CN107035834B - A kind of group of double-linked cam transmission device - Google Patents
A kind of group of double-linked cam transmission device Download PDFInfo
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- CN107035834B CN107035834B CN201710185678.5A CN201710185678A CN107035834B CN 107035834 B CN107035834 B CN 107035834B CN 201710185678 A CN201710185678 A CN 201710185678A CN 107035834 B CN107035834 B CN 107035834B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
- F16H25/14—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation perpendicular to the axis of rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
- F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
- F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
- F16H53/025—Single-track cams for single-revolution cycles; Camshafts with such cams characterised by their construction, e.g. assembling or manufacturing features
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Abstract
A kind of group of double-linked cam transmission device of the invention belongs to mechanical driving device field, is related to a kind of continuous cam gear realized using cam structure principle.In device, there to be the actuating cam of several identical and uniformly distributed lift and backhaul profile to there is the inverted cam of several identical and uniformly distributed lift and backhaul profile to constitute linkage cam mechanism by middleware with another, a few set linkage cam mechanism connection groups are used again, form the connection group double-linked cam device that can be continuously driven.The present invention utilizes Cam Design principle, and gear-driven direct conjugate relation is converted to the indirect conjugate relation of intervention middleware.By the flexibility of Cam Design, a variety of novel transmission modes engaged indirectly can be achieved, gear drive can be overcome to have, and minimum number of teeth limitation, low strength, design method is single, is not suitable for the defects of big distance transmission, has many advantages outstanding, can be used for various transmission occasions.
Description
Technical field
The invention belongs to technical field of mechanical transmission, are related to a kind of continuous cam drive realized using cam structure principle
Device.
Background technique
Gear drive, especially gradually tooth punching wheel, have a wide range of applications in modern industry, have high status.Tooth
Wheel transmission is that movable connection is directly realized by the form of gear high pair the conjugate tooth profiles of two gear teeth.With compact-sized,
Transmission balance, feature with high accuracy.But one during gear drive is instantaneous, and only a small amount of tooth participates in transmission, registration compared with
It is low, thus in terms of transmission capacity fail to give full play to the bearing capacity of gear entirety.It fights like big legion, and uses one
The tactics challenge by oneself to one are the same.Also, it is influenced by the defects of minimum not root cutting number and topping, in fact, gear passes
Dynamic structural compactness is not played fully.On the other hand, due to gear-driven design feature, when facing big distance
The occasion of transmission then seems structure bulky using gear drive.
Cam drive is the movable connection realized using higher pair form is constituted between cam and its driven member.Cam drive can be
Cam carries out realizing the reciprocal of its driven member, the linear motion of interval, dead axle swing or plane motion when continuous rotary movement,
Usually unconjugated, the movement of driven member is discrete.Driving link is only generally done with cam in cam mechanism.
As gear-driven expansion, it is thus proposed that and have studied Oscillating Tooth Gear Reducer.It can be found in China Machine Press 1993
" Oscillating Tooth Gear Reducer is theoretical " written by version, Qu Jifang.It points out as its page 5, Oscillating Tooth Gear Reducer is passed by K-H-V type fewer differential teeth planetary
Made of developing on the basis of dynamic, correlative study in recent years is for identical mentality of designing.Transmission dress according to the present invention
Although set has similarity therewith in macrostructure, there are basic difference in design principle, the design method of tooth form is obtained
Greatly simplify.
Summary of the invention
The purpose of the present invention is overcome the deficiencies in the prior art will be gear-driven straight using Cam Design principle
Connect the indirect conjugate relation that conjugate relation is converted to intervention middleware.Flexibility by Cam Design is, it can be achieved that a variety of
The novel transmission mode engaged indirectly can overcome gear drive to have minimum number of teeth limitation, low strength, design method single, no
The defects of being suitble to big distance transmission, the design method of tooth form is greatly simplified.With many advantages outstanding, can be used for each
Kind transmission occasion.
The technical solution adopted by the present invention is that a kind of group of double-linked cam transmission device, in device, will have it is several identical and
The actuating cam of uniformly distributed lift and backhaul profile has the inverted cam of several identical and uniformly distributed lift and backhaul profile with another
Linkage cam mechanism is constituted by middleware, then a few set linkage cam mechanism connection groups are used, forms the connection group that can be continuously driven
Double-linked cam device；
There is the convex or concave tooth being made of adjacent lift and backhaul on cam, each tooth is circumferentially uniformly distributed；Two dead axle revolutions
Cam cam follower made by a middleware constitute the linkage cam mechanism that engages indirectly；In in linkage cam mechanism
Between part make between the lift and backhaul of two cams while constituting the closed cam mechanism connection of driven member kinematic geometry；Actuating cam
Lift correspond to the backhaul of inverted cam just, engaged in this section, actuating cam is by its contact point with middleware from the lowest point
While pushing summit to, the contact point of middleware and inverted cam is fallen after rise by its summit to the lowest point, realizes actuating cam to driven
The driving process that cam is driven；The backhaul of actuating cam corresponds to the lift of inverted cam, engages in this section, inverted cam
Lift while push the contact point of itself and middleware to summit from its lowest point, the contact point of middleware and actuating cam is by it
Summit is fallen after rise to the lowest point, realizes the reseting procedure that middleware resets, and is ready for next driving process；Adjacent teeth is successively real
A kind of drive connection driven and reset consecutive interruption power output is realized in now engagement indirectly between driving and driven cam；
At least two sets of linkage cam mechanisms are applied in combination, and connection group linkage cam mechanism are constituted, so that each actuating cam is to each
The section corner connection of the driving process of inverted cam is continuous or connects with partially overlapping, and first set linkage is completely covered in one week
Section angle corresponding to the reseting procedure of cam mechanism realizes that the movement of each component within the scope of 360 ° keeps having geometry closing
Relationship.
Ratio, the actuating cam of the motion angle for return travel at the lifting movement angle and inverted cam of actuating cam in linkage cam mechanism
Motion angle for return travel it is identical as the ratio three of the ratio of the lifting movement of inverted cam, the inverted cam number of teeth and the actuating cam number of teeth,
The lifting movement rule of actuating cam is identical with the return motion program of inverted cam, the return motion program of actuating cam and from
The lifting movement rule of moving cam is identical.
The lift of actuating cam and motion angle for return travel be not identical in linkage cam mechanism, and lifting movement angle is equal to or more than back
The angle Cheng Yundong.
Connection group double-linked cam transmission device middleware contains the compliant section that hydraulic drive or flexible axle connection are constituted.
The actuating cam and inverted cam structure type different types of connection group double-linked cam transmission device linkage cam mechanism.
The quantity of connection group double-linked cam transmission device middleware be equal to or less than actuating cam and the inverted cam number of teeth and.
Connection group double-linked cam transmission device cam structure is dish type, flute profile, flange type, cylinder end face shape, chou configuration.
The connection group mode of connection group double-linked cam transmission device linkage cam mechanism is axial connection group or circumferential connection group.
It is to expand to come based on cam mechanism the beneficial effects of the invention are as follows disclosed group of linkage cam mechanism.
Since cam mechanism has the flexibility of height in design, thus, the transmission realized in this way, so that two groups of cams
Between, the movement relation between cam and middleware also there is the designability of height.Speed ratio transmission such as can be achieved, gear ratio passes
It moves, it can be achieved that complete cycle is turned round the conversion between reciprocally swinging, it can be achieved that continuous transmission and intermittently-driving etc..In short, reasonably setting
Meter, can inherit and develop cam drive institute it is advantageous and overcome its deficiency.Such as, the limit of gear drive minimum number of teeth is overcome
System, the number of teeth of single cam can be taken as 1.All cams simultaneously participate in engagement simultaneously or even same surface multiple spot is simultaneously participated in and nibbled
It closes, has given full play to the integral strength of part material, improve the utilization rate of material, thus transmitting identical transmission capacity requirement
Shi Kewang volume is smaller.Under the premise of can be the characteristics of keeping structural compactness, the transmission of big distance, this point be advantageously realized
It is that gear drive is incomparable.
Detailed description of the invention
Fig. 1 connection group linkage cam mechanism conceptual model schematic diagram, driving and driven cam is outer profile disc cam, intermediate
Part is pinnacle radial translating follower form, and parallel shaft arrangement, reverse drive, the actuating cam number of teeth is 3, and the inverted cam number of teeth is
4, it is made of two sets of linkage cam mechanisms, is axially arranged in juxtaposition.
Fig. 2 connection group linkage cam mechanism conceptual model schematic diagram, driving and driven cam is outer profile disc cam, intermediate
Part is pinnacle radial translating follower form, and gear ratio 3:4 is made of two sets of linkage cam mechanisms, and shared one driven convex
Wheel, actuating cam circumference, but need to be realized and be synchronized by other connections.
Fig. 3 Internal periphery cam and outer profile cam constitute linkage cam mechanism, and two cams share when connection group, coaxial to pacify
Dress only increases middleware, and middleware is up to the sum of the two cam numbers of teeth, and the position of middleware is not arbitrarily.Label declaration: 1-
Gabarit cam, wide cam, 3- direct acting middleware, 4- rack in 2-.
Fig. 4 cylindrical end face cam coaxially constitutes linkage cam mechanism, and when connection group shares driving and driven cam, only increases intermediate
The quantity of part, middleware quantity are up to the sum of the two cam numbers of teeth, and the position of middleware is not arbitrarily.
Fig. 5 is realized using cylindrical end face cam in a kind of structure type figure of parallel axes, concurrent aces or the transmission of antarafacial between centers
Middleware is the form of swinging block；Hydraulic drive realization can also be used when big distance transmission, big spacing can also be realized by flexible axle
Swing transmission.
Fig. 6 is the example that different type cam constitutes connection group linkage cam mechanism, uses cylindrical end face cam and disk in figure
Shape cam combination, middleware are the form of direct acting sliding block；Hydraulic drive realization can also be used when big distance transmission.Label declaration:
1- disc cam, 2- cylindrical end face cam, 3- direct acting middleware, 4- rack.
Fig. 7 realizes the flexible purpose lengthened of middleware for big distance transmission using hydraulic transmission mode.
Label declaration: 1- cam, 2- cam, 3- plunger middleware, 4- rack upper oil cylinder, 5- oil pipe beam.
Fig. 8 is to mitigate the mobile friction of translation cam driven member, can increase the example that rolling element is converted into rolling friction.Mark
Number explanation: 1- gabarit cam, wide cam, 3- direct acting middleware, 4- rack, 6- circulating rolling body in 2-.
Fig. 9 middleware is the example of swinging block.
Label declaration: 1- gabarit cam, wide cam, 3- swing middleware, 4- rack, 31- swinging axle in 2-.
Figure 10 middleware is the example of plane motion form.Label declaration: 1- gabarit cam, wide cam, 3- plane in 2-
Middleware is moved, constraint, 4- rack are slided on 31- middleware, 5- swings constraint, 51- sliding slot.
Figure 11, other applicable cam types, (a), cylinder grooved cam, (b), cylinder flange cam, (c), inner cylinder
Grooved cam, (d), spherical surface grooved cam.
Specific embodiment
With reference to the accompanying drawing with the technical solution specific implementation that the present invention will be described in detail.
The working principle of cam drive sets the cam of two dead axles revolution, and for movement relation, one is driving link
Another is driven member, and for design feature, one is single raised wave crest profile, and a referred to as double wedge, another is single
A indent trough profile, referred to as a concave tooth.Two cams make cam follower by a middleware, make the convex and concave teeth of two cams
Between constitute the closed cam mechanism connection of driven member kinematic geometry, referred to as engagement indirectly simultaneously.The lift of actuating cam is proper
Correspond to the backhaul of inverted cam well, when operating engages in this section, and actuating cam pushes middleware to summit from its lowest point, simultaneously
It is fallen after rise by the summit of inverted cam to the lowest point, realizes that actuating cam drives inverted cam in one section of section, claim this mistake
Journey is known as driving process；Next, the backhaul of actuating cam also just respectively corresponds the lift of inverted cam, the lift of driven wheel
Push middleware to summit from its lowest point again, while being fallen after rise by the summit of actuating cam to the lowest point, this process is known as reseting procedure.
Although actuating cam fails to provide power to inverted cam in reseting procedure, to drive process to get ready next time；Such as
Different numbers is arranged under conditions of meeting forgoing relationship, by the convex or concave tooth of driving and driven cam in fruit along respective circumference respectively
Amount, and connect driving process and reseting procedure and carry out, then a kind of biography for being interrupted power output is realized between driving and driven cam
Dynamic relationship, referred to as linkage cam mechanism.
In linkage cam mechanism engagement, the steering relationship of driving and driven cam selects inverted cam when being only dependent upon beginning
Which side contoured surface make reverse-running section use: for single concave tooth, side be forward direction, the other side is then reversed.Therefore it turns to
Relationship is artificially selected as a result, rather than gear drive being determined by structural relation like that.
The average ratios relationship of driving and driven cam monodentate engaged section depend on actuating cam monodentate lifting movement angle with
The ratio of inverted cam monodentate motion angle for return travel, the i.e. size of average ratios are related to preset motion angle of cam.Due to going out
In the convex or concave tooth number on the single cam of purpose being continuously driven can only round numbers, in addition movement the proportional corresponding requirement in angle,
Transmission ratio is also related with convex or concave tooth number.
The instantaneous velocity transformational relation of driving and driven cam additionally depends on the setting of respective contour curve.Based on contour curve
Has the characteristics that extensive alternative, instantaneous speed relationship can meet permanent ratio or unsteady variation both when engagement.If
The characteristics of motion of the controlled middleware at the lifting movement angle of actuating cam is controlled with the motion angle for return travel of inverted cam just
The characteristics of motion of middleware processed is consistent, then constant ratio transmission can be achieved between two cams, otherwise, instantaneous transmission ratio may be
Variation.That is, two transmissions between cam can be and be conjugated indirectly, be also possible to unconjugated.Conjugate condition functional relation
General formulation are as follows: if the characteristics of motion of the controlled middleware at the lifting movement angle of actuating cam is f (a), indirectly with it
The characteristics of motion of the controlled middleware of the motion angle for return travel of the inverted cam of engagement is f (b), and a, b are phase angle, and a/b is
Constant, then the transmission between driving and driven cam and inverted cam is stable drive ratio, similarly, if the lift of inverted cam
The characteristics of motion for moving the controlled middleware at angle is g (b), with being controlled for the motion angle for return travel of its inverted cam engaged indirectly
The characteristics of motion of middleware processed is g (a), and a, b are phase angle, and a/b is constant, then between driving and driven cam and inverted cam
Transmission be stable drive ratio.
In above-mentioned linkage cam mechanism, actuating cam is limited the monodentate of inverted cam driving process, different teeth it
Between driving section and reset section connect carry out.Driving process be by structural factor force realize, reseting procedure be then according to
It is completed by inertia, is non-enforceable, thus there is the possibility of transmission Out of phase, be unable to operate stably transmission process.For
It solves the problems, such as this, is at least further added by a set of linkage cam mechanism, make it or they driving section and first set double-linked cam
The driving section of mechanism connects or partially overlapping connects, and the reset section of first set linkage cam mechanism is completely covered, then
So that there is structural pressure factor in the transmission in 360 °, it can be ensured that actuating cam is passed to inverted cam during continuous rotary
Dynamic phase relation is stable.Such linkage cam mechanism combination, referred to as connection group linkage cam mechanism.
If transmission is reversible, it is intended to meet above-mentioned requirements when should make just inversely to be driven in structure design.
In summary the constituent element of connection group linkage cam mechanism includes mainly cam and middleware, it is characterized in that dead axle
The cam and middleware of revolution constitute linkage cam mechanism, include two in every set linkage cam mechanism by several convex or concave tooth structure
At the cam of cam contour and a middleware as cam follower, middleware is synchronous between the convex and concave teeth of two cams
Ground constitutes and realizes the closed cam mechanism of driven member kinematic geometry each other, realizes that driving section connects with section is resetted between two cams
Continuous indirect meshing relation；At least two sets of linkage cam mechanisms are used in combination, and constitute connection group linkage cam mechanism, and each set is made to link
Driving section and reset section between cam mechanism are mutually completely covered.
The axis of two groups of cams in connection group linkage cam mechanism can be coaxial, can also parallel, intersection or staggeredly.
The design of cam mechanism carries out according to a conventional method.Disc cam, cylindrical end may be selected in the structure type of cam
Face cam, cylinder or face cam, spherical space cam etc.；Cam follower motion form may be selected direct acting, swing or
Plane motion, hydraulic drive connection even can be used in big distance when being driven or flexible axle connects, and the contact jaw of driven member and cam can
Select forms or the small flat forms such as pinnacle, dome, roller；Monodentate lift and the selection of backhaul contour curve have arbitrariness, with
The movement generation rigid shock and soft impulse for not making its driven member are preferred.
It illustrates, when covering linkage cam mechanisms and carrying out connection group, each all actuating cams can coaxial and axial cloth more
Connection group is set, each set linkage cam mechanism can also be used and share an actuating cam or inverted cam, another cam is around its axis circle
It arranges in week, alternatively, if two cams use the knot of the disc-like shapes cam such as dish type or face cam, end face flange-shaped cam
Structure, can be used one be outer profile another be the encirclement form connection group of Internal periphery, if it is cylindrical cam or cylinder flute profile, column
Face flange-shaped cam, using shared inverted cam, the connection group mode of driven member circle distribution.Specific embodiment portion is shown in detailed description
Point.
When carrying out connection group double-linked cam transmission designs, comprising the following steps:
A. the structure arrangement relation of selected double-linked cam transmission, the i.e. relative positional relationship of axis, including coaxial, parallel,
Intersection interlocks；
B. input and output component is selected, determines respective steering, sets the transmission ratio of actuating cam and inverted cam；
C. the transmission ratio for combining setting, selectes actuating cam and inverted cam is convex or the quantity of concave tooth, Ying Junwei integer；
D. it determines the corresponding movement angle of driving and driven cam monodentate, and distributes lift and motion angle for return travel, is i.e. driving process fortune
Dynamic angle and reseting procedure move angle, and driving course motion angle preferably greater than or is equal to reseting procedure and moves angle when distribution.Correspondingly really
Determine the corresponding movement angle of inverted cam.
E. select the forms of motion of cam follower, that is, middleware, mounting means, both ends and cam contact form and knot
Structure parameter；
F. the lift and return motion program of middleware are set；
G. the profile of driving and driven cam monodentate lift and backhaul is designed；
H. by the selected number of teeth, driving and driven cam monodentate profile is evenly distributed on circumference；
I. the tricks and arrangement of linkage cam mechanism are selected.
Embodiment one is to the example that embodiment nine is all that design philosophy according to the invention designs.
Embodiment one: Fig. 1 shows that driving and driven cam is outer profile disc cam, and monodentate flank profil lift and backhaul are adopted
With constant velocity motion, middleware is pinnacle radial translating follower form, is made of two sets of linkage cam mechanisms, axial arranged side by side
Arrangement.The formula that middleware uses is to heart direct acting form, and in this case, the lift size of driving and driven cam is identical.It is actively convex
Tooth number is 3, and the corresponding movement angle of monodentate is 120 °, and the inverted cam number of teeth is 4, and the corresponding movement angle of monodentate is 90 °, i.e.,
The ratio at the corresponding movement angle of monodentate is equal to the inverse of gear ratio；Further, it arbitrarily divides driven wheel lift flank profil and moves angle
Angle is moved with backhaul flank profil, the general lifting movement angle of single-direction transmission is relatively larger to help to obtain biggish registration.In Fig. 1
Driving wheel lifting movement angle is taken as 90 °, and motion angle for return travel is taken as 30 °, and the driven wheel meeting angle Cheng Yundong is taken as 67.5 °, drawback movement
Angle is taken as 22.5 °, i.e. the ratio at actuating cam lifting movement angle and motion angle for return travel is equal to inverted cam motion angle for return travel and lift
Move the ratio at angle.The lift of two cams and backhaul press uniform motion pattern setting to the characteristics of motion that middleware drives.Basic circle
Diameter can be selected according to stress or drive line angle, without specific limitation.
To realize that driving process is completely covered reseting procedure, when connection group, the initial phase changing of the relative positions amount of two inner room actuating cams
Should be between 30~60 °, the initial phase changing of the relative positions amount of inverted cam should be between 22.5~45 °, and the ratio with the former
Meeting the relationship of transmission ratio, the second actuating cam is staggered 40 ° of phase with respect to the first actuating cam in Fig. 1, because of formula reverse drive,
Second inverted cam is staggered -30 ° of phase with respect to the first inverted cam.
This structure tricks arranged side by side can arbitrarily increase, and be suitable for that band, chain conveyer is replaced to realize greatly to pass apart from densification engagement
It is dynamic to require, bicycle chain is such as replaced, power transmitting in mechanical arm etc..In addition, to make middleware movement not generate impact, it can be
Transition region is set at tooth top, tooth root, but set transition region also will keep the corresponding relationship at aforementioned movement angle constant.In can also changing
Between part pinnacle be roller, with enhance wearability reduce friction, processing method is with cam design requirement, and and will not be described here in detail.Fig. 2
It is similar, only show adoptable circumferentially mode.
Embodiment two:
Fig. 3 shows that actuating cam 1 uses Internal periphery disc cam form using outer profile cams, inverted cam 2, and
It is co-axially mounted composition linkage cam mechanism.Figure label 3 is middleware, and for dome to heart direct acting form, label 4 is middleware guiding
Frame.The Internal periphery cam number of teeth takes 5, and the lesser outer profile cam number of teeth of size takes 4.This example transmission is reversible, and is used symmetrical
The monodentate profile of structure, i.e. lifting movement angle are equal to motion angle for return travel, so that forward and reverse drive characteristic is consistent.It is driving and driven when connection group
Cam need not accelerate, and only increase middleware and appropriate position relationship.When reverse drive, middleware quantity is most
For the sum of the two cam numbers of teeth, the position of middleware is not arbitrarily, to be divided equally on resulting position at one week by number of packages among maximum
Installation middleware is only feasible.
There are about half middlewares to simultaneously participate in driving process for this structure type, and registration is passed much higher than involute gear
Dynamic, it requires have larger radial space, but axial space requirement is smaller.
Embodiment three:
Fig. 4 is that cylindrical end face cam is co-axially mounted composition linkage cam mechanism, when connection group be also need not increase it is driving and driven convex
Quantity is taken turns, middleware quantity and appropriate position relationship are only increased.In this example, transmission is also reversible, a cam
The number of teeth takes 1, and another cam number of teeth takes 3.When reverse drive, middleware quantity can be taken as 4, and middleware is evenly arranged.Co-rotating transmission
When, middleware quantity can be taken as the difference of the two cam numbers of teeth, i.e., 2, and middleware is also evenly arranged.
There are about half middlewares to simultaneously participate in driving process for this structure type, and registration is larger, it requires have larger axis
To space, but radial space require it is smaller.It is especially applicable in long-distance transmission, Multi-stage transmission coaxial arrangement, space utilization
Rate is high.
Example IV:
Fig. 5 shows a kind of structure type that parallel axes, concurrent aces or the transmission of antarafacial between centers are realized using cylindrical end face cam.
Originally the form matches form for swinging middleware is exemplified, but specifically limited to having no relatively for the relationship of setting for two camshafts.Even
If two cams are apart from each other, swing middleware two contact jaws can by propeller shaft couplings, or with flexible axle connection, hydraulic link
Holding moves synchronously relationship.In addition, the lift of two cams is not necessarily equal when using swinging middleware two cam of connection, but
Brachium relationship depending on two contact jaws.
Embodiment five
Fig. 6 shows that different type cam constitutes the example of connection group linkage cam mechanism, uses 2 He of cylindrical end face cam in figure
Disc cam 1 combines, and middleware 3 is direct acting form, and label 4 is rack.This example also demonstrates the transmission of different location relationship between centers
A kind of structure mentality of designing also can also be used hydraulic drive and realize remote connection.
Embodiment six:
Fig. 7 is the flexible purpose lengthened for realizing middleware using hydraulic transmission mode for big distance transmission；Two cams 1
With 2, cam mechanism is constituted with the plunger middleware 3 being mounted on the rack in oil cylinder 4 respectively, utilizes the Incoercibility of hydraulic oil
The linkage of both ends middleware is realized by oil pipe beam 5, and the geometry of linkage cam mechanism is kept to close.
Embodiment seven
Fig. 8 is the friction for mitigating translation cam driven member prismatic pair, can increase the example that rolling element is converted into rolling friction.
Sliding friction between connection gabarit cam 1 and the direct acting middleware 3 and rack 4 of interior wide cam 2 is converted to by circulating rolling body 6
Rolling friction.
Embodiment eight
Fig. 9 is the example that middleware is swinging block.
Gabarit cam 1 and interior wide cam 2 pass through the swing of the swinging axle 31 middleware 3 realization connection group double-linked cam in rack 4
Transmission.
Embodiment nine
Figure 10 is the example that middleware is plane motion form.
Gabarit cam 1 and interior wide cam 2 pass through the realization connection group double-linked cam transmission of plane motion middleware 3.Middleware 3 by
Constraint 5, sliding constraint 31 and sliding slot 51 are swung in rack 4, and plane motion is done in constraint jointly.
Figure 11 provides some other applicable cam structure figure, (a), cylinder grooved cam, (b), cylinder flange cam,
(c), inner cylinder grooved cam, (d), spherical surface grooved cam.
The same with gear drive, train combination also may be implemented in the transmission of connection group double-linked cam, and dead axle transmission both may be implemented
Cyclic train also may be implemented in train.
Claims (8)
1. a kind of group of double-linked cam transmission device, including cam and middleware, characterized in that in device, will have several identical
And the actuating cam of uniformly distributed lift and backhaul profile have with another it is several identical and uniformly lift and backhaul profile driven convex
Wheel constitutes linkage cam mechanism by middleware, then a few set linkage cam mechanism connection groups are used, and forms the connection that can be continuously driven
Group double-linked cam device；
There is the convex or concave tooth being made of adjacent lift and backhaul on cam, each tooth is circumferentially uniformly distributed；Two dead axles turn round convex
Wheel makees cam follower by a middleware and constitutes the linkage cam mechanism engaged indirectly；The middleware in linkage cam mechanism
Make between the lift and backhaul of two cams while constituting the closed cam mechanism connection of driven member kinematic geometry；The liter of actuating cam
Journey corresponds to the backhaul of inverted cam just, and actuating cam is engaged by middleware with inverted cam in lift section, actuating cam
While pushing the contact point of itself and middleware to summit from the lowest point, the contact point of middleware and inverted cam is fallen after rise by its summit
To the lowest point, the driving process that actuating cam drives inverted cam is realized；The backhaul of actuating cam corresponds to inverted cam
Lift, actuating cam are engaged by middleware with inverted cam in backhaul section, and the lift of inverted cam is by itself and middleware
While contact point pushes summit to from its lowest point, the contact point of middleware and actuating cam is fallen after rise by its summit to the lowest point, is realized
The reseting procedure that middleware resets is ready for next driving process；Adjacent teeth successively realizes indirect engagement, master and slave
A kind of drive connection driven and reset consecutive interruption power output is realized between moving cam；
At least two sets of linkage cam mechanisms are applied in combination, and connection group linkage cam mechanism are constituted, so that each actuating cam is to each driven
The section corner connection of the driving process of cam is continuous or connects with partially overlapping, and first set is completely covered in a rotation period
Each driving and driven cam and middleware within the scope of 360 ° are realized in section angle corresponding to the reseting procedure of linkage cam mechanism
Movement keeps having the closed relationship of geometry.
2. described in claim 1 group of double-linked cam transmission device, characterized in that the liter of actuating cam in linkage cam mechanism
The lifting movement angle of the ratio of the motion angle for return travel of the angle Cheng Yundong and inverted cam, the motion angle for return travel of actuating cam and inverted cam
Ratio, the ratio three of the inverted cam number of teeth and the actuating cam number of teeth it is identical, the lifting movement rule and inverted cam of actuating cam
Return motion program it is identical, the return motion program of actuating cam and the lifting movement rule of inverted cam are identical.
3. described in claim 1 group of double-linked cam transmission device, characterized in that the liter of actuating cam in linkage cam mechanism
The angle Cheng Yundong is greater than motion angle for return travel.
4. described in claim 1 group of double-linked cam transmission device, characterized in that middleware contains hydraulic drive or flexible axle connection
Connect the compliant section of composition.
5. described in claim 1 group of double-linked cam transmission device, characterized in that the actuating cam of linkage cam mechanism with from
Moving cam structure type different types.
6. described in claim 1 group of double-linked cam transmission device, characterized in that the quantity of middleware is equal to or less than actively
Cam and the inverted cam number of teeth and.
7. described in claim 1 group of double-linked cam transmission device, characterized in that the cam structure be dish type or flute profile,
Or flange type or cylinder end face shape or chou configuration.
8. described in claim 1 group of double-linked cam transmission device, characterized in that the connection group mode of the linkage cam mechanism
For axial group or circumferential connection group.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710185678.5A CN107035834B (en) | 2017-03-27 | 2017-03-27 | A kind of group of double-linked cam transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710185678.5A CN107035834B (en) | 2017-03-27 | 2017-03-27 | A kind of group of double-linked cam transmission device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107035834A CN107035834A (en) | 2017-08-11 |
| CN107035834B true CN107035834B (en) | 2019-04-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710185678.5A Expired - Fee Related CN107035834B (en) | 2017-03-27 | 2017-03-27 | A kind of group of double-linked cam transmission device |
Country Status (1)
| Country | Link |
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| CN (1) | CN107035834B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7195248B2 (en) * | 2019-12-26 | 2022-12-23 | 株式会社ジェイテクトマシンシステム | Cam device, work supply device and cutting device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6367342B1 (en) * | 2000-02-11 | 2002-04-09 | Christopher A. Weismann | Indexing drive and transmission |
| CN101201087A (en) * | 2007-10-08 | 2008-06-18 | 赵容冰 | Apparatus for braking and linking convex and concave |
| EP2142361A1 (en) * | 2007-03-30 | 2010-01-13 | Wilhelm Settele | Cam mechanism having transfer rollers |
| CN102877942A (en) * | 2012-10-17 | 2013-01-16 | 四川大学 | Two-phase outer cam sleeve type high-rotational-speed internal-combustion engine |
| CN103225673A (en) * | 2013-04-09 | 2013-07-31 | 苏州瑞佳新能源动力科技有限公司 | Cam slide block linkage device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005010226A1 (en) * | 2003-07-29 | 2005-02-03 | Nippon Piston Ring Co., Ltd. | Cam lobe member, camshaft using the same and method for producing cam lobe member |
-
2017
- 2017-03-27 CN CN201710185678.5A patent/CN107035834B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6367342B1 (en) * | 2000-02-11 | 2002-04-09 | Christopher A. Weismann | Indexing drive and transmission |
| EP2142361A1 (en) * | 2007-03-30 | 2010-01-13 | Wilhelm Settele | Cam mechanism having transfer rollers |
| CN101201087A (en) * | 2007-10-08 | 2008-06-18 | 赵容冰 | Apparatus for braking and linking convex and concave |
| CN102877942A (en) * | 2012-10-17 | 2013-01-16 | 四川大学 | Two-phase outer cam sleeve type high-rotational-speed internal-combustion engine |
| CN103225673A (en) * | 2013-04-09 | 2013-07-31 | 苏州瑞佳新能源动力科技有限公司 | Cam slide block linkage device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107035834A (en) | 2017-08-11 |
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Granted publication date: 20190412 |