GB2277499A - Device for driving a carriage along a rail - Google Patents
Device for driving a carriage along a rail Download PDFInfo
- Publication number
- GB2277499A GB2277499A GB9407970A GB9407970A GB2277499A GB 2277499 A GB2277499 A GB 2277499A GB 9407970 A GB9407970 A GB 9407970A GB 9407970 A GB9407970 A GB 9407970A GB 2277499 A GB2277499 A GB 2277499A
- Authority
- GB
- United Kingdom
- Prior art keywords
- driving member
- support
- pinion
- rail
- motive unit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61C—LOCOMOTIVES; MOTOR RAILCARS
- B61C13/00—Locomotives or motor railcars characterised by their application to special systems or purposes
- B61C13/04—Locomotives or motor railcars characterised by their application to special systems or purposes for elevated railways with rigid rails
Landscapes
- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Transmission Devices (AREA)
Abstract
The driving device for the translation of a carriage (10) on a rail (12) comprises a friction roller (20) rolling on the upper face of the rail (12) and a chain wheel (18) cooperating with a chain (14) situated on the lower side of the rail (12) along the sloping sections (12a). The friction roller (20) is linked to a motor (16) by a free-wheeling device (22) and the chain wheel (18) is in constant kinematic linkage with the motor (16). The chain wheel (18) has a peripheral linear speed greater than that of the friction roller (20) so that the engagement of the chain wheel (18) with the chain (14) produces the free-wheeling of the friction roller (20). In an alternative embodiment, the chain wheel (18) is replaced with another friction roller which, along the sloping sections (12a), engages the rail. <IMAGE>
Description
DEVICE FOR DRIVING A MOVING BODY ON A
LINEAR SUPPORT
The present invention relates to a driving device for translation of a moving body, such as a carriage, moving on a fixed linear support, such as a rail, comprising two rotating driving members of the moving body moved from the same motive unit, cooperating respectively with the opposite longitudinal faces of the same support, one of which is a discontinuously cooperating driving member which only cooperates on certain sections of its route along the support to move the moving body along the support.
Mechanical systems comprising a rolling carriage on a rail by the friction of rollers driven in rotation on the upper face of the rail by a motive unit rigid with the carriage are well known. These systems generally operate on horizontal rails.
If it is desired to operate such systems on sloping sections of rail, the adhesion of the rollers cooperating with the upper face of trail must be reinforced by auxiliary rollers cooperating by ciamping, arranged against the lower face of the rail.
Besides the fact that such a system is limited in its performances by the risk of sliding, and by the risk of wear of the rail or rollers, it introduces into travel on bends on the vertical plane a problem of differencein speed between upper rollers and lower rollers, which causes friction of the non-motive rollers if it is desired to link the movement of the latter with that of the motive rollers.
In order to ensure the negotiation of ramps, another solution consists in using a fixed chain, rigid with the rail, with which a chain sprocket driven by the motive unit of the carriage cooperates.
On great lengths of rail, this solution has the drawback of imposing the use of a chain over the whole journey, which is costly and which is hardly compatible, for the roller chains, with rail curves situated in the plane of the roller axes, which is then generally the horizontal plane.
The aim of the invention is to remedy the disadvantages of these systems well known in prior art and to construct a driving device of the type described above which prevents friction of the non-motive rollers on the support.
According to the present invention, in order to achieve this, the driving device is characterized by the fact that the discontinuously cooperating driving member is kinematically linked in a constant manner with the motive unit and cooperates with said support, at a peripheral linear speed greater than that of the other driving member and, on account of the fact that this other driving member is linked kinematically with the motive unit by means of a free-wheeling device in such a way that the entry into cooperation with the support of the driving member in constant kinematic linkage with the motive unit automatically brings about the freewheeling of the other driving member and in such a way that the cessation of cooperation with the support of the driving member in constant kinematic linkage with the motive unit automatically brings about the re-establishment of the kinematic linkage of the other driving member with the motive unit.
A system is thus achieved by the present invention which allows, from a single motive source, rigid with the carriage, the latter to be driven alternatively (and not simultaneously) by the driving member in constant kinematic linkage with the motive unit for the sections of the rail where there is cooperation between this driving member and the rail, or by the other driving member for the sections of the rail where there is no cooperation between the rail and driving member in constant kinematic linkage with the motive unit. The system is designed in order that the entry into operation of the constantly linked driving member automatically brings about the disconnection of the other driving member and in such a way that the operating output of the constantly linked driving means automatically brings about the entry into operation of the other driving member.
This automatic alternation must be guaranteed for all slope configurations in the vertical plane and in the two slope directions for the same translational direction. The present invention achieves all of these conditions by a simple combination of exclusively mechanical elements operating as a function of the difference in peripheral linear speed of the constantly linked driving member and of the other driving member, established by extension from a straight route. If the two driving members are simultaneously in cooperating contact with the linear support, and if the moving body moves on a curve section in the vertical plane, the respective peripheral (or circumferential) linear speed of each varies with respect to that of the other, the difference in speed increasing for an upwardly facing concave curve and decreasing for a downwardly facing concave curve.For the operation of the driving device according to the invention, the diameters of the driving members and the transmission ratios from the motive unit to each of the kinematic links connecting the two driving members must be chosen in such a way that the cooperating peripheral linear speed of the driving member in constant linkage with the linear support is greater than the cooperating peripheral linear speed of the other driving member with the upper surface of the rail. This difference in speed must be calculated for a given track in such a way as not to be annulled by the curve of the track situated in the vertical plane, which is concave and faces downwards and which has the smaller radius of curvature.
The free-wheeling device is, preferably, made up of a skew toothed pinion mounted freely rotating and translating on a shaft controlling the other driving member, .e. the driving member controlled by the free-wheeling device and on which two wheels each equipped with a free-wheeling reversely operating system are arranged respectively on each side of said pinion.The pinion on the one hand and the wheels provided on both sides of the pinion on the shaft have their corresponding side faces made up in such a way that the rotation of one wheel or the other is integral with that of the pinion when the latter comes into contact with the former through a lateral translation of the pinion resulting from the direction of rotation received by an upstream pinion driven by the motive unit in such a way that the free wheeling and the re-establishment in kinematic linkage of said other driving member operate identically in the two directions of translation of the moving body. According to this embodiment, the upstream pinion driven by the motive unit is also provided with skew teeth and it is linked to the pinion placed between the two wheels situated on the shaft of the pinion by a skew toothed gear train. The side faces of the central pinion coming into contact according to the direction of rotation with the internal side surfaces of the wheels placed on the shaft of the other driving member are provided with crowns having ramps with a profile corresponding to that of crowns having with which the internal side faces of the above-stated wheels are provided. The direction of interlocking of the ramps is reversed on one side of the pinion with respect to the other side of the pinion. Preferably, the lateral displac-ement travel of the pinion of the free-wheeling device is determined in such a way that the ramps situated on one side of the pinion engage on the ramps of the wheel towards which they move before the ramps situated on the other side of the same pinion disengage completely from the ramps of the wheel from which they move away.
According to one embodiment, the driving member controlled by the free-wheeling device may be made up of a friction roller cooperating with the upper surface of the support -such that the rail, whilst the driving member in constant linkage with the motive unit of the carriage is a sprocket cooperating with a chain longitudinally fixed to the lower side of the support on certain sections only of its length. The chain is preferably arranged and fixed in a lower longitudinal, continuous cavity of the rail, comprising a continuous opening downwards for the passage of the sprocket.
This arrangement allows the risks of humidity, crushing and lodging of foreign bodies to be avoided.
According to another embodiment, the driving member in kinematic linkage with the motive unit is a friction roller coming into joint operation with the lower face of the support only in said certain sections of the route along the support, the support being provided for this purpose with discontinuities in its lower face so that the friction roller of the driving member in constant kinematic linkage with the motive unit turns in empty space along these discontinuities.
The discontinuities may be-fo-rmed by parts of the support of reduced height.
It is understood that the described device is of more general application than that of a load-bearing carriage with a load moving on a rail of varying slopes and can pertain to all systems comprising a moving body moving on a fixed linear support by rotating driving components.
The driving device will now be described in greater detail with reference to the attached drawings where:
Figure 1 represents a moving carriage on a rail having part on a slope and equipped with the driving device according to the invention.
Figure 2 is a schematic representation of the driving device according to the invention.
Figure 2a is a front view in the directions of the arrows a-a of Figure 2, of the wheel equipped with a free-wheeling system and situated on one of the sides of the skew toothed pinion.
Figure 2b is a front view, in the direction of the arrows b-b of figure 2, of the wheel equipped with a free-wheeling system and situated on the other side of the skew toothed pinion.
Figure 3 is a schematic representation of another embodiment.
As shown in Figure 1, a carriage 10 moves on a rail 12 which has a sloping section 12a. A roller chain indicated by the dotted line extends along the sloping section 12a of the rail 12 as well as on the horizontal parts of the rail close to the sloping section.
The carriage 10 is fitted with a geared motor 16 which is linked kinematically in a constant manner to a sprocket 18 arranged so as to engage with the chain 14 when the carriage 10 moves along the rail 12. The geared motor 16 is linked kinematically to a friction roller 20 through a free-wheeling device 22. The friction roller 20 rolls on the upper side of the rail 12 and the chain wheel 18 is received on its lower side in a slot 24, see Figure 2, produced at the lower end of the rail and extending longitudinally along the latter to engage with the chain 14 placed in a cavity 26 of the rail communicating with the longitudinal slot 24.
In Figure 2, the chain 14 is represented by a chain roller 28 mounted for free rotation on a shaft 30. The chain wheel 18 is fixed by wedges on a shaft 30 of the geared motor 16. A skew toothed pinion 32 driven by the geared motor 16 is also fixed by wedges on the shaft 30 of the geared motor 16.
The friction roller 20 for friction driving of the carriage 10 is fixed by wedges on a shaft 34 rotationally mounted in the carriage 10. On this shaft 34 is mounted a skew toothed pinion which is driven in rotation by a skew toothed gear train 38 by the geared motor 16 by means of the pinion 32. The skew toothed pinion 36 can be moved laterally or longitudinally on the shaft 34 and it is free to rotate with respect to this shaft 34. the lateral displacement pinion 36, also called "dog clutch gear" is provided on each of its side faces with a crown of dog clutch ramps 44. On both sides of the lateral displacement pinion 36 two wheels 40 and 42 are arranged, each of which is equipped with a freewheeling system. As shown in Figures 2a and 2b, each wheel 40, 42 equipped with a free-wheeling system, comprises a dog clutch ramp crown 46 mounted on a hub 47 fixed by wedges on the shaft 34.The dog clutch ramps are formed on the sides of the crowns 46 turned towards the dog clutch pinion 36, the dog clutches of the wheel 40 and of the corresponding side of the lateral displacement pinion 36 being oriented in reverse with respect to the dog clutches formed on the other side of the pinion 36 and the corresponding wheel 42. Depending on the direction of rotation, the dog clutch pinion 36 moves in one direction or another on the shaft 34 to engage with the wheel 40 or with the wheel 42 mounted on the shaft 34.
Zone 48 situated between the crown 46 and the hub 47 is filled with plastic~49 and lined with eccentric or non-radial keys 50. If, through its direction of rotation, the pinion 36 interlocks on the wheel 40 or 42, it causes it to turn in the direction of the arrows indicated in Figures 2, 2a and 2b.
If the angular speed of the crown 46 of the wheel 40 or 42 is greater than that of its hub 47, the keys 50 become rigid with the crown 46 or hub 47 to drive it in rotation. In contrast,
if the angular speed of the hub 34 is greater than that of the crown, the system is placed in free wheeling.
The embodiment described above of the free-wheeling systems is non-restrictive. Ball bearing free-wheeling systems could also be provided in placed of the keys embedded
in plastic.
Let us now suppose that he system is placed in movement on a section of the track not provided with chain,a part of which is horizontal. In the absence of chain in the lower cavity 26 of rail 12, the sprocket 18 will turn in empty space, and its movement will not enter in the kinematics of the system.
In this case, the rotation of the motive unit 16 produces the rotation of the dog clutch pinion 36 through that of the intermediate pinions 38. However, whilst the intermediate pinions 38 are jammed in translation on their respective axes, the dog clutch pinion 36 may move towards the left or towards the right on its shaft 34. Owing to the inclination of the teeth of the pinion train,--the dog clutch pinion 36, at the same time as it is driven in rotation, will be subjected to a lateral thrust in one direction or another according to the direction of rotation which will be impressed on it from the motor 16.
On account of this, the dog clutch pinion 36 will engage, according to the direction of rotation, with one or other of the wheels 40, 42, these two wheels 40, 42 being arranged in such a way as to drive, each in a reverse direction to that of the other, the shaft 34 on which the friction roller 20 is fixed by wedges.
If the carriage 10 engages with the edge of a slope, i.e.
on a section of the rail provided with a chain 14, the sprocket 19 will engage on the chain 14. Owing to the fact that its peripheral speed is greater than that of the roller 20, the surplus speed which will occur with respect to the driving speed of the roller 20 will declutch the free-wheeling device 22 which was previously driving the roller 20, thus disconnecting the friction roller 20 from the motive kinematic linkage and thus avoiding skidding of this roller 20 on the rail 12. If the carriage 10 engages, from a horizontal route already provided with a chain, on any slope, it will have to cross a curve situated in the vertical plane and oriented upwards or downwards. According to the direction of orientation of the curve, the difference in linear speed between the two driving members 18, 20 will either increase or decrease.The only constraint of the invention is then to specify the ratio of the two speeds in such a way that their difference is not cancelled out on any curve of the track in question.
If the carriage 10 has rejoined a horizontal section of the rail and leaves the part fitted with a chain, the sprocket 18 loses its motive role and the transmission system reestablishes the linkage between the motor 16 and the friction roller 20.
According to the embodiment shown in Figure 2, the same diameter has been specified for all the pinions, thus establishing a total transmission ratio of 1:1, the difference in linear speed between the sprocket 18 and the friction roller 20 resulting, as from that time, only from the direct ratio of their respective diameters. It is obvious that the necessary difference in the linear speeds could also be
obtained by selecting an appropriate transmission ratio
between the pinion 32 and the dog clutch pinion 36.
As shown in Figure 3, instead of using, for the
discontinuously cooperating driving member, a chain wheel
engaging with a chain of the linear support provided on the
sections of the route where the action of the discontinuously
cooperating driving member is wanted, a friction roller 12'
engaging with the lower side of the rail 12' only on certain
sections of the rail 12' may also be used for the
discontinuously cooperating driving member. To this end, the
rail 12' may have a smaller height formed by the cut-out part
52 of the lower surface of the rail 12' at the places where
the action of the discontinuously cooperating driving member
18' is not wanted. If the carriage is located on a pat of the
rail 12' with a reduced height, the friction roller 18' turns
in empty space as shown by the position in broken lines in
Figure 3.
According to the previous description, the
discontinuously cooperating driving means goes into operation
to drive the carriage on the sloping sections of the rail.
However, on the horizontal sections of the rail, places may
be present where the action of the discontinuously coperating -driving member is desirable. Certain horizontal sections of
the rail may then also be provided with a chain or with a
reduced height of the rail.made up of a cut-out part of the
lower face of the rail.
Claims (9)
1. Driving device for the translation of a moving body such as a carriage, moving on a fixed linear support, such as a rail, comprising two rotating driving members of the moving body moved from the same motive unit, cooperating respectively with the opposite longitudinal faces of the same support, one of which is a discontinuously cooperating driving member which only cooperates on certain sections of its route along the support to move the moving body along the support, characterized by the fact that the discontinuously cooperating driving member is kinematically linked in a constant manner with the motive unit and cooperates with said support, at a peripheral linear speed greater than that of the other driving member and, on account of the fact that this other driving member is linked kinematically with the motive unit by means of a free-wheeling device in such a way that the entry into cooperation with the support of the driving member in constant kinematic linkage with the motive unit automatically brings about the free-wheeling of the other driving member and in such a way that the cessation of cooperation with the support of the driving. member in constant kinematic linkage with the motive unit automatically brings about the re-establishment of the kinematic linkage of the other driving member with the motive unit.
2. Driving device according to Claim 1, characterized in that the free-wheeling device is made up of a central skew toothed pinion mounted freely rotating and translating on a control shaft of said other driving member, and on which two wheels each equipped with a free-wheeling reversely operating system are arranged respectively on each side of said pinion, said pinion on the one hand and said wheels on the other hand having their corresponding side faces made up in such a way that the rotation of one or other of the two wheels is integral with that of the pinion when the latter comes into contact with the former through its lateral translation on the shaft on the side resulting from the direction of rotation received by an upstream pinion driven by the motive unit in such a way that the free wheeling and re-establishment in kinematic linkage of said other driving member operates identically in the two directions of translation of the moving body.
3. Device according to Claim 1 or 2, characterized in that the side faces of the central pinion coming into contact, as the case may be, with the internal side surfaces of the two wheels are provided with crowns having ramps with a profile corresponding to that of crowns having ramps with which the internal side faces of said wheels are provided, ramps whose direction of interlocking is reversed on one side of the central pinion with respect to the other in the direction where the interlocking is produced from the translation and rotation movements of the central pinion.
4. Device according to Claim 3, characterized in that the lateral displacement travel of the central pinion of the freewheeling device is determined in such a manner that the ramps situated on one side of the central pinion above engage on the ramps of the wheels towards which it moves before the ramps situated on the other side of the same central pinion disengage completely from the ramps of the wheel from which it moves away.
5. Device according to Claim 2 or 4, characterized in that the driving member controlled by the free-wheeling device is a friction roller cooperating with the upper face of the support such as a rail but that the driving member in constant linkage with the motive unit is a sprocket cooperating with a chain fixed longitudinally to the lower side of the support on certain sections-only of its length.
6. Device according to Claim 5, characterized in that the chain is arranged and fixed in a lower longitudinal and continuous cavity of a rail, comprising a continuous opening downwards for the passage of the sprocket.
7. Device according to Claim 1, characterized in that the diameter of the driving member in constant kinematic linkage with the motive member, the diameter of said other driving member and the transmission ratio of the kinematic linkage between the motive unit and said other driving member are chosen in such a way that, at any point whatever of the support, the circumferential speed of the driving member in constant kinematic linkage with the motive unit is always greater than the circumferential speed of said other driving member.
8. Device according to Claim 1, characterized in that the driving member in constant kinematic linkage with the motive unit is a friction roller cooperating with the lower face of the support only in said certain sections of the route along the support, the support being provided for this purpose with discontinuities in its lower face between said sections in such a way that the friction wheel of the driving member in constant kinematic linkage with the motive unit turns in empty space along these discontinuities.
9. Device according to Claim 8, characterized in that the discontinuities are formed by parts of reduced height of the support.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR9304950A FR2704506B1 (en) | 1993-04-27 | 1993-04-27 | DEVICE FOR DRIVING A MOBILE ON A LINEAR SUPPORT. |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB9407970D0 GB9407970D0 (en) | 1994-06-15 |
| GB2277499A true GB2277499A (en) | 1994-11-02 |
Family
ID=9446482
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9407970A Withdrawn GB2277499A (en) | 1993-04-27 | 1994-04-21 | Device for driving a carriage along a rail |
Country Status (2)
| Country | Link |
|---|---|
| FR (1) | FR2704506B1 (en) |
| GB (1) | GB2277499A (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2541733A1 (en) * | 1975-09-19 | 1977-03-24 | Demag Ag | Conveyor rail trolley with gear drive for inclines - has gear linked to motor by free wheeling unit for smoother drive change |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1490620A (en) * | 1966-06-20 | 1967-08-04 | Noirot Et Fils Et Cie | Improvements to suspended air carriers |
| DE3403460A1 (en) * | 1984-02-01 | 1985-08-08 | Georg 8200 Rosenheim Uttscheid | ELECTRIC RAILWAY |
-
1993
- 1993-04-27 FR FR9304950A patent/FR2704506B1/en not_active Expired - Fee Related
-
1994
- 1994-04-21 GB GB9407970A patent/GB2277499A/en not_active Withdrawn
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2541733A1 (en) * | 1975-09-19 | 1977-03-24 | Demag Ag | Conveyor rail trolley with gear drive for inclines - has gear linked to motor by free wheeling unit for smoother drive change |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2704506A1 (en) | 1994-11-04 |
| GB9407970D0 (en) | 1994-06-15 |
| FR2704506B1 (en) | 1995-07-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |