CN106660743B - Safety device for elevator operation - Google Patents
Safety device for elevator operation Download PDFInfo
- Publication number
- CN106660743B CN106660743B CN201580039535.2A CN201580039535A CN106660743B CN 106660743 B CN106660743 B CN 106660743B CN 201580039535 A CN201580039535 A CN 201580039535A CN 106660743 B CN106660743 B CN 106660743B
- Authority
- CN
- China
- Prior art keywords
- brake
- hydraulic
- elevator
- valve
- brake lining
- 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.)
- Active
Links
- 230000001133 acceleration Effects 0.000 claims description 35
- 230000033001 locomotion Effects 0.000 claims description 21
- 230000000694 effects Effects 0.000 claims description 17
- 230000008901 benefit Effects 0.000 claims description 14
- 238000004891 communication Methods 0.000 claims description 10
- 230000005611 electricity Effects 0.000 claims description 9
- 230000003111 delayed effect Effects 0.000 claims description 3
- 235000006508 Nelumbo nucifera Nutrition 0.000 claims 1
- 240000002853 Nelumbo nucifera Species 0.000 claims 1
- 235000006510 Nelumbo pentapetala Nutrition 0.000 claims 1
- 239000012530 fluid Substances 0.000 description 77
- 230000006870 function Effects 0.000 description 24
- 238000000034 method Methods 0.000 description 20
- 239000007788 liquid Substances 0.000 description 19
- 238000011144 upstream manufacturing Methods 0.000 description 14
- 238000013461 design Methods 0.000 description 13
- 230000008569 process Effects 0.000 description 13
- 230000004044 response Effects 0.000 description 13
- 230000009471 action Effects 0.000 description 10
- 230000006835 compression Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 10
- 230000002829 reductive effect Effects 0.000 description 9
- 210000003128 head Anatomy 0.000 description 8
- 230000008859 change Effects 0.000 description 6
- 238000007667 floating Methods 0.000 description 6
- 230000002159 abnormal effect Effects 0.000 description 5
- 230000009977 dual effect Effects 0.000 description 5
- 239000010410 layer Substances 0.000 description 5
- 238000005086 pumping Methods 0.000 description 5
- 238000006467 substitution reaction Methods 0.000 description 5
- 240000005523 Peganum harmala Species 0.000 description 4
- 210000000080 chela (arthropods) Anatomy 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000003993 interaction Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 230000036961 partial effect Effects 0.000 description 3
- 238000010008 shearing Methods 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 208000032953 Device battery issue Diseases 0.000 description 1
- 240000007594 Oryza sativa Species 0.000 description 1
- 235000007164 Oryza sativa Nutrition 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000002337 anti-port Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 239000011229 interlayer Substances 0.000 description 1
- 238000003475 lamination Methods 0.000 description 1
- 230000002045 lasting effect Effects 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003032 molecular docking Methods 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 235000009566 rice Nutrition 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 239000011800 void material Substances 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B5/00—Applications of checking, fault-correcting, or safety devices in elevators
- B66B5/02—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions
- B66B5/16—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B5/00—Applications of checking, fault-correcting, or safety devices in elevators
- B66B5/02—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions
- B66B5/16—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well
- B66B5/18—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well and applying frictional retarding forces
-
- 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
- B66D5/06—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with radial effect
- B66D5/08—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with radial effect embodying blocks or shoes
-
- 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
- B66D5/24—Operating devices
- B66D5/26—Operating devices pneumatic or hydraulic
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Maintenance And Inspection Apparatuses For Elevators (AREA)
- Elevator Control (AREA)
Abstract
Safety device for elevator operation, the elevator car brake unit that there is elevator lift car different track or guide rail are respectively acting on at least one car brake unit or preferably at least two, wherein at least one brake lining can be operated by hydraulic actuator (11), and at least one described brake lining (16) is articulated to caliper (24) by plate spring member or laminated leaf spring (27) in a manner of fricton-tight guiding.
Description
Technical field
The present invention relates to the elevators of preamble according to claim 1, have and act on different tracks and/or lead
The elevator car brake unit of rail.
Background technique
The various completely different embodiments of elevator car brake unit are known and are each of realization elevator
Required for the completely different purpose of kind.
For a long time, elevator is only equipped with mechanically actuated formula elevator car brake unit, passes through stay in an overspeed situation
It is activated in the subsequent speed limit rope of lift car.
In recent years, the demand to elevator car brake unit is increasing always.It is desirable to elevator car brake lists
Member not only only control emergency such as lift car hypervelocity or free falling.But also should be able to as brake come using, so as to
The lift car accident carriage movement before bus stop is reliably prevented in order to avoid leaving bus stop in advance, such as in the carriage of variation
Under the influence of load-carrying.
Therefore, mechanically actuated formula elevator car brake unit gradually lies on the table on one side and more commonly using hydraulic behaviour
Make formula elevator car brake unit.Demand to these elevator car brake units is also higher and higher.Recently, it is also desirable to this
The elevator car brake unit of sample can in case of emergency cope with the adjustment of brake force itself, at least elevator car brake list
Member in operation should be as unremarkable as possible, and especially they because of too application suddenly and/or " intervention " or cannot applied
Noise is issued in journey and interferes with the terraced comfort of row.
Actually it has been suggested that hydraulic operation formula elevator brake.These hydraulic pressure elevator brakes show braking
Pincers, herein, brake lining activity is maintained in sliding guide mechanism.In these sliding guide mechanisms almost invariably
It rubs, friction reduces the power that brake lining can be pressed on braking orbit or guide rail by hydraulic piston, or friction is initially
It is not considered problematic, because hydraulic actuation power is large enough to unquestionably overcome these frictional force.
Goal of the invention
But tightened inspection is found, if liquid braking device is not only used as emergency stopper, is also transported in normal elevator
Task in row and especially is shouldered when wanting accurate control brake force, then the frictional force will be especially disagreeable.Occur
Such case is kept constant because of cannot be guaranteed that it is onesize that frictional force is always shown in the long period.Exist instead
Following danger, frictional force are gradually changed because dirty or even corroding, thus brake force is not up to the practical maximum value controlled,
But only reach the value reduced by unexpected biggish friction.
Present invention aim to address this problems.
Summary of the invention
Inventive solution
The purpose is reached using the feature of elevator according to claim 1.
That is independent claimed or other spies also with other claims or from specification and suitable attached drawing
Following solution is claimed in sign in combination:
It is designed in this way the elevator and/or each lift car brake component, horizontally and/or is preferably existed by plate spring member
It is perpendicular at least one described active brake liner of holding on the direction of the track interacted therewith, i.e., absolutely not or substantive
Upper sliding guidance not relevant to caliper.That is the brake lining is supported by leaf spring or " suspension ", so that it is available
Hydraulic coupling is by being forced into leaf spring flexible deformation on braking rail or guide rail.When so done, leaf spring preferably protects brake lining
It holds in its predetermined position.That is the brake lining not along leaf spring longitudinal sliding motion or rolling, is at least no more than 1 millimeter.In this way
It just prevents to operate caliper and must overcome frictional force between brake lining seat and caliper, which may be current
Under brake loading effects and/or at any time (burn into dirty etc.) and change.This also facilitates accurate opened loop control or closed loop control
System.
Preferred embodiment is provided by dependent claims.
All realize that caliper is exactly to be able to achieve the principle of the invention preferably in the form of floating clamp under any circumstance
Say, caliper activity is maintained at lift car, thus caliper can and being moved upwards in the side perpendicular to guide rail about
Car guide rail (or more broadly say about braking orbit) is from centering.
The track that the brake shoe that the longitudinal axis of plate spring member preferably completely or substantially parallel to it is kept is acted on extends.It is special
This, plate spring member is held against caliper in its along its longitudinal axis line direction two petiolareas opposite each other.Preceding in moving downward
Bearing be fixed bearing.The bearing delayed in moving downward is floating support, and floating support at least allows plate spring member at it
Small movements in longitudinal axis.This prevents from leading to have stretching on the direction for be parallel to longitudinal axis in plate spring member migration process
Stress, the tensile stress resist plate spring member and further deform, thus brake lining is hindered further to move to track.
It must should be mentioned that, for this solution, can be served as a contrast herein using the passive braking being movably arranged in caliper
Piece (because it is with can resisting spring part power mobile).But it can also be used and can not substantially or completely be moved relative to caliper
The passive brake lining of ground placement, in the case where especially realization in the form of floating clamp in caliper, i.e., its floating mount is in elevator
In carriage or elevator car frame, the possibility in braking process relative to the guide rail as brake surfaces certainly in is brought
Property.
It is desirable that it is designed in this way the plate spring member, once hydraulic actuator is retracted into " open position " and no longer applies any
Pressure is to brake lining and/or brake lining seat, and brake lining is pulled back and/or withdrawn to plate spring member and/or brake lining seat arrives it
Open position.This is avoided realizing the fixed company between brake lining and/or brake lining seat and at least one hydraulic actuator
It connects.On the one hand, this allows the actuator of several independent actuations that can act on identical brake lining seat and/or brake lining.Separately
On the one hand, actuator can only substantially transmit compressing force to brake lining and/or brake lining seat, and vice versa, which protects
It has demonstrate,proved brake lining and/or brake lining seat can not transmit the shearing force of any substance to actuator, the shearing force is for example
Pull the piston guide mechanism or piston seal of actuator.
The caliper is preferably so constructed, caliper at least partly covers the brake lining kept by plate spring member, excellent
It is selected at its narrow end surface and covers, so that brake lining is trapped in caliper, even if plate spring member fails, so that causing can be whole
The brake action only having been turned on.
Several hydraulic actuators preferably act on single brake lining and/or brake lining seat, these actuators all do not have
It is firmly connected to individual brake lining and/or brake lining seat, herein, without reference to other claim features
In the case of require separately protected entire further solution.In this way, brake force can be generated in cascaded fashion, to cause only
Need the position of the brake force of very little only to operate an actuator, or and not all actuator operated, at this time at least one
Actuator stays open position, but in the case where needing maximum braking force all actuators by common actuation.
It is preferred that being equipped at least two elevator car brake units on elevator of the invention, they are designed to hydraulic
Aspect is self-centered.If they include mostly in the complete or substantive of so-called hydraulic pressure unit or control unit form
Upper whole hydraulic connecting pipeline (all that pipeline that especially working chamber of cylinder is interconnected), all required valves, liquid
Press pump and (if necessary) equalizing box and individual actuator, situation just will be such.Individual actuator can be integrated
Directly by flanged joint to thereon into control unit or preferably in a manner of hydraulic conduction.So, each elevator
Car brake unit can form closed hydraulic circuit, and need only be connected to after installing to lift car for voltage
The electric connector of supply and control signal supply, the hydraulic work in construction site is unwanted.Such lift car can
Thoroughly to complete in factory, manufacturer for hydraulic system.
Being equipped at least two elevator car brake units to elevator may be easily that they show individually controllable
Hydraulic actuator operation several active brake liners, so that brake force can be by causing how many active brake liners to apply
The fact influence.In this way, a part of brake lining can be saved, the brake lining be used to generate very high brake force and
Contact track is prevented from regular job.
Elevator car brake unit advantageously shows acceleration transducer, is used for corresponding lift car braking
The switch control or closed-loop control of the brake force of device unit are not preferably involved and individually to be put to good use by elevator car brake unit
Lift car control.
It is desirable that the two or several preferred direct communications of elevator car brake unit, i.e., do not involve central elevator control
Device processed or even lift car control device.They compare its acceleration transducer signals especially to find failure.
To elevator of the present invention advantageously, being preferably designed as with elevator car brake unit being the lift car separated
Control device is designed to communicate with elevator cab movement with central elevator control gear, and hoistway signal system is directly supplied
Signal, and can be about central elevator control gear stand alone autonomous operation elevator car brake unit.
The lift car of elevator of the present invention ideally has the Emergency Power with elevator cab movement.
The lift car preferably has the load measuring system for determining current elevator lift car load.
Also separately protected elevator car brake unit is required, is designed to realize that there is special lift car system
The elevator of dynamic device (as claimed).
Subject of the present invention or a kind of opened loop control or closed-loop control of being used for are according to disclosed by Fig. 3 a-3k and Fig. 4 a, 4b
The brake of hydraulic elevator as claimed in claim 1 method.
Other operation modes, advantage and designability of the invention comes from by attached drawing the embodiment described.
Optionally/substitution design scheme
In order to show the additional options that can improve the invention as limited just now, following the description must be mentioned:
It is proposed that a kind of elevator with lift car, lift car keep at least two elevators acted on different tracks
Car brake unit.Theoretically, track can be individual braking orbit, but use lift car thus certainly in practice
Track.
Each elevator car brake unit has caliper, and caliper is kept in the side of track by one or several portions
Divide the active brake liner constituted and keeps the corresponding passive brake lining being also made of one or several parts in the other side.
In the case, only active brake liner is directly operated by least one hydraulic actuator.Alternatively, actively
Brake lining can by least one hydraulic actuator through a lever or a lever system by indirect operation.
But under the influence of relevant pressure, which neutralizes the work of the power of main spring unit completely or partially
With the main spring unit is integrated into actuator mostly and therefore becomes part of it, which tends to oppress
Brake lining reclines track.In the direction of the opening not under the influence of by pressure, main spring unit is to apply required for specified brake force
Power compressing brake lining recline track.In the case, passive brake lining can with but be not necessarily attached to auxiliary spring list
Member, thus it can avoid the power certain time (or to a certain degree) of auxiliary spring unit, as a result, active brake liner must shift to rail
Road is until the distance for reaching braking limit increases.
Certainly, generally, at least one described actuator does not act on brake lining itself, but acts on holding by one
The brake lining seat for the brake lining that a or multiple portions are constituted.But at least one actuator is to the brake lining seat
This effect is considered as the direct operation of brake lining.
Above-mentioned main spring unit is sized to, if all corresponding actuators are complete or are at least mainly depressurized
So that they do not resettle any counter-force or apparent counter-force, then main spring unit will be to generate power required for specified brake force
Keep the brake lining brake that reclines in place.According to structure, it is considered to be the maximum from corresponding elevator car brake unit
The brake force of brake force is referred to as specified brake force.This does not exclude accidentally realize so-called excessive system in some cases
It is dynamic, because with hydraulic at least one hydraulic actuator of influence so that it will more strongly be braked than what main spring unit can be accomplished
Liner is pressed against in orbit.But excessive braking is not provided in most cases.
As described, passive brake lining can optionally be attached to auxiliary spring unit, thus it can avoid (i.e. by gram
Clothes) auxiliary spring unit power.This means that spring force caused by auxiliary spring unit can be similar with main spring unit.In
It is that must accordingly design the auxiliary spring of strength.Generally, it is designed in this way the interaction of main spring unit and auxiliary spring unit, this two
Final (when applying specified brake force) is in such position by a spring unit, i.e., its power is balanced and actively makes herein
Dynamic liner or passive brake lining and/or corresponding brake lining seat do not pass through corresponding affiliated spring unit pressure directly and no longer
By caliper.
This preferred embodiment is selected to solve following problems, i.e., known hydraulic elevator car brake unit does not have generally
There are response first and then unexpected very kickback.The reason is that the pressure reduced in hydraulic actuator does not generate at the beginning
Any brake action, because enough hydraulic fluids must be discharged from the relevant work chamber of actuator so as to reality first
On make brake lining contact track.But once contact track, brake force just increase brake lining suddenly, this is because once certainly
First working chamber is extracted pressure of a small amount of hydraulic fluid then in the first working chamber out again and is cleared up suddenly now.Such extreme response
System can not be by reasonably opened loop control or closed-loop control.
By this preferred embodiment, the response characteristic of the hydraulic system is high balance.
The reason is that following facts, brake lining is placed the track to recline and is not served as a contrast in braking after brake lining application
It is strictly clamped between piece.On the contrary, passive brake lining can avoid one section and overcoming the power of increase of auxiliary spring unit
Time reaches balance until the power generated by main spring unit and by auxiliary spring unit generated reaction force.In this way, must and can be with
Further make active brake liner close to track to generate complete specified brake force, although it has got at the latter.Then,
Before still small initial brake force becomes complete specified brake force in brake lining first contacts CloseTrack process, it is necessary to arrange
Out from the considerable amount of hydraulic fluid of the first working chamber of at least one hydraulic actuator.Lift car system is obviously reduced in this
The invasive of dynamic device unit response characteristic, and the response of elevator car brake unit can be made to arrange because of the throttling of hydraulic fluid
Out and/or the opened loop control of even current braking effort or closed-loop control and it is softer.The latter can be by by some hydraulic fluids
Quick pumped back actuator working chamber makes other hydraulic fluid eject realization from actuator working chamber.
Elevator with brake type of the invention is for realizing that it is outstanding for having the system of following arrester control devices
Its is significant:
Elevator of the invention may include the open ring control device of the liquid braking device for making lift car slow down or close
Ring control device, especially under improper travel situations such as overspeed situation.
As already described, which includes the piston rod being connected with piston, and piston is according to being present in corresponding to piston
Hydraulic and possible basis in first working chamber is present in hydraulic complete or partial compensation in the second working chamber corresponding to piston
The power of main spring unit.
The speed of brake application and/or final power used in track is urged to by the brake lining of rod operable leads to
Hydraulic power source is crossed by opened loop control or closed-loop control.Above-mentioned first working chamber of on the pressure side at least one piston to described in of pressure source
Fill hydraulic fluid.The suction side of pressure source can be from the second working chamber pumping hydraulic fluid of at least one piston.
Finally, setting additional control pipeline, the first working chamber is connected by it with the second working chamber.Flow through the liquid of control pipeline
The actual flow velocity of pressure fluid is determined that the control valve is preferably designed as remote-controlled valve by control valve.
The working principle that the control valve of its practical flowing is flowed through in control pipeline and decision is as follows:
If control valve standard-sized sheet, the pressure that can occur between the first working chamber and the second working chamber is balanced.As a result,
Hydraulic fluid can be drained into from the first working chamber by the second working chamber by the piston that at least one main spring unit pre-tightens, to brake
Device application.The appearance of such case is unrelated with following facts, that is, pressure source may still tend to (according to hydraulic layout) to the
One working chamber tends to synchronize from the second working chamber while filling pressurized hydraulic fluid siphons away (suction) hydraulic fluid.Standard-sized sheet
Control pipeline will also guarantee pressure compensation related to this.
If control valve be it is fully closed, pressure compensation will not be proceeded through between the first working chamber and the second working chamber
The pressure compensation of pipeline.Because pressure source is sucked out while to the first working chamber filling pressurized hydraulic fluid from the second working chamber
The fact that hydraulic fluid (cannot achieve the pressure compensation by pressure compensation pipeline), piston will be moved toward the second working chamber, directly
It arrived fully open position to piston, in this way, brake is released.
Obviously, the pressure compensation degree between the first working chamber and the second working chamber can be by so operating the control
Valve is by opened loop control or closed-loop control, i.e. its both non-standard-sized sheet is not also fully closed, so that its practical flowed friction decision applies braking
The size of power.
One extremely preferred embodiment regulation, at least one described valve is the switching valve for the operation of dedicated on-off.
Such valve is not proportioning valve.The characteristics of proportioning valve is it by making its spool enter the fixation between " fully closed " and " standard-sized sheet "
Thus position simultaneously reserves the defined hydraulic effective cross section corresponding to desired flow rate to control the flow velocity for flowing through hydraulic path.With
It is that spool possessed by it can not be using between " fully closed " and " standard-sized sheet " in the characteristics of above-mentioned valve of dedicated on-off operation
Fixed middle position, as long as being at least energized.(according to particular design) can be exactly " complete by only fixed position that spool uses
Close " position or " standard-sized sheet " position.
Flow velocity by hydraulic path is controlled by switching spool back and forth between "ON" and " closing ", it is this back and forth
Switching should preferably repeated in 1 second.It is desirable that switching frequency reaches 15 hertz or higher.
Valve for the operation of dedicated on-off is seat valve is advantageous, i.e., if valve is closed, valve seat possessed by valve
(fluid tight) spool in sealing contact.
Valve for the operation of dedicated on-off is preferably controlled by pulsewidth modulation or frequency modulation(PFM) or combinations thereof mode.
There are two types of the modes toggled described in different completions:
First mode is so to switch, that is, spool is before handover against its valve seat, so that spool starts and reversed fortune
It is dynamic.According to same way, the valve is before handover again against the backstop for limiting its " maximum open position ".The liquid of the valve as a result,
How long how long pressure resistance can be controlled with the valve standard-sized sheet by determining that in each time interval, the valve is fully closed.
Second mode be referred to as " trajectory " mode: spool be constantly present before valve seat from make spool a side
Move upwards the switching for being switched to and moving it in the opposite direction.In the same fashion, valve against it is limited, " open by maximum
There is switching again before the backstop of position ".
" shock " number between spool and valve seat and/or backstop significantly reduces as a result, with regard to contact zone abrasion and/
It or is actively advantageous for fatigue.
The combining form of first and second operational modes is feasible.
In any case, people can this valve be referred to as " pulse " valve.This allows extremely dynamic when needing accurate control
Control, for example, control may along andfrictional conditions that guide rail changes in short distance and/or control in lift car only above well
Wire cable rupture at several meters.One important advantage is, pulse valve obviously can more tolerate the solid particle of pollution hydraulic fluid, because
Pulse valve (being different from slide valve) is not slack in following positions, which forms and can be blocked up by the little particle entrained by hydraulic fluid
The close gap of plug.
According to another preferred embodiment, which also has other than the pressure control pipe line with control valve
There is the throttle pipe with throttling control valve of the noise abatement application for liquid braking device among lift car stop layers or later
Line, and/or the short-circuit pipeline with short valve quickly applied for brake in case of emergency, and/or for not opening
Hydrodynamic press pump discharges brake just with the brake discharge line with brake relief valve of the new row ladder of enable starting.
The soft application of brake may be implemented in above-mentioned choke flow line, thus lift car stopped or will stop layers when
Application elevator car brake avoids issuing audible noise when in order to avoid unexpectedly carriage moving.It is comfortable that this mainly improves row ladder
Property.When throttling control valve V3 is standard-sized sheet, choke flow line still shows flowed friction, and the flowed friction is more preferably greater than corresponding at it
The flowed friction of control pipeline and/or short-circuit pipeline when valve is standard-sized sheet.
There is provided, there is the additional short-circuit pipeline of short valve, which quickly to apply for brake, ensure that redundancy.If short valve is
The valve opened when not being energized becomes absolute failure safety in the system, and when an emergency happens, brake will be applied,
Even if in power control and/or battery failures.The best very little of the flowed friction of short-circuit pipeline.Hydraulic fluid can as a result,
Another working chamber is quickly drained into from one of working chamber, so that brake is applied as early as possible.
Additional brake discharge line with brake relief valve improves again takes comfort.
The brake discharge line will keep practical at least one cause being closed of brake in brake relief valve actuation
Dynamic device and accumulator or at least one other brake actuator for not applying braking maneuver this moment even interconnect.It is possible thereby to send out
The raw pressure between at least one active brake actuator and accumulator or at least one non-active brake actuator
Compensation.It discharges active brake actuator and is at least up to the degree that can start new row ladder.Advantage was not needed in this stage
Hydraulic pump is operated at least partly to discharge brake.Then, once speed of elevator car movement height is to being more than or hide by liquid
The noise that press pump issues, then hydraulic pump be actuated to guarantee complete brake release and/or be actuated to the accumulator or
At least one other brake actuator feed flow of quiet brake release is involved.
The brake preferably includes be associated at least one brake(-holder) block at least two in the hydraulic actuator of initial specification
It is a, and one of them described hydraulic actuator is used as hydraulic accumulator in normal operation, which does not operate liquid
Pressure required for opening elevator car brake is conveyed to press pump when setting out and starting.Equipped with required for this operation of execution
Corresponding valve.
The basis of this way is following tricks of the trade: in order to open belong to be administered to guide rail with stop the movement of unexpected carriage one
First brake(-holder) block of the first brake(-holder) block of group, it is another in second group of brake(-holder) block at least so that elevator cab movement can start again at
Second brake(-holder) block is moved toward guide rail so that not hindering the beginning.The movement of second brake(-holder) block is so that open the first braking
Amount of hydraulic fluid required for piece is mobile.Even if not needing, can also be dragged now along guide rail one in the brake(-holder) block or
Two, but this is harmless.Once lift car obtains speed again, hydraulic pump is just activated and guarantees to withdraw/mention completely now
Rise the brake(-holder) block.
Other operational modes, advantage and designability of the invention comes from by attached drawing the embodiment described.
Detailed description of the invention
List of drawings
Fig. 1 shows the first foundation for understanding elevator of the invention and conceives.
Fig. 2 shows for understanding the second basis conception of elevator of the invention.
Fig. 3 a is shown using independent two groups of actuators, different switch valves and the control valve for dedicated on-off operation
The hydraulic tube line chart of the first embodiment of car brake unit of the present invention.
Fig. 3 b shows using independent two groups of actuators, the pump drive of speed variable but without grasping for dedicated on-off
The hydraulic tube line chart of the second embodiment of the car brake unit of the present invention of the control valve of work.Fig. 3 c is shown using only one group of cause
The 3rd embodiment of the car brake unit of the present invention of dynamic device, additional accumulator and the control valve for dedicated on-off operation
Hydraulic tube line chart.
Fig. 3 d shows this hair using two groups of actuators, different switch valves and the control valve for dedicated on-off operation
The hydraulic tube line chart of the fourth embodiment of bright car brake unit.
Fig. 3 e shows hydraulic tube line chart identical with Fig. 3 d, and Fig. 3 e shows the flow direction by each hydraulic valve.
Fig. 3 f shows the slightly change of the hydraulic tube line chart according to Fig. 3 d, and valve V4 is changed herein.
Fig. 3 g shows the slightly change of the hydraulic tube line chart according to Fig. 3 d, and valve V3 and V4 as shown in Figure 3d are combined herein
Valve V34 substitution.
Fig. 3 h is shown using the only one group of actuator arranged in a special way, additional accumulator, different switch valves and use
In the hydraulic tube line chart of the 7th embodiment of the car brake unit of the present invention of the control valve of dedicated on-off operation.
Fig. 3 i shows the hydraulic of the 8th embodiment of the of the present invention car brake unit closely related with the structure of Fig. 3 h
Conduit line map uses the only one group of actuator arranged in a special way, additional accumulator, different switch valves and two for special
With the control valve of on-off operation.
Fig. 3 j shows using two groups of actuators and grasps according to what special shape was arranged together with other valves for dedicated on-off
The hydraulic tube line chart of 9th embodiment of the car brake unit of the present invention of the control valve of work.
Fig. 3 k shows the hydraulic tube line chart of the tenth embodiment of the simplification modification based on the 9th embodiment.
If it is not hydraulic that Fig. 3 L, which is shown for the opened loop control of one or more actuators 11 or the pressure source of closed-loop control,
Pump 19 itself and can the direct hydraulic configuration principle that without intermediate means uses.
Fig. 4 a shows the 11st reality of the independent two groups of actuators of use, the pump drive of speed variable and several switch valves
Apply the hydraulic tube line chart of example.
Fig. 4 b show based on according to the basic principle as the embodiment of Fig. 3 b and compared to embodiment shown in Fig. 4 a
The hydraulic tube line chart for the 12nd embodiment being simplified.
Fig. 5 shows the positive beneficial embodiment of of the invention one with seeing obliquely from the front.
Fig. 6 shows positive beneficial embodiment of the invention shown in fig. 5 along the sectional view of A-A with seeing obliquely from the front.
Fig. 7 be show again actively and passively brake lining seat how to pass through laminated leaf spring be maintained at it is basic in caliper
The view of principle.
Specific embodiment
Preferred embodiment shown in the drawings
General preliminary comment
Certain general preliminary comments are made herein for elevator described in preferred embodiment framework, are fitted
For all embodiments:
The elevator includes the drive unit for lift 1 and lift car 4 for being preferably designed to gearless, and lift car is along elevator
Car guide rail 2 is guided 3 longitudinal guide of device when driving, and it is generally in the form of closing compartment room.
Elevator is preferably wirerope elevator, is maintained on more hoist cables, hoist cable is not shown by symbol and passes through mostly
The traction sheave that drive unit for lift is driven is guided, and traction sheave is also had been not shown.
Therefrom, hoist cable directly or indirectly extends to counterweight, and counterweight can be in counterweight moving on rails, and counterweight is herein not yet
It is shown by symbol.They are attached to counterweight or they bear the counterweight installed according to pulley blocks form.
Elevator according to the present invention preferably abandons so-called driving brake, or uses only for spare reason
The latter.Related to this, " driving brake " is not the driving device regeneration operation for possible energy regenerating, but additional
Mechanical brake, generally act on the braked wheel being connected with drive shaft or brake disc, so as to for example stop stop when keep away
Exempt from unexpected carriage movement.
The elevator abandons traditional hypervelocity control device, exceeds the speed limit control device to be fixed to the endless rope of lift car
Form realize that therefore by its imperative operation, and the rope, by hypervelocity control device operation, which is exceeding
The rope is braked when certain speed, then generates mechanical force, which starts lift car clamping device, then makes lift car
Stop.
On the contrary, elevator of the invention is in most cases equipped with hoistway massaging device.Generally, the latter is by route benchmark
5 and displacement sensor 6 constitute, the route benchmark along travel route close to lift car 4 be fixedly mounted, the displacement sensor quilt
It is attached to lift car and interacts with route benchmark 5.In the case, hoistway information system can not only determine road, and
Being on the contrary can be with or it is preferable to determine relevant velocity information and/or acceleration information.
Alternatively, hoistway information system can also with or additionally (spare) is made of measuring device, pass through one or more
The wheel rolled on track and/or guide rail collects the information about route, speed and/or acceleration.
Again, alternatively or additionally, hoistway information system can be made of contactless rangefinder, be continued or close
It cuts and ordinatedly measures to the current distance for referring to fixed point, this is preferably placed in hoistway hole and/or hoistway head with reference to fixed point, and
Thus the information of required route, speed and/or acceleration is collected.Hoistway massaging device preferably passes through such as in hoistway is cheated extremely
A few reference point measures absolute position.
First basic conception
Fig. 1 shows the function that can be used for realizing the above-mentioned type elevator of first embodiment of the invention.
In the first conception, elevator according to the present invention is equipped with deadman's brake ESB, preferably by least two
Electronic elevator car brake unit 7a, 7b composition, they are connected to lift car and act on and lead in different positions
Rail.Generally, each of deadman's brake elevator car brake unit is formed to be so designed and can be by lift car
Control device 10 controls, that is, the application rate of its brake lining or power can be affected whereby.The control device of the lift car
10 can be the control device for being specific to brake, not control the opening and closing of other functions such as car door.In order to control it
Its function, lift car can be equipped with another control devices realized in the form of separate part, and the device is not by Fig. 1 or Fig. 2
It shows.The control device for being only associated with brake can be by physical integration into brake unit.
In this way, the terraced comfort of row can be improved, such as because softer application brake lining becomes after stop stop
It is feasible, it does not make a noise or does not almost make a noise.Optionally, safety can also be improved, because it is contemplated that very
In the terraced situation of rule row more slowly and thus more mildly starting braking.In order to realize deadman's brake ESB, it is preferred to use below will
The elevator car brake unit being more described in detail in the application framework.
In addition, elevator according to the present invention is equipped with electronic additional brake ESG, itself is preferably electronic by least two
Additional brake unit 8a, 8b are constituted, they are attached to the different parts of lift car and act on guide rail.Additional brake
ESG is controlled also by the control device 10 of lift car.For the sake of complete and it is to be noted that the control device of lift car
10 can be optionally the control device for being only attached in and being possible to be integrated into car brake.Then, it can be by
The referred to as control device 10 of elevator car brake.Being designed in this way additional brake may be advantageous, that is, with deadman's brake
And its preferably variable response time is compared with response intensity, the response time of additional brake is always most short, and response intensity is total
It is highest.It in the case can be using the brake in traditional brake gear, safety tongs and progressive safety gear form
Unit.
But typically, they are not designed to not apply required brake force individually, and only apply part of it,
And the remainder of brake force needed for maximum is applied by deadman's brake.Then, it is different from standard, the free falling feelings of worst
Condition by deadman's brake and additional brake come co- controlling, so that these brakes be caused necessarily to interact.
It should be mentioned that the control of deadman's brake ESB and the control of additional brake ESG are preferably by above-mentioned elevator
Carriage control device complete or at least one of which described in brake can also be controlled by central elevator control gear and/
Or triggering.
In order to realize additional brake ESG, preferably such brake unit is also as described later in the application framework
Inside be used, can cascade operation and will be combined for realizing brake unit needed for deadman's brake with additional brake
At the brake unit of single elevator car brake unit.
Preferably realize power distribution between deadman's brake ESB and additional brake ESG, with realize two brakes it
One can apply at least the 40% of brake force, more preferably at least 45%, which pacified in lift car full and down
Necessary to full control free falling, and supplies 100% brake force part and applied by another brake.With regard to the two brakes
Preferably not fully or it is substantially identical for, additional brake ESG is preferably capable of applying that of more a part of brake force
Brake.
In order to realize the present invention it may be advantageous that according to the introduction of the first conception, deadman's brake ESB makes with additional
Dynamic device ESG is attached to the different parts of lift car.Brake unit 8a, 8b of the additional brake ESG of strong reaction is excellent
Choosing is attached in the lower half of lift car, ideally in the lower a quarter of lift car.React soft safety system
Elevator car brake unit 7a, 7b of dynamic device ESB is preferably attached in the upper half of lift car, ideally in elevator car
In the upper a quarter in compartment.
As already described, the control device 10 that lift car can be set is moved with lift car 4.Control device
10 be the above-mentioned type.Elevator control gear 9 of the control device 10 of lift car preferably with execution stairlift unit comprehensive management
Communication.Nevertheless, the control device 10 of lift car is generally also configured to its energy auto-action, i.e., open loop is executed automatically
Control or closed-loop control.
Generally, the control device 10 of lift car or elevator car brake itself (brake unit itself) equipped with
Emergency Power, even if thus under power blackout situation, Emergency Power can at least keep additional brake ESG open and control it.
Generally, the control device 10 of already mentioned lift car is connect directly to hoistway information system, then continues
Ground directly through central elevator control gear 9 receive or through central elevator control gear 9 handle receive current route, speed and/
Or the information of acceleration, current location and the current motion state of lift car can be determined whereby.
Independently with hoistway information system and the information of the route conveyed by it, speed and/or acceleration, lift car
Control device 10 can add including at least one, more preferably at least two acceleration transducers, they individually generate acceleration
Signal or use have included the acceleration signal of the sensor in brake unit.Being designed in this way brake is an option,
I.e. they can be by the acceleration signal of above-mentioned acceleration transducer by direct actuation.
As already described, it is attached to be preferably connected directly to ESB deadman's brake 7a, 7b and ESG for lift car control device 10
Add brake 8a, 8b, (and if is needed with causing lift car control device 10 that can start deadman's brake ESB independently
Want additional brake ESG), do not involve central elevator control gear 9.
The control device 10 of lift car preferably includes the circuit of two independent roles, one of them is considering hoistway information
ESB deadman's brake 7a, 7b are controlled under system situation, another is considering the letter from least one coriolis acceleration sensor
ESG additional brake 8a, 8b are controlled in the case of breath.
The control device 10 and deadman's brake ESB and additional brake ESG and (optionally) center electricity of lift car
The combination of terraced control device is designed to may be implemented at least one of the following conditions, more preferably several and preferably all:
Free falling:
If such as find free falling because there is abnormal acceleration signal and do not power off, it is preferred to pacify
Full application of brake device ESB and additional brake ESG are activated, thus their common brakings.Hereby, the starting of deadman's brake ESB
It is preferred that so carrying out, i.e., it is at full throttle applied.Same situation is preferably adapted to additional brake ESG, as long as the latter is not
It is configured to always at full throttle to apply after its starting.
Hereby, deadman's brake ESB and additional brake ESG is designed to them and is assisted jointly with the deceleration of 0.2g to 1g
Make to intercept the lift car for being furnished with rated load, and can exceed that 1g with the deceleration of empty lift car.
Generally, the starting of deadman's brake ESB will be by the signal conveyed by hoistway signal system and by lift car
At least one first circuit of brake occurs.The starting of additional brake ESG can be additional by least one above-mentioned
Acceleration transducer or occur by least one other independent circuits of elevator car brake control device.
If such as find free falling due to there is abnormal acceleration signal while power-off, safety arrestment
Device ESB is responded because of power-off, unless it before because cross high acceleration and based on by hoistway information system or at least one
The signal that acceleration transducer is conveyed has been activated.Generally, occur inevitably to apply (closure) peace under power blackout situation
Full application of brake device ESB, this is because the power for maintaining it in open position disappears because of power-off.Additional brake ESG is different.
It is connected to the Emergency Power for actually keeping it to open, so that additional brake ESG itself is not still opened because of power-off
It is dynamic, but preferably because at least one described additional acceleration transducer conveying shows the acceleration signal or electricity of free falling
The control device of terraced car brake finds the carriage undermoderated by ESB.If Emergency Power also fails, additional brake
Device ESG will also be applied because of power-off.
Herein, the two brakes are designed to them again can cooperate interception equipped with specified with the deceleration of 0.2g to 1g
The lift car of load, and can exceed that 1g with the deceleration of empty lift car.
Promptly stop ladder:
For example because one of elevator shaft door be expert at ladder during open and without power-off promptly stop terraced situation under,
Deadman's brake ESB is started by safety return circuit, and additional brake keeps invalid.Deadman's brake is preferably at full throttle applied
With.
Hereby, deadman's brake is preferably designed to it and causes deceleration less than 1g with this starting, usually because
It has an instinct for for maximum deceleration degree obtained by it less than 1g.
Similarly, same situation is suitable for promptly stopping the interference of ladder and power-off, and it is disconnected that difference is that deadman's brake passes through
Electricity is activated, unless having responded to before safety return circuit.
It exceeds the speed limit (tow strap):
If such as because there is ultraspeed signal (in the case where may having at the same time non-critical acceleration signal)
And detect tow strap hypervelocity and do not power off, then deadman's brake ESB will be activated, and additional brake ESG is stayed open.
The deadman's brake is preferably at full throttle applied.Hereby, deadman's brake is designed to it and applies the deceleration for being less than 1g.One
As, the starting of deadman's brake will occur by the signal conveyed by hoistway information system.
Similarly, same situation is suitable for the interference that tow strap exceeds the speed limit and powers off, and it is disconnected that difference is that deadman's brake passes through
Electricity is activated, unless having responded before safety return circuit.
Stop is stopped:
Deadman's brake ESB is activated, and additional brake ESG is stayed open.
The starting of deadman's brake ESB, which is slowed down, to be occurred, and is applied before reaching maximum braking force and/or retentivity with realizing
The speed of deadman's brake, which is reduced in order to not issue, disturbs people's noise.
If powered off at the place of stopping, deadman's brake ESB is closed completely (unless having done so) simultaneously because of power-off
And closure is always maintained at during power-off.But additional brake ESG is stayed open.
Deadman's brake ESB will be always closed, thus if lift car has pulled up the correct position stopped, it
Lift car is maintained at some position, the current lift car weight no matter changed due to the loading at the place of stopping herein and unloading
How.
So load and uninstall process after do not throw open but slow down that open deadman's brake ESB may be to have
Benefit, i.e., lift car does not decline several millis under load that now may be heavier before starting practical row ladder noticeablely
Rice.The control device 10 of lift car is accordingly designed.
This moment, it is important that emphasize again that another invention (also requiring independent protective) be such improvement and design elevator and
Its brake, that is, when starting to sail out of, elevator car brake (being in most cases deadman's brake ESB) passes through storage
Pressure in accumulator is opened, and hydraulic pump delay start.This substantially improves the terraced comfort of row: hydraulic pump will be in elevator
Carriage is enough not to be activated before the speed traveling for covering the traveling noise that hydraulic pump makes a noise with generation again.It is best thus
As it is above it is described in more detail as accumulator use additional brake ESG.Equipped with the speed control for hydraulic pump
Device is an advantage, allows to improve hydraulic pump speed according to the elevator car speed of quickening when new row ladder starts.This
Sample, hydraulic pump are preferably controlled such, and revolving speed and in turn its noise issued are with the practical speed of the lift car for leaving stop
It spends and increases.
Wait ladder
If it is in its waiting position for next row ladder that lift car, which is in and waits ladder, deadman's brake ESB will
It remains closed to reduce energy consumption.But additional brake ESG is stayed open and keeps stopping so as to can be no matter any reason occurs
Intervene at once when free falling.
Emergency terminal is slowed down
Deadman's brake ESB and its corresponding control device are preferably designed as deadman's brake once having found lift car
It is just closed with excessively high speed for normally stopping ladder close to minimum stop or highest stop.
Emergency relief
Deadman's brake ESB and its affiliated control device are preferably designed as automatic emergency occurring when by lower button
Rescue: when corresponding starting, deadman's brake ESB is partially opened, thus lift car can be moved to limited speed it is attached
Close stop, even without the motor power by carriage or the main gravity drive of counterweight.Motor equipped with traction sheave is grasped herein
It will be preferably short-circuited to generate braking moment during work.
Guard space in pit or hoistway head
Deadman's brake ESB and its corresponding control device are preferably designed as once finding that someone enters pit or well
Trace header they will guarantee the guard space in pit or hoistway head automatically.
Second basic conception
Fig. 2 shows the function of the elevator of the above-mentioned type, can be used to realize the second embodiment of the present invention.
In this embodiment, elevator according to the present invention equipped with deadman's brake ISB, it by least one and it is best
Two electronic elevator car brake unit 7'a, 7'b are constituted, they are attached to the different parts of lift car and effect
In guide rail.
Deadman's brake ISB can be so designed and control, i.e., its application rate can be affected, and its brake force
It can be affected, be affected preferably by closed-loop control.
Different from first embodiment of the invention, not set additional brake herein.Deadman's brake ISB is designed to
It can individually manage all possible normal and abnormal operation conditions.
For this purpose, each described elevator car brake unit 7'a, 7'b is equipped at least one actuator, it is more preferably several
Actuator is preferably made of several piston-cylinder units, especially for acquisition partial redundance.
In addition, Emergency Power is typically provided, to deadman's brake ISB and in most cases to hoistway signal system
Energy supply.
Special thing about this system is that it is designed and configured to the system for making to be provided by elevator car brake unit
Power can be by opened loop control and/or preferably by closed-loop control.
Acceleration transducer 10a, the 10b of itself are preferably associated with each elevator car brake unit 7'a, 7'b, letter
It number is opened loop control or the basis of preferably closed-loop control of the brake force of corresponding elevator car brake unit 7'a, 7'b.
Corresponding acceleration transducer 10a, 10b are preferably integrated into and/or are connected to corresponding elevator car brake unit.It is ideal
Ground, at the control signal of elevator car brake unit 7'a and/or 7'b and/or the generation of adjustment signal and corresponding signal
Reason also directly within corresponding elevator car brake unit and/or place occur.For this purpose, each elevator car brake list
Member be preferably designed to it by it is hydraulic it is self-sufficient in a manner of work, i.e., each elevator car brake unit has itself hydraulic
A full set of hydraulic valve, pipeline and other hydraulic auxiliary required for pump 19, the equalizing box of itself or pressure equalising vessel 20 and its operation
Facility.
Several elevator car brake units are connected with each other, and are preferably connected directly, but at least through lift car
The control device of brake connects.Then, corresponding signal and/or movement can be compared with each other to find in early stage
Presumable failure.It is desirable that even there is dual connection: between several elevator car brake units, both existing and pass through
The direct information of signal wire 10c exchanges, and there is also the exchanges of the collateral information of the control device by elevator car brake.
If it find that failure, then lift car will be stopped after reaching next bus stop.
The system is designed to may be implemented at least one of the following conditions, more preferably several and preferably all.
Free falling:
If such as finding free falling because there is correspondingly high acceleration signal, brake is applied simultaneously with prestissimo
And preferably by such closed-loop control, that is, setting is less than the deceleration of 1g, it is generally desirable to subtract in 0.5g to medium between 0.7g
Velocity form.As previously mentioned, acceleration transducer 10a, 10b are assigned to each elevator car brake unit, signal quilt
For adjusting.Because there are closed-loop control, therefore which type of load lift car is assigned not important, required deceleration
Always it is conditioned.
This is also suitable under power blackout situation, as long as Emergency Power power supply correctly plays a role.
If such as finding free falling because there is correspondingly high acceleration signal and if total power-off (electric wire electricity also occur
Stream interrupts and Emergency Power failure), deadman's brake ISB will make a response because of power-off, unless it is because crossing high acceleration
And the information conveyed based on hoistway information system is started in advance.The latter keeps it generally because following facts will occur
Power in an open position disappears because fully powered-off.
Promptly stop ladder:
In the case where having opened during for example being taken because of one of elevator door and promptly stopped ladder, safety arrestment
Device ISB is started by safety return circuit.The preferred prestissimo application of the deadman's brake.Then, deadman's brake is preferably so closed
Ring controls, i.e., it causes the deceleration less than 1g, it is generally desirable in 0.5g to the medium deceleration form between 0.7g.
Similarly, same situation is suitable for promptly stopping ladder and fully powered-off interference (cuts off wire current and urgent electricity
Source failure), difference is exactly that deadman's brake is started by power-off, unless having responded before safety return circuit.In the case, safety system
Dynamic device will generate maximum deceleration.
It exceeds the speed limit (tow strap):
If such as because there is ultraspeed signal (may have at the same time non-critical acceleration signal in the case of) and
It was found that tow strap exceeds the speed limit, then deadman's brake will be activated.The deadman's brake preferably at full throttle application and therefore preferably by
The deceleration that so control, i.e. setting are less than 1g, ideally in the medium deceleration form between 0.5g and 0.7g.
Stop is stopped:
Deadman's brake ISB is activated.
The starting of deadman's brake preferably passes through throttle valve or is occurred by opened loop control or closed-loop control, to realize safety
The application rate of brake is affected by throttle valve or opened loop control or closed-loop control and/or is reduced so as not to generate and disturb people and make an uproar
Sound.This might mean that the deadman's brake is closed with all strength, but it has taken certain time before it can get all one's effort.
If had fully powered-off (wire current interrupt and Emergency Power failure) at the place of stopping, deadman's brake ISB because
It powers off and is closed completely (unless having done so) and is remained closed during power-off.
The deadman's brake will be always closed, thus if lift car has pulled up the correct position stopped, it
Lift car is maintained on some position, the current weight of the lift car no matter changed due to the place of stopping loads and unloads herein
How is amount.
This moment, it is important that emphasize again that another invention (also requiring separately protected) be such improvement and design elevator and its
Brake, that is, when sailing out of beginning, elevator car brake ISB is opened by the pressure being stored in accumulator, and hydraulic
Pump delay start.It has been explained hereinbefore that details.
Emergency terminal is slowed down
Elevator car brake ISB and its corresponding control device are preferably designed as once finding lift car for just
Excessively high speed is just closed close to minimum or highest stop deadman's brake for often stopping.
Emergency relief
Elevator car brake ISB and its corresponding control device are preferably designed as to occur when by lower button certainly
Dynamic emergency relief: when corresponding starting, elevator car brake ISB is partially opened, so that lift car can be with limited speed
Degree moves to neighbouring stop, even without by be mainly carriage or counterweight gravity drive motor power.Equipped with traction sheave
Motor will be preferably short-circuited to generate braking moment in this operating process.
Guard space in pit or hoistway head
Elevator car brake ISB and its control device are preferably designed as once finding that someone enters pit or hoistway
Head they will guarantee the guard space in pit or hoistway head automatically.
The hydraulic principle of elevator car brake unit according to the present invention
First of all, it is necessary to provide the general information about brake unit of the invention.
Theoretically, one be only arranged in car brake unit of the present invention is just much of that.It is thus also claimed to this.Electricity
Terraced carriage is preferably equipped at least two car brake units of the present invention from different rail interactions.
First of all, it is necessary to provide certain general informations about the valve.
Referred to below as the valve of V1 is so-called short valve, it blocks or disconnect the first work directly by hydraulic actuator
The so-called short-circuit pipeline of chamber 14 and the interconnection of the second working chamber 15.The valve will need emergency braking to terminate abnormal operating condition
In the case where be opened.Valve V1 is for making brake become failure safe, this is because it guarantees quick brake application, i.e.,
Just other valves do not work correctly.
Unless otherwise defined, otherwise referred to below as the valve of V2 is so-called control valve, opened loop control or closed-loop control
Moment brake force in braking process.The valve of the V2 type is preferably in the valve form of so-called dedicated on-off operation, the institute as before
As explaining in detail.
It is below so-called throttling control valve as the V3 valve being previously mentioned, is used to open or closes choke flow line so as to electricity
Terraced carriage applies liquid braking device while noise is reduced among the process that stop is stopped or later.Throttling control valve itself can produce
Raw throttling action and/or choke flow line itself can produce required throttling action, as previously detailed.
It is below combination valve as the V23 valve being previously mentioned, realizes the function of above-mentioned valve V2 and the function of above-mentioned valve V3 simultaneously
Energy.
It is below brake relief valve as the V4 valve being previously mentioned, opens or closes brake discharge line so as to not
Brake is at least partly discharged in the case of starting hydraulic pump to the degree that can start new row ladder.
It is below combination valve as the V34 valve being previously mentioned, realizes the function of above-mentioned valve V3 and the function of above-mentioned valve V4 simultaneously
Energy.
Unless otherwise expressly provided, otherwise valve is proportioning valve, rather than switching valve in the sense of the present invention.
Unless otherwise clearly notifying, otherwise all valves are following valves, and open allows hydraulic fluid stream when power is off
It crosses.
In the accompanying drawings, this is indicated by spring part, and spring part is pressed on movable spool.Principle is exactly, once no matter which kind of
Reason can not obtain the power supply to valve again, and valve is opened at once and thus applies maximum braking force.
Fig. 3 a shows the hydraulic tube line chart for the car brake unit of the invention that be used in elevator claimed.
Car brake unit includes first group of hydraulic actuator 11.1.1-11.1.x and second group of hydraulic actuator
11.2.1-11.2.x.Each actuator includes the cylinder 12 with piston 13, and cylinder is divided into the first working chamber 14 and the by piston
Two working chambers 15.In addition, each actuator includes the piston rod 31 and spring part 17 for acting on brake lining 16, spring part
It is main spring unit a part responsible to brake force needed for generating, even if in hydraulic failure.
About brake lining 16, it is necessary to notify the following contents with being generally adapted for all embodiments:
Each of at least two actuators can act on (compressing) single brake lining or shared brake lining.
As can be seen, all first working chambers 14 of actuator 11.1.1-11.1.x are in direct hydraulic communication
In, they connect along a hydraulic loop 114.In addition, the second all working chambers 15 of actuator 11.1.1-11.1.x are in
In direct hydraulic communication, connect along the hydraulic loop 115 for forming " common rail ".If valve V4 is open, it is all have it is hydraulic
First working chamber 14 of actuator is connected as all second working chambers 15.
The hydraulic pump and control valve V23 are in place in 14 front upstream of working chamber.It is used herein and in the application to place
Term " upstream " be related to single quadrant run when hydraulic pump 19 pumping direction.It means that the on the pressure side D of pump 19 is the
The upstream of one working chamber 14 pumps 19 suction side S in the downstream of the second working chamber 15.
Downstream of the short valve V1 after working chamber 14 is in place.Only valve V4 be located at the identical working chamber of two functions it
Between, it is between two the first working chambers 14 in that particular case.
It is assumed to be normal condition, hydraulic pump is under single quadrant operating condition in continuous deceleration lift car into stopped process
It is operated without speed control, power control, Torque Control or frequency control.The first work of on the pressure side D supply of hydraulic pump 19
Chamber 14, and the suction side S of hydraulic pump 19 is connected to the second working chamber 15, so that hydraulic fluid can be sucked out in it therefrom.Equipped with list
To valve CV be used for guarantee pump shut down when and valve V23 be closed when not by pump 19 hydraulic fluid return.
Equipped with control pipeline 39, by the hydraulic loop of the hydraulic loop 115 of the second working chamber 15 and the first working chamber 14
114 are connected directly.Control pipeline 39 is operated by control valve V23.
When the delivering hydraulic fluid in the case where control valve V23 is in fully closed always of hydraulic pump 19, brake will be fast
Quick-release is put, because hydraulic pump extracts hydraulic fluid out from the second working chamber 15, is pumped into the first working chamber 14, if valve V4 is to close
This closed occurs in hydraulic actuator 11.1.1-11.1.x, and in all hydraulic actuator if valve 4 is open
11.1.1-11.2.x occur.
If control valve V23 is shown in a fully open operation always, pipeline 39 is controlled by the hydraulic loop 115 of the second working chamber 15
It is short-circuit with the hydraulic loop 114 of the first working chamber 14, so that brake will be applied quickly, because hydraulic fluid will be from the first work
Chamber 14 is discharged to the second working chamber 15.The lasting pump-absorb action of hydraulic pump 19 will be kept to no effect, because hydraulic in the case
Pump is also short-circuited.
In consideration of it, obviously can be by accordingly adjusting from the amount of hydraulic fluid that the first working chamber 14 flows into the second working chamber 15
The moment flowed friction of control valve V23 controls.As explained above, " open degree " of valve V23 can be by being associated with valve V23's
Controller remote control, the frequency being such as moved forward and backward by adjusting spool.
As described above, valve V23 can be realized throttling action, it is accordingly provided in slow braking among stop layers process or later
Device application.Thus one, unexpected carriage can not be avoided to move with making a noise.
As can be seen, it adds and is equipped with short-circuit pipeline 40, it works the hydraulic loop 114 of the first working chamber 14 and second
The hydraulic loop 115 of chamber 15 is connected directly.Short-circuit pipeline 40 is short-circuited valve V1 operation.In an emergency braking situation, valve V1 and
Valve V23 is opened, to generate the braking action of hydraulic actuator 11.2.1-11.2.x as early as possible.Even if all other valves are answered
Occlusion, valve V1 also brake actuator 11.2.1-11.2.x.In general, all valves are opened to realize emergency braking, thus hydraulic
Fluid can be discharged into the second working chamber 15 from the first working chamber 14 as early as possible.
Valve V4 has several Xiang Gongneng.
Firstly, actuation actuator 11.1.1-11.1.x and 11.2.1-11.2.x independently of each other may be implemented in valve V4.This
Sample can realize above-mentioned conception " ESB and independent ESG " with one in these brake units.As long as valve V4 is remained turned-off,
ESB function is only then realized by actuator 11.1.1-11.1.x.When valve V4 and/or valve V1 is additional to be opened, actuator
11.2.1-11.2.x ESG function is executed.
In addition, valve V4 can prepare to start to discharge actuator 11.1.1-11.1.x when row newly is terraced in carriage, and hydraulic pump 19
Still shutting down in order to avoid issuing the noise that can hear, lift car is still in stop at this time.
For this purpose, valve V4 is opened, thus by loop 114,115 will occur in actuator 11.1.1-11.1.x and
11.2.1-11.2.x the first working chamber and the second working chamber between pressure compensation.As a result, actuator 11.2.1-11.2.x
Part is closed, and part discharges actuator 11.1.1-11.1.x.Now, brake force at least reduces to following degree, i.e. lift car
It can start new row ladder, but start hydraulic pump 19 not during lift car stops at stop.
Hydraulic pump 19 will be activated after new row ladder has started, preferably not lift car traveling noise at least with it is hydraulic
Pump issued noise it is equally big before, thus hydraulic pump noise does not influence the terraced comfort of row.
Valve V4 preferably guarantee actuator 11.1.1-11.1.x with the throttling of actuator 11.2.1-11.2.x is hydraulic is connected.This
Sample, the pressure compensation between the actuator group will not occur suddenly and audibly when valve V4 is opened, but sluggish
Without making a sound pulse.
Fig. 3 b shows and to be used in and car brake unit as shown in Figure 3a and as explained above is closely related is wanted
Seek the hydraulic tube line chart of the car brake unit of the invention in the elevator of protection.
The all situations explained before are also applied for the embodiment according to Fig. 3 b, if the difference then explained without for fear of
This.
It is that check valve CV is omitted and valve V23 exists according to the embodiment of Fig. 3 b and unique difference of the embodiment according to Fig. 3 a
Functionally it is divided into valve V2, V3.
This allows the hydraulic pump to operate under dual quadrant operation, such as that being explained in detail below when discussing Fig. 4 a and 4b
Sample: moment in the first and second working chambers 14,15 is hydraulic by the conveying direction or antiport hydraulic pump is as hydraulic
Generator or for hydraulic fluid flowing retarder by opened loop control or closed-loop control.In that particular case, valve V2 is preferred
It is not intended to the valve of dedicated on-off operation.Its unique function be prevent through hydraulic pump, cause first and second working chamber it
Between the equilibrium of undesirable pressure small amount of leakage, such as lift car overnight long period period wait ladder when.
Valve V3 does not make a noise at stop for brake as explained above, and ground is slow to be applied.
Fig. 3 c show will be used in elevator claimed in, compared to what is changed according to the embodiment of Fig. 3 a
The hydraulic tube line chart of car brake unit of the present invention.
This embodiment is only with one group of hydraulic actuator 11.1.1-11.1.x and additional accumulator 111.Preferably, pressure accumulation
Device 111 have with the structure as actuator 11.1.1 etc., except for the facts that, the piston rod 31 of accumulator is not attached to braking
Piece.Advantage of this is that even if the piston rod 31 of accumulator is drained to discharge actuator 11.1.1- in the first working chamber
Mobile when 11.1.x, this is contacted without result in the towing between the brake(-holder) block and braking rail for corresponding to its piston rod.
About a working chamber and preferably the second working chamber 15, all actuator 11.1.1-11.1.x and accumulator are forever
Long in directly hydraulically interconnected.That is their the second working chamber including the second working chamber of actuator along
Form a hydraulic loop 115 series connection of the permanent common rail for these hydraulic chambers.
About another working chamber and preferably the first working chamber 14, all actuator 11.1.1-11.1.x are in direct
In hydraulically interconnected.That is the first working chamber 14 is connected along a hydraulic loop 114.If valve V4 is open, pressure accumulation
Device 111 is also connected to hydraulic loop 114 with its first working chamber.Otherwise, accumulator 111 is switched off.
Equipped with hydraulic pump 19, it is by the downstream of upstream end (pump is on the pressure side) and hydraulic loop 115 of hydraulic loop 114
(suction side of pump) is connected directly.Pump is single quadrant operation, as explained above.Furthermore it is possible to which pressure equalising vessel 20 is arranged.
Because designing thus, all actuator 11.1.1-11.1.x can only be synchronized actuation.That is single this elevator
Car brake can not be used to realize ESB and ESG as described above.On the contrary, this elevator car brake is set as described above
It sets and is run for ISB.
Different from shown in Fig. 3 a, valve V1 and V3 herein and are not disposed on the end of hydraulic loop 114,115.On the contrary, will
The hydraulic loop or hydraulic line that valve V1-V3 is connected with hydraulic loop 114 and 115 between two adjacent hydraulic actuators
Hydraulic loop 114,115 central fascicles come out.This means that this embodiment has more than one control hydraulic line or loop
Valve, the hydraulic line or loop are branched off between the identical working chamber of two neighboring function.In this embodiment, in this way
Valve be at least valve V2, V3.The control pipeline 39 of valve V2 is from two the first working chambers 14 (one in upstream and one in downstream)
Between hydraulic loop 114 be branched off and between two the second working chambers 15 (one upstream and one in downstream)
Hydraulic loop 115 is branched off.The choke flow line 41 controlled by valve V3 is arranged according to principle identical with control pipeline 39.
The each function of being separated from each other valve completely may be implemented in this.Therefore, it is possible to ground entirely independent of each other valve design V2, V3
And V4.
Another advantage of this hydraulic design is the fact that, is not needed during lift car is stopped at before stop to any
Valve energy supply.Nevertheless, complete brake force still can be obtained.
Especially brake can be applied with not making a noise by throttle valve V3 before stop.
The brake can be discharged with not running hydraulic pump when lift car is just starting another row ladder.For this purpose, valve V4 will
It is opened.In this way, a part of hydraulic fluid of the savings in the first working chamber 14 of accumulator 111 will be forced into actuator
11.1.1-11.1.x the first working chamber, so that these actuators can at least be released to the degree that can start new row ladder.
The opened loop control for the brake force that moment applies or closed-loop control as explained above can be by designed for special
It is realized with the valve V2 that on-off is run.
Fig. 3 d shows the hydraulic of the another kind that be used in elevator claimed car brake unit of the invention
Conduit line map.
Hydraulic car brake unit includes one group of hydraulic actuator 11.1.1-11.1.x and another group of hydraulic actuator
11.2.1-11.2.x, it is explained as before about Fig. 3 c.
About a hydraulic chamber and preferably the second hydraulic chamber 15, all actuator 11.1.1-11.2.x are again
It is secondary in directly hydraulically interconnected.That is all working chambers 15 are permanently gone here and there along a hydraulic loop 115 for forming common rail
Connection.
About another working chamber and preferably the first working chamber 14, these actuators are divided into two groups by valve V4: as long as should
Valve V4 is closed, and just has one group of actuator 11.1.1-11.1.x to have working chamber (such as the chamber for being permanently in direct hydraulic communication
14), there are also another group of actuator 11.2.1-11.2.x, wherein such working chamber is also permanently in direct hydraulic communication.
Equipped with hydraulic pump 19, by the downstream of upstream end (the pump pressure side) and hydraulic loop 115 of hydraulic loop 114
(pump suction side) is connected directly.Pump is that single quadrant is run as described above.In addition, pressure equalisation container 20 can be equipped with.
There are also another loop for being in 41 form of choke flow line, it is by the upstream end of hydraulic loop 114 and hydraulic loop 115
Downstream is connected.Choke flow line 41 is opened or is turned off by valve V3.The opening of valve V3 allows by first group of actuator 1.1.1-
11.1.x the soft application of the brake(-holder) block operated, and the noise that can be heard is not issued or the reduction that makes a noise.Therefore reason, valve
V3 applies restriction effect or with restriction effect control loop.
The valve V2 and V1 of parallel arrangement itself are located at hydraulic loop, and hydraulic loop is directly by second group of actuator 11.2.1-
11.2.x downstream of first working chamber 14 through hydraulic loop 114 is connected with the upstream end of hydraulic loop 115.
Unexpected carriage movement during stop layers in order to prevent, only one group of actuator is by actuation, it is described herein
Group 11.1.1-11.1.x.This group of actuator is by actuation, so that it is dynamic to generate braking by the valve V3 for opening control choke flow line 41
Make.By the choke flow line 41, hydraulic fluid can be discharged into from the first working chamber 14 of actuator 11.1.1-11.1.x its
Two working chambers 15.
In order to not discharge brake with not running hydraulic pump when lift car to be ready starting another row ladder, valve V4 will be beaten
It opens.In this way, a part of hydraulic fluid of the savings in the first working chamber 14 of second group of actuator 11.2.1-11.2.x will be forced
It is pressed into the first working chamber 14 of first group of actuator 11.1.1-11.1.x, so that these actuators, which are at least released to, to be started
The degree of new row ladder.
In order to execute the lift car automatic brake of opened loop control or closed-loop control, valve V2 opened loop control or closed-loop control by
The brake force that actuator 11.1.1-11.2.x is generated.Hydraulic pump delivering hydraulic fluid enters the of actuator 11.1.1-11.1.x
One working chamber 14, and the first working chamber 14 of actuator 11.2.1-11.2.x is flowed to through loop 118,119 and check valve CV2,
And hydraulic fluid is extracted by pump from all second working chambers 15 through loop 115 (common rail) at this time.The practical liquid of control valve V2
Pressure resistance is lower, and the actual pressure in the first working chamber is lower, and actual braking force will be higher.
Because of particular topology thus, the execution of ESB/ESG operation as described above can not be realized with practical degree of correlation.
Check valve CV2 allows to fill this group of actuator 11.2.1-11.2.x, this is not before for running 19 ground of hydraulic pump
Open brake: if pressurized fluid is conveyed into the upstream end of hydraulic loop 114 by the pump, which can be through check valve CV2
Reach the working chamber 14 of actuator 11.2.1-11.2.x.
Check valve CV1 prevents the dangerous leakage when hydraulic pump stops from flowing to ring from the upstream end of loop 114 through hydraulic pump
The downstream on road 115.
Individual embodiment is not shown in Fig. 3 e.On the contrary, embodiment shown in Fig. 3 e is identical as embodiment shown in Fig. 3 d.Figure
3e is served only for alloing visible by the corresponding arrow in valve member picture by the hydraulic flow direction of valve.It can see in this way
The hydraulic fluid that the valve is channeled out using common hydraulic loop to valve V1 and V2, which is entered, orderly connects all second
The hydraulic loop 115 of working chamber 15.
It can thus see that it is two-way for flowing through the flow of pressurized of valve V4.Then, it can be seen that flow through valve V3 (when opening)
Flow of pressurized be guided to hydraulic loop 115 from hydraulic loop 114.
Fig. 3 f shows the embodiment being slightly different compared to Fig. 3 e, the two embodiments are closely related.Therefore reason, for
All things that embodiment 3d and 3e are explained are correspondingly suitable for use in the embodiment according to Fig. 3 f.
Above-mentioned Fig. 3 d and 3e and unique difference of the embodiment according to Fig. 3 f can be relatively seen with valve V4.According to figure
In the embodiment of 3f, valve V4 is designed to its closing when not energizing, and in other embodiments described above, valve V4 is not being energized
When open.This design change is for energy conservation, if lift car is just waited before stop.
Fig. 3 g show will be used in elevator claimed in the brake list as shown in Fig. 3 d, 3e and 3f before
The hydraulic tube line chart of the closely related brake unit of the invention of member.Therefore reason, the thing explained above in relation to these figures
Feelings are accordingly applicable in herein.
Unique difference is that valve V3 and V4 have been merged now.The two valves be combined valve V34 substitution.This substitution can be smooth
It realizes, because valve V4 and V3 used by before must always inverted running, that is, if valve V3 is turned off, valve V4 is
It opens, or vice versa.
In order to explain this point, people must imagine when what lift car had occurred when stop has stopped.
This moment, valve V34 is so switched, i.e., it completes the hydraulic function originally executed by valve V3.
In order to complete the function of previous valve V3, valve V34 is so switched, i.e., it directly will be in actuator by throttling passage
11.1.x the hydraulic loop 114 in downstream is connected with hydraulic loop 115, which forms for the second working chamber 15
Above-mentioned " common rail ", as Fig. 3 g directly shown in.In this way, hydraulic fluid can be from the first work of hydraulic actuator 11.1.1-11.1.x
Make the second working chamber 15 that chamber 14 is discharged into hydraulic actuator 11.1.1-11.1.x.As a result, these hydraulic actuators are not issued and are made an uproar
It is closed to sound (because throttling) and generates the braking maneuver for preventing unexpected carriage movement.
Once lift car starts new row ladder, valve V34 is handed off its another operating position.In this position (as schemed
3g is as shown in action position or energization position) on, valve V34 is by the working chamber 14 of actuator 11.2.1-11.2.x and hydraulic cause
The working chamber 14 of dynamic device 11.1.1-11.1.x is connected, so that all working chamber 14 of all actuators is now by continuous
" common rail " of 114 form of loop is connected.In this way, a part of savings in the working chamber of hydraulic actuator 11.2.1-11.2.x
Hydraulic fluid can be discharged into the working chamber 14 of hydraulic actuator 11.1.1-11.1.x, and the hydraulic actuator is in this stage
19 ground of hydraulic pump is not operated is at least discharged into the degree for allowing to start new row ladder.That is having been reached again in lift car
To being enough to generate traveling noise so that hydraulic pump 19 will not be opened before the speed that the noise that hydraulic pump 19 issues no longer disturbs people
It is dynamic.
One advantage of this hydraulic layout by combination valve V34 is can to save an independent valve, it reduce at
This.
The disadvantage is that a certain extent " pressure loss " will when valve V34 just switches between two position, because
For in handoff procedure, hydraulic pressure short circuit occurs within a very short time.This disadvantage can be by being mended with slide valve form design valve V34
It repays.But slide valve is sensitive to dust and usually also shows that certain internal leakage for disturbing people herein.
Fig. 3 h shows another embodiment for the car brake unit of the invention that be used in elevator claimed
Hydraulic tube line chart.
One actuator 11.1.1 is only shown in this figure.But this embodiment is not limited to using an actuator.Phase
Instead, one group of actuator 11.1.1-11.1.x can be used.The thing uniquely to be done be exactly by the form of common rail realize loop 114,
115 are connected all working chamber 14 of these actuators with all working chamber 15.
In this embodiment, the downstream below working chamber 14 is equipped with valve V1, V2 and V3.These valves are in a manner of hydraulic parallel
Arrangement.Loop in parallel including these valves is passed through the common loop 116 for the suction side for being directly communicated to hydraulic pump 19.
Upstream in the hydraulic loop 114 for the first working chamber 14 for leading to actuator is equipped with valve V4.The input side of valve V4
With being on the pressure side connected for hydraulic pump 19.
Here, special thing is exactly accumulator 111, it directly with the suction side of hydraulic pump 19 and with hydraulic pump 19
On the pressure side it is connected.
The very special design of another kind as used herein is connection loop 117, is provided from loop 116 to hydraulic actuation
The direct path of second working chamber 15 of device.
Valve V2 is used for opened loop control or the closed-loop control of brake force in an emergency braking situation.In emergency braking situation
Under, valve V4 is energized, so that it fully opens the hydraulic loop including valve V4.In an emergency braking situation, hydraulic pump is always such as
Mode described in detail above is operated.Keep firmly in mind in this, it is clear that the actual hydraulic pressure resistance of control valve V2 is (according to performed by reality
Handover operation) determine that (it passes through valve V2 and liquid by first working chamber 14 that is on the pressure side forced into of hydraulic pump 19 for how many
Pressure ring road 116 is directly connected with the suction side of hydraulic pump 19) hydraulic fluid return to hydraulic pump suction side.
Fully closed valve V2 clearly results in the maximum speed of release brake, because being pressed into the first work by hydraulic pump 19
All pressurized hydraulic fluids of chamber 14 make hydraulic actuator piston shift to the second working chamber 15.
On the other hand, it is clear that the valve V2 of standard-sized sheet by the first working chamber 14 generate hydraulic pump 19 on the pressure side with its suction
Direct short-circuit between side.It allows hydraulic fluid being discharged to the second work through hydraulic loop 116,117 from the first working chamber 14
Make chamber 15, acts on brake in this way.
Valve V3 control throttling passage is throttled in itself.As explained above, valve V3 is used for the braking when stop is stopped
Device peace and quiet application is to avoid the movement of unexpected carriage.
Allowing people more interested herein is valve V4.If when stop is stopped, the hydraulic pump is shut down, brake
Release to start again at new row ladder is completed by accumulator 111 and valve V4.Valve V4 is opened.In this way, accumulator passes through section
Hydraulic fluid is discharged into the first working chamber 14 of hydraulic actuator 11.1.1 by stream valve 21 from its first working chamber 14 through valve V4.?
Increase pressure in one working chamber 14 is led hydraulic fluid and is discharged from the second working chamber 15 of hydraulic actuator 11.1.1.In this way, system
Dynamic device is released to the degree that can at least start new row ladder.
Once elevator car speed is enough to cover the noise of hydraulic pump 19, hydraulic pump 19 is energized again.It can be first
Guarantee that brake discharges completely.Then, valve V4 can be closed.Nevertheless, hydraulic pump 19 remains to refill accumulator 111,
Because accumulator also as described directly with hydraulic pump 19 on the pressure side and suction side is connected.
Fig. 3 i shows the embodiment being slightly different compared to Fig. 3 h.Nevertheless, the two embodiments are still closely related.Cause
This reason is correspondingly suitable for use in the embodiment according to Fig. 3 i for all these things that embodiment 3h is explained.
It is that throttle valve 21 has saved according to the embodiment of Fig. 3 i and according to unique difference between the embodiment of Fig. 3 h.It is this
It is possible for saving, because valve V4 has also been changed to valve V5.Valve V5 can be controlled as valve V2.That is valve V5 with
Valve V2 is identical or it at least works according to principle identical with valve V2.
Valve V5 is used for opened loop control or the closed-loop control of brake force in an emergency braking situation together with valve V2.Urgent
Under brake condition, valve V5 is energized, so that the actual hydraulic pressure resistance of control valve V5 determines that how many hydraulic fluid passes through pressure
Side (the first working chamber 14 and/or hydraulic pump 19 of accumulator 111 are on the pressure side) is pressed into the first working chamber of hydraulic actuator
14 and the brake is thus discharged, because entering the first working chamber 14 by the hydraulic pressure side pressure of hydraulic accumulator 111 (or pump)
All pressurized hydraulic fluids make hydraulic actuator piston shift to the second working chamber 15.
Because of the thing that all actuators for this embodiment are connected by the loop 114,115 realized in the form of common rail
Real, this embodiment can not be used to realize the ESB/ESG in above-mentioned meaning.
Due to identical reason, another group of additional actuator of one group of actuator of actuation first and subsequent actuation cannot achieve
Cascade operation.
One advantage of this embodiment is when lift car is not necessarily to energize to valve when stop waits ladder.
Another advantage is that hydraulic accumulator 111 can be independently filled with the work of the actuator responsible to braking.
Finally, important function is completely independent, thus important component such as valve V2 and V3 can by each other entirely without
Close ground design.
These advantages are also applied for situation shown in Fig. 3 h.
Deviation:
Solution expression such as Fig. 3 h and as shown in figure 3i, which has understood, preferably but not necessarily in opened loop control or closes
Hydraulic pump is itself served as into pressure source in the braking process of ring control.On the contrary, accumulator 111 can convey opened loop control or closed loop control
It is hydraulic required for system ground compressing brake lining to its corresponding track.
Fig. 3 j shows another embodiment for the car brake unit of the invention that be used in elevator claimed
Hydraulic tube line chart.
Hydraulic car brake unit includes first group of hydraulic actuator 11.1.1-11.1.x and second group of hydraulic cause again
Dynamic device 11.2.x, x can be 1 or the value between 1 and n at this time.
As explained above, a chamber of these hydraulic actuators and preferably the second working chamber 15 is by forming common rail
Hydraulic loop 115 is in direct hydraulic communication.
About another working chamber and preferably the first working chamber 14, only at first group of hydraulic actuator 11.1.1-11.1.x
In direct hydraulic communication, and another or another group of hydraulic actuator 11.2.x be not in about working chamber 14 it is permanent directly hydraulic
In connection.
The characteristics of this embodiment, is the fact that all valves are together with the hydraulic pump for being set to the first working chamber upstream
Arrangement.
The on the pressure side D of hydraulic pump 19 is also connected to the first working chamber in first group of actuator 11.1.1-11.1.x
Upstream loop 114.On the other hand, the suction side of hydraulic pump 19 is directly connected to be formed for all actuator 11.1.1-
11.1.x with the hydraulic loop 115 of the common rail of 11.2.x.In this way, valve V2 is with allowing opened loop control or closed-loop control by first group of cause
Dynamic device 11.1.1-11.1.x applies brake force.If valve V2 is fully closed, 19 full power of hydraulic pump gives first group of hydraulic cause
The first working chamber 14 pressurization of dynamic device.At the same time, reach maximum from the suction of the second working chamber 15 through loop 115 by hydraulic pump 19
Degree.That is hydraulic actuator is at full throttle released.
On the other hand, if valve V2 is standard-sized sheet, hydraulic pump 19 is by dead short, so that it can not influence first group of liquid
Hydraulic actuator 11.1.1-11.1.x.On the contrary, the first working chamber 14 of first group of hydraulic actuator and it is described first group it is hydraulic
The first working chamber 14 and second group of hydraulic actuator of second working chamber 15 of actuator and second group of hydraulic actuator
Second working chamber 15 (passing through check valve) is short-circuited also by the valve V2 of standard-sized sheet.That is applying maximum braking force.If valve V2
State between the fully closed somewhere between standard-sized sheet, then obviously will apply corresponding small or big brake force.
Herein, valve V3, which is also used in stop docking process quiet closure brake, prevents accidental movement to realize.Such as
The foregoing description, valve V3 pass through restricted flow path for the second hydraulic actuator or the first working chamber of second group of hydraulic actuator 11.2.x
14 are connected with the second working chamber 15, so that thus this or these actuator applies brake.
Valve V4 also has the function as explained before.Valve V4 allows the first working chamber 14 of first group of actuator
It is interconnected with the first working chamber 14 of second group of actuator, so that thus second group of actuator discharges.In explanation before, it is clear that
ESB/ESG function can not be realized using this embodiment.Therefore, the cascade application of the different components of brake is not accomplished.
In order to keep lift car to be in when before stopping in stop, safety is static, and two valves must be energized.
The part brake as accumulator can also be independently filled with brake remaining part herein.
Fig. 3 k is shown and the embodiment closely related according to the embodiment of Fig. 3 j.Unique difference is exactly that brake is being schemed
Simplify in 3k.Valve V3 and V4 have been saved.It as a result is exactly the brake peace before can not accomplishing during stop layers and sailing out of stop
Quiet closure and quiet release.This embodiment is reduced to the emergency braking that can execute closed-loop control braking or opened loop control braking
Device.
If it is not liquid that Fig. 3 L, which is shown for the opened loop control of one or more actuators 11 or the pressure source of closed-loop control,
Press pump 19 itself then may not need intermediary agency and the principle of hydraulic configuration that directlys adopt.
The pressure source is realized in the form of hydraulic accumulator 111 herein.Valve V2 is with its flowed friction opened loop control or closed loop control
Hydraulic fluid processed whether and how many first working chamber 14 of brake actuator 11 will be forced by accumulator.It is same with this
When, hydraulic accumulator can be received from the hydraulic fluid of the second working chamber 15 discharge and/or by the flow of pressurized of control valve V2 short circuit
Body.Valve VV controls whether the accumulator works.
Accumulator is preferably " round trip ", " double rod " cylinder, and the piston in cylinder forms the first accumulator chamber and the second accumulator chamber,
And the cylinder is designed to the equivalent hydraulic fluid being discharged from the first accumulator chamber and is received when piston is mobile by the second accumulator chamber,
The piston is preferably driven by spring.
Hydraulic pump 19 is only run when needing to refill accumulator 111.
Fig. 4 a shows the hydraulic tube line chart of one of them elevator car brake unit, can be used to realize institute
One of two conceptions proposed.This embodiment is similar to the embodiment of Fig. 3 b, because herein, not to the control of institute's braking forces thereto
It is carried out by control valve V2, but passes through hydraulic pump itself.
Generally, brake is not made of single hydraulic actuator, is made of several hydraulic actuators, they again phase
Like composition, preferably two-piece type or multi-piece type.
Therefore, the right area of Fig. 4 a schematically shows three hydraulic actuator 11.1-11.3, each hydraulic actuator by
Cylinder 12 with piston 13 is constituted, and corresponding cylinder is preferably divided into the first work positioned at 13 two sides of piston opposite each otherly by piston
Chamber 14 and the second working chamber 15, for the sake of more preferable general view, appended drawing reference 12,13,14 and 15 is just for the first actuator 11.1
It is labeled.
Each hydraulic actuator and two brake lining 16 interact, which acts on track and/or elevator
The guide rail 2 of carriage.
As long as have in corresponding first working chamber 14 it is hydraulic enough, hydraulic actuator resist its respective springs part 17 guarantor
It holds its piston and/or connected piston rod is in and opens position, herein, no pressure is applied to corresponding brake lining
16.So-called primary spring element is collectively formed in these spring parts 17.
Hydraulic pump 19 is preferably driven by motor 18 hydraulic to guarantee to supply.Generally but not necessarily it is equipped with pressure equalising vessel
20, the total volume and heat expansion of balanced hydraulic fluid and possible micro- leakage.
Hydraulic pump 19 be in normal operation on the pressure side D side (brake/decrease brake action of opening)
It is connected to the first working chamber 14 of hydraulic actuator, and it is connected with the other side for being in normal operation suction side S
To the second working chamber 15 of hydraulic actuator.
Which kind of pumped using to realize that idea of the invention is inessential.For all proposed solutions, leaf
Wheel pump is preferred option.More quadrants are run, using piston pump sometimes as hydraulic pump 19 is most preferably, preferably to have
The pump/motor of multiple cylinders.This is because piston pump is particularly suitable for realizing dual quadrant fortune when being engaged to suitable motor
Turn (Zweiquadrantenbetrieb).Dual quadrant operation refers to following modes herein, and wherein be once used as will be hydraulic for the pump
Fluid is pressed into the pump operation of working chamber, and again, which runs as hydraulic motor, which is left above-mentioned working chamber
Hydraulic fluid, and hydraulic motor by motor be provided with determine outflow working chamber hydraulic fluid speed braking moment.
As all other embodiments, the characteristics of this embodiment, is preferably the fact that it is as closed system quilt
Operation.That is hydraulic fluid is not pumped into the working chamber of hydraulic cylinder by hydraulic pump from liquid reserve tank, the hydraulic fluid the time
It is drained when arrival and returns to liquid reserve tank.On the contrary, hydraulic fluid is located at the work of the first side of respective hydraulic piston by hydraulic pump certainly
Chamber 14 is recycled to the working chamber 15 positioned at hydraulic piston opposite side.This is allowed for working chamber is left to be used to keep brake
Open or or flow into above-mentioned working chamber the intrinsic speed of hydraulic fluid, quickly speed and the opened loop control of sensitivity response or
Closed-loop control.This is because closed system allows the dual quadrant without the time difference to run, (otherwise the time difference may be by that must inhale again from liquid case
Enter hydraulic fluid to cause, liquid case no pressure described herein).
Equipped with external control valve V2 (can be common slide valve herein).If the latter close, it by working chamber 14 with it is hydraulic
Hydraulic system branch locating for pump 19 and the second working chamber 15 separates.The valve assists in keeping brake and almost beats with no energy
It opens, if valve V2 is to close, in pressure and guarantee overcomes the power acted on closure brake direction from spring 17
First working chamber will be separated with remaining hydraulic circuit, and internal pressure will be locked, to need only apply for keeping valve to close
The power for the very little closed.
In addition, be equipped with the second external control hydraulic valve V1, it is in opening state by the first working chamber 14 of hydraulic actuator and the
Two working chambers, 15 hydraulic pressure short circuit, i.e. its hydraulic company of guarantee to pressure equilibrium between the first and second working chambers without substantial hindrance
It is logical, and do not arrange restricting element herein especially, i.e., no any element for increasing flowed friction.
Optionally, it is equipped with third external control hydraulic valve V3, it guarantees between the first working chamber 14 and the second working chamber 15
Throttle fluid channel.As explained above, restriction effect can be based on valve V3 itself or narrow pipeline and/or come from
With the conventional conduit with the concatenated built-in throttle valve 21 of valve.
In normal operation, the first working chamber 14 be filled in pressure hydraulic fluid, all valves be close and
What hydraulic pump was preferably off.Brake lining 16 is in being held in its open position, without paying special energy, because in addition to
It is energized to valve and does not need other energy to maintain it in outside closed position.
In order to cause brake quickly to apply as far as possible, the control device 10 of (preferred) lift car open valve V1 and
V4, so that hydraulic disappeared in working chamber 14 by the pressure equilibrium between working chamber 14,15, this passes through valve V1 and V4 and sends out
Raw (hydraulic actuator 11.1).After pressure equilibrium has occurred, this or these brake lining 16 is by this or these spring
The maximum, force to be administered of part 17 is crushed in track and/or car guide rail 2, then brake within the very of short duration time with
Specified brake force is i.e. with the response of its maximum braking force.
In order to cause the delay of brake to apply (such as do not generate and intercept carriage when stop is stopped with can hearing noise),
10 opening valve V3 of lift car control device.Therefore, the pressure between first and second working chamber 14,15 is only with party in delay
Formula is released, and the time history of pressure reduction is provided by throttle valve 21 herein.This leads to following facts, and brake is to postpone
Mode does not generate to be applied in which can hear noise.
Valve V2 can be used to further influence brake application rate, if necessary.
Valve V1, V3 (if there is) remains turned-off.Valve V2 is opened, and hydraulic pump 19 is activated or formerly has been turned on simultaneously.
Theoretically, hydraulic pump 19 especially can also be used so, it generates certain pumping effect on 14 direction of working chamber,
But this effect is only big to be greater than pumping effect to the hydraulic fluid leakage current being discharged under the effect of spring part 17 from relevant work chamber 14,
To which hydraulic fluid can be controlled or be adjusted by the current conveying speed of hydraulic pump from the speed that corresponding working chamber 14 is discharged
Section, to influence the speed or power of brake application.Hydraulic pump is then preferably in following areas adjacent oscillatory operations, in the area
Domain, the attempted loopback of corresponding spring part by the hydraulic fluid leakage current of pump be in in the balance of hydraulic fluid stream, to pump
Speed need to only be reduced by a small margin to realize that current brake force reduces, and must be increased by a small margin to realize current system
Power increases.
The precondition of this operational mode is being not driven or is being shown with weakening when power is driven using following pumps
The leakage that can not ignore is shown.
In the case where high-quality hydraulic pump and especially piston pump, leakage current can make hydraulic pump according to institute for considerably less
The mode of stating influences the speed that hydraulic fluid is discharged from relevant work chamber 14.Alternatively, which can then replace
Ground is used as the pump in conveying direction by motor drive, or as hydraulic motor i.e. during pump operation in conveying direction
Drive motor in opposite direction, may be according to generator mode drive motor.By accordingly as generator operation
The electric wiring of motor, the torque that hydraulic motor must be resisted can be set and/or hydraulic motor rev/min can be set.Institute
There are these to influence brake application rate.
For this purpose, the motor that speed control or more preferably speed are adjusted be used to drive hydraulic pump.Hydraulic pump is preferably following
Areas adjacent vibration operation, in the region, corresponding the attempted loopback of spring part by the pump hydraulic fluid leakage current in
In the balance of hydraulic fluid stream, so that pump speed need to only be reduced by a small margin to realize that current brake force reduces, and must be small
Amplitude increases to realize that current brake force increases.Then, this or these spring part 17 compressing this or these brake lining
16 can more or less be cancelled to the power of track, so that current braking effort can be well controlled or adjust.
In appropriate situations, valve V2 can also abandon valve V3.This can actively realize that the hydraulic pump is according to institute by hydraulic pump
Mode is stated by Special controlling, so that the pressure balance between the chamber is slower.In appropriate situations, it is accordingly set in hydraulic pump
This can also passively be realized by the leakage current through pumping in the case where meter.
It is noted that so operation hydraulic pump may be advantageous, i.e., it is actively by hydraulic fluid from working chamber 14
It is pumped into working chamber 15, then ensure that brake with maximum braking force faster compared to the only hydraulic pressure short circuit by opening valve V1
Speed application.
It should be mentioned that according to the elevator car brake unit of the embodiment of Fig. 4 a particularly suitable for realization above by figure
1 the first conception proposed.It is true, can optionally turn on and off one whereby because another valve V4 can be set
Or several actuators (being actuator 11.1 in the condition shown in fig. 4 a).
Two in elevator car brake unit as shown in fig. 4 a are enough to realize by two deadman's brake ESB and two
The above-mentioned conception that a additional brake ESG is formed, because actuator (is actuator 11.2 in the case where Fig. 4 a illustrated embodiment
The repertoire for distributing to deadman's brake is realized with first part 11.3), and one or several actuators are (shown in Fig. 4 a
Example in the case where be actuator 11.1) be switched on by valve V4.The function of additional brake is distributed to if necessary to realize
And applying maximum braking force to control such as free falling, then valve V4 is activated.
Fig. 4 b shows the hydraulic wiring diagram of another simplified version of brake unit, it can especially be used by using horse
Up to hydraulic pump so that opened loop control or the closed-loop control brake force realize above-mentioned second basic conception.
In order to realize certain redundancy, the actuator 11.1 and 11.2 of two or more simultaneously operatings is used herein.
Not a possibility that cascade operation of actuator 11.1,11.2 is not provided herein, it is especially related to high-volume high efficiency manufacture herein, but
It may be effective if necessary.
For this embodiment, valve used is optimised for cost.It also is provided with external control valve V1, the valve is in open shape
The first working chamber 14 and the second working chamber 15 of hydraulic actuator described in state hydraulic pressure short circuit guarantee to be not apparent from obstruction first and the
The hydraulic communication of pressure between two working chambers.If brake will be applied more quickly, valve V1 will be always on.V2 pairs of valve
The slow application of brake is responsible for.Once the latter is opened, then the power of this or these spring part 17 oppresses hydraulic fluid conduct
Leakage current is flowed along the pump part of hydraulic pump 19, or flows to chamber by the alternatively current pump as hydraulic motor operating
15.According to the revolutions per minute of pump operation, it influences the speed that the hydraulic fluid stream of chamber 15 is flowed into from chamber 14.Brake application speed
Degree and (if available) current brake force can be adjust or controlled in same manner described above.
The specific embodiment of elevator car brake unit according to the present invention.
Fig. 5 and Fig. 6 shows the practical embodiment of the brake unit preferably used in framework of the present invention.
About Fig. 5, following detection can be made:
Elevator car brake unit includes hydraulic control unit 22.
It is desirable that all hydraulic units are located in control unit 22 and/or are directly attached to control unit by flange, and
Hose is not used.Caliper also least substantially at or completely (not signifying to show) is the integral part of control unit is optimal.
Otherwise, this design corresponds to the following explanation by figure.
In most cases, hydraulic actuator 11.1-11.3 is attached to the side of control unit 22 by flange, is herein
Three actuators.They are passed to corresponding interior in the contact surface of the shape complementation of hydraulic control unit 22 in succession by hydraulic direct
Hole preferably passes through the inner hole in its contact surface.Also it can be clearly seen by the piston rod 31 of actuator (can not be identified in Fig. 5)
The compression spring 33 passed through.Main spring unit is collectively formed in compression spring 33, and in terms of functional perspective, they correspond to such as Fig. 3 a-
Spring 17 shown in 4b.
Fixed bracket 23 is preferably attached to sides adjacent by flange with an angle of control unit, and actual braking is housed
Pincers 24,16 activity of brake lining for being attached to brake lining seat 25 is held in place in caliper, so that they can be from two sides quilt
It places or is pressed on raceway surface.
Control unit 22 forms live hydraulic system together with actuator 11.1-11.3, i.e., it equipped with hydraulic pump 19 and its drives
Dynamic device and/or motor 18, valve V1, V2 and if available also V3, V4 (or V23/V34) and pressure equalisation container 20.Individually
Pipeline is extra with regard to this, because all pipelines required for individually hydraulic unit connects are in control unit by appropriate interior
Hole is shown, the pipeline in addition to leading directly to the pipeline of hydraulic pump 19 or by suitable inner hole directly off hydraulic pump.This
The advantages of kind of practising way is, hydraulic line system be it is very rigid, mainly avoiding unwanted almost not can avoid usually
The elasticity that ground plays a role.This is especially important in following situations, and regulating brake force or important is carried out by hydraulic pump
Property involve can only be opened by valve generate as defined in choke pressure the fact that reduce, cause brake lining by a Duan Yan
The slow time is gradually closed, until reaching maximum braking force over time.
The electronic control unit of itself and at least one acceleration transducer are preferably allocated to control unit 22, but herein
Do not signify that control unit is shown.As can be from understanding in information above, the current braking effort of elevator car brake unit can be borrowed
Acceleration transducer is helped to determine and by opened loop control or preferred closed-loop control.
Elevator car brake unit including above-mentioned component be preferably designed to it can at least in hydraulic side plug and play,
It only needs to be connected with power supply and signal network, and no longer needs installment work in hydraulic side.
Caliper 24 is preferably designed to box-shaped, and with bottom plate, border member R is preferably prominent along the entire main side of the bottom plate
Out, see Fig. 5.Border member R position opposite each other be separation, the position necessarily formed U-shaped channel 26 with for
The track of brake lining interaction, and see Fig. 5.
According to the present invention, the characteristics of the brake unit especially, brake lining 16 is not slidably mounted in caliper 24,
But it is flexibly kept with a gap relative to caliper 24.
Brake lining 16 is attached to brake lining with being individually attached or be preferably divided into multiple local liners as a result,
Seat 25, preferably by screw tightening to brake lining seat.
As best shown in fig. 6, each brake lining seat 25 is passed through by laminated leaf spring 27 thus, and laminated leaf spring is in two sides from corresponding
Brake lining seat is prominent and generates an eye 28 there, this facilitate by pass through it positioning screw 29 laminated leaf spring is attached
It is connected to caliper 24.The laminated leaf spring 27 of one brake lining seat 25 is preferably fixed by screw to a side of U-shaped channel 26, and another
The laminated leaf spring 27 of one brake lining seat 25 is fixed by screw to another opposed side of U-shaped channel 26.It should be emphasized that lamination
Spring 27 have guiding function, therefore functionally unrelated with main spring unit or auxiliary spring unit and be especially not construed as
Part of it.They do not provide any noticeable brake engagement resistance especially.
Hereby, two eyes 28 of each laminated leaf spring 27 are designed to be different.The forward eye on moving downward direction
(being installed according to its use scope) is designed to it and actually seamlessly accommodates corresponding positioning screw 29.Therefore, greatly
Pulling force can be transmitted by the eye, when the big pulling force appears in interception lift car.On the contrary, on moving downward direction
The eye delayed is designed to it and so generates floating support together with corresponding positioning screw 29, that is, laminated leaf spring 27 can be substantially
Smoothly deformation, while it being forced on track but not interfering the tensile stress on the direction of longitudinal axis for being parallel to independent leaf spring, prevent
The case where occurring when only just as using following leaf springs, the leaf spring is located at the intraocular positioning by gapless in two sides
Screw 29 is securely clamped.
It can be seen that two brake lining seats 25 are pinned, or by spring set screw just as herein
30 are fixed by screw to laminated leaf spring, preferably in its center in region, so that brake lining seat 25 can not leave its laminated leaf spring 27.One
As, this screw-driving also absorbs lateral brake force, i.e., rubs in response to the braking acted between raceway surface and brake lining
The power wiped and occurred.
It is also meaningful that each brake lining seat on it front edge and lower front end edge from caliper 24
And/or the use that the border member R of caliper 24 risesThe overlay region of mark partly overlaps, referring to Fig. 5.This improves safety, because
Even if corresponding brake lining seat 25 is mutually broken through because caliper 24 can not be pushed out for the failure of laminated leaf spring supporting role
It is now arranged in directly to contact between dynamic pincers 24 and brake lining seat 25 and still transmits brake force, this is not such as in normal function
This.
So far, opposed brake lining seat 25 is that mirror image is identical for structure.
The main distinction is the fact that the opposed brake lining seat 25 of only one of which is directly born from hydraulic actuation
The power of device 11.1-11.3.The brake lining seat keeps so-called active brake liner.
These three actuators 11.1-11.3 can be easily identified in Fig. 6, Fig. 6 shows cylinder 12 and is connected with piston rod 31
Piston 13, and piston 13 divides cylinder 12 for the first working chamber 14 and the second working chamber 15, as shown in Fig. 3 a, 3b and Fig. 4 a, 4b, by
This, for the sake of more preferable general view, appended drawing reference 12,13,14,15 are labeled out in the first actuator of Fig. 6, but also corresponding
Suitable for actuator 11.2,11.3.
The brake lining seat 25 that directly bear the power of actuator 11 is preferably not linked to the piston rod 31 of actuator 11.
Piston rod 31 preferably can the only back side that does not face brake lining 16 of the transmitting compressing force to brake lining seat 25, and brake lining
Seat does not transmit any shearing force to piston rod 31 because of its specific position at laminated leaf spring 27 substantially.Although relative to Fig. 3 a,
In single brake lining seat 25, this allows according to the current desired braking wanted several actuator collective effects in 3b and Fig. 4 a, 4b
Power by all actuator 11.1-11.3 or only co-operates brake lining by one or the less actuator of quantity
Seat.In addition, such design protection piston rod packing and piston rod guidance.
In conjunction with as described in Fig. 5, each bearing of piston rod 31 preferably helically compression spring 33 of form of springs.It is so
It is seated between piston rod 31 and caliper 24, as long as it is in closing direction without hydraulic that is, at the piston 13 being attached thereto
Upper forces piston bar 31.These compression springs 33 limit nominal force, and brake lining seat 25 is such as with the volume under power blackout situation
Determine power to be forced on track, thus is specified brake force.Then, entire compression spring is also referred to as main spring unit herein.Instead
, if having in the first working chamber 14 corresponding hydraulic, piston rod 31 will overcome the masterpiece land used of compression spring 33
It is forced into open position.If all piston rods, all in open position, brake lining seat 25 can be together with the system kept
Dynamic liner 16 is brought to open position from application position by the laminated leaf spring belonging to it.
Each piston rod 31 preferably passes through the compression spring 33 for belonging to it, and compression spring is with it not towards brake lining seat
Side is connected against caliper 24 as already described above and/or its border member, and with its other side to piston rod 31
Latch plate 34.
The opposed brake lining seat 25 for not bearing actuator force directly keeps so-called passive brake lining herein.It is excellent
Choosing is not rigid, but is elastically mounted in caliper 24 (not only by another spring part of 36 form of laminated leaf spring
Independently).So size of setting auxiliary spring unit, that is, kept and the master by being in some position by the spring force that it applies
The balance for the spring force that spring unit applies.
The reasons why installing auxiliary spring unit is that the rigidity installation of brake lining seat will will cause brake and so consumingly do
It reacts out, so that cannot achieve the application of braking force delay, (brake force increases by certain extension time up to reaching maximum braking
Power), and cannot achieve brake force closed-loop control certainly.It, will in the case where rigidly installing opposed brake lining seat to pincers
Can be in this way, i.e. 14 volume of working chamber can actually since brake lining contact track no longer change the case where, thus
The further increasing or reduce of pressure in working chamber 14 can soon result in can not sensitive control the external variation of brake force.
In order to guarantee the flexibility of the second brake lining seat 25, several guide pins are fixed and/or adjust screw 35 and are screwed into
Its back side, guide pin or adjusting screw do not pass through caliper 24 and/or its above-mentioned border member towards the side of brake lining seat with it.
Have between them it is multiple herein be in 36 form of laminated leaf spring compression spring part, slide into corresponding adjusting screw 35
On.So, the second brake lining seat can avoid the auxiliary spring unit preferably generated herein by laminated leaf spring (by overcoming)
Increase tension.It is many that this mitigates characteristic curve, because small pressure change is no longer result in the very big variation of brake force.
But strikingly, the second brake lining seat 25 is also substantially attached to laminated leaf spring 27, and laminated leaf spring is by least
The interlayer of three or preferably more leaf springs side by side is constituted, so that the power occurred when braking is led to completely or at least substantially
It crosses laminated leaf spring 27 and is passed to caliper 24, rather than by adjusting screw 35.These are in caliper 24 preferably between big
Gap extends, so as not to interfere the flexibility of the second brake lining seat or distort it with frictional force.Adjust the function base of screw 35
This upper limit on the fact that, i.e., laminated leaf spring 36 is held in place, and with it not towards the locking of brake lining seat and/or lower section
The head that the side of nut 37 protrudes from caliper avoids the brake lining seat relative to caliper in laminated leaf spring and possible convex
It shifts up under the influence of ear in the side of track and/or guide rail 2 too far.Especially setting lock nut 37 is convenient, because
The position can be set like this.In other words, adjusting screw 35, which is fixed, is associated with brake lining 16 and/or brake lining
Seat 25, and/or kept by brake lining 16 and/or brake lining seat 25, while they can slide back and forth in 24 wall of caliper,
Unless its head of screw or lock nut 37 are against caliper 24.
For the sake of complete, referring to the adjustable stop 38 being preferably provided with, backstop is designed to stop screw shape herein, preferably logical
Locking is crossed to be fastened.In this way, the distance can be limited, thus the second brake lining seat can be avoided.So, it can need
When guarantee that brake unit shows the characteristic curve that jumps lighted from some, then generate the brake force of surge together with causing respectively
The further pressure of dynamic device side increases, if there is.
For the sake of most clear, Fig. 7 is shown again before it has been described that basic principle:
Each brake lining seat 25 preferably has channel, and seat 25 can be fixed/sliding sleeve to laminated leaf spring 27 by the channel.Cause
The fact that be limited to displaying principle for Fig. 7, therefore two leaf springs are only shown.Preferably exist in the center of brake lining seat 25 or central area
Exist between seat 25 and laminated leaf spring 27 and fix, so that seat 25 can not be along laminated leaf spring longitudinal movement, such as in the center of Fig. 7 by click and sweep void
Line signifies ground.Laminated leaf spring 27 includes at least two 28 for fixing, one of to provide lost motion or gap to brake
Liner seat 25 will be eliminated when will be pressed towards guide rail (being not shown here) or reduces the longitudinal stress in laminated leaf spring 25e, thus laminated leaf spring
It will be extended.
Also the function of adjusting screw is seen in Fig. 7 again:
Under the action of the power signified by F1, once the power is large enough to compressing (or " flattening ") in the form of laminated leaf spring 36
The spring part of composition and adjust simultaneously screw 35 be not fixed to because being fixed on brake lining seat caliper 24 wall it is (logical
Hole) in and moved together with brake lining seat 25, brake lining seat 25 can be moved.It adjusts screw and lock nut 37 is housed,
It can be determined when brake is released at a distance from brake lining seat 25 is between guide rail.
It can be seen that, the maximum displacement of brake lining seat can be limited by adjusting backstop 38 again.
It is self-evident, shown in " leaf spring suspension " also active brake piece side realize.This signifies in Fig. 7 by arrow F2,
The arrow represents the brake force generated by hydraulic actuator.
Have to, it is noted once again that being just also used as servo brakes by brake described in attached drawing.Then,
Mostly in the motor system of disk brake or drum brake form for brake motor or drive shaft required at present
Dynamic device be no longer it is required, this at least compensates for quite a few cost caused by brake provided by the present invention.
Finally, looking like to the overall conclusion prompt of the following contents required:
Preferably, it is claimed by the feature below independently of other feature or with belong to the other of the application
Content described in the feature that claim feature or feature from specification combine:
Elevator with the lift car (4) to move up and down along guide rail (2), it is hydraulic including opened loop control or closed-loop control
Brake is for the lift car (4) that slows down, and brake includes for oppressing one group of brake lining (16) extremely in closing direction
The hydraulic actuator (11) of brake component, hydraulic actuator (11) are rubbed by main spring unit on closing direction with generating brake
The power of wiping is pre-tightened, and hydraulic actuator (11) includes hydraulic cylinder (12) and piston (13), and cylinder (12) are divided into the first work by piston
Make chamber (14) and the second working chamber (15), and piston (13) is hydraulic complete or partial in the first working chamber (14) according to being present in
The power of main spring unit is compensated, difference with the prior art is brake application rate and/or final power under any circumstance
By hydraulic pressure source by opened loop control or closed-loop control, the brake lining (16) of device (11) operation is hydraulically actuated by the power
It is forced on track (2), on the pressure side (D) of the hydraulic pressure source fills the upper of at least one piston (13) with hydraulic fluid
It states the first working chamber (14), suction side (S) can aspirate flow of pressurized from the second working chamber (15) of at least one piston (13)
Body, and additonal pressure control pipeline (39) interconnects the first working chamber (14) and the second working chamber (15), and flows through pressure control
The actual flow velocity of the hydraulic fluid of tubulation line (39) is determined by control valve.
The characteristics of above-mentioned elevator, is preferably, the control valve (V2；V23) it is the valve run for dedicated on-off, has only
Two settling positions, i.e. " valve is fully closed " or " valve standard-sized sheet ".
The characteristics of above-mentioned elevator, is preferably, the control valve (V2；V23) be the valve with spool, the valve block or open through
Cross valve (V2；V23 access), and valve (V2；V23) it is designed to flow through valve (V2；V23 flow) can be by the state
It is per second between " moving up movable valve plug in closing direction " and " moving spool in the direction of the opening " to switch the valve (V2 back and forth；
V23 it) determines.
The characteristics of elevator as described in the previous paragraph is preferably that the hydraulic system includes the pressure in addition to having control valve (V2)
Power control pipeline (39) also has the choke flow line (41) including throttling control valve (V3) for stopping in lift car (4) stop outside
Among process or liquid braking device is applied in noise abatement later, and/or the short-circuit pipeline (40) including short valve (V1) is used for tight
Brake in anxious situation is quickly applied, and/or the brake discharge line (42) including brake relief valve (V4) is used for
Release brake can extremely start the terraced degree of new row in the case of not starting hydraulic pump (19).
The characteristics of elevator as described in the previous paragraph is preferably to be equipped with to the hydraulic pump of hydraulic actuator (11) feed flow
(19), wherein pump (19) braked when by lift car (4) abnormal operating condition to normal operational condition or to stop ladder process
Middle continuous operation, itself is not controlled or power consumption control by speed control, Torque Control, frequency.
The characteristics of elevator as described in the previous paragraph, is preferably, the hydraulic cylinder as hydraulic actuator (11) a part
It (12) is " round trip ", " double rod " cylinder (12), the piston (13) in cylinder forms the first working chamber (14) and the second working chamber (15),
Middle cylinder (12) is designed to when piston (13) are mobile, the hydraulic fluid and the second working chamber that are discharged from the first working chamber (14)
(15) hydraulic fluid received is equivalent.
The characteristics of elevator as described in the previous paragraph, is preferably, and the elevator car brake and controls elevator car brake
Control device be designed to when the sailing out of beginning elevator car brake and pass through the pressure quilt that is stored in accumulator (111)
Open, and hydraulic pump (19) delay start and preferably lift car (4) reach its normally travel speed at least 30% and more
It is not activated before being at least 50% well.
Previous paragraphs as described in elevator the characteristics of be preferably, which includes hydraulic actuator described at least two
(11), the two is designed to act on brake(-holder) block, hydraulic actuator described at least one of which (11) quilt in normal operating
As hydraulic accumulator (111), conveying opens elevator car brake institute to inoperative hydraulic pump (19) when sailing out of beginning
Beginning is being sailed out of in hydraulic actuator (11) described in the pressure or at least one of which needed and additional accumulator (111) conveying
When inoperative hydraulic pump (19) open pressure required for elevator car brake.
The characteristics of elevator as described in the previous paragraph, is preferably, and the hydraulic elevator car brake itself includes that acceleration passes
Sensor (10a, 10b), is preferably integrated into brake unit, and signal is preferably so used to control brake force, that is, leads
≤ 1g is caused.
The method of opened loop control or closed-loop control for the hydraulic elevator car brake with hydraulic actuator (11),
The hydraulic actuator has at least one piston rod (31), braking needed for being generated on closing direction by main spring unit
Power required for power is pre-tightened, and piston rod (31) is connected to piston (13), and piston is hydraulic complete according to what is be applied thereto
Or part compensates the power of the main spring unit, characterized in that is crushed on track by the brake lining (16) that piston rod (31) operate
On final power by opened loop control or closed by speed control and/or Torque Control and/or more quadrant operations motors
Ring control, the motor as first substitution optional way according to actual needs or so that hydraulic pump (19) delivering hydraulic fluid simultaneously
Therefore the mode for reducing the final power for acting on brake lining (16) drives hydraulic pump (19) or the motor as generator
Or brake motor brake fluid press pump (19) as follows, i.e. hydraulic fluid it is preferred by closed-loop control or the liquid stream of opened loop control
By being flowed back to by the hydraulic pump (19) of hydraulic fluid to the direction opposite with its practical conveying direction and thus increase acts on
In the final power of brake lining (16), and the motor substitutes optional way according to actual needs as follows as second
Drive hydraulic pump (19), even if hydraulic pump (19) or delivering hydraulic fluid and thus reduce act on brake lining (16) most
Whole power, or so that leakage current is flowed back to the direction opposite with conveying direction and is therefore increased through hydraulic pump (19) and act on braking lining
The final power of piece (16).
The characteristics of method as described above, is, in order to execute emergency braking, compensates the spring part (17) completely or partially
Power it is described hydraulic by being eliminated by short-circuit pipeline around the hydraulic pump (19), which can be by motor-driven valve
(V1) it is opened completely or partially.
One of 1 to 13 method according to claim 1, characterized in that the lift car actuator includes for directly making
For several hydraulic actuators (11) of at least one brake lining (16), and according to the size of current desired brake force,
All or predetermined quantity actuators (11) of one elevator car brake unit are activated.
It is claimed a kind of to be designed to execute one of preceding method or a variety of elevator car brakes and outfit
There is the elevator of this elevator car brake.
Previous paragraphs listed by claim can to pass through the one or more from other claims or specification special
Sign is to supply.
Reference signs list
1 drive unit for lift
2 car guide rails
3 guide devices
4 lift cars
5 route benchmark
6 displacement sensors
First elevator car brake unit of 7a deadman's brake
Another elevator car brake unit of 7b deadman's brake
First elevator car brake unit of 7'a another kind brake form
Second elevator car brake unit of 7'b another kind brake form
First additional brake unit of 8a additional brake
Another additional brake unit of 8b additional brake
9 another central elevator control gears
The control device of 10 lift cars
10a acceleration transducer
10b acceleration transducer
10c signal wire
11 hydraulic actuators (are separately presented as 11.1.1-11.1.x and/or 11.2.1-11.2.x and/or 11.1,11.2
With 11.3)
12 cylinders
13 pistons
First working chamber of 14 cylinders
Second working chamber of 15 cylinders
16 brake lining
17 spring parts, a part of main spring unit
18 motor
19 hydraulic pumps
20 pressure equalising vessels
21 throttle valves
22 control units
23 fixed brackets
24 calipers
25 brake lining seats
26 channels with caliper
27 laminated leaf springs
The eye of 28 laminated leaf springs
29 fixing screws laminated leaf springs
30 spring set screws
31 piston rods
32 (unallocated)
33 compression springs
34 latch plates
35 adjust screw
36 laminated leaf springs
37 adjust the locking nut of screw
38 adjustable stops
39 control pipelines
40 short-circuit pipelines
41 choke flow lines
42 brake discharge lines
111 accumulators
The loop of 114 the first working chambers of connection
The loop of 115 the second working chambers of connection
116 are used for the common loop of multiple valves
The loop of 117 interconnection
The loop of 118 interconnection
The loop of 119 interconnection
Overlay region on front side of caliper and brake lining seat
The border member of R caliper
ESB deadman's brake
ESG additional brake
ISB intelligent and safe brake
D prexxure of the hydraulic pump side
S hydraulic pump suction side
SE1 pressure sensor
SE2 pressure sensor
V1 valve 1
V2 valve 2
V3 valve 3
V4 valve 4
V5 valve 5
V23 valve 23
V34 valve 34
VV is used for the valve that accumulator temporarily connects
CV check valve (is separately presented as CV1, CV2, CV3)
BP forms the hydraulic pipeline for the bypass for allowing pressure to control
The first hydraulic pipeline of HS1
The second hydraulic pipeline of HS2
LM lost motion
Claims (22)
1. a kind of elevator is respectively acting on difference with lift car and at least one car brake unit or at least two
Guide rail elevator car brake unit,
Wherein, at least one brake lining can be operated by hydraulic actuator (11),
It is characterized in that
At least one described brake lining (16) is articulated to caliper (24) by plate spring member with fricton-tight guidance mode,
Wherein, the brake lining is maintained at its predetermined position by the leaf spring.
2. elevator according to claim 1, characterized in that at least one described brake lining (16) is by laminated leaf spring with nothing
Sliding guidance mode is articulated to caliper (24).
3. elevator according to claim 1, characterized in that the longitudinal axis of the plate spring member (27) is parallel to the longitudinal axis of guide rail
Extend, when brake lining effect, the brake lining is maintained on the guide rail,
Wherein, which is held against caliper in its in the direction of its longitudinal axis region at mutually opposed both ends
(24),
Wherein, preceding bearing (28) is fixed bearing in moving downward, and the bearing delayed in moving downward is to float
It supports (28), which allows the plate spring member (27) to move in longitudinal axis.
4. elevator according to claim 1 or 3, characterized in that the plate spring member (27) is designed in this way, once the hydraulic actuation
Device (11) no longer applies any pressure to the brake lining (16) and/or brake lining seat (25), which just pulls back the system
Liner (16) and/or brake lining seat (25) are moved to its open position.
5. elevator according to claim 1, characterized in that the caliper (24) is at least partly covered by the plate spring member
(27) brake lining (16) or brake lining seat (25) kept, thus the brake lining (16) or brake lining seat
(25) even if also by overlapping under plate spring member (27) fault conditionIt is blocked in the caliper (24).
6. elevator according to claim 1, characterized in that the caliper (24) at least partly covers at its narrow end surface
The brake lining (16) or brake lining seat (25) kept by the plate spring member (27), thus the brake lining (16)
Or brake lining seat (25) is even if also by overlapping under plate spring member (27) fault conditionIt is blocked in the caliper (24)
In.
7. elevator according to claim 1, characterized in that at least one and usually each hydraulic actuator (11)
Show that at least one piston rod (31), the piston rod are not connected to the brake lining (16) or its brake lining seat
(25), to can only or can only substantially be transmitted between the piston rod (31) and the brake lining and/or its brake lining seat
Compressing force.
8. elevator according to claim 1, characterized in that several hydraulic actuators (11) are available, these hydraulic causes
Dynamic device can be by individually hydraulic control, wherein the piston rod (31) of the actuator (11) is not connected to the brake lining
(16) or its brake lining seat (25), to belong at least one for an actuator being hydraulically controlled on " combined floodgate " direction
Brake lining or its liner seat can be lifted off an actuator for being not belonging to be hydraulically controlled on " combined floodgate " direction by piston rod
At least one piston rod.
9. elevator according to claim 1, characterized in that be equipped at least two lift car brake components, the elevator car
Compartment brake component is designed at hydraulic aspect be independent by forming self-centered hydraulic circuit.
10. elevator according to claim 7, characterized in that be equipped at least two lift car brake components, each electricity
Terraced carriage brake component shows the control unit equipped with electric drive hydraulic pump and one or more valves, wherein the control
Unit also includes that one or more hydraulic actuators or one or more of hydraulic actuators directly extremely should by flanged joint
Control unit.
11. elevator according to claim 10, characterized in that each lift car brake component is shown equipped with benefit
Repay the control unit of case and actually all or most of connecting pipeline.
12. elevator according to claim 10, characterized in that one or more of hydraulic actuators are with hydraulic conduction side
Formula is directly by flanged joint to the control unit.
13. elevator according to claim 1, characterized in that at least two elevator car brake units are available, this
A little elevator car brake units show several active brake linings operated by individually controllable hydraulic actuator (11)
Piece, so that brake force can be influenced by following facts: so that the how many active brake liners are administered.
14. elevator according to claim 1, characterized in that these elevator car brake units show that acceleration passes
Sensor, it distributes to the brake force of its elevator car brake unit for opened loop control or closed-loop control.
15. elevator according to claim 14, characterized in that do not involve and separated in fact with the elevator car brake unit
Existing lift car control device.
16. elevator according to claim 10, characterized in that two elevator car brake unit direct communications and adjust
The signal of its acceleration transducer is saved to find to fail.
17. elevator according to claim 1, characterized in that be equipped with lift car control device, lift car control dress
It sets with elevator cab movement, is communicated with central elevator control gear, is provided directly with the signal of hoistway signal system, and just
It, being capable of the stand alone autonomous operation elevator car brake unit for the center elevator control gear.
18. elevator according to claim 17, characterized in that the lift car control device is and the lift car system
What dynamic device unit separately designed.
19. elevator according to claim 1, characterized in that the lift car has the urgent confession with elevator cab movement
Power supply.
20. elevator according to claim 1, characterized in that lift car has the load for determining current elevator lift car load
Lotus measuring system.
21. elevator according to claim 1 is respectively acting on different guide rails with lift car and at least two
Elevator car brake unit, each elevator car brake unit have caliper, which protects active brake liner
It holds in the side of the guide rail as rubbing surface, and passive brake lining is maintained to the other side of guide rail,
It is characterized in that
Only the active brake liner is directly to be operated by hydraulic actuator, effect of the hydraulic actuator in relevant pressure
Under completely or partially neutralize and tend to push the brake lining and acted on against the power of the main spring unit of the guide rail, otherwise with system
It is pushed required for dynamic and presses the brake lining against the guide rail,
Wherein, which is so articulated to auxiliary spring unit, it is enabled to evade the power of auxiliary spring unit,
To which the distance that the active brake liner must shift to guide rail before reaching braking limit is increased.
22. a kind of elevator car brake unit, the elevator car brake list with elevator according to claim 1
The feature of member.
Applications Claiming Priority (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE202014102356.9 | 2014-05-20 | ||
| DE102014107110.7 | 2014-05-20 | ||
| DE102014107110 | 2014-05-20 | ||
| DE202014102356 | 2014-05-20 | ||
| DE102014111359.4 | 2014-08-08 | ||
| DE202014103702.0 | 2014-08-08 | ||
| DE202014103702.0U DE202014103702U1 (en) | 2014-05-20 | 2014-08-08 | Safety device for operating an elevator |
| DE102014111359.4A DE102014111359A1 (en) | 2014-05-20 | 2014-08-08 | Method for operating a car brake unit |
| EP14004276 | 2014-12-18 | ||
| EP14004276.3 | 2014-12-18 | ||
| EP14199025 | 2014-12-18 | ||
| EP14199025.9 | 2014-12-18 | ||
| PCT/EP2015/061155 WO2015177234A1 (en) | 2014-05-20 | 2015-05-20 | Safety device for operating an elevator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106660743A CN106660743A (en) | 2017-05-10 |
| CN106660743B true CN106660743B (en) | 2019-08-27 |
Family
ID=54553460
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580039425.6A Active CN106536395B (en) | 2014-05-20 | 2015-05-20 | Hydraulic elevator car brake unit with controllable brake force |
| CN201580039535.2A Active CN106660743B (en) | 2014-05-20 | 2015-05-20 | Safety device for elevator operation |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580039425.6A Active CN106536395B (en) | 2014-05-20 | 2015-05-20 | Hydraulic elevator car brake unit with controllable brake force |
Country Status (5)
| Country | Link |
|---|---|
| EP (2) | EP3145847B1 (en) |
| CN (2) | CN106536395B (en) |
| ES (2) | ES2907453T3 (en) |
| HU (1) | HUE057026T2 (en) |
| WO (2) | WO2015177228A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014116281A1 (en) | 2014-11-07 | 2016-05-12 | Thyssenkrupp Ag | Elevator with a braking device |
| EP3239085B1 (en) * | 2016-04-28 | 2019-03-20 | KONE Corporation | Solution for compensating an effect of temperature change in a proximity sensor in a machinery brake of an elevator |
| US10352805B2 (en) * | 2016-10-26 | 2019-07-16 | National Oilwell Varco, L.P. | Load-measuring hydraulic cylinder |
| CN109775508B (en) * | 2017-11-10 | 2020-07-14 | 上海三菱电梯有限公司 | Emergency braking device and elevator system with same |
| DE102018120000A1 (en) * | 2018-08-16 | 2020-02-20 | Moog Gmbh | Electrohydrostatic actuator system with suction tank |
| CN112357718B (en) * | 2020-11-09 | 2021-09-21 | 山东奔速电梯股份有限公司 | Quick braking device of household elevator without pit |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2241488A (en) * | 1990-03-01 | 1991-09-04 | Alphatrad Sa | Lift brake with safety release |
| DE19715224A1 (en) * | 1997-04-11 | 1998-10-15 | Leistritz Ag | Hydro rope elevator |
| WO2002057170A2 (en) * | 2001-01-18 | 2002-07-25 | Thyssen Elevator Capital Corp. | Elevator safety brake |
| EP1323660A1 (en) * | 2001-12-24 | 2003-07-02 | Inventio Ag | Safety brake for elevator system |
| CN1428287A (en) * | 2001-12-24 | 2003-07-09 | 因温特奥股份公司 | Safety brake device for elevator equipment |
| CN103459290A (en) * | 2011-03-22 | 2013-12-18 | 奥的斯电梯公司 | Elevator braking system |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5228540A (en) * | 1992-07-24 | 1993-07-20 | Hollister-Whitney Elevator Corp. | Elevator car brake with shoes actuated by springs |
| DE4318744C1 (en) * | 1993-06-05 | 1994-09-01 | Teves Gmbh Alfred | Floating calliper disc brake for motor vehicles |
| EP0648703B1 (en) * | 1993-10-18 | 1999-01-20 | Inventio Ag | Safety braking device for an elevator |
| KR200221450Y1 (en) * | 2000-10-21 | 2001-04-16 | 편준기 | Brake system for rope of a elevator |
| DE202004017587U1 (en) * | 2004-11-12 | 2005-01-20 | Hydraulik-Liftsysteme Walter Mayer Gmbh | Guided lifting device with damped safety gear |
| DE202004017585U1 (en) * | 2004-11-12 | 2005-01-20 | Hydraulik-Liftsysteme Walter Mayer Gmbh | Guided lifting device with holding and safety gear |
| CN200940616Y (en) * | 2006-08-18 | 2007-08-29 | 武汉船用机械有限责任公司 | Plunger hydraulic oil cylinder of braker |
| CN102303803A (en) * | 2011-05-28 | 2012-01-04 | 赵强 | Sliding rope braking scheme and device for friction type hoist |
| EP2666743A1 (en) * | 2012-05-25 | 2013-11-27 | Inventio AG | Brake system with a cleaning device |
| CN102774719B (en) * | 2012-07-02 | 2014-07-09 | 太原理工大学 | Intelligent elevator safety tongs |
| CN203442025U (en) * | 2013-08-22 | 2014-02-19 | 刘茂山 | Quick oil return brake cylinder of monorail hoist for mine |
-
2015
- 2015-05-20 WO PCT/EP2015/061143 patent/WO2015177228A1/en active Application Filing
- 2015-05-20 ES ES15723248T patent/ES2907453T3/en active Active
- 2015-05-20 CN CN201580039425.6A patent/CN106536395B/en active Active
- 2015-05-20 EP EP15723246.3A patent/EP3145847B1/en active Active
- 2015-05-20 CN CN201580039535.2A patent/CN106660743B/en active Active
- 2015-05-20 ES ES15723246T patent/ES2902845T3/en active Active
- 2015-05-20 WO PCT/EP2015/061155 patent/WO2015177234A1/en active Application Filing
- 2015-05-20 HU HUE15723246A patent/HUE057026T2/en unknown
- 2015-05-20 EP EP15723248.9A patent/EP3145848B1/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2241488A (en) * | 1990-03-01 | 1991-09-04 | Alphatrad Sa | Lift brake with safety release |
| DE19715224A1 (en) * | 1997-04-11 | 1998-10-15 | Leistritz Ag | Hydro rope elevator |
| WO2002057170A2 (en) * | 2001-01-18 | 2002-07-25 | Thyssen Elevator Capital Corp. | Elevator safety brake |
| EP1323660A1 (en) * | 2001-12-24 | 2003-07-02 | Inventio Ag | Safety brake for elevator system |
| CN1428287A (en) * | 2001-12-24 | 2003-07-09 | 因温特奥股份公司 | Safety brake device for elevator equipment |
| CN103459290A (en) * | 2011-03-22 | 2013-12-18 | 奥的斯电梯公司 | Elevator braking system |
Also Published As
| Publication number | Publication date |
|---|---|
| HUE057026T2 (en) | 2022-04-28 |
| EP3145848B1 (en) | 2021-11-03 |
| ES2907453T3 (en) | 2022-04-25 |
| CN106536395A (en) | 2017-03-22 |
| WO2015177234A1 (en) | 2015-11-26 |
| CN106536395B (en) | 2019-09-20 |
| EP3145848A1 (en) | 2017-03-29 |
| EP3145847B1 (en) | 2021-10-20 |
| EP3145847A1 (en) | 2017-03-29 |
| CN106660743A (en) | 2017-05-10 |
| WO2015177228A1 (en) | 2015-11-26 |
| ES2902845T3 (en) | 2022-03-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106660743B (en) | Safety device for elevator operation | |
| US20070290550A1 (en) | Electropneumatic Braking Device of a Rail Vehicle Comprising a Continuous Regulating Range | |
| Li et al. | Electro-hydraulic proportional control of twin-cylinder hydraulic elevators | |
| US9688510B2 (en) | Hydraulic brake system for elevator | |
| JP5726641B2 (en) | RAILWAY VEHICLE WITH EMERGENCY PRESSURE PRESSURE DEVICE AND PRESSURE METHOD OF AIR TUBE IN RAILWAY VEHICLE | |
| CN105196998B (en) | Braking system for working truck | |
| US10214381B2 (en) | Elevator system, brake system for an elevator system and method for controlling a brake system of an elevator system | |
| US10279791B2 (en) | Systems for retarding the speed of a railcar | |
| CA2875742C (en) | Disk brake system | |
| US20100038184A1 (en) | Lift System Having A Lift Car With A Brake Device Which Is Arranged In The Region Of The Lift Car For Holding And Braking The Lift Car, And A Method For Holding And Braking A Lift Car Of This Type | |
| KR102624360B1 (en) | Method and brake system for controlling or regulating a brake system | |
| CN110836205A (en) | Active radial executing system and control method for bogie | |
| JPH01237255A (en) | Overload alarm device for trailer brake | |
| CN110526152A (en) | Multichannel protecting against shock intelligent constant deceleration brake fluid system | |
| US11834019B2 (en) | Hydraulic braking system having an electronic control unit and method for operating same | |
| KR101941388B1 (en) | Elevator with a brake device | |
| RU2733670C1 (en) | Device for control of clamping force of current collector with relay valve | |
| CN107244596B (en) | The leveling of Gear-and-rack elevator controls and safety catch | |
| RU2115576C1 (en) | Vehicle brake system | |
| US11958462B2 (en) | Brake control apparatus | |
| CN115009244A (en) | Motion monitoring air brake control system and method for engineering vehicle straight-through braking | |
| ITFI20100091A1 (en) | ELECTROPNEUMATIC APPARATUS FOR COMMANDING THE PNEUMATIC BRAKING OF RAILWAY VEHICLES. | |
| CA2879284A1 (en) | Systems for retarding the speed of a railcar | |
| CZ307118B6 (en) | A device for braking railway cars, in particular freight wagons, and a method of controlling its valve device with refraction characteristics | |
| JPH04112177A (en) | Controller for hydraulic elevator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |