EP2219984A1 - Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method - Google Patents
Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated methodInfo
- Publication number
- EP2219984A1 EP2219984A1 EP08849117A EP08849117A EP2219984A1 EP 2219984 A1 EP2219984 A1 EP 2219984A1 EP 08849117 A EP08849117 A EP 08849117A EP 08849117 A EP08849117 A EP 08849117A EP 2219984 A1 EP2219984 A1 EP 2219984A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- relative
- braking
- force
- braking device
- elevator
- 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.)
- Granted
Links
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- 238000009434 installation Methods 0.000 claims description 11
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
- B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
- B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect
- B66D5/14—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect embodying discs
Definitions
- Elevator drive and method for driving and holding an elevator car a corresponding method and a braking device and method for decelerating and holding an elevator car and an associated method.
- the present invention relates to an elevator drive for driving and holding a
- Elevator car according to the preamble of claim 1 a corresponding method according to the preamble of claim 10, an elevator installation according to claim 11, and a braking device according to the preamble of claim 12, a corresponding method according to the preamble of claim 26 and an elevator installation according to claim 22.
- an electromagnetically actuated braking device as can be used in an elevator drive, known with a stationary housing and a rotating work shaft therein. With the working shaft, two brake discs rotatably, but axially displaceable connected.
- a respective spring axially displaceable armature discs are biased with a normal force against the brake discs so that a first frictional contact between the brake discs and the housing and a second frictional contact between the rotatable relative to the housing armature discs and the brake disc is closed.
- the frictional forces acting in these contacts counteract a rotation between the brake disk rotatably fixed to the working shaft and the housing or the armature disks rotatably connected therewith, thus braking the working shaft.
- the armature discs are released electromagnetically against the springs.
- the armature discs are made in three parts.
- An object of the present invention is therefore to provide an elevator drive with a braking device which increases the safety of the elevator drive.
- an elevator drive according to the preamble of claim 1 is further developed by the characterizing features.
- Claim 10 protects a corresponding method and with claim 11, a corresponding elevator system is protected.
- the solution further comprises a braking device according to the preamble of claim 12 further developed by its characterizing features, and a corresponding elevator system as in claim 22 characterized and further a method for detecting the function of the braking device according to claim 26.
- a brake device is usually installed in an elevator drive.
- the drive is used for driving and holding an elevator car and it essentially comprises a traction sheave for transmitting a drive and / or holding force to the elevator car, a motor for driving the traction wheel and a brake assembly for holding the traction wheel.
- a drive shaft connects the traction wheel, the engine and the brake assembly together.
- the brake assembly includes at least two brake devices, wherein, according to one aspect of the invention, the traction wheel is disposed between the brake devices. This is advantageous because the braking moments which must be transmitted from the traction wheel to the brake devices divide. In an advantageous symmetrical distribution of the braking devices, each half on both sides of the traction wheel, reduces a torque to be transmitted in the drive shaft to half.
- a risk of failure, or risk of breakage of the drive shaft is thereby significantly reduced.
- a possible failure of the drive shaft is still a braking function given that the braking devices are distributed on both sides of the traction wheel.
- the terms traction wheel and traction sheave are synonymous with respect to the present invention.
- the braking devices are arranged substantially at the two-sided ends of the drive shaft. This provides easy maintenance and accessibility.
- the brake devices arranged on both sides of the traction wheel can be controlled individually.
- monitoring logic can specifically determine whether a braking device alone is able to hold the elevator car at a standstill. This is advantageously done by the fact that the control of the braking devices for closing the same takes place with a small time delay, or that alternately during a stop of the elevator car and when advantageously no transport requirement is logged, a braking device is opened briefly.
- the monitoring logic can, during the period when only one of the brake device is closed, determine whether a braking device alone is able to hold the elevator car at a standstill. This in turn is advantageous because it allows the overall function of the brake assembly to be tested.
- the elevator drive according to the invention is usually arranged stationarily in a driving shaft and it drives the elevator car by means of a suspension element.
- the suspension elements are in this case wound up or unwound by the elevator drive or by the traction wheel or they are driven by the traction wheel or by the traction sheave via friction.
- a counterweight is usually attached to the elevator car opposite end of the support means, which ensures a sufficient reaction force.
- the elevator car and accordingly the counterweight can be hung directly or it can be hung several times by means of pulley.
- the elevator drive can also be arranged to ride, be arranged directly on the elevator car, in which case the traction wheel acts on a stationary part, such as a rail with friction surface, a gear rod or a threaded rod or for example on a rope.
- a stationary part such as a rail with friction surface, a gear rod or a threaded rod or for example on a rope.
- the braking device or at least one of the braking devices of such an elevator drive, further generally includes a static element and a movable element or drive shaft which is movable relative to the static element in a first degree of freedom and is to be braked relative to the static element.
- braking may equally include braking the movable element relative to the static element, ie reducing its relative speed, as well as completely stopping or holding the movable element
- the present invention distinguishes between static and movable elements only to distinguish two relative ones
- one of the static and movable elements may be arranged inertially fixed in order to brake the other from the static and movable element with respect to the environment, in which case the braking device may be designed in particular as a parking brake for holding the car ,
- the first degree of freedom may be, for example, a rotational degree of freedom.
- the movable element can be rotatably mounted in the static element.
- the term "forceā generally includes the forces or torques acting in the respective degree of freedom in order to jointly present the present invention which can be applied to different braking devices acting in different degrees of freedom.
- the friction torque acting on it can equally be included in rotational degrees of freedom.
- the first degree of freedom can also be a translational degree of freedom.
- the movable element can be displaceably mounted in the static element, as is known for example from DE 41 06 595 Al, in which a static element in the form of a measuring brake slides linearly along a movable element in the form of a brake application rail.
- a first frictional contact in a first contact surface are closed.
- a first frictional force counteracts a movement of the movable element relative to the static element.
- the brake disks are pressed against the housing in a first contact surface for this purpose.
- the first frictional forces occurring in these frictional engagements counteract a rotation of the working shaft rotatably connected to the brake discs.
- the term "frictional force" in this case includes the frictional torque acting thereon due to the rotational freedom of the working shaft.
- one or more relative elements are provided such that a second frictional contact in a second contact surface is closed between the movable element and each of the relative elements by the normal force and in the second frictional contact a second frictional force counteracts a movement of the movable element relative to the relative element.
- a first part disk of each three-piece armature disk presses against the associated brake disk when the normal force biases the brake disk against the housing.
- the second frictional forces occurring in these frictional engagements counteract a rotation of the working shaft, which is non-rotatably connected to the brake disks, relative to the first partial disks which are connected to the housing in a rotationally fixed manner.
- each relative element is associated with an actuating element, which is fixed in the first degree of freedom with respect to the static element, wherein between the actuating element and the relative element is closed by the normal force a third frictional contact in a third contact surface and in the third frictional contact a third frictional force counteracts a movement of the relative element relative to the actuating element.
- a second part disk of the three-part armature disk presses against the first part disk when the normal force biases the brake disk against the housing.
- the third frictional forces occurring in these frictional engagements counteract rotation of the first dividing discs relative to the second dividing discs.
- the first, second and / or third contact surface is acted upon by the same normal force.
- sliding friction also includes rolling friction, as occurs for example when rolling bearings.
- a relative element of the braking device in the first degree of freedom relative to the static element between a normal position and a braking position is biased elastically and elastically into the normal position, wherein the second and third contact surfaces are designed such that a maximum second frictional force, especially when adhering in the second and third frictional contact, greater than a maximum third frictional force.
- a movement of the relative element in the first degree of freedom beyond the brake position is, for example, positive and / or non-positive, prevented.
- stops preferably limit the movement of the relative element between the normal position and the braking position.
- the movable element also moves under effective normal force FN in the first degree of freedom. Since the maximum second frictional force between the relative element and the movable element according to the invention is greater than the maximum third frictional force between relative element and aktuierendem element, is in the second frictional contact before static friction, while the third frictional contact comes into sliding (or rolling).
- the movable member takes the relative element in the first degree of freedom, until it passes from its normal to the braking position and there, for example, positively stopped by a stop or the like. The relative element thus becomes self-acting, i. Without control influence from the outside, switched from the normal position to the braking position and this change takes place in both traversing directions, ie backwards and forwards.
- a safety margin S (FR1 + FR2) / (FR1 + FR3) can thus be made available in the event that the normal total frictional force is no longer sufficient, since, for example, the first and / or third contact surface has wear, is oiled or the normal force subsides.
- This staggered build-up of the entire force required for braking further has a favorable effect in that a force pulse is reduced to the entire moving system, since the braking force is built up over two stages.
- a pressure spring can be used, which on the one hand can cause pressing of the relative element in the second degree of freedom and on the other hand enables Relatiwerschiebung the relative element in the first degree of freedom between normal and braking position.
- the relative element can be performed in this embodiment, for example, at the same time as an anchor plate.
- the value of the frictional force of the third contact surface (FR3) is reduced to practically zero.
- the third contact surface is always used. The content of this also means that this third contact surface is omitted as described and the associated friction force (FR3) assumes the value zero.
- a malfunction In a braking device, it can be difficult to detect a malfunction easily and reliably. Such a malfunction may be present, for example, if the braking device does not open during driving, or if, as described above, it only applies a reduced braking force. For this purpose, it is internally known, for example, to manually check the braking force and the wear in maintenance intervals, which is time-consuming, labor-intensive and error-prone.
- the braking device therefore comprises a sensor device for detecting the normal and / or braking position of the relative element.
- a sensor device may for example be a contact which is closed when the relative element comes into the braking position, and / or is opened as soon as it leaves the normal position.
- optical sensors can monitor the position of the relative element or position sensors detect the position of the relative element.
- the movable member also under effective normal force FN in the first degree of freedom, the movable member takes the relative element in the first degree of freedom, until it passes from its normal to the braking position.
- An advantage of the invention results from the use of a suitable monitoring logic which monitors the correct functioning of the braking device.
- This monitoring logic comprises the sensor device for detecting the normal and / or braking position of the relative element, a speed and / or path measuring device and the control signal to the braking device.
- the brake device can be repealed with another sensor to determine the state contact play, or brake closed or contact play available or brake released be provided.
- a "control signal brakeā signals in the following the instruction state which a control device as a control signal ("toā or "open") to the brake device.
- the "speedā corresponds to the state of the movable element or the driving body or the elevator car and indicates whether the movable element is at a standstill (o) or in motion ( ā O).
- a diagnosis of the condition can follow, for example, the following scheme:
- This diagnostic scheme allows an almost continuous monitoring of the function of the braking device, in particular because at each stop (Fl, F2), the target state can be detected and appropriate measures can be taken in case of deviation. There is no danger since, when the braking position is reached, an increased braking force, as a rule a braking force increased by approximately 2 times, is available. This ensures a secure hold. Equally, if a faulty position is detected (F5), the system can be stopped and the function verified. Due to an error history, which is stored in the monitoring logic, a service can be carried out purposefully.
- a freewheeling of the relative element can be kept low. It can only be chosen so large that a reliable determination of the position of the relative element by the sensor device is easily possible and on the other hand by the resulting displacement of the movable element or the driving body no dangerous holding deviation, such as a step formation in an elevator car arises.
- the selected freewheeling path is approximately 3 to 10 mm in both directions of movement corresponding to the first degree of freedom.
- the relative element is held by means of a bias voltage in its normal position or returned to the normal position after a successful Relatiwerschiebung.
- This bias can be generated for example by means of an elastic spring, such as a simple spring bar, a mechanical rotary or coil spring or a hydraulic spring.
- a bias by means of magnetic force is possible by magnetic poles are arranged accordingly.
- the biasing device can be combined with a magnetic air unit.
- the preload to be overcome by the relative element during the movement from the normal position to the braking position, which attempts to bias the relative element into the normal position has been neglected.
- the second and third contact surface are formed such that the maximum second friction force, in particular in the case of adhesion in the second and third friction contact, is also greater than the sum of the maximum third friction force and the force KV biasing the relative element into its normal position: FR2max H > FR3max H + KV (2)
- Equation (2) is satisfied, in particular, when the second friction force is significantly greater than the third friction force: FR2max H Ā»FR3max H (2"). Moreover, since relatively large frictional forces FR2 H , FR3 H occur regularly in braking devices, in particular for elevator systems, Equation (2 ') or (2 ") also applies Equation (2) to a good approximation.
- the force KV which biases the relative element in the normal position
- the bias voltage can generally be generated, for example, by means of an elastic spring, such as a mechanical rotary or coil spring or a hydraulic spring. If the movable element is finally decelerated to a standstill and then held, the contact states change from sliding to static friction in the first, second or third frictional contact. The occurring static friction forces are generally significantly greater than the friction forces prevailing during braking during sliding friction (or rolling friction).
- the second and third contact surfaces are therefore designed such that the second friction force FR2 G , which occurs when sliding in the second friction contact, is less than the sum of the force KV, which biases the relative element in its normal position, and the third Frictional force FR3 G and / or FR3 H , which occurs when sliding or sticking in the third frictional contact.
- the relative element is held during a deceleration in its normal position.
- the second and third contact surface are formed such that the maximum second frictional force FR2max H , which can be maximally set when adhering in the second frictional contact, is greater than the sum of the force KV, which biases the relative element in its normal position , and the third frictional force FR3max H , which may occur when stuck in third frictional contact.
- FR2 G ā KV + FR3 G (3)
- Frictional contact before In the third frictional contact between the relative element and the actuating element is initially, as long as the relative element is not accelerated, static friction before. Now, as stated above, in general, the sliding friction is significantly lower than the maximum static friction. Thus, the second frictional force FR2 G acting in the second frictional contact is generally lower than the third frictional force FR3max H , which can be maximally set in the third frictional contact. Thus, as a rule (if the relative element and the actuating element do not move relative to one another), the second frictional force in the second frictional contact, in which sliding friction prevails, will be permanently smaller during braking than the third frictional force in the third frictional contact in which static friction prevails.
- the relative element is displaced from its normal position into the braking position and fixed there, advantageously detecting a malfunction
- the fulfillment of condition (2) or neglecting the force KV of the condition (2 ') is sufficient to increase the safety of the braking device and to detect a malfunction in a braking device that only holds it the braking device also slows down the movable element, moreover satisfies the fulfillment of condition (3) or (3 ') to ensure that the relative element remains in its normal position during normal braking, so that subsequently the safety reserve described above is available and advantageously detected a malfunction when holding t can be.
- Condition (3 ') is usually satisfied simultaneously with condition (2) or (2'), since the sliding friction (or rolling friction) is usually much lower than the static friction. According to the invention, therefore, it is generally only necessary that the maximum frictional force FR2max, which is present in the second frictional contact and is as a rule defined by the maximum static frictional force FR2max H , be greater than the maximum frictional force FR3max present in the third frictional contact and in the third frictional contact
- condition (3 ') is fulfilled, so that even when braking, the relative element is held in its normal position until the holding state is reached.
- condition (3 ') is fulfilled, so that even when braking, the relative element is held in its normal position until the holding state is reached.
- a requirement is, for example, a response of a speed monitoring circuit or a power failure, etc.
- the requirement for the bias voltage are then correspondingly low, it is only designed to move the unloaded relative element (3) again in the normal position and to keep loose there with little force.
- the second and third contact surface for example, consist of different materials.
- the relative element on the second contact surface may have a coating for increasing the coefficient of friction ā 2 and / or the actuating element may have a coating for reducing the coefficient of friction ā 3 on the third contact surface.
- the third contact surface and rolling bearings in particular needle roller bearings can be arranged to represent certain coefficients of friction.
- the coefficients of friction of the first and second contact surfaces are substantially the same, so that substantially identical frictional forces are set in the first and second frictional contact, which can advantageously distribute the loads more uniformly.
- the term "coefficient of friction" may in the present case comprise both the adhesion and the sliding or rolling friction value of a frictional contact, wherein in practical application the first and the second frictional contact are designed in a proven manner as friction brake lining.
- the maximum second friction force can alternatively or additionally be greater than the maximum third friction force predetermined that the third contact surface is inclined relative to the normal force.
- the maximum second friction force can alternatively or additionally be greater than the maximum third friction force predetermined that the third contact surface is inclined relative to the normal force.
- the term "forceā in the present application is understood to mean translational forces and torques acting in the respective degree of freedom.
- different friction forces can also be represented by different lever arms, for example a larger second friction force (in this case a torque ) are represented by the fact that the second frictional contact is radially further spaced from a rotational axis of the movable element as the third frictional contact., With the same normal force resulting in different frictional forces, in this case torques.
- the relative element and the actuating element can be moved by the normal force in the second degree of freedom so that the first, second and third frictional contact is closed. This allows a simple mechanical realization of the friction contacts.
- a braking element may be provided, which is fixed in the first degree of freedom relative to the movable element and is moved by the normal force in the second degree of freedom so that the first, second and third frictional contact is closed.
- the movable element may be displaced relative to the static element by the normal force in the second
- the actuator element in particular by an elastic means to be biased with the normal force and electromagnetic and / or hydraulic optionally be ventilated.
- the actuating element In the event of failure of a voltage applied to an electromagnet, a pressure drop in a hydraulic line or a fault in the control of the braking device, the actuating element is no longer released, so that the normal force closes the friction contacts and thus the braking device. In the case of a defect, the braking device thus closes automatically and automatically.
- the erf ā ndungsdorfe elevator drive accordingly includes a braking device which is designed such that the braking device can be switched in a stationary position in stationary body or stationary moving element, in a normal position in which
- the braking device Normal position the braking device generates a first holding force. This holding force is designed to keep the movable element at a standstill. Further, the brake device automatically changes in a possible movement of the movable element, regardless of a direction of movement of the normal position in a braking position. In the braking position, the braking device generates a substantially doubled or multiplied holding force or braking force.
- this automatic change from the normal position to the braking position is monitored by means of a sensor device.
- the advantage of this part of the invention is that a first slippage of the movable element can be detected by means of sensor device and that there is an automatic reinforcement of the holding force, whereby further slippage is prevented.
- the elevator drive is used in an elevator, which accelerates the vehicle body, for example, electric motor or hydraulically controlled from standstill away and in turn retarded to a standstill, whereby the braking device is usually used only for holding the vehicle body at a standstill.
- An elevator drive according to the invention with a braking device can comprise a plurality of relative elements and actuation elements associated therewith, as is known in principle from DE 197 37 485 C1, for example.
- the above-explained total frictional forces then result from the sums of the first and third or second frictional forces.
- one of the possible malfunctions of a braking device may be that a total frictional force, which is composed of the first and the third friction force, is too small to hold the movable element at a standstill.
- This malfunction can be detected when the sensor device detects that the relative element is not in its normal position.
- a movement of the relative element is limited by stops.
- the second frictional force which is higher in comparison with the third frictional force, is used and holds the movable element.
- This malfunction can thus be detected without endangering the function of holding the movable element as a whole. It is only an indication that the safety reserve S is used.
- the safety of the braking device is increased and a service can be initialized.
- Another possible malfunction is that the braking device is not properly released, i.e. the first, second and third frictional contact remain closed while driving. This malfunction may result, for example, from a defect of brake control units. This malfunction can also be detected if the sensor device detects that the relative element is not in its normal position. Because, as described above, takes in such a case, the movable element, the relative element in the first degree of freedom, whereby this is displaced from its normal to its braking position.
- Driving operation can be stopped, for example, when such a malfunction occurs, before the corresponding contact surfaces have overheated, worn or otherwise damaged.
- a corresponding braking device in new systems, advantageously delivered directly together with a corresponding drive unit.
- a corresponding braking device can also be used in existing systems and elevator systems as a replacement for an existing braking device. This can be achieved especially in connection with a possible modernization of a drive control increased security.
- a corresponding modernization set can be prepared in tune with known elevator systems.
- Fig. Ia is a braking device according to a first embodiment of the present invention in the released state in a section I-I in Fig. Ib;
- Fig. Ib the braking device of Fig. Ia in a lateral section
- Fig. 2a, 2b the braking device of Figure 1 in a normal holding state.
- Fig. 3a, 3b the braking device of Figure 1 in a malfunction with monitoring logic.
- Fig. 4 is a braking device according to a second embodiment of the present invention
- Fig. 5 the braking device of Figure 4 in a normal holding state.
- Fig. 7 is a schematic diagram of a third embodiment of the present invention.
- Fig. 8a, 8b the braking device of Figure 1 with serial brake discs.
- 9 shows an elevator drive with mounted braking device
- 10 shows an elevator drive with braking device mounted on both sides of a traction wheel
- FIG. 11 shows an alternative embodiment of an elevator drive
- FIG. 12 shows a detail of a brake arrangement in a drive according to FIG. 11.
- FIG. 13 shows an example of an elevator installation
- Fig. Ia, Ib show a braking device as it is used for an elevator drive, according to an embodiment of the present invention in the ventilated, non-braking state in a side or frontal view.
- the braking device comprises a static element in the form of a multi-part housing 1 which is inertially fixed.
- a movable element in the form of a working shaft 2 is rotatably mounted and has with respect to the housing 1 to the rotational degree of freedom ā .
- On the shaft are two brake elements in the form of brake discs 5 axially displaceable, but rotationally fixed, for example by means of a spline or a key (not shown).
- Two actuator elements in the form of armature discs 4 are axially displaceable, but rotatably mounted in the housing 1.
- three bolts 9 are distributed over the circumference, pass through the passage or blind holes in the housing 1 and the armature discs 4 and on which the armature discs 4 slide.
- a relative element in the form of a disc 3 is mounted axially displaceable.
- the discs 3 each have three groove-like recesses 10 with a groove bottom, which pass through the bolts 9 in such a way that they rest on the respective groove base and thus rotatably support the discs 3.
- a rotation of the discs 3 is positively limited by the flanks of the grooves 10, wherein the discs can be rotated by a certain angle before the bolts 9 abut the respective flanks.
- Fig. Ia, Ib show the brake device in the released state.
- electromagnets pull the armature disks 4 against the tension of a compression spring 7 away from the brake disks 5, which thereby can rotate freely with the working shaft 2.
- Fig. 2a, 2b show the braking device in the closed state.
- the electromagnets are no longer supplied with energy, so that the armature discs 4 are acted upon by the springs 7 with a normal force FN in the direction of a second, axial degree of freedom y.
- the armature discs 4 press the relative elements 3 against the brake discs 5, which are thereby axially displaced and pressed against the housing 1 with the same normal force.
- ā i G denotes the Gleitreibwert in the first and second frictional contact.
- FR3max H ā 3 H x FN
- ā 3 H is the coefficient of friction in the third frictional contact. This is chosen such that the maximum third static friction force is greater than the second sliding friction force: ā 3 H > ā 2 G (5)
- the definition ā 3 H > ā 2 G is to be understood such that the value of ā 3 H , irrespective of its tolerance position, is greater than the value of ā 2 G , irrespective of its tolerance position.
- the brake device incorrectly does not dissolve when the working shaft is put into operation again.
- the monitoring logic 11 evaluates the signal of the sensor device 8 using other signals, such as movement or speed state of the driving body or the movable element 2 and / or a brake signal indicating whether the brake to or is open, and outputs any error information to an elevator control (not shown), which stops the drive of the working shaft 2 and thus prevents annealing of the brake discs 5 and triggers a corresponding service message.
- signals such as movement or speed state of the driving body or the movable element 2 and / or a brake signal indicating whether the brake to or is open
- a further possible malfunction of the braking device is that the holding force applied by the braking device is insufficient.
- the braking force FRmax applied in the normal position A by the brake means at most is due to the design with two brake discs
- Fig. 4 shows a braking device according to a second embodiment in the released state in a lateral section.
- This braking device is provided for an elevator installation, in which the braking device 24.1, 24.2 is attached to a brake disk of an elevator drive, as shown in FIGS. 11 and 12, or in which the housing 1, which is connected to an elevator car 16, similar to FIG 13, may be fastened, moved along a brake rail 2, 15 in a first degree of freedom x.
- an electromagnet pulls an armature element 4 against the bias of a compression spring 7 in a second degree of freedom y into the housing 1, so that the housing 1 can slide smoothly along the brake rail.
- the electromagnet (or other suitable air drives) is switched off (FIG. 5), the compression spring 7 presses the armature element 4 in the second degree of freedom y with a normal force FN against a relative element 3, which is located in the armature element 4 along the first Degree of freedom x is arranged displaceably and is held by two-sided compression springs in a normal position A (Fig. 4, 5).
- the relative element 3 is pressed with the normal force FN against the brake rail 2, 15, which in turn is pressed against the housing 1.
- the maximum second and third friction force in each case by appropriate selection of the coefficients of friction ā 2, ā 3, in particular the Haftreib values ā 2 H , ā 3 H realized.
- the different maximum frictional forces can also be realized in that the third contact surface 6.3 is inclined relative to the normal force.
- 7 shows a schematic diagram of the forces acting on a relative element 3 when exposed to the common normal force FN.
- a movement of the relative element 3 relative to the actuating element in the first degree of freedom x in the positive direction (upward in FIG. 7) is additionally counteracted by a component FN.sub.x.sub.cos ( effective maximum third friction increased.
- these components FN X cos ( ā ) reduce the effective maximum third frictional force so that different maximum third frictional forces result in both directions of movement. This can be advantageously used if, for example, the elevator car, which is held by the braking device, is only partially balanced, ie the movable element 2 must be kept stronger in one direction of movement than in the other.
- a displacement of the relative element 3 relative to the actuating element 4 inevitably results in a change in a feed path along the degree of freedom y.
- This change causes an increase or decrease of the normal force FN according to a force characteristic of Zustellaktoren such as the compression spring 7 (Fig. 4 to 6).
- a braking force can be influenced according to a movement or braking direction.
- the exemplary embodiments refer to a coordination of the sliding and static friction coefficients of the friction surfaces, in order to be able to reliably detect a malfunction both during sole holding as well as during braking and subsequent holding. This is achieved by satisfying the condition ā 2 G ā 3 H ā 2 H (7).
- This is not mandatory, since in many of today's applications a braking device is normally used only for holding, for example, an elevator car at a standstill. A use of the braking device for braking is only necessary in an error case and therefore already constitutes an error situation itself. It is not necessary in these individual cases that the relative element 3 remains in its normal position. It may well be moved from its normal position in the braking position, which then the correspondingly higher braking force
- FR FR1 + FR2 (1 ') is used. This can be achieved by selecting the coefficients of friction ā 3 H , ā 3 G of the third contact surface to be significantly smaller than the coefficients of friction ā 2 H , ā 2 Ā° of the second contact surface. ā 3 G ā 3 H Ā« ā 2 G ā 2 H (7 ')
- the braking device 24.1, 24.2 as shown in FIGS. 9 and 10 in a drive 20 of an elevator installation 18 (as explained below with reference to FIG. 13) on or grown.
- the drive 20 includes one or more traction sheaves or traction wheels 22 which is integrated or mounted in a drive shaft 2.
- the drive shaft 2 is driven by a motor 21 and held by the brake device 24.1, 24.2 at a standstill or braked, if necessary. In some cases, a translation can be arranged between the motor 21 and the drive shaft 2.
- the drive 20 thus also includes the braking device 24.1, 24.2 which usually two substantially identical units is divided. Each of the units is in its braking position (B) taken in a position to the moving body and hold on.
- the two units are assembled into a single braking device and arranged at one end of the drive shaft.
- the drive shaft in this embodiment corresponds to the movable element 2.
- This type of arrangement is cost-effective, since the braking device can be pre-assembled, for example, as a complete unit.
- the two units of the braking device 24.1, 24.2 are attached to the two ends of the drive shaft 2.
- braking a braking or holding torque is thus distributed away from the traction sheave 22 on the two units.
- significantly better power distributions in the drive shaft 2 and a risk of failure of the brake device due to a fraction of the drive shaft 2 is reduced.
- the braking effect between normal position and braking position is doubled. This is the case when the coefficient of friction ā 3 in the third contact surface is approximately zero.
- the brake force gain between normal and braking position can be influenced. If, for example, a plurality of brake discs 5 and relative elements 3 or static elements 1 can be arranged one behind the other, a desired brake gains can be achieved by carrying out the freewheeling path of the individual relative or static elements.
- three second contact surfaces 6.2 which only come into effect in the braking position, are arranged to form a first contact surface 6.1. Neglecting the frictional force of the third contact surface 6.3 thus results in a quadrupling of the braking force upon reaching the braking position.
- a person skilled in the art can determine any combinations
- FIGS. 11 and 12 show an alternative arrangement of an elevator drive 20 with brake devices.
- brake devices here are several braking devices 24.1, 24.2, 24.3, etc., as described in Figure 4 to 6 over a circumference of a brake disc 2, which forms a unit with the drive shaft, arranged distributed.
- FIG. 13 shows an elevator installation 18 with an elevator drive 20 which is arranged in the upper area of a travel shaft 12.
- the elevator drive 20 drives the elevator car 16 by means of the traction wheel 22 via carrying and propelling means 13.
- the carrying and propelling means 13 connects the elevator car 16 to a counterweight 17, so that, corresponding to a driving direction the elevator drive the cabin 16 upwards, and the counterweight 17 is moved downwards or reversed accordingly with a changed direction of rotation of the elevator drive.
- the elevator drive 20 is held by its brake devices 24.1, 24.2, the car and counterweight 17 are also at a stop or at a standstill.
- cab 16 and counterweight 17 are connected via pulleys 14 to the carrying and propellant 13.
- the drive 20 may also be arranged instead of one of the deflection rollers 14.
- the two units of the braking device at the two ends of the drive shaft 2 grown. This means that the traction sheave 22 is arranged between the units of the braking device 24.1, 24.2. When braking a braking or holding torque is thus distributed away from the traction sheave 22 on the two units. Thus, significantly better power distributions in the drive shaft 2 and a risk of failure of the brake device due to a fraction of the drive shaft 2 is reduced.
- the individual units or devices of the brake arrangement preferably units as shown and explained in the embodiment variants of FIGS. 4 to 7, are arranged directly on the elevator car, it is advantageous to divide the brake units on both sides of the elevator car.
- the resulting braking and holding forces can thus be introduced in half each in the corresponding brake or guide rails.
- the brake arrangement is divided among, for example, four brake devices, two of the brake devices are advantageously arranged below the elevator car and the remaining two brake devices are arranged in the upper region of the elevator car. This not only optimizes the introduction of force into the brake or guide rails, but also optimizes the introduction of force into the elevator car itself.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
- Cage And Drive Apparatuses For Elevators (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL08849117T PL2219984T3 (en) | 2007-11-14 | 2008-11-06 | Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method |
EP08849117A EP2219984B1 (en) | 2007-11-14 | 2008-11-06 | Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20070120652 EP1923346B1 (en) | 2006-11-16 | 2007-11-14 | Braking device, lift facility, a method for recording the function of the braking device and a modernisation set |
EP08102368 | 2008-03-07 | ||
PCT/EP2008/065066 WO2009062881A1 (en) | 2007-11-14 | 2008-11-06 | Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method |
EP08849117A EP2219984B1 (en) | 2007-11-14 | 2008-11-06 | Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2219984A1 true EP2219984A1 (en) | 2010-08-25 |
EP2219984B1 EP2219984B1 (en) | 2011-08-17 |
Family
ID=40351897
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08849117A Active EP2219984B1 (en) | 2007-11-14 | 2008-11-06 | Lift drive and method for driving and detaining a lift car, a corresponding method and a braking device, and method for decelerating and detaining a lift car, and an associated method |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2219984B1 (en) |
AU (1) | AU2008323024B2 (en) |
PL (1) | PL2219984T3 (en) |
WO (1) | WO2009062881A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009053131B3 (en) * | 2009-11-05 | 2011-05-19 | Db Services West Gmbh | Method and device for checking the brake system of an elevator installation |
CN102431866B (en) * | 2011-10-20 | 2012-11-21 | čå·é궦驱åØč®¾å¤č”份ęéå ¬åø | Safety braking device clamped on traction wheel of traction machine |
US11020383B2 (en) | 2017-04-20 | 2021-06-01 | The Board Of Regents Of The University Of Texas System | Methods for the treatment of cancer metastasis |
DE102019209529B4 (en) * | 2019-06-28 | 2021-05-06 | Continental Teves Ag & Co. Ohg | Multi-disc brake for a rotatable element |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH537539A (en) * | 1972-07-26 | 1973-05-31 | Inventio Ag | Load-dependent braking device for conveyor systems |
GB1488374A (en) * | 1974-06-21 | 1977-10-12 | Coal Ind | Brakes for vehicles |
FI109596B (en) * | 1997-01-23 | 2002-09-13 | Kone Corp | Lift and lift drive machinery |
DE19737485C1 (en) * | 1997-08-28 | 1999-06-17 | Stromag Ag | Electromagnetically-operated brake |
JP2000344449A (en) * | 1999-06-02 | 2000-12-12 | Teijin Seiki Co Ltd | Elevator drive |
FI106192B (en) * | 1999-09-16 | 2000-12-15 | Kone Corp | Lifting machinery for a lift |
DE102004054013A1 (en) * | 2004-11-09 | 2006-05-11 | Robert Bosch Gmbh | disc brake |
PL1671912T3 (en) * | 2004-12-17 | 2011-07-29 | Inventio Ag | Elevator system with braking unit and method to keep the elevator stopped |
BRPI0601926B1 (en) * | 2005-06-17 | 2018-06-12 | Inventio Aktiengesellschaft | BRAKE PARACHUTE DEVICE |
FI119877B (en) * | 2005-08-19 | 2009-04-30 | Kone Corp | Elevator security |
SG138531A1 (en) * | 2006-06-19 | 2008-01-28 | Inventio Ag | Method of checking lift braking equipment, a method for placing a lift installation in operation and equipment for carrying out placing in operation |
-
2008
- 2008-11-06 EP EP08849117A patent/EP2219984B1/en active Active
- 2008-11-06 WO PCT/EP2008/065066 patent/WO2009062881A1/en active Application Filing
- 2008-11-06 AU AU2008323024A patent/AU2008323024B2/en active Active
- 2008-11-06 PL PL08849117T patent/PL2219984T3/en unknown
Non-Patent Citations (1)
Title |
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See references of WO2009062881A1 * |
Also Published As
Publication number | Publication date |
---|---|
AU2008323024A1 (en) | 2009-05-22 |
EP2219984B1 (en) | 2011-08-17 |
PL2219984T3 (en) | 2012-01-31 |
WO2009062881A1 (en) | 2009-05-22 |
AU2008323024B2 (en) | 2015-06-04 |
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