[0001] The present invention relates to sliding door operator apparatus.
[0002] The invention is particularly applicable to sectional overhead doors of the multiple
panel type and will be described with particular reference thereto. However, the invention
has broader applications and may also be adapted for use in many other environments,
such as single panel overhead doors and even sideward sliding doors or the like.
[0003] Most overhead doors are counterbalanced by a torsion spring or a counterweight system
for storing energy during door closing, which energy may be released during door opening.
During opening, most of the energy for lifting such a door is derived from the energy
stored in the spring or counterweight system. If the door is accurately counterbalanced,
the amount of manual energy required to open the door need only be sufficient to overcome
the frictional and other losses in the system. During door closing, the energy required
is that for overcoming the frictional and other losses since most of the energy which
is transferred to the spring or counterweight storage system is derived from the weight
of the descending door.
[0004] In general, conventional overhead doors of this nature are actuated by a cable which
is wound around a drum, axially driven by the torsion spring, with the drum being
rotated by a chain driven sprocket. Generally, the chain is driven by an electric
motor. In some environments, however, the use of electrical motors is undesirable
because of the possible danger of a spark causing an explosion or a fire. It has also
been found that electric motors are disadvantageous since, if the door becomes jammed,
the motor will continue rotating and will probably cause the cable between the drum
and the door to unwind which could prove hazardous to personnel and may also damage
property.
[0005] Also, when such doors are used frequently, such as in car washes or the like, the
chains, sprockets, electrical motors, and bearings wear out at a relatively rapid
rate and this results in frequent breakdowns of the door opening mechanism. Moreover,
malfunctions of the door opening mechanism may also lead to damage to the upper portion
of the door which can be relatively expensive to repair.
[0006] One recent suggestion has been to utilize a pair of pneumatic cylinders in a side
mounted operator for moving the chain of the chain driven sprocket thereby rotating
the sprocket. However, side mounted operators are disadvantageous since any interruption
in the door travel results in an unwinding of the cable from the torsion bar drum
which makes the door liable to a free fall that could cause grave injury to people
as well as damage to objects under the door and to the door itself. The pneumatic
cylinder actuated side mounted operator mechanism is also disadvantageous since chains
and sprockets which undergo a high number of cycles wear out at a relatively rapid
rate resulting in frequent breakdowns of the door operator mechanism and, sometimes,
damage to the door.
[0007] Accordingly, it would therefore be advantageous to develop a new and improved door
operator system which may overcome the foregoing difficulties, and others, while providing
improved and more advantageous overall results.
[0008] US-A-2 710 186 discloses a sliding door operator system according to the pre-characterising
portion of Claim 1, which comprises a fluid cylinder mechanism having a rodless piston
reciprocable in the cylinder body which is adapted to be coupled to the sliding door
and control means for controlling the operation of the fluid cylinder and hence the
position of the sliding door. The invention as defined by the features in the characterizing
part of Claim 1 is characterised in that the piston is secured to a carriage reciprocable
externally along the length of the cylinder body and in that arm means comprising
a pair of telescoped tubular sections are provided for connecting the carriage to
the sliding door with the first of said tubular sections being pivotably secured to
said fluid cylinder carriage and a second of said tubular sections being pivotably
secured to the associated sliding door and a resilient shock absorber means for cushioning
the telescope action of the tubular sections.
[0009] In accordance with another aspect of the present invention, the system further comprises
a bracket means for securing the fluid cylinder to an adjacent wall.
[0010] In accordance with still another aspect of the present invention, the system further
comprises a switch means located at each end of the cylinder with the switch means
being in electrical contact with the control means to activate associated electrical
equipment.
[0011] In accordance with yet still another aspect of the present invention, the control
means comprises a source of pressurized fluid and a conduit means for connecting the
source of pressurized fluid to the fluid cylinder. A control panel is also provided
for controlling the flow of pressurized fluid through the conduit means.
[0012] In accordance with a further aspect of the present invention, the source of pressurized
fluid is in fluid communication with both ends of the fluid cylinder so that it can
act on either end of the rodless piston. Preferably, the cylinder is provided with
seal means for preventing the pressurized fluid from flowing out of the cylinder.
Preferably, both ends of the fluid cylinder also include an adjustable valve means
communicating with the environment.
[0013] One advantage of the present invention is the provision of a door operator system
which actuates a door by the movement of a rodless piston which reciprocates in a
cylinder.
[0014] Another advantage of the present invention is the provision of a door operator system
which can actuate most types of overhead doors that have a counterbalance means and
can also actuate selected sideward sliding doors.
[0015] Yet another advantage of the present invention is the provision of a trolley-type
door operator system which eliminates the need for chains, sprockets, bearings, and
motors, all of which are prone to breakdowns when frequently used.
[0016] A further advantage of the present invention is the provision of a door operator
system which opens and closes a door with a minimum of force thereby preventing injury
to persons or damage to objects which are inadvertently positioned in the path of
the door when the door is being moved.
[0017] The invention is described further hereinafter, by way of example only, with reference
to the accompanying drawings, in which:-
Fig. 1 is a perspective view of one embodiment of a door operator system according
to the present invention in conjunction with a door of a building;
Fig. 2 is a side elevational view of the door operator system of Fig. 1;
Fig. 2A is an enlarged side elevational view, partially in cross-section, of an arm
member of the door operator system of Fig. 2;
Fig. 3 is an enlarged side elevational view, partially in cross-section, of the cylinder
of Fig. 1; and
Fig. 4 is a cross-section through the line 4-4 of Fig. 3.
[0018] Fig. 1 shows a door operator system A as it is utilized on a door B which closes
an opening in a building C. While the door operator is primarily designed for and
will hereinafter be described in connection with a sectional overhead sliding door,
it should be appreciated that the overall inventive concept involved could be adapted
for use with many other overhead and sideward sliding door arrangements.
[0019] With reference to Fig. 3, the operator system A includes a cylinder member 10 which
comprises a tubular body 12 that has an outer periphery 13 having two spaced substantially
square sides and two spaced rounded sides (Fig. 4) and a longitudinal bore 14 extending
therethrough. A first end of the bore is closed by a first end cap member 16 and a
second, opposite, end of the bore 14 is closed by a second end cap member 18. Suitable
fasteners 20 secure the first and second end caps 16,18 to the tubular body 12. A
suitable seal means 22 is provided for each of the end caps 16,18 to prevent pressurized
air from leaking therethrough.
[0020] As shown in Fig. 4, a slot 24 extends longitudinally along one of the square sides
of the tubular body 12 to allow the bore 14 to communicate with the environment. A
pair of spaced sealing bands or strips 25,26 seal the slot 24 to isolate the bore
14 and prevent pressurized fluid from leaking therethrough. The bands are secured
to the two end caps 16,18.
[0021] A piston body 30 is adapted to reciprocate longitudinally in the bore 14 of the cylinder
which piston body comprises a pair of identical opposing sections 32,34 which are
joined together in a suitable conventional manner. A seal means 36 extends peripherally
around each section 32,34 of the piston to provide a seal between the piston section
and the cylinder bore 14.
[0022] A piston bracket 38 (Fig. 4) is secured at a yoke-like section 39, by suitable conventional
fasteners 40, to the first and second sections 32,34 and is adapted to extend through
the cylinder slot 24. A section 41 of the bracket 38 is positioned outwardly of the
tubular body 12 and extends substantially along the width of one face thereof as is
illustrated in Fig. 4. It can be seen that the bracket 38 is substantially T-shaped,
with the section 41 of the T-shape extending outside of the cylinder tubular body
12. This outer section 41 has depending sides 42, to each of which an inwardly extending
bearing rod 44 is secured. The bearing rods slide in suitably configured grooves 46
formed in the outer periphery 13 of the tubular body so as to allow a smooth sliding
motion of the piston bracket 38 as the piston moves. This system allows the cylinder
10 to withstand high axial and radial loads and moments, while eliminating the requirement
for external guides and supports.
[0023] A carriage 50 is secured to a pair of spaced depending flanges 48 of the piston bracket
38 by suitable conventional fasteners 49. The carriage has a base wall 52, a pair
of side walls 54, and a pair of opposing end walls 56. Seal means 58 in the form of
wiper seals are provided on the end walls 56 of the carriage and act to clean the
second seal band 26 of the cylinder 10.
[0024] With reference to Fig. 2, a shock absorbing connecting means such as an arm means
70 is secured to the carriage 50 in suitable conventional manner. The arm means can
be substantially L-shaped as illustrated and includes a first tubular arm member 72
which is secured by a bracket 74 to the carriage 50. Preferably, a fastener 76 which
enables a pivoting motion of the arm member 72 with respect to the bracket 74 is provided
for securing the arm member to the bracket.
[0025] A second arm member 78, having a first section 80 and a second section 82 which is
disposed at an approximately 90° angle to the first section is also provided. The
second arm member 78 is secured to a bracket 84 by a suitable fastener 86. The bracket
84 is in turn secured to the door B as shown in Fig. 1. Preferably, the fastener 86
enables a pivoting motion of the second arm member 78 with respect of the bracket
84.
[0026] With reference now to Fig. 2A, a slot 90 extends in a portion of the second arm member
as is illustrated. A stem portion 92 of the first arm member 72 extends outwardly
through the slot 90 of the second arm member. As such, a limit means is provided for
the telescopic action of the first arm 72 in the second arm 78. Preferably, a rod
member 94 extends downwardly from the first arm member 72. In order to provide a resilient
biasing means for the arm 70, a spring 96 is disposed within the first section 80
of the second arm member 78 beneath the first arm 72 such that the rod 94 of the first
arm extends thereinto. This positions the spring correctly in relation to the first
arm member. Preferably, the spring 96 is a compression spring which resiliently biases
the telescopic motion of the first arm member 72 into the second arm member 78.
[0027] The arm means 70 also acts as a shock absorber during movement of the door B due
to the positioning of the compression spring 96 between the telescopic pair of members
72,78. As is evident from Fig. 2, it is necessary for the arm means 70 to pivot in
relation to both the door B and the cylinder 10 during the travel of the door from
the closed position to the open position, and vice versa.
[0028] With reference again to Fig. 1, a mounting pad 100 is secured to a first end of the
cylinder 10, with a front mounting bracket 102 securing the mounting pad and hence
the cylinder to a suitable wall of the building C. A rear mounting bracket 104 is
secured to the cylinder and a pair of hangers 106 are fastened to the mounting bracket
and to the adjacent ceiling (not illustrated).
[0029] Preferably, the door B includes a door member 110 comprising a plurality of articulated
longitudinally extending slats or planks. The door is adapted to slide up and down
on a pair of spaced tracks 112, only one of which is illustrated in Fig. 1. In general,
doors of this nature conventionally include a counterbalancing means such as an axial
torsion spring 114 which is secured above the door B. Co-operating with the torsion
spring is a cable 116 which is secured on a first end to the door B (not visible in
Fig. 1) and wound at its second end on a drum 118 axially driven by the torsion spring
114.
[0030] In order to actuate the cylinder 10, a pressurized fluid circuit 120, preferably
pneumatic, is provided. The circuit includes a first fluid conduit 122 and a second
fluid conduit 124 each of which is contiguous with a respective end of the cylinder
through the cylinder end caps 16,18. A source of pressurized fluid 126 such as a compressor
is contiguous with a respective one of the conduits 122,124 as directed by a control
means 130. The control means can be in the form of a control panel which is interposed
between the conduits 122,124 and the source 126 in order to control the movement of
the rodless piston in the cylinder.
[0031] The control means 130 can be either a straight pneumatic control provided with a
conventional three position directional valve that includes open, close, and stop
(not shown) or a conventional control module with electrical push buttons for the
operations open, close, and stop.
[0032] A bore 140 in the first end cap 16 enables pressurized fluid from the first conduit
122 to enter one end of the cylinder behind the piston first section 32 to urge the
piston 30 toward the second end cap 18 of the cylinder. The second conduit 124 extends
longitudinally down the cylinder 10 and is secured thereto by suitable hose clamps
142. The second conduit 124 communicates through a bore 144 in the second end cap
18 with the second end of the cylinder. A suitable conventional adjustable valve means
such as a needle valve, of which a bore 146 is illustrated, can be provided in each
end cap 16,18 to cushion the movement of the piston 30 adjacent the two ends of the
cylinder.
[0033] As shown in Fig. 2, if desired, suitable conventional micro switches 150,152 can
be secured to the end caps 16,18 to activate additional electronic functions in conjunction
with the opening and closing of the door is desired. The micro switches 150,152 are
connected to the control means 130 by suitable wiring 154. Alternatively, proximity
switches can be utilized at the ends of the cylinder. Also, conventional magnetic
reed switches could be positioned alongside the cylinder for position sensing of the
piston between the ends of the cylinder.
[0034] When a pressurized fluid such as compressed air or another suitable compressed gas
is supplied by the pressurized fluid source 126 and the control means 130 is switched
to a door open position, the rodless piston 30 and its attached carriage 50 are urged,
by pressurized air flowing through the first end cap 16, to move from a front end
of the cylinder 10 towards a rear end thereof. At this time the air supply port 144
and the second conduit 124 act as an exhaust means for the air flowing from a section
of the cylinder between the second piston section 34 and the end cap 18 through the
control means 130 to the environment. The carriage 50 thus moves pulling the door
B with it thereby opening the door. The piston 30 slows down just before contacting
the cylinder body second end cap 18, the speed of movement of the piston 30 adjacent
the end caps 16,18 being regulated by means of the adjustable valve means. Generally,
the piston's speed of movement can be regulated through the directional valve in the
control means 130.
[0035] The piston 30, and hence the carriage 50 remains under pressure while the door B
is in the open position until the control means 130 receives a signal electrically
or manually to shift to another position.
[0036] When the valve 130 shifts to the closing position, the bore or port 144 in the rear
end cap 18 becomes an air supply while the bore or port 140 in the front end cap 16
becomes the exhaust. Therefore, the speed with which the door closes can be different
from the speed with which the door opens. In some cases, for example in automated
car washes, the door B is required to open relatively rapidly. This operating speed
can be regulated by the adjustable valve means such as by adjusting the conventional
exhaust restrictors of the directional valve in the control means 130. On the other
hand, for safety reasons, the closing cycle may be required to be at a normal speed,
which is, at a maximum, approximately 1 second per foot (0.31 m per sec.) as is recommended
by the Canadian Door Institute.
[0037] However, the door's speed could be set to slow, normal, or rapid speed to suit the
particular door application involved. This setting can be achieved through an adjustment
in the combination of the air flow and the exhaust restrictors. To stop the door at
any intermediate position, it is merely necessary to change the three position control
valve to a neutral or stop position in which it will block the flow of pressurized
air to either end of the cylinder 10. Also, the motion of the door can instantly be
reversed by causing the directional valve to shift from one direction to the other.
This can be done either manually or electrically depending upon the type of controls
used.
[0038] Since the cylinder 10 operates with a low volume of pressurized gas or air, the cylinder
does not move with enough force to cause damage to the door. More importantly, the
door does not move with enough force to cause damage to objects or be hazardous to
personnel.
[0039] When the cylinder 10 reaches the end of its stroke, the door will be in a closed
position and will be locked automatically without any additional locking mechanism
being necessary since the arm means 70 will be located at a 90° angle to the door
B as is indicated in Figs. 1 and 2. Thus, if it was attempted to force the door open,
the arm means 70 would simply be forced against the cylinder 10 and the door would
not open.
[0040] The cylinder 10, carriage 50, and end caps 16,18 may all be made from any suitable
material such as anodized aluminium. The piston 30 and the piston bracket 38 may be
made from a suitable conventional material such as aluminium or steel. The sealing
bands 25,26 may be made from a high density oil, resistant plastic, or another suitable
material and the various seals may be made from Buna N or another suitable rubber.
One such suitable cylinder assembly is sold by the Norgren Martonair Co. under the
designation LINTRA C/45000.
[0041] The present invention thus provides a door operator system which minimizes frequent
breakdowns, hazard to personnel, and damage to the door or objects which might be
in the way of the door. Such a door operator may also have a greatly improved life
cycle in relation to the conventional electrically driven chain drive trolley door
operators.
1. A sliding door operator system which comprises a fluid cylinder mechanism (10) having
a rodless piston (30) reciprocable in the cylinder body (12) which is adapted to be
coupled to the sliding door and control means for controlling the operation of the
fluid cylinder (10) and hence the position of the sliding door, characterised in that
the piston (30) is secured to a carriage (50) reciprocable externally along the length
of the cylinder body (12) and in that arm means (70) comprising a pair of telescoped
tubular sections (72, 78) are provided for connecting the carriage (50) to the sliding
door with the first (72) of said tubular sections being pivotably secured to said
fluid cylinder carriage (50) and a second (78) of said tubular sections being pivotably
secured to the associated sliding door and a resilient shock absorber means for cushioning
the telescope action of the tubular sections (72, 78).
2. A system as claimed in claim 1 further comprising bracket means (102) for securing
said fluid cylinder (10) to an adjacent wall.
3. A system as claimed in claim 1 or 2 further comprising a swtich means (150, 152) located
at each end of said cylinder (10), each of said switch means (150, 152) being in electrical
contact with said control means to activate associated electrical components.
4. A system as claimed in claim 1 further comprising guideways which extend upwardly
alongside a door opening and then rearwardly, and also comprising guides secured to
said door and engaging said guideway means so as to faciliate an overhead movement
of said sliding door wherein said first telescopic tubular section (72) is substantially
uniformly elongate and said second section (78) is substantially L-shaped with one
of the elongate portions (80) of the L-shaped section being adapted to receive said
first section (72).
5. A system as claimed in claim 4 further comprising a counterbalance means for counterbalancing
the weight of said door.
6. A system as claimed in any of the preceding claims wherein said control means comprises
a source of pressurized fluid (126), a conduit means (122, 124) for connecting said
source of pressurized fluid (126) to said fluid cylinder (10) and, a control panel
for controlling the flow of pressurized fluid through said conduit means.
7. A system as claimed in claim 6, wherein said source of pressurized fluid (126) is
contiguous, via a selective valve means (130) with both ends of said fluid cylinder
(10) so that it can selectively act on either of the faces of said rodless piston
(30).
8. A system as claimed in any of the preceding claims wherein said cylinder (10) comprises
a pair of end caps (16, 18) for sealing a respective end of said cylinder body (10),
adjustable valve means (146) being located in each of said end caps (16, 18), for
communication between the interior and exterior of said cylinder body (10).
9. A system as claimed in any of claims 6 to 8, wherein said cylinder is provided with
seal means (22) for preventing the pressurized fluid from flowing out of said cylinder
(10).
10. A system as claimed in any of claims 1 to 3, and 6 to 9 exept when appendant to claim
4 or 5, further comprising guideway means (112) in which said door is movable, and
guides secured to said door, said guides engaging said guideway means (112).
11. A system as claimed in any of claims 4, 5 or 6 to 9 when appendant thereto, or 10,
wherein said cylinder longitudinal axis is substantially parallel to a longitudinal
axis of said guideways means (112).
12. A system as claimed in any one of claims 3, or 6 to 11 wherein said switch means (150,
152) are micro switches.
13. A system as claimed in any of the preceding claims wherein said fluid comprises one
of either air or gas.
1. Schiebetür-Antriebssystem mit einem Fluidzylindermechanismus (10), der einen im Zylinderkörper
(12) hin- und herbewegbaren stangenlosen Kolben (30) aufweist, der zur Kopplung mit
der Schiebetür ausgebildet ist, und mit einer Steuereinrichtung zur Steuerung des
Betriebs des Fluidzylinders (10) und damit der Position der Schiebetür, dadurch gekennzeichnet,
daß der Kolben (30) an einem Schlitten (50) befestigt ist, der außerhalb des Zylinderkörpers
(12) entlang dessen Erstreckung hin- und herbewegbar ist, und daß Armvorrichtungen
(70) einschließlich eines Paares von ineinander schiebbaren rohrförmigen Gliedern
(72, 78) zur Verbindung des Schlittens (50) mit der Schiebetür vorgesehen sind, wobei
das erste (72) der rohrförmigen Glieder schwenkbar am Fluidzylinderschlitten (50)
und das zweite rohrförmige Glied (78) schwenkbar an der zugehörigen Schiebetür und
einem elastischen Stoßdämpfer zur Dämpfung der Zusammenschiebebewegung der rohrförmigen
Glieder (72, 78) befestigt ist.
2. System nach Anspruch 1, das ferner Trägereinrichtungen (102) zur Befestigung des Fluidzylinders
(10) an einer angrenzenden Wand umfaßt.
3. System nach Anspruch 1 oder 2, das Schalteinrichtungen (150, 152) umfaßt, die an jedem
Ende des Zylinders (10) vorgesehen sind, und jede der Schalteinrichtungen (150, 152)
in elektrischem Kontakt mit der Steuereinrichtung zur Aktivierung zugeordneter elektrischer
Komponenten steht.
4. System nach Anspruch 1, das ferner Führungsschienen umfaßt, die sich entlang einer
Türöffnung nach oben und im Anschluß daran nach hinten erstrecken, und das außerdem
Führungen umfaßt, die an der Tür angebracht sind und in die Führungsschienen eingreifen,
um eine Überkopfbewegung der Schiebetür zu erleichtern, wobei das erste zusammenschiebbare
rohrförmige Glied (72) im wesentlichen gleichmäßig geradlinig ist und das zweite Glied
(78) im wesentlichen L-förmig ist, wobei einer der Arme (80) des L-förmigen Gliedes
ausgebildet ist, um das erste Glied (72) aufzunehmen.
5. System nach Anspruch 4, das ferner Gegengewichtsmittel zum Ausgleichen des Türgewichts
aufweist.
6. System nach einem der vorhergehenden Ansprüche, bei dem die Steuereinrichtung eine
Druckfluidquelle (126), ein Leitungssystem (122, 124) zur Verbindung der Druckfluidquelle
(126) mit dem Fluidzylinder (10) und eine Steuertafel zur Steuerung der Strömung des
Druckfluides durch das Leitungssystem aufweist.
7. System nach Anspruch 6, bei dem die Druckfluidquelle (126) über ein Umschaltventil
(130) mit beiden Enden des Fluidzylinders (10) verbindbar ist, so daß diese wahlweise
auf jede der Stirnflächen des stangenlosen Kolbens (30) wirken kann.
8. System nach einem der vorhergehenden Ansprüche, bei dem der Zylinder (10) ein Endkappenpaar
(16, 18) zur Abdichtung der jeweiligen Enden des Zylinderkörpers (12) aufweist, wobei
einstellbare Ventileinrichtungen (146) in jeder der Endkappen (16, 18) für die Verbindung
des Inneren mit dem Äußeren des Zylinderkörpers (12) angeordnet sind.
9. System nach einem der Ansprüche 6 bis 8, wobei der Zylinder mit einer Dichtungseinrichtung
(22) versehen ist, um zu verhindern, daß Druckfluid aus dem Zylinder (10) strömt.
10. System nach einem der Ansprüche 1 bis 3 und 6 bis 9, außer wenn abhängig von Anspruch
4 oder 5, das ferner Führungsschieneneinrichtungen (112), in denen die Tür bewegbar
ist, und mit der Tür verbundene Führungen aufweist, wobei die Führungen in die Führungsschieneneinrichtungen
(112) eingreifen.
11. System nach einem der Ansprüche 4, 5 oder 6 bis 9, wenn von diesen abhängig, oder
10, wobei die Zylinderlängsachse im wesentlichen parallel zu einer Längsachse der
Führungsschieneneinrichtungen (112) ist.
12. System nach einem der Ansprüche 3 oder 6 bis 11, wobei die Schalteinrichtungen (150,
152) Mikroschalter sind.
13. System nach einem der vorhergehenden Ansprüche, wobei das Fluid entweder Luft oder
Gas ist.
1. Dispositif d'actionnement de porte coulissante comprenant un mécanisme à cylindre
hydraulique (10) muni d'un piston sans tige (30) se déplaçant de façon alternée dans
le corps de cylindre (12) et prévu pour être accouplé à la porte coulissante et un
moyen de commande du fonctionnement du cylindre hydraulique (10) et, par là, de la
position de la porte coulissante,
dispositif caractérisé en ce que le piston (30) est fixé à un chariot (50) pouvant
se déplacer de façon alternée à l'extérieur le long du corps de cylindre (12) et en
ce que des moyens de bras (70), comprenant une paire de sections tubulaires télescopiques
(72, 78), sont prévus pour raccorder le chariot (50) à la porte coulissante, la première
(72) desdites sections tubulaires étant montée pivotante sur ledit chariot de cylindre
hydraulique (50) et une seconde (78) desdites sections tubulaires étant montée sur
la porte coulissante associée et un amortisseur élastique de choc amortissant le déplacement
télescopique des sections tubulaires (72, 78).
2. Dispositif selon la revendication 1, comprenant de plus un gousset (102) pour la fixation
dudit cylindre hydraulique (10) sur une paroi adjacente.
3. Dispositif selon la revendication 1 ou 2, comprenant de plus un commutateur (150,
152) situé à chaque extrémité dudit cylindre (10), chacun desdits commutateurs (150,
152) étant en contact électrique avec ledit moyen de commande pour activer les composants
électriques associés.
4. Dispositif selon la revendication 1, comprenant de plus des glissières s'étendant
vers le haut le long d'une ouverture de la porte puis vers l'arrière et comprenant,
de plus, des guides fixés sur ladite porte et coopérant avec lesdites glissières de
façon à faciliter un passage en-dessus de ladite porte coulissante, dispositif dans
lequel ladite première section tubulaire télescopique (72) est de forme globale uniformément
allongée et ladite seconde section (78) est de forme globale en L, une des parties
allongées (80) de la section en L étant prévue pour recevoir ladite première section
(72).
5. Dispositif selon la revendication 4, comprenant de plus un moyen d'équilibrage du
poids de ladite porte.
6. Dispositif selon l'une quelconque des revendications précédentes, dans lequel ledit
moyen de commande comprend une source de fluide sous pression (126), un moyen de conduite
(122, 124) raccordant ladite source de fluide sous pression (126) audit cylindre hydraulique
(10) et un panneau de commande du débit du fluide sous pression à travers lesdits
moyens de conduite.
7. Dispositif selon la revendication 6, dans lequel ladite source de fluide sous pression
(126) est contigüe, via une soupape de sélection (130), à chaque extrémité dudit cylindre
hydraulique (10) de façon à pouvoir agir sélectivement sur chacune des faces dudit
piston sans tige (30).
8. Dispositif selon l'une quelconque des revendications précédentes, dans lequel ledit
cylindre (10) comprend une paire de chapeaux d'extrémité (16, 18) pour fermer de façon
étanche une extrémité respective dudit corps de cylindre (12), une soupape réglable
(146) étant située dans chacun desdits chapeaux d'extrémité (16, 18) pour une communication
entre l'intérieur et l'extérieur dudit corps de cylindre (12).
9. Dispositif selon l'une quelconque des revendications 6 à 8, dans lequel ledit cylindre
est muni d'un moyen d'étanchéité (22) empêchant le fluide sous pression de sortir
dudit cylindre (10).
10. Dispositif selon l'une des quelconque revendications 1 à 3 et 6 à 9, indépendamment
de la revendication 4 ou 5, comprenant, de plus, une glissière (112) dans laquelle
se déplace la porte et des guides fixés sur ladite porte, lesdits guides coopérant
avec ladite glissière (112).
11. Dispositif selon l'une quelconque des revendications 4, 5 ou 6 à 9 ou 10, dans lequel
l'axe longitudinal dudit cylindre est globalement parallèle à l'axe longitudinal de
ladite glissière (112).
12. Dispositif selon l'une quelconque des revendications 3 ou 6 à 11, dans lequel lesdits
commutateurs (150, 152) sont des micro-contacts.
13. Dispositif selon l'une quelconque des revendications précédentes, dans lequel ledit
fluide est soit de l'air, soit un gaz.