, one
For the motor synchronous belt pulley transmission that is mounted on doffer's motor to the driven synchronous pulley of motor, motor can move left and right on the rack
It is dynamic, it is ensured that the tensioning of belt passes through apron drive coordination belt wheel transmission to cross apron web-collecting system synchronous pulley；The second is passing through pressure
During which lower compression roller synchronous pulley of the roller drive coordination belt wheel transmission into pressure roller component is tensioned by tensioning pulley and tensioning pulley
And commutation；Thirdly for by three roller drive coordination belt wheel transmissions to three roller stripping devices, using double-sided toothed belt, in change
During which the rotation direction of roll synchronous pulley is tensioned by tensioning wheel, can left and right adjusting on the rack, be finally by stripping
Roller synchronous belt pulley transmission is tensioned to doffer's synchronous pulley by tensioning wheel, it can up and down adjustment on the rack.
Further technical solution, the cross apron web-collecting system transmission mechanism include two pairs of revolution skins at a distance of set distance
Band, the two turn on the contrary, apron is mounted on apron belt wheel, and apron belt wheel is mounted on belt wheel transmission axis, on belt wheel transmission axis
Tapered roller bearing to be installed, is positioned by the shaft shoulder, tapered roller bearing is mounted on bearing block, and bearing block is fixed on the rack,
The lower end of belt wheel transmission axis is equipped with driven wheel of differential, and drive bevel gear and driven wheel of differential are meshed will be on apron transmission shaft
Torque is transferred on belt wheel transmission axis, and belt wheel transmission axis drives apron movement by apron belt wheel.
Further technical solution, pressure roller section transmission mechanism include upper pressure roller shaft and pushing roll shaft, the upper pressure
One end of roll shaft is mounted in oscillation bearing seat, and the other end of the upper pressure roller shaft installs pressure roller, the one of oscillation bearing seat
End installation mandrel, oscillation bearing seat is fixed on cabinet by mandrel, when oscillation bearing seat is around body pivot, upper pressure roller also with
It floats up and down with it；
The lower part for pushing roll shaft and being mounted on cabinet, lower compression roller are mounted on the one end for pushing roll shaft, push the another of roll shaft
Lower compression roller synchronous pulley is installed in one end, by synchronous belt pressure roller transmission shaft driven to lower compression roller, draws sliver to fortune at circle machine
It is dynamic.
Further technical solution is equipped with compressed spring in the upper end of oscillation bearing seat, given pressure is provided, in pressure
Clamp nut limit is installed on spring.
The disclosure also proposed a kind of carding machine, including above-mentioned carding machine transmission system, utilize above-mentioned carding machine power train
System realizes the transmission of power.
The disclosure also proposed a kind of drive method of carding machine transmission system, comprising:
Cylinder and licker-in link, and transmission is changed transmission direction by duplex tensioning wheel and passed by cylinder motor drive to cylinder
It moves to licker-in, removable cover transmission shaft is driven to by belt by cylinder, a retarder is installed between the two；
Pressure roller part, bottom roll, topping roll, pattern doffing roller and doffer use doffer's motor drive, are driven by doffer's motor
Pressure roller transmission shaft is reached by synchronous pulley, pressure roller transmission shaft drives to cross apron web-collecting system, stripping by two-sided synchronous toothed belt
Cotton roller, bottom roll, topping roll and doffer.
Compared with prior art, the beneficial effect of the disclosure is:
Its transmission process synchronism of the transmission scheme of disclosed technique scheme offer is good.It is driving to accelerate and stop deceleration rank
Section, each comb unit can guarantee that fixed speed ratio remains unchanged, will not cause to draw to cotton fiber in the machine start and stop stage
Stretch or squeeze equivalent damage.It is driven between cover board and cylinder using retarder, guarantees to have ensured cover board and tin while rate request
Synchronism between woods.Retarder can improve the operation strategies and economy of machine according to the requirement shift speed change of different material
Value, while clutch is used, greatly improve the efficiency of removable cover cleaning.The body structure of retarder has not easy to pollute
Cotton and convenient for lubrication the advantages of.Doffer part uses double-sided synchronous belt, effectively simplifies transmission system, while ensuring biography
The accuracy of dynamic ratio, cross apron web-collecting system enable the automatic shaping of machine, and the soft readjustment of pressure roller substantially increases shaping matter
Amount.
The program greatly reduces relative to its transmission mechanism quantity of single motor transmission scheme.Each comb unit is individually equipped with electricity
Machine transmission enormously simplifies original transmission scheme, so that machine drive part greatly reduces, reduces the volume of complete machine, while
The energy loss of complete machine is greatly reduced, so that capacity usage ratio greatly improves, the fever slowed down during machine operation is existing
As improving complete machine service life.
Detailed description of the invention
The accompanying drawings constituting a part of this application is used to provide further understanding of the present application, and the application's shows
Meaning property embodiment and its explanation are not constituted an undue limitation on the present application for explaining the application.
Fig. 1 (a) is that the tractor parameter of some examples of implementation of the disclosure is driven schematic diagram；
Fig. 1 (b) is the transmission scheme schematic diagram of some examples of implementation of the disclosure；
Fig. 2 is the cylinder section transmission schematic diagram of some examples of implementation of the disclosure；
Fig. 3 is doffer's section transmission schematic diagram of some examples of implementation of the disclosure；
Fig. 4 is the cover board retarder gearshift structural schematic diagram of some examples of implementation of the disclosure；
Fig. 5 (a)-Fig. 5 (b) is the cover board retarder manual operation device structural schematic diagram of some examples of implementation of the disclosure；
Fig. 6 is the cross apron web-collecting system schematic diagram of some examples of implementation of the disclosure；
Fig. 7 is the roller structure schematic diagram of some examples of implementation of the disclosure；
Fig. 8 (a)-Fig. 8 (b) is the bell-mouth structure of air schematic diagram of some examples of implementation of the disclosure；
In figure, 1 pressure roller part, 2 bottom rolls, 3 topping rolls, 4 pattern doffing rollers, 5 doffers, 6 removable cover transmission shafts, 7 cylinders,
8 cover board retarders, 9 licker-ins, 10 feed roll motors；
I -1 mainframe, I -2 cylinder motor, I -3 electrical machine belt pulley, I -4 duplex tensioning pulley, I -5 cylinder flat belt, I -6 tin
Forest belt wheel, I -7 removable cover sprocket wheel, I -8 cover board flat belt, I -9 retarder belt wheel, I -10 licker-in flat belt, I -11 licker-in band
Wheel, I -12 tensioning pulley；
II -1 doffer's motor, II -2 motor synchronous pulley, II -3 pressure roller transmission shaft (are equipped with 4 synchronous pulleys, press on axis
The driven synchronous pulley of II -3a motor, II -3b apron drive coordination belt wheel, II -3c, three roller are followed successively by according to sequence from outside to inside
Drive coordination belt wheel, II -3d pressure roller drive coordination belt wheel), II -4 tensioning wheel, II -5 lower compression roller synchronous pulley, II -6 tensioning wheel,
II -7 cross apron web-collecting system synchronous pulley, II -8 topping roll synchronous pulley, II -9 bottom roll synchronous pulley, II -10 pattern doffing roller
Axis (is equipped with 2 synchronous pulleys, is followed successively by II -10a doffer's drive coordination belt wheel and II-according to sequence from outside to inside on axis
10b pattern doffing roller synchronous pulley), II -11 tensioning wheel, II -12 tensioning wheel, II -13 doffer's synchronous pulley；
III -1 axis I, III -2 sliding duplicate gear, III -3 cabinet, III -4 tapered roller bearing, III -5 gear (19T), III -6
Worm screw, III -7 gear (29T), III -8 axis II；
IV -1 cabinet, IV -2 axis III, IV -3 tapered roller bearing, IV -4 clutch helical gear, IV -5 clutch, IV -6 clutch
Device shift fork, IV -7 worm screw, IV -8 helical gear, IV -9 selector fork；IV -10 spacing ball, IV -11 spring；
V -1 apron transmission shaft, V -2 drive bevel gear, V -3 driven wheel of differential, V -4 belt wheel transmission axis, V -5 apron
Belt wheel, V -6 apron；
VI -1 synchronous belt, VI -2 pushing roll shaft, VI -3 oscillation bearing seat, VI -4 compressed spring, VI -5 clamp nut, VI -6
Upper pressure roller, pressure roller shaft on VI -7, VI -8 lower compression roller, VI -9 cabinet；
1-1 magnet, 1-2- supporting plate, VI -9- cabinet, the flat axis of 1-4-, 1-5- pedestal, 1-6- bolt, 1-7- holding screw, 1-
8- oscillation bearing seat, 1-9- adjusting sleeve, 1-10- fulcrum.
Specific embodiment
It is noted that following detailed description is all illustrative, it is intended to provide further instruction to the application.Unless another
It indicates, all technical and scientific terms used herein has usual with the application person of an ordinary skill in the technical field
The identical meanings of understanding.
It should be noted that term used herein above is merely to describe specific embodiment, and be not intended to restricted root
According to the illustrative embodiments of the application.As used herein, unless the context clearly indicates otherwise, otherwise singular
Also it is intended to include plural form, additionally, it should be understood that, when in the present specification using term "comprising" and/or " packet
Include " when, indicate existing characteristics, step, operation, device, component and/or their combination.
In a kind of typical embodiment of the application, a kind of Novel carding machine transmission mechanism, it includes: that cylinder part passes
Motivation structure, deck portion transmission mechanism, doffer's section transmission mechanism, cross apron web-collecting system transmission mechanism and pressure roller section transmission
Mechanism.
In the examples of implementation, complete machine is using Belt Driven by Double Motor (bi-motor refers to " cylinder motor and doffer's motor ") as schemed
Shown shown in 1 (b), cylinder 7 and licker-in 9 link, and transmission is changed first by cylinder motor drive to cylinder 7 by duplex tensioning wheel
Transmission direction drives to licker-in 7, and another route drives to removable cover transmission shaft 6 by belt by cylinder 7, pacify between the two
Fill a retarder.Pressure roller part 1, bottom roll 2, topping roll 3, pattern doffing roller 4 and doffer 5 are using a variable-frequency motor transmission
(being doffer's motor herein), transmission first reach pressure roller transmission shaft by synchronous pulley by motor, and pressure roller transmission shaft passes through two-sided same
Step toothed belt drives to cross apron web-collecting system, 4 pattern doffing rollers, bottom roll 2, topping roll 3 and doffer 5.
Cylinder section transmission mechanism is flat-belt drive mechanism, including cylinder main shaft, licker-in main shaft and retarder input
Axis, cylinder main shaft are integrated with cylinder, and cylinder main shaft is integrated with licker-in, and cylinder and licker-in are cylindrical body, and axis is in cylinder
On the center line of body, by being welded to connect reducer input shaft, which needs the component being driven to have cylinder roller, cover board and thorn
Roller.This drive path speed can achieve 1000r/mm, and center is away from larger.Chain conveyer run in high speed it is unstable,
Therefore should not be using it as driving member, while cylinder diameter is 1289mm, if driving member can mistake using gear as being driven
Greatly.Therefore, the part select belt transmission it is relatively reasonable, it is low with running noise, run smoothly, be suitable for big center away from biography
The advantages that dynamic.It is save the cost, while facilitating installation since the section transmission ratio can be non-constant, it is final to determine using strength
Nylon flat belt, referred to herein as the flat belt of cylinder section transmission, which not only has the advantages that belt is original, can also prevent
Electrostatic generates, and prevents Electrostatic Absorption cotton-wool.
In specific embodiment, licker-in, cylinder, doffer and stripping device (three roller stripping devices) are all cylindrical body,
All there is the axis welded with it in center line, driving member is mounted on an axle, and muti-piece cover board both ends are separately mounted to two symmetrically
On chain, chain is mounted on symmetrical sprocket wheel, and sprocket wheel is mounted on sprocket shaft.
In order to simplify the technique of belt wheel while guarantee not take off band, certain radian is designed in pulley face, when tensing, is put down
Belt can be closely fitted on pulley face.Referred to herein as whole belt wheels of cylinder section transmission.
In the examples of implementation, as shown in Fig. 2, cylinder motor I -2 is mounted on the mainframe I -1 of 7 lower end of cylinder, first
The big belt wheel for driving to cylinder belt wheel I -6 by cylinder flat belt I -5 by electrical machine belt pulley I -3, during which passes through duplex tension band
Wheel I -4 and tensioning pulley I -12, tensioning pulley I -12 can facilitate installation with up and down adjustment, advantage, can be by adjusting tensioning wheel
Position adjust belt it is elastic, duplex tensioning pulley I -4 can with left and right adjusting, be biserial belt wheel, it have there are two effect,
First is that the driving wheel as licker-in transmission, transmits torque to licker-in belt wheel I -11 by licker-in flat belt I -10, two are responsible for adjusting
Section tensioning, by being acted on while two tensioning wheels, cylinder 7, licker-in 9 (the two need and meanwhile move, keep certain speed ratio,
Belt wheel connection) and cylinder motor I -2 between link.Cylinder belt wheel I -6 is also biserial belt wheel, but pulley diameters are not identical, cylinder
The retarder belt wheel I -9 on small pulley and cover board retarder 8 on belt wheel I -6 transmits power by cover board flat belt I -8, finally
Torque drives to removable cover chain wheel I -7 by cover board retarder 8, realizes the rotary motion of removable cover.
Deck portion transmission mechanism includes that cover board retarder, cover board transmission shaft and cover board sprocket wheel, removable cover pass through spiral shell
Bolt is fastened on chain, and cover board sprocket wheel is fixed on cover board transmission shaft, and cover board transmission shaft is axis III IV -2, to become in deceleration
Output shaft after speed, the component which needs to be driven are removable cover.Cylinder speed is that (cylinder motor is variable by 397.5r/min
Frequency modulation speed), removable cover speed is 254.8mm/min or 109.5mm/min.Cylinder differs larger with the speed of cover board, direction
On the contrary, therefore needing to use a retarder in the driven Design, between cylinder and cover board.Retarder uses closed box knot
Structure shares four axis in cabinet, and reducer input shaft is axis I, is equipped with sliding duplicate gear thereon, can be mounted on II liang of axis
The gear at end engages, and realizes double speed shift, while II interlude of axis is processed into worm screw, worm screw nibbles with the clutch helical gear on axis III
Transmission is closed, when clutch engagement of the clutch helical gear not with rear end, the power of front end transmitting makes clutch helical gear in axis III
Upper idle running can be realized manual operation cover board by the handle of III other end of axis, substantially increase the efficiency of cleaning cover board.Instead
It, when the clutch engagement of clutch helical gear and rear end, the powered belt moving axis III of front end transmitting rotates, and passes through the snail on axis III
Bar is engaged with helical gear on cover board transmission shaft realizes that torque is transferred at removable cover sprocket wheel, final to realize removable cover revolution fortune
It is dynamic.Sliding duplicate gear and clutch move on axis to be realized by shift fork.
Sliding duplicate gear can be moved axially on axis I by shift fork impetus, pass through the bearing and axis at I both ends of axis
Shoulder realizes positioning, and shift fork uses axis III as fulcrum；One is installed respectively at the both ends of axis II to engage with sliding duplicate gear
Two gears (pinion gear and gear wheel) are connect with axis II using flat key, and pinion gear and gear wheel are processed into worm screw, which makes
Retarder realizes two grades of throw-overs.
As shown in figure 4, axis I III -1 is equipped with retarder belt wheel I -9 in retarder, transmitted from cylinder small pulley
The torque come rotates axis I III -1, and sliding duplicate gear III -2 is also mounted on axis I III -1, can be pushed and be made by shift fork
It is moved axially on axis I III -1, positioning is realized by the tapered roller bearing III -4 and the shaft shoulder at axis both ends；In axis II III -8
Both ends are installed by one two gears engaged with sliding duplicate gear III -2 (gear (19T) III -5 and gear (29T) III-respectively
7), they are connect with axis using flat key, and the axis between two gears is processed to worm screw III -6, convey power to reducer shaft III,
Retarder is set to realize folk art term throw-over by the device.
As shown in Fig. 5 (a)-Fig. 5 (b), deck portion cleans manually for convenience and maintenance, needs to design a behaviour manually
Make device, the switching of the retarder primary speed-down and double reduction is realized by mechanical clutch, i.e., in manual operation,
Make clutch separation, is driven using level-one gear on worm retarder；Conversely, in removable cover work, using second-stage worm tooth
Wheel decelerator transmission.
II interlude of axis is processed into worm screw, and IV -4 engaged transmission of clutch helical gear on worm screw and axis III IV -2 works as clutch
When helical gear IV -4 is not engaged with the clutch IV -5 of rear end, the power of front end transmitting makes clutch helical gear IV -4 in axis III
It dallies on IV -2, manual operation cover board can be realized by the handle of III other end of axis, substantially increases the efficiency of cleaning cover board.
Conversely, the powered belt moving axis III of front end transmitting rotates, by axis III when the clutch engagement of clutch helical gear and rear end
Worm screw IV -7 engages with helical gear IV -8 on cover board transmission shaft 6 realizes that torque is transferred at removable cover sprocket wheel, and final realize is lived
Dynamic cover board rotary motion.Sliding duplicate gear is moved on axis by the realization of clutch shifter IV -6, and selector fork IV -9 is installed
It is that fulcrum realizes movement of the shifting slide gear on axis with axis III, retarder is sealed using cabinet IV -1 on axis III.
The mechanical clutch is made of gear with clutch and clutch, by the tooth engagement in the two and disconnects control
System.Through axle sleeve empty set on axis III, clutch is connect with axis III by flat key gear with clutch, and shift fork swings can be with
The engagement and disconnection between gear and clutch with clutch are controlled, when the two engagement, the receiving of axis III is transmitted by front end axis
Torque, retarder is double reduction at this time；Otherwise when the two disconnects, gear with clutch dallies on axis III, passes through at this time
Handle transmission, retarder are first stage decelerator, and clutch is limited by the spacing ball IV -10 being fixed on axis, and spacing ball passes through
Spring IV -11 is moved back and forth in the radial direction of axis.The right end of axis III is worm screw, drives to removable cover transmission shaft.
Doffer's section transmission mechanism includes leather ring cotton guide running part, pressure roller running part, three roller stripping parts and road
Husband part, the part need the component that is driven be pressure roller transmission shaft, leather ring cotton guide transmission shaft, top and bottom rolls, pattern doffing roller and
Doffer's main shaft.It is designed referring to cylinder running part, still uses belt wheel transmission, but doffer speed is acted on by sensor, needed in real time
Speed regulation, it is more demanding to transmission ratio, therefore synchronous toothed V belt translation is used, it runs smoothly, without slipping phenomenon, low noise.The road
Line moving component is more, and machine run resistance is smaller, to simplify transmission system, using Double-side Synchronous tooth-like belt, shells in three rollers
At cotton, the commutation for pricking roller is realized by the effect of double-sided synchronous belt, reduces the use of tensioning.
As shown in figure 3, doffer's running part refers to all parts by doffer's motor as power source, including leather ring cotton guide
Device, pressure roller part, three roller stripping parts and doffer part, the section transmission include 4 routes (linkage, synchronous pulley and
Belt wheel), one is that the motor synchronous pulley II -2 being mounted on doffer's motor II -1 drives to the driven synchronous pulley of motor II -
3a, motor can move left and right on the rack, it is ensured that the tensioning of belt drives to skin by II -3b of apron drive coordination belt wheel
Circle leads cotton device synchronous pulley II -7；The second is driving to the pushing in pressure roller component by II -3d of pressure roller drive coordination belt wheel
During which roller synchronous pulley II -5 passes through tensioning pulley II -4 and the tensioning of tensioning pulley II -6 and commutation；Thirdly to pass through three rollers
II -3c of drive coordination belt wheel drive to three roller stripping devices (topping roll synchronous pulley II -8, bottom roll synchronous pulley II -9 and
II -10a of doffer's drive coordination belt wheel), using double-sided toothed belt, change the rotation direction of topping roll synchronous pulley II -8, during which
It is used as tensioning wheel by tensioning wheel II -11, it can left and right adjusting on the rack.It is finally by pattern doffing roller synchronous pulley II-
10b drives to doffer's synchronous pulley II -13, is tensioned by tensioning wheel II -12, it can up and down adjustment on the rack.
As shown in fig. 6, the component that cross apron web-collecting system transmission mechanism needs to be driven is apron.Cross apron web-collecting system is by three
The cotton net aggregation that roller stripping device peels, traction to press-roller device.Its structure is by two pairs at a distance of the revolution belt group for being 10mm
It is turned at, the two on the contrary, apron V-6 is mounted on apron belt wheel V-5, tapered roller bearing is installed on belt wheel transmission axis V-4, is led to
Shaft shoulder positioning is crossed, bearing block is fixed on the rack, and the lower end of belt wheel transmission axis V-4 is equipped with driven wheel of differential V-3, active conical tooth
Torque on apron transmission shaft V-1 is transferred on belt wheel transmission axis by wheel V-2 and driven wheel of differential V-3.
The transmission parts of pressure roller section transmission mechanism are upper lower compression roller.Pressure roller is located at the least significant end of machine, is for cotton
Shaping and traction, cotton item is pulled into can coiler by pressure roller, and pressure roller is important shaping component, pressure, shaping
Speed, tractive force etc. all directly determine the quality and machine operation efficiency of sliver.Pressure roller is realized using lever principle on pressure roller
Its small floating up and down in cabinet, lower compression roller are cooperated according to the technological requirements by synchronous belt pulley transmission, upper lower compression roller, and the two is total
Same-action completes task.
As shown in fig. 7, upper pressure roller part, when cotton thickness is excessive, cotton is weighed wounded in order to prevent, upper pressure roller VI -6 should can
To float up and down, therefore lever principle is utilized, design one is equivalent to the component of lever: oscillation bearing seat VI -3, wherein upper pressure
Roller VI -6 is mounted on one end of pressure roller shaft VI -7, and upper pressure roller shaft is mounted in oscillation bearing seat, oscillation bearing seat it is another
End installation mandrel, is fixed on cabinet VI -9, and when it can be around body pivot, upper pressure roller also follows it to float up and down,
There is compressed spring VI -4 in the upper end of oscillation bearing seat simultaneously, given pressure is provided, finally installs and compress on compression spring
Nut VI -5 limits, and hold-down bolt, the screw-internal thread fit of bolt and cabinet VI -9 are installed in the top of compression spring.
The lower section that roll shaft VI -2 is mounted on box house is pushed, lower compression roller VI -8 is mounted on the one end for pushing roll shaft, pushes
The other end of roll shaft installs lower compression roller synchronous pulley II -5, passes through VI -1 pressure roller transmission shaft driven of synchronous belt to lower compression roller, traction
Sliver to circle machine at move.
Upper pressure roller and lower compression roller have the little groove of same widths, have a high rank on the right of the little groove of upper pressure roller
There is a high ladder on the left side of ladder, the upper pressure roller little groove of lower compression roller, and the two acts on simultaneously, limit sliver in level side
To width；The two passes through biography once surface layer is blocked up equipped with a sensor in the gap for radially having 2mm, and at this simultaneously
Sensor adjusts out cotton speed, can be realized the limitation to the height of sliver.
Except above-mentioned pressure roller workpiece, pressure roller part further includes running part, horn section and box portion.
Running part is mainly made of lower compression roller synchronous pulley and tensioning wheel, and power passes through pressure roller transmission shaft driven to pushing
Roller synchronous pulley, two tensioning wheels are mounted on tension pulley support, can adjust on cabinet, the two collective effect, realize and open
Tightly and commutation function.
Horn section uses contoured design, and in horn-like, the upper end is cylindrical, passes through holding screw cooperation with support
Connection, lower end cylinder edge process two special-shaped grooves, it is ensured that it can cooperate with upper lower compression roller, and processing one is ellipse in its center
Circular through hole, bell-mouthed effect are to carry out first time setting treatment to sliver, are mounted on supporting plate.
As shown in Fig. 8 (a)-Fig. 8 (b), the upper end supporting plate 1-2 is adsorbed on cabinet by magnet 1-1, and lower end uses flat axis 1-
4 realize fixation with the flat shaft hole matching in pedestal 1-5, and pedestal is fastened on cabinet by bolt 1-6, among fulcrum 1-10
Axle sleeve is installed, makes oscillation bearing seat 1-8 empty set on axis, flat axis is processed into left end, and right end mounting and adjusting covers 1-9, by tight
Determine the fixation that screw 1-7 realizes it with cabinet.Cabinet design minimizes volume, and using totally-enclosed design, lower end passes through bolt
It is fixed on bottom plate.
In the examples of implementation, the relevant calculation of carding machine transmission system is disclosed:
One, carding machine important parameter
It is as shown in table 1 according to experiment and experience, some parameters of carding machine.
The parameter of 1 carding machine important component of table
Two, the selection of motor
Operating power needed for carding machine:
Pw=Pw1+Pw2+Pw3 (2)
P in formulaw1、Pw2、Pw3、PwRespectively operating power needed for cylinder, licker-in, cover board and three, kW；F1、F2、F3
The respectively working resistance of cylinder, licker-in and cover board；v1、v2、v3The respectively speed of cylinder, licker-in and cover board, according to formula
(1) and (2) can obtain Pw=1.58kW.
The transmission efficiency of each transmission is as shown in table 2 below known to tabling look-up.
2 primary drive auxiliary driving efficiency of table
It is η that formula (3), which is acquired by total transmission efficiency of cylinder motor to main motion parts,1=0.428.
η1=η1 8η2η3 4η4 2 (3)
Formula (2) and (3) calculated result are substituted into formula (3-4) and acquire Pd=3.69.
The motor of carding machine motor special FO2 series, Specifeca tion speeification such as table 3 are selected according to the effective power of output
It is shown:
3 FO2-72-4 type motor performance parameter of table
Three, transmission device resultant gear ratio is determining and distributes
(1) cylinder part: the speed of cylinder is 397r/min, and the speed of motor is 1460r/min.Therefore cylinder and motor it
Between transmission ratio be 3.67.
(2) licker-in part: the speed of licker-in is 985r/min and 1047r/min, motor speed 1460r/min, therefore is pierced
Transmission ratio between roller and motor is 1.48 and 1.39.It is due to licker-in and motor steering on the contrary, first according to chapter 2 motor
A tensioning wheel is driven to, licker-in is then driven to, therefore there is two transmission ratios, i between the two1=0.67；i21=2.22；
i21=2.09.
(3) removable cover part: cover plate speed 109.4mm/min；254.8mm/min, the speed of cylinder are 397r/
Min, the sprocket wheel on transmission shaft make removable cover shuttling movement, transmission ratio i3, according to cover board specification, we can determine chain
The parameter of wheel is Z=14；P=36.5.Therefore cylinder is to the resultant gear ratio i=796.6 or 1856.6 between cover board transmission shaft, therebetween
There are 2 transmission ratios, retarder i is respectively driven to by belt1, retarder exports to cover board transmission shaft i2, while retarder is two
Grade gear on worm shifting reducing, i2Including axis I to II i of axis21OrAxis II is to III i of axis22, axis III to cover board transmission shaft i23。
That is i2=i21i22i23.In order to facilitate manufacture, set identical for the transmission ratio of two-stage gear on worm.That is i2=i21i22 2, total to pass
Dynamic ratio is i=i1i21i22 2。
Since removable cover velocity variations are completed by the shifting slide gear of axis I and axis II, therefore:
i1i22 2=1216.6 (6)
The transmission ratio general range of known V belt translation is 2-4, enables i1=2, which substitute into formula (6), acquires i22=24.6.
Nominal transmission ratio known to tabling look-up is 25, but since error is larger, it is therefore desirable to correct the reality, it is specified that two stage reducer
Border transmission ratio and nominal transmission ratio relative deviation Δi≤ 4%, i is changed to by worm-gear drive ratio known to checking computations22=26, i1=
Error is smaller when 1.8.
Four, the parameter of primary drive axis
We distribute transmission ratio above, borrow transmission ratio can calculate primary drive axis speed,
Input, output power and torque, as shown in table 4
The kinematic parameter table of 4 primary drive axis of table
Five, belt transmission calculation
Cylinder, retarder input terminal and licker-in are realized by flat belt, by taking cylinder as an example, between motor and cylinder
Belt driven Design calculate it is as follows:
The transmission of motor and cylinder, it is known that cylinder output power of motor is P=3.8KW；Motor speed n1=1460r/
min；Cylinder revolving speed is 397.5r/min；Center is away from for a=813mm；Transmission ratio is 3.67.
The diameter d of small pulley is acquired according to formula (7)1=150mm；
3.67 < i of transmission ratiomax=10, which meets the requirements；The Elastic Sliding coefficient substitution of ε=0.02 formula (8) is taken to acquire
The diameter d of big belt wheel2=540mm；
d2=id1(1-ε) (8)
Belt speed v=11.46m/s < v is acquired according to formula (9)max=30m/s, therefore belt speed is met the requirements；
Strip length L=2756mm is acquired according to formula (10)；Thickness δ=1.2 × n=4.8 of band；
Small pulley cornerite known to solution formula (11)Cornerite is greater than 150 degree and meets design requirement；Deflect numberProperly；
Select KA=1.2, it is known that Pd=KA× P=4.56KW, takes K0=1, Kβ=1, P0Band is acquired in=2.6 substitutions formula (12)
Sectional area A=1.75；BandwidthTake normal tensile stress σ0=1.8N/mm2；
Formula (13) seeks effective circle force F=398N；
Formula (14) acquires the power F acted on axisr=6.3N；Finally choose belt wheel width B=450mm.
The V belt translation of design other parts can similarly be calculated.Known cylinder axis and tension wheel shaft output power are P=
3.58KW；Cylinder axis and tension wheel shaft revolving speed are respectively n1=397.5r/min, n1=2190r/min；Reducer shaft I and licker-in
Revolving speed is respectively 220.8r/min, 985 or 1047r/min；Center is away from respectively a=588mm, 510mm；Transmission ratio is respectively
1.8,2.22 or 2.09.Specific calculating parameter is shown in Table 5:
5 cylinder part V belt translation parameter of table
Six, second-stage worm design of gear speed reducer
(1) shift shifting slide gear design.There are two desin speed, above structure designs to determine using sliding for retarder tool
Gear shift throw-over calculates shifting slide gear design as follows.
Because gear needs slide on axis, for the engagement convenient for operation and gear, spur gear transmission is selected,
Pressure angle is 20 °；It tables look-up using 8 class precisions, the material and the number of teeth of driving gear and driven gear see the table below 6.
6 gear material of table and the number of teeth are selected
ZE=189.8Mpa1/2；T1=9.55 × 106P/n1=1.48 × 105Nmm,ZH=2.5；KHt=1.3,
Pass through formula (15)
Calculate to obtain αa1=31.77；
αa1=arccos [z1cosα/(z1+2ha *) (15)
αa2=28.47, it substitutes into formula (16) and obtains εα=1.596；
Contact fatigue strength Superposition degree modulus Z is calculated in formula (17)s=0.895；σHlim1=600Mpa, σHlim2=
550Mpa；
Calculating stress-number of cycles according to formula (18) and (19) is N2=4.17 × 108；
N1=60n1jLh (3-18)
Taking failure probability is 1.00%；S=1；Substitution formula (20) obtains [σH]1=540Mpa,
[σH]2=523Mpa；Because of [σH]1> [σH]2, therefore [σH]=[σH]2=523Mpa；
Finally coefficient above is substituted into formula (21), finding out driving wheel reference diameter is d1t=73.65.
Formula (22) seeks peripheral speed v=0.85m/s；
Formula (23) seeks facewidth b=73.65；
Table look-up to obtain KA=1；According to v=0.8m/s, 8 class precisions, K is takenv=1；The force of periphery of formula (24) calculating gear；
Ft1=4.019 × 103N (24)
Check in KHα=1.2；K is obtained using differential techniqueHβ=1.352, formula (25) obtains real load COEFFICIENT KH=1.62；
KH=KAKvKHαKHβ (25)
The counted reference diameter d of real load coefficient is pressed in formula (26) and (27)1=79.256mm and module m=
4.17mm。
Select KFt=1.3；Formula (28) calculates overlap coefficient Yε=0.720；
Know δFlim1=500MPa；δFlim2=380Mpa；KFN1=0.85, KFN2=0.88；S=1.4 is counted by formula (29)
Calculate [σF]1=303.57Mpa and [σF]2=238.86Mpa；YFa1=2.87；YFa2=2.5；YFSa1=1.54；YFSa2=1.62
It calculatesBoth compare, the larger value is taken, i.e.,Finally
Modulus m=2.372mm is calculated by formula (30).
Formula (22) seeks peripheral speed v=0.521m/s；Formula (23) seeks facewidth b=45.068mm；It is calculated by formula (31)
H=(2h*+c*)mt (31)
According to v=0.521m/s, 8 class precisions check in KV=1.08；KFα=1；K is acquired with interpolation methodHβ=1.355, in conjunction withCheck in KFβ=1.432, it substitutes into data to formula (32) and acquires KF=1.547 press formula (33) counted module.
KF=KAKVKFαKFβ (32)
Comparison between calculation results take and calculate m=2.58 by bending strength, and rounding is standard value m=3mm, by d1=
56.923mm, the number of teeth for calculating driving wheel is z1=18.97；Take z1=19, the then number of teeth z of driven wheel2=iz1=1.53 × 19
=29.07, take z2=29.
Calculate the geometric parameter of gear.(1) reference diameter d1=z1M=57mm；d2=87mm；(2) center away from(3) gear widthError is had when installation, takes b=65, makes the facewidth of gear wheel
Equal to the design facewidth.
Tooth face contact fatigue strength is checked.Each parameter is respectively K in formula (34)H=1.91；T1=4.5 × 105；d1
=57；U=29/19；ZH=2.36；ZE=189.8；Zs=0.91；Substitution formula, acquires σH=534 < [σH], intensity satisfaction is wanted
It asks.
Tooth root bending-fatigue strength is checked.Each parameter is respectively K in formula (35) and (36)F=1.85；T1=4.5 × 105；
YFa1=2.11； Ysa1=1.85；Ys=0.74；YFa2=2.05；Ysa2=1.93；Z1=19；M=3 is substituted them in
σ is obtained in formulaF1=150；σF2=162, intensity is met the requirements.
(2) cylindrical worm helical gear designs
Worm screw and Helical gear Transmission are non-common transmissions, and bibliography [18] matches method of gathering it is found that design method uses, in order to
Meet meshing condition, choose helical gear modulus, when processing helical gear using hobboing cutter, helical angle will be with the lead angle phase of worm screw
Together.When machining worm, its axial module should be made identical as helical gear modulus.Input power P=3.26KW known to table 3；Worm screw
Revolving speed is n1=144.7r/min；Transmission ratio i=26.By with gather helical gear and worm screw basic parameter it is as shown in table 7 below.
The basic parameter of table 7 helical gear and worm screw
The helical gear helixangleβ of meshing condition is identical as the lead angle γ of worm screw, thus by formula (37) know β=γ=
2.86°。
Formula (38) calculates helical gear reference diameter d=78mm
Formula (39) calculates reference diameter of worm d=60mm
Formula (40) calculates center away from a=69mm
A=0.5 (d1+d2) (40)
Calculate the geometric parameter of worm screw (being shown in Table 8) and helical gear (being shown in Table 9).
8 worm screw parameter of table
9 helical gear parameter of table
Worm screw tooth root bending-fatigue strength is checked.Y in formula (41)Fa2=2.38；Yβ=0.9192；σF=56Mpa≤[σF]；
Met according to calculation and check bending strength.
Beveled gear teeth face contact checking fatigue strength.Each parameter is respectively K in formula (42)H=2.23；T1=9 × 104；d1=78；U=26；ZH=2.45；ZE=189.8；Zs=0.64；ZβIn=0.99 substitution formula, σ is acquiredH=534 <
[σH], it is met the requirements by intensity known to calculation and check.
Helical gear tooth root bending-fatigue strength is checked.Each parameter is respectively K in formula (42) and (43)F=2.07；T1=9 ×
104；YFa1=2.50； Ysa1=1.65；Ys=0.68；YFa2=2.18；Ysa2=1.79；Z1=1；M=3, by their generations
Enter and obtains σ in formulaF1=150Mpa；σF2=162Mpa, intensity are met the requirements.
Using identical method, the worm- gear drive on axis III can be designed that, parameter and calculated above consistent.
Seven, the calculating of doffer's transmission parts
It is identical as design calculating above by structure design it is found that the part uses toothed belt transmission, motor is first selected, then
Belt wheel transmission design is synchronized to calculate.
(1) doffer's parameter of electric machine such as table 10.
10 Y100L-4 type motor performance parameter of table
(2) transmission ratio distributes
Doffer's motor and pressure roller transmission shaft i1=2.57；Pressure roller transmission shaft respectively with lower compression roller i2=0.824；Pressure roller transmission
Axis and pattern doffing roller i3=1.93；With upper bundle roller i3=1；With bottom roll i4=1.47；Pattern doffing roller and doffer i5=6.13.
(3) primary drive axis parameter, as shown in table 11.
The kinematic parameter table of 11 primary drive axis of table
(4) synchronous pulley design calculates:
By taking motor to pressure roller transmission shaft synchronous pulley design as an example.Known motor rated power P=2.2kW, rated speed
n1=1420r/min, transmission ratio i=7/18, double shift, work for 10 years, 200 days 1 year.
Check in KA=1.4, it substitutes into (37) and obtains design power Pd=3.08kW；
Pd=KAP (37)
According to Pd=4kW, n1=1420r/min is determined as H-type, pitch P by table 13b=12.7mm；
According to banding pattern H and small band wheel speed n1, z is taken by table 121=14, formula (38) d1=56.60mm is checked in outer by table 12
Diameter da1=55.23mm；
Formula (39) obtains z2=36；
Formula (40) obtains d2=145.60mm checks in d by table 12α2=144.16mm；
Formula (41) obtains belt speed v=4.2m/s；
First dead axle spacing, takes α0=300mm, formula (42) obtain L0It is synchronous to check in the H-type that belt length code name is 370 by=943.8mm
Band, pitch length LP=933.45mm, the number of teeth z=72 on nodel line；
Formula (43) obtains practical distance between axles α=310mm；
Formula (44) small pulley total number of teeth in engagement obtains zm=6；
Check in Ta=2100N, m=0.488kg/m substitutes into (45) and obtains P0=2.09kW；
Check in the b of H-type banda0=76.2mm, zm=8, Kat=1, it substitutes into (46) and obtains bα=24.8mm, checks in, and should select bandwidth
Code name is 125 H-type band, wherein bα=25.8mm.
The synchronous belt that transmission is selected is 370H125 belt wheel basic parameter such as the following table 12.
12 belt wheel parameter of table
Pnmary Synchronization belt wheel design parameter is shown in Table 13.
13 synchronous pulley parameter of table
In conclusion driving system includes cylinder running part and doffer's running part, calculate above each
Partial parameter, Fig. 1 (a) are that the drive mechanism of each transmission parts of complete machine and parameter are illustrated.
Eight, the calculating of spring
Pressure roller part is to prevent from weighing material wounded, and in the design of its structure, upper pressure roller is realized by installation compressed spring in upper end
Swing up and down.It calculates known conditions and is shown in Table 14, end is simultaneously tight, polishes, and branch holds round as 1 circle.
The design of 14 spring of table calculates known quantity
Formula (47) just calculates spring rate P '=40N/mm；
Formula (48) calculates working ultimate load Pj=668N, while according to DzIt tables look-up to obtain parameters in series in table 3-15；
Pj≥1.67Pm (48)
15 compressed spring computational chart of table
The calculating of remaining parameter of spring is shown in Table 16
Remaining the parameter computational chart of table 16
The checking computations of spring are shown in Table 17
The checking table of 17 spring of table
The foregoing is merely preferred embodiment of the present application, are not intended to limit this application, for the skill of this field
For art personnel, various changes and changes are possible in this application.Within the spirit and principles of this application, made any to repair
Change, equivalent replacement, improvement etc., should be included within the scope of protection of this application.
Claims (10)
1. a kind of carding machine transmission system, characterized in that include: cylinder section transmission mechanism, deck portion transmission mechanism, doffer
Section transmission mechanism, cross apron web-collecting system transmission mechanism and pressure roller section transmission mechanism；
Cylinder section transmission mechanism, by power transmission to cylinder, changes transmission direction by duplex tensioning wheel by cylinder motor
Drive to licker-in；
In the deck portion transmission mechanism, cylinder drives to removable cover transmission shaft by belt；
Doffer's section transmission mechanism reaches pressure roller transmission shaft by synchronous pulley by doffer's motor；
Pressure roller transmission shaft drives to cross apron web-collecting system, stripping by two-sided synchronous toothed belt in pressure roller section transmission mechanism
Roller, bottom roll, topping roll and doffer；
The cross apron web-collecting system transmission mechanism drives cross apron web-collecting system movement.
2. a kind of carding machine transmission system as described in claim 1, characterized in that cylinder section transmission mechanism is flat skin
Tape handler, including cylinder main shaft, licker-in main shaft and reducer input shaft, the component for needing to be driven have cylinder roller, cover board
And licker-in；
The cylinder motor is mounted on the mainframe of cylinder lower end, passes through cylinder flat-belt drive to cylinder band by electrical machine belt pulley
At the big belt wheel of wheel, during which by duplex tensioning pulley and tensioning pulley, tensioning pulley can be with up and down adjustment, duplex tensioning pulley
It can be biserial belt wheel with left and right adjusting；
The cylinder belt wheel is biserial belt wheel, but pulley diameters are not identical, on the small pulley on cylinder belt wheel and cover board retarder
Retarder belt wheel power is transmitted by cover board flat belt, final torque drives to removable cover sprocket wheel by cover board retarder,
Realize the rotary motion of removable cover.
3. a kind of carding machine transmission system as described in claim 1, characterized in that the deck portion transmission mechanism includes subtracting
Fast device, cover board transmission shaft and cover board sprocket wheel, removable cover, which is bolted, to be fixed on chain, and cover board sprocket wheel is fixed on lid
On plate transmission shaft, retarder is provided between cylinder and cover board；
Cover board transmission shaft is axis III, and for the output shaft after speed change in deceleration, the component which needs to be driven is removable cover.
4. a kind of carding machine transmission system as claimed in claim 3, characterized in that the retarder uses closed box knot
Structure, reducer input shaft are axis I, are equipped with sliding duplicate gear thereon, can engage with the gear for being mounted on II both ends of axis, are realized
Double speed shift, while II interlude of axis is processed into worm screw, the clutch helical gear engaged transmission on worm screw and axis III, when clutch helical teeth
When taking turns the clutch engagement not with rear end, the power of front end transmitting makes clutch helical gear dally on axis III, can pass through axis
The handle of III other end realizes manual operation cover board, conversely, when the clutch engagement of clutch helical gear and rear end, front end transmitting
Powered belt moving axis III rotate, realization torque is engaged with helical gear on cover board transmission shaft by the worm screw on axis III and is transferred to activity
It is final to realize removable cover rotary motion at cover board sprocket wheel.
5. a kind of carding machine transmission system as claimed in claim 4, characterized in that the sliding duplicate gear and clutch exist
It moves on axis and is realized by shift fork；
In retarder, axis I is equipped with retarder belt wheel, and the torque passed over from cylinder small pulley rotates axis I, sliding
Duplicate gear is also mounted on axis I, is moved axially on axis I by shift fork impetus, is passed through the taper roller axis at axis both ends
It holds and realizes positioning with the shaft shoulder；One two gear engaged with sliding duplicate gear is installed respectively at the both ends of axis II, they with
Axis is connected using flat key, and the axis between two gears is processed to worm screw, is conveyed power to reducer shaft III, is made to subtract by the device
Fast device realizes folk art term throw-over.
6. a kind of carding machine transmission system as claimed in claim 3, characterized in that cover board is provided with manual operation device, borrows
Mechanical clutch is helped to realize that the switching of the retarder primary speed-down and double reduction makes clutch that is, in manual operation
Separation is driven using level-one gear on worm retarder；Conversely, in removable cover work, using second-stage worm gear reduction unit
Transmission；
The mechanical clutch is made of gear with clutch and clutch, by the tooth engagement in the two and disconnects control, band
Through axle sleeve empty set on axis III, clutch is connect with axis III by flat key clutch gear, and the shift fork control that swings takes away
Engagement and disconnection between clutch gear and clutch, when the two engagement, axis III receives the torque transmitted by front end axis, at this time
Retarder is double reduction；Otherwise when the two disconnects, gear with clutch dallies on axis III, is driven at this time by handle,
Retarder is first stage decelerator, and clutch is limited by the spacing ball being fixed on axis, and spacing ball passes through spring in the radial direction of axis
It moves back and forth, the right end of axis III is worm screw, drives to removable cover transmission shaft；
Sliding duplicate gear realizes by clutch shifter and moves on axis that selector fork is mounted on axis III, is branch with axis III
Movement of the point realization shifting slide gear on axis, retarder use box sealing.
7. a kind of carding machine transmission system as described in claim 1, characterized in that doffer's section transmission mechanism refer to by
All parts of doffer's motor as power source, including cross apron web-collecting system, pressure roller part, three roller stripping parts and doffer portion
Point, which includes 4 routes, and one is that the motor synchronous belt pulley transmission that is mounted on doffer's motor is driven same to motor
Belt wheel is walked, apron drive coordination belt wheel transmission to cross apron web-collecting system synchronous pulley is passed through；The second is passing through pressure roller drive coordination
During which lower compression roller synchronous pulley of the belt wheel transmission into pressure roller component is tensioned and is commutated by tensioning pulley；Thirdly to pass through three
Roller drive coordination belt wheel transmission changes the rotation of topping roll synchronous pulley using double-sided toothed belt to three roller stripping devices
During which direction is tensioned by tensioning wheel, is finally to pass through tensioning wheel to doffer's synchronous pulley by pattern doffing roller synchronous belt pulley transmission
Tensioning.
8. a kind of carding machine transmission system as described in claim 1, characterized in that the cross apron web-collecting system transmission mechanism packet
Two pairs of revolution belts at a distance of set distance are included, the two turns on the contrary, apron is mounted on apron belt wheel, and apron belt wheel is mounted on
On belt wheel transmission axis, tapered roller bearing is installed on belt wheel transmission axis, is positioned by the shaft shoulder, tapered roller bearing is mounted on bearing
On seat, bearing block is fixed on the rack, and the lower end of belt wheel transmission axis is equipped with driven wheel of differential, drive bevel gear and from mantle tooth
Wheel, which is meshed, is transferred to the torque on apron transmission shaft on belt wheel transmission axis, and belt wheel transmission axis drives apron by apron belt wheel
Movement.
9. a kind of carding machine transmission system as described in claim 1, characterized in that pressure roller section transmission mechanism includes upper
Pressure roller shaft and pushing roll shaft, one end of the upper pressure roller shaft are mounted in oscillation bearing seat, the other end peace of the upper pressure roller shaft
Pressure roller is loaded onto, mandrel is installed in one end of oscillation bearing seat, oscillation bearing seat is fixed on cabinet by mandrel, works as oscillation bearing
When seat is around body pivot, upper pressure roller also follows it to float up and down；
The lower part for pushing roll shaft and being mounted on cabinet, lower compression roller are mounted on the one end for pushing roll shaft, push the other end of roll shaft
Lower compression roller synchronous pulley is installed, by synchronous belt pressure roller transmission shaft driven to lower compression roller, draws sliver to movement at circle machine；
It is equipped with compressed spring in the upper end of oscillation bearing seat, given pressure is provided, clamp nut limit is installed on compression spring
Position.
10. a kind of carding machine, characterized in that any described using the claims 1-9 including above-mentioned carding machine transmission system
Carding machine transmission system realize power transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821942627.9U CN209307533U (en) | 2018-11-23 | 2018-11-23 | A kind of carding machine transmission system and carding machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821942627.9U CN209307533U (en) | 2018-11-23 | 2018-11-23 | A kind of carding machine transmission system and carding machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209307533U true CN209307533U (en) | 2019-08-27 |
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ID=67674252
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|---|---|---|---|
| CN201821942627.9U Expired - Fee Related CN209307533U (en) | 2018-11-23 | 2018-11-23 | A kind of carding machine transmission system and carding machine |
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| CN (1) | CN209307533U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113550029A (en) * | 2021-09-03 | 2021-10-26 | 南通双弘纺织有限公司 | Carding main transmission system |
-
2018
- 2018-11-23 CN CN201821942627.9U patent/CN209307533U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113550029A (en) * | 2021-09-03 | 2021-10-26 | 南通双弘纺织有限公司 | Carding main transmission system |
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| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20190827 Termination date: 20201123 |