EP1860051B1 - Elevator with Frictional Drive - Google Patents
Elevator with Frictional Drive Download PDFInfo
- Publication number
- EP1860051B1 EP1860051B1 EP20070108660 EP07108660A EP1860051B1 EP 1860051 B1 EP1860051 B1 EP 1860051B1 EP 20070108660 EP20070108660 EP 20070108660 EP 07108660 A EP07108660 A EP 07108660A EP 1860051 B1 EP1860051 B1 EP 1860051B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- elevator
- lever
- track
- frictional engagement
- car
- 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.)
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- 230000001133 acceleration Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B9/00—Kinds or types of lifts in, or associated with, buildings or other structures
- B66B9/02—Kinds or types of lifts in, or associated with, buildings or other structures actuated mechanically otherwise than by rope or cable
Description
- The invention relates to an elevator and, more particularly, to an elevator frictionally driven along a track.
- A frictionally driven elevator is described in
EP-A1-0870718 in which a drive wheel and a support wheel are rotatably mounted on levers which are pivotally attached to a lower yoke of a car frame. A compression spring biases the support wheel towards the drive wheel thereby clamping a track therebetween. The compression spring provides a constant normal force to ensure that there is sufficient frictional engagement between the drive wheel and the track during all operating conditions. This constant normal force is determined from the critical operating condition when the elevator car is fully loaded and moving upwards at maximum acceleration. - An objective of the present invention is to provide alternative ways of clamping the frictional drive to the track. This objective is achieved by an elevator according to
claim 1 of the present invention. - Accordingly, the driven frictional engagement means are self-gripping against a track. This effect is achieved primarily by converting the effective weight of the moving component into normal force acting on the frictional engagement means.
- The present invention is herein described by way of specific examples with reference to the accompanying drawings in which:
-
Figure 1 is a partial plan view of an elevator according to a first embodiment of the present invention; -
Figure 2 is an exploded view of the frictional drive unit of the elevator ofFig. 1 ; -
Figure 3 is a diagram representing the forces acting on the drive unit ofFig. 2 ; -
Figure 4 is a plan view of an elevator according to a second embodiment of the invention; -
Figure 5 is an exploded view of the frictional drive unit of the elevator ofFig. 4 ; -
Figure 6 is a plan view of an alternative frictional drive unit according to a third embodiment of the invention; and -
Figures 7A to 7C are plan views of a frictional drive unit according to a fourth embodiment of the invention in different operating conditions. - A self-propelled
elevator 1 according to the invention is shown schematically inFigs. 1 and 2 . Theelevator 1 comprises acar 2 which is driven by africtional drive unit 10 along avertical track 6 mounted in ashaft 4. Thedrive unit 10 comprises a pair of drivenwheels track 6 to frictionally engage opposing sides of thetrack 6. The wheels can be rotated in a conventional manner by one or two motors (not shown). Thewheels levers hinge 20 from which thecar 2 is suspended. Each of the levers is inclined at an angle α1 to the horizontal H. - The forces acting on the
frictional drive unit 10 are illustrated inFig. 3 . The total weight of the car mcg is transmitted through thesymmetric levers wheels track 6. The total frictional force Ff of thedrive unit 10 is a combination of the individual frictional forces and the motive forces M developed by thewheels track 6. The difference between the total frictional force Ff and the weight mcg provides the necessary elevator acceleration A. - To determine an acceptable range for the angle α which ensures that the driven
wheels track 6 it is necessary to consider theelevator 1 at rest. In this condition, thewheels wheels track 6 and therefore the total stationary frictional force Ffstat is developed solely from the normal forces N applied to thetrack 6 from thewheels car 2 for all loads otherwise thedrive unit 10 will slip. This condition is expressed mathematically in Eqn. 1.
However since the total frictional force Ffstat is derived solely from the normal forces N, the equation can be rewritten in the following sequences: - Considering a specific application where the
car 2 has a mass of 200kg and a rated load of 450kg, the coefficient of friction µ1 between thetrack 6 and each of the drivenwheels -
-
- On the contrary, if the prior art frictional drive of
EP-A1-0870718 is used for the same system, the biasing spring must exert constant force equal to the maximum normal force Nmax (1028N) through the wheels during all operating conditions which ultimately reduces the lifespan of the wheels. -
Figs. 4 and5 illustrate an alternative embodiment of the present invention wherein africtional drive unit 30 is used to drive a counterbalanced elevator 1'. As in the previous embodiment, thedrive unit 30 comprises a pair of drivenwheels track 6 to frictionally engage opposing sides of thetrack 6. Thewheels levers first hinge 20 from which thecar 2 is suspended. Each of thelevers drive unit 30 also includes a second pair oflevers levers levers second hinge 32 which is disposed above thefirst hinge 20. Thesecond hinge 32 is attached by arope 22 which is deflected over one ormore pulleys 24 mounted in the top of theelevator shaft 4 to acounterweight 8. - Using the same parameters from the last embodiment and assuming the mass of the counterweight mW is the mass of the car (200kg) plus half the rated load (225kg), the maximum normal force Nmax developed by each of the
wheels car 2 is fully loaded (mcmax= 650kg) and travelling upwards at full acceleration: -
-
Fig. 6 show an alternativefrictional drive unit 40 which can be used in theelevator 1 ofFig. 1 or in the counterbalanced elevator 1' ofFig. 4 . Thedrive unit 40 has a similar arrangement to that ofFig. 5 with the exception that apassive support roll 40 replaces one of the drivenwheels wheel 12 is mounted on alower lever 16 and anupper lever 36 at one side of thetrack 6. Each of thelevers wheel 12 is inclined at an angle α2 to the horizontal H. Thepassive roll 40 is mounted at the opposing side of thetrack 6 on alower support lever 46 and anupper support lever 48. Thelower levers first hinge 20, while theupper levers second hinge 32. - Since the
passive support roll 44 generates no frictional force against thetrack 6, the single drivenwheel 12 is responsible for developing the total frictional force Ff for driving, holding and braking theelevator 1,1'. Accordingly,equations 1 to 4 need to be modified and thedrive unit 40 is self-clamping so long as the following expression is fulfilled: - Hence, if the coefficient of friction µ1 between the
track 6 and the drivenwheel 12 is 0.3 as in the previous embodiments, then the angle α2 at which each of thelevers wheel 12 is inclined to the horizontal H must be equal to or less than 8.5°. The angle β1 at which each of thelevers roll 44 is inclined to the horizontal H is not critical since thesupport roll 44 generates no frictional force against thetrack 6. - In a typical application, the
car 2 is suspended from the first hinge 20 (as inFigs. 1 and4 ) and, if present, acounterweight 8 can be interconnected to the second hinge 32 (as inFig. 4 ). -
Figs. 7A to 7C illustrate africtional drive unit 50 according to the presently preferred embodiment of the invention. Thedrive unit 50 comprises a pair ofbelt drives track 6 to frictionally engage opposing sides of thetrack 6. Eachbelt drive toothed drive wheel 56 which engages with a toothed internal surface of anendless belt 58. Thebelt 58 passes around adeflection roller 60 to come into engagement with thetrack 6, along pressingrollers 62 spring biased towards the track, and comes out of engagement with thetrack 6 at asecond deflection roller 60 where it is returned to thedrive wheel 56. - The
rollers retainer 64 which is pivotally mounted on alower lever upper lever lower levers first hinge 20 and theupper levers second hinge 32 arranged vertically above thefirst hinge 20. Each of thelevers equation 1. As shown specifically inFig. 7C , acompression spring 72 biases thefirst hinge 20 and thesecond hinge 32 apart. - The
drive unit 50 is particularly useful in a counterbalanced elevator 1' such as that shown inFig. 4 . However, instead of connecting thecar 2 directly to thefirst hinge 20 and thecounterweight rope 22 to thesecond hinge 32, both thecar 2 and thecounterweight rope 22 are connected to aconnector 66. Accordingly, the effective weight g(mw-mc) acting on theconnector 66 is the imbalance between the weights of thecar 2 and thecounterweight 8. - The
connector 66 includes afirst recess 68 retaining thefirst hinge 20 and asecond recess 70 retaining thesecond hinge 32. As illustrated inFig. 7A , when thecar 2 is empty, thecounterweight 8 is heavier than thecar 2 and this imbalance in the respective weights acts as an upwards force g(mw-mc) on theconnector 66. Theconnector 66 in turn engages with thesecond hinge 32 to impart forces through theupper levers roller retainers 64. These imparted forces are converted by therollers belts 58 into frictional engagement with the respective sides of thetrack 6. During this procedure, thefirst hinge 20 is loosely retained in itsrecess 68 and a clearance C between theconnector 66 and thefirst hinge 20 ensures there is no force transmission therethrough. -
Fig. 7B illustrates the reverse situation when thecar 2 is fully loaded and the weight imbalance acts as a downwards force g(mc-mw) on theconnector 66. Theconnector 66 engages with thefirst hinge 20 to impart forces through thelower levers roller retainers 64. These imparted forces are converted by therollers belts 58 into frictional engagement with the respective sides of thetrack 6. During this procedure, thesecond hinge 32 is loosely retained in itsrecess 70 and a clearance C between theconnector 66 and thesecond hinge 20 ensures there is no force transmission therethrough. - When the
car 2 and thecounterweight 8 are balanced and stationary, as shown inFig. 7C , there is no effective weight acting on theconnector 66. Thecompression spring 72 ensures that thebelts 58 remain in engagement with thetrack 6 by counteracting any weight component ofroller retainers 64 or any elasticity in thebelts 58 which would otherwise tend to draw thebelts 58 away from thetrack 6. Once, thedrive 50 unit commences to move, one of thehinges connector 66 and forces will be transmitted through the levers, retainers and rollers to develop normal forces between thebelts 58 and thetrack 6. - Considering a specific application where the
car 2 again has a mass of 200kg and a rated load of 450kg, the mass of the counterweight mw is 425kg, the maximum acceleration A is 2m/s2 and the coefficient of friction µ3 between thetrack 6 and each of thebelts 58 is 0.2. For self-gripping, the angle α3 must be equal to or less than 11.3° (arctan 0.2) and in this instance is set to 10°. -
- Assuming that this is distributed evenly over the
rollers roller - The skilled person will readily appreciate that specific elements of any one of the embodiments described above can be substituted with corresponding elements from another embodiment to give a new variant of the invention. For example, any of the driven
wheels Figs. 2 ,5 or 6 can be replaced by abelt drive Figs. 7A-7C and vice versa. Similarly, either of the belts drives 52,54 ofFigs. 7A-7C can be substituted with a passive support roller ofFig. 6 provided that the angle α3 is modified accordingly.
Claims (12)
- An elevator (1,1') comprising a movable component (2,8,22,66), a vertical track (6) mounted along an elevator shaft (4), driven frictional engagement means (12;58,60,62,64) for frictional engagement with one side of the track (6) with a first coefficient of friction (µ1;µ3), and support means (14;44;58,60,62,64) disposed on an opposite side of the track (6) wherein
the frictional engagement means (12;58,60,62,64) is pivotally mounted on at least one first lever (16;36),
the support means (14;44;58,60,62,64) is pivotally mounted on at least one second lever (18;38), and
the at least one first lever (16;36) and the at least one second lever (18;38) are interconnected to pivotally support an effective weight (mg) of the movable component (2,8,22,66)
whereby the first lever (16;36) makes a first angle (a1;a2;a3) with the horizontal (H) characterised in that
a tangent of the first angle (a1;a2;a3) is less than or equal to the first coefficient of friction (µ1;µ3). - An elevator (1,1') according to claim 1, wherein the frictional engagement means is a friction wheel (14).
- An elevator according to claim 1, wherein the frictional engagement means includes a plurality of rollers (60,62) pressing a motor driven belt (58) into engagement with the track (6).
- An elevator according to claim 3, wherein the rollers (60,62) are housed in a retainer (64) and at least one of the rollers (62) is spring biased towards the track (6).
- An elevator according to any preceding claim having a single first lever (16) and single second lever (18) interconnected at a first hinge (20) which supports the weight (mcg) of an elevator car (2) and wherein the support means is a second driven frictional engagement means (14;58,60,62,64).
- An elevator according to any of claims 1 to 4, wherein the frictional engagement means is pivotally mounted on an upper first lever (38) and a lower first lever (16) arranged symmetrically about the horizontal (H) at the first angle (a1;a2;a3), the support means (14;44;58,60,62,64) is pivotally mounted on an upper second lever (38) and a lower second lever (18) arranged symmetrically about the horizontal (H) at a second angle (a1;β;a3), the lower levers (16,18) are interconnected at a first hinge (20), and the upper levers (36,36) are interconnected at a second hinge (32).
- An elevator according to claim 6, wherein the moving component is an interconnected elevator car (2) and counterweight (8), whereby the car (2) is connected to one of the first and the second hinges (20,32) and the counterweight (8) is connected to the other of the first and the second hinges (32,20).
- An elevator according to claim 6, wherein the moving component is a connector (66) interconnecting an elevator car (2) to a counterweight (8), whereby the connecter (66) selectively engages with the first and the second hinges (20,32) depending on a weight imbalance between the car (2) and the counterweight (8).
- An elevator according to claim 8 further comprising biasing means (72) to bias the first and the second hinges (20,32) apart.
- An elevator according to any of claims 6 to 9, wherein the support means is a roll (44).
- An elevator according to any of claims 6 to 9, wherein the support means is a second driven frictional engagement means (14;58,60,62,64).
- An elevator according to claim 11, wherein the second driven frictional engagement means (14;58,60,62,64) engages the opposite side of the track (6) with a second coefficient of friction (µ1;µ3), and a tangent of the second angle (a1;a3) is less than or equal to the second coefficient of friction (µ1;µ3).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20070108660 EP1860051B1 (en) | 2006-05-24 | 2007-05-22 | Elevator with Frictional Drive |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06114506 | 2006-05-24 | ||
EP20070108660 EP1860051B1 (en) | 2006-05-24 | 2007-05-22 | Elevator with Frictional Drive |
Publications (2)
Publication Number | Publication Date |
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EP1860051A1 EP1860051A1 (en) | 2007-11-28 |
EP1860051B1 true EP1860051B1 (en) | 2010-10-06 |
Family
ID=38621826
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20070108660 Active EP1860051B1 (en) | 2006-05-24 | 2007-05-22 | Elevator with Frictional Drive |
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Country | Link |
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EP (1) | EP1860051B1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU2637702C2 (en) * | 2016-05-26 | 2017-12-06 | Алексей Иванович Карпенков | Friction drive of vertical hoist carriage |
US20210221647A1 (en) * | 2020-01-21 | 2021-07-22 | Otis Elevator Company | Climbing elevator with load-based traction force |
US11584621B2 (en) * | 2020-07-30 | 2023-02-21 | Otis Elevator Company | Autonomous elevator car movers and traction surfaces therefor, configured with traction increasing and guidance enhancing implements |
US20220048729A1 (en) * | 2020-08-17 | 2022-02-17 | Otis Elevator Company | Autonomous elevator car mover configured for self-learning gap control |
US11673773B2 (en) * | 2020-11-07 | 2023-06-13 | Otis Elevator Company | Ropeless elevator propulsion system |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES2042805T3 (en) * | 1988-03-03 | 1993-12-16 | Schaffer Dagmar | ELEVATOR WITHOUT MACHINE ROOM. |
EP0681984A1 (en) * | 1994-05-13 | 1995-11-15 | Inventio Ag | Self-propelled elevator |
DE4418480A1 (en) * | 1994-05-27 | 1995-11-30 | Hillenkoetter & Ronsieck | Vertical elevator |
EP0870718B1 (en) * | 1997-04-11 | 2003-06-25 | Inventio Ag | Gripping device for anchoring a lift cabin |
DE10140390B4 (en) * | 2001-08-23 | 2005-12-01 | HIRO LIFT Hillenkötter + Ronsieck GmbH | vertical lift |
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2007
- 2007-05-22 EP EP20070108660 patent/EP1860051B1/en active Active
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EP1860051A1 (en) | 2007-11-28 |
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