WO2010066939A1 - Agencement et procédé pour réduire le bruit et la vibration provoqués par une machine de levage d'ascenseur, et procédé pour réduire le bruit et la vibration provoqués par une machine - Google Patents

Agencement et procédé pour réduire le bruit et la vibration provoqués par une machine de levage d'ascenseur, et procédé pour réduire le bruit et la vibration provoqués par une machine Download PDF

Info

Publication number
WO2010066939A1
WO2010066939A1 PCT/FI2009/000103 FI2009000103W WO2010066939A1 WO 2010066939 A1 WO2010066939 A1 WO 2010066939A1 FI 2009000103 W FI2009000103 W FI 2009000103W WO 2010066939 A1 WO2010066939 A1 WO 2010066939A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
functional element
machine
hoisting machine
problematic
Prior art date
Application number
PCT/FI2009/000103
Other languages
English (en)
Other versions
WO2010066939A8 (fr
Inventor
Giovani Hawkins
Miikka Niranenm
Original Assignee
Kone Corporation
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kone Corporation filed Critical Kone Corporation
Publication of WO2010066939A1 publication Critical patent/WO2010066939A1/fr
Publication of WO2010066939A8 publication Critical patent/WO2010066939A8/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/04—Driving gear ; Details thereof, e.g. seals
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B1/00—Control systems of elevators in general
    • B66B1/24—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration
    • B66B1/28—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration electrical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/26—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper characterised by adjusting or regulating devices responsive to exterior conditions
    • F16F13/30—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper characterised by adjusting or regulating devices responsive to exterior conditions comprising means for varying fluid viscosity, e.g. of magnetic or electrorheological fluids

Definitions

  • the present invention relates to an arrangement as defined in the preamble of claim 1, to method as defined in the preamble of claim 15 for reducing the noise and vibration caused by an elevator hoisting machine, and to a method as defined in the preamble of claim 24 for reducing the noise and vibration caused by a machine .
  • Elevators often involve the problem that the elevator hoisting machine produces noise and vibration in the elevator car and in the rooms and floors of the building.
  • vibration is transmitted e.g. via the machine bed and machine room floor, and in elevators without machine room e.g. via the guide rails and elevator shaft walls .
  • an expedient used to reduce the vibration caused by the hoisting machine is to place elastomeric bodies between the machine bed and the machine room floor.
  • These solutions involve the problem that they only damp vibration oc- curring in a limited frequency range, which frequency range depends, among other things, on the weight of the machine. Moreover, these solutions only eliminate a limited proportion of the vibration.
  • Such " solutions also reduce the stability of the machine bed as well as that of the machine itself and re- quire a heavy machine and machine bed.
  • the object of the present invention is to overcome the above- mentioned drawbacks and to achieve a simple and advantageous arrangement and method for reducing the noise and vibration caused by an elevator hoisting machine over a large frequency range.
  • a FIELD OF THE INVENTION further object of the inven- tion is to produce a method for reducing the noise and vibration caused by any machine.
  • the arrangement of the invention is characterized by what is disclosed in the characterizing part of claim 1, and the method of the invention for reducing the noise and vibration caused by an elevator hoisting ma- chine is characterized by what is disclosed in the characterizing part of claim 15.
  • the method of the invention for reducing the noise and vibration caused by a machine is characterized by what is disclosed in the characterizing part of claim 24.
  • Other embodiments of the invention are correspond- ingly characterized by what is disclosed in the other claims.
  • inventive embodiments are also presented in the description part and drawings of the present application.
  • the inventive content disclosed in the application can also be defined in other ways than is done in the claims below.
  • the inventive content may also consist of several separate inventions, especially if the invention is considered in the light of explicit or implicit sub-tasks or with respect to advantages or sets of advantages achieved.
  • some of the attributes con- tained in the claims below may be superfluous from the point of view of separate inventive concepts.
  • different details described in connection with each embodiment example of the invention may also be applied in other embodiment examples.
  • at least some of the sub-claims can be regarded as being inventive in themselves at least in appropriate situations.
  • the arrangement of the invention has the advantage that it works more efficiently as compared to completely passive vi- bration damping methods.
  • the features of different embodiments of the invention can be applied in connection with other embodiments within the scope of the basic inventive concept.
  • a further advantage is compact construction, which allows the machine and machine bed to be made lighter.
  • the arrangement also has the advantage that it permits selective noise suppression.
  • An additional advantage is that the arrangement of the invention is easy to install in a finished elevator.
  • Yet another advantage is that the arrangement is implemented utilizing well-known and approved technology that has been used in other branches of industry.
  • Still another advantage is that the arrangement is economical and simple to implement .
  • the elevator in the arrangement for reducing vibration and noise caused by an elevator hoisting machine, the elevator comprises at least a hoisting machine fitted on a mounting base, a drive sheave connected to the hoisting ma- chine, measuring means for the measurement of vibration and at least one functional element for damping vibration.
  • the rigidity of the said at least one functional element is adapted to be varied on the basis of the measurement results obtained from the measuring means. Varying the rigidity is a fast, effective and fail-safe way of influencing the suspension of the machine. For example, if the functional element is damaged, this will not lead to dangerously aggravated vibration problems .
  • the functional elements are fitted substantially in the direction of the vibrating motion to be damped between the mounting base and the hoisting machine.
  • the hoisting machine is thus supported on the mounting base via the said at least one functional element .
  • the hoisting machine is secured to a mounting element and the functional elements are fitted in a vertical direction between the mounting base and the mounting element .
  • the arrangement comprises a control system which is arranged to receive the measurement data from the measuring means and to issue directives based on the measurement data to each functional element sepa- rately.
  • the functional elements are arranged to be stiffened when the vibration occurs in a direction away from a balanced state.
  • the functional element contains substance, preferably magnetorheologic fluid, by varying the viscosity of which the rigidity of the functional element is arranged to be varied. In this way is achieved a simple and fast controllable efficient solution in which the properties of the functional element are actively varied according to the situation.
  • the functional element contains substance, preferably magnetorheologic fluid, and the rigidity of the functional element is arranged to be varied by exposing the said fluid to a magnetic field.
  • the hoisting machine is supported on the mounting base via the at least one functional element .
  • each functional element at least one measuring means is provided.
  • each functional element two measuring means are provided. This makes it possible to produce a difference value and to control the functional element based on the difference value.
  • the measuring means are acceleration sensors.
  • the arrangement addition- ally comprises a passive damper, preferably an elastomer damper, via which the hoisting machine is supported on the mounting base (directly or indirectly via the machine bed) .
  • a passive damper preferably an elastomer damper
  • the functional element and the passive damper are arranged to have a parallel influence on the motion between the mounting base and the hoisting machine.
  • the functional element can enhance the damping in problematic areas of the passive damper. This also makes it possible to reduce the problems caused by a possible fail- ure of the functional element and always to maintain at least a safe damping level .
  • the elevator comprises at least a hoisting machine fitted against a mounting base, a drive sheave (4) connected to the hoisting machine, measuring means for the measurement of vibration and at least one functional element (6) for damping vibration.
  • the hoisting machine is supported on the mounting base via the said at least one functional element, and vibration is reduced in the method by exerting an effect on the functional element on the basis of the measurement results obtained from the measuring means .
  • an effect is exerted on the functional element by varying the rigidity of the functional element. In this way is achieved a simple and fast controllable efficient solution in which the properties of the functional element are actively varied according to the situation.
  • the elevator comprises measuring means which measure the vibration of the mounting base and measuring means which measure the vibration of the hoisting machine, and the measurement result obtained from the measuring means of the mounting base and the measurement result obtained from the measuring means of the hoisting machine are mutually compared and the functional element is controlled on the basis of the comparison result.
  • the functional element contains substance, preferably magnetorheologic fluid, and the rigidity of the functional element is arranged to be varied by varying the viscosity of the said fluid. In this way is achieved a simple and fast controllable efficient solution in which the properties of the functional element are actively varied according to the situation.
  • the hoisting machine is additionally supported on the mounting base via a passive damper, preferably an elastomer damper.
  • a passive damper preferably an elastomer damper.
  • the hoisting machine is supported on the mounting base in such a way that the functional element and the passive damper have a parallel influence on the motion between the mounting base and the hoisting machine.
  • the functional element and the passive damper can make up for the deficiencies of each other, and the functional element can be kept active for only part of the time .
  • the functional element is rigidified when the distance of vibration from a balanced state exceeds a given predetermined limit. As a result of momentary increase of rigidity thus implemented, a powerful effect is produced by the functional element.
  • the functional element is rigidified when the absolute value of the vibrating motion exceeds a given predetermined limit. As a result of momentary- increase of rigidity thus implemented, a powerful effect is produced by the functional element.
  • the functional element is rigidified when the vibration occurs in a direction away from a balanced state.
  • a powerful effect is produced by the functional element.
  • measuring means are used for measuring the vibration and at least one functional element is used for damping the vibration.
  • the hoisting machine is supported on the mounting base via the said at least one functional element, and vibration is reduced in the method by exerting an effect on the functional element on the basis of the measurement results produced by the measuring means. It is thus possible to exert at a desired instant a desired effect on the suspension of the hoisting machine, e.g. on the rigidity of the suspen- sion.
  • Such an arrangement can be used to reduce vibration problems e.g.
  • the hoisting machine is supported on the mounting base via the at least one functional element, the transmission of vibration from the hoisting machine to the mounting base can be reduced.
  • the functional element is used for active damping of vibration on the basis of previ- ously acquired information regarding problematic vibration frequencies and/or problematic rotational speeds. It is thus possible to select a vibration frequency to be damped that, based on previously acquired information, is problematic, preferably the most problematic. Different rotational speeds may involve different problematic frequencies, and thus the method can be used to damp, if desirable, the most problematic vibration frequency for each rotational speed, which frequency, as stated above, is pre-determined, e.g. by meas- uring. Thus, the damping effect of the functional element can be applied at each instant of time to that vibration frequency which is the most problematic.
  • the pre-determined information may indicate that the machine has rotational speeds at which no problematic vibration occurs, so the functional element need not be employed during such rotational speeds at all.
  • the functional element is used for damping a vibration frequency that has been pre- determined as being problematic, preferably for damping the most problematic vibration frequency.
  • the functional element can be controlled so as to damp the most problematic one of the vibration frequencies substantially appearing at each instant of time.
  • vibration is generated by means of the machine at different frequencies and problematic vibration frequencies are observed, such as e.g. frequencies at which there occur vibration peaks, fre- quencies that produce a large vibration amplitude, loud noise or, say, a problematic resonance in their vicinity, and information regarding the problematic frequencies is stored in memory .
  • vibration is generated by means of the machine at different frequencies and the vibration produced is observed, and the frequency- producing the highest vibration peak is selected and informa- tion regarding the frequency having produced the highest vibration peak is stored in memory, and the functional element is utilized during operation (normal use) to damp vibration occurring at the aforesaid frequency having produced the highest vibration peak.
  • said vibration at different frequencies is generated by means of the machine by accelerating the rotational speed of the machine.
  • the said machine is an elevator hoisting machine, and in the method vibration at different frequencies is generated by accelerating the velocity of the elevator car, and problematic frequencies are observed, such as e.g. frequencies at which there occur vibration peaks, frequencies producing a large vibration amplitude, loud noise or, say, a problematic resonance in their vicinity.
  • problematic frequencies such as e.g. frequencies at which there occur vibration peaks, frequencies producing a large vibration amplitude, loud noise or, say, a problematic resonance in their vicinity.
  • the functional element during operation in a constant-speed range, is utilized to damp vibration occurring at the frequency having produced the highest vibration peak.
  • the functional element is used for active damping of vibration on the basis of previously acquired information regarding problematic rotational speeds of the machine, e.g. by employing the functional ele- ment especially or even exclusively during problematic rotational speeds, for example rotational speeds at which there occur vibration peaks or which produce a large vibration amplitude, loud noise or, say, a problematic resonance in their vicinity.
  • information regarding the rotational speed of the machine may be supplied to the control unit.
  • This embodiment could also be utilized without vibration measurement.
  • An advantage achieved is a longer service life of the functional element.
  • the functional element is used in parallel with a passive damper, whose performance can be enhanced by the functional element .
  • an effect is exerted on the functional element by varying the rigidity of the func- tional element.
  • the functional element is rigidified when the speed of the vibrating motion, especially the absolute value of the speed exceeds a given predetermined limit. As a result of momentary increase of rigidity thus implemented, a powerful effect is produced by the -functional element .
  • the functional element is rigidified when the direction of vibration is away from the balanced state.
  • a powerful effect is produced by the func- tional element.
  • the functional element is rigidified when the distance of the vibrating motion from the balanced state exceeds a given predetermined limit. As a re- suit of momentary increase of rigidity thus implemented, a powerful effect is produced by the functional element.
  • the functional element contains substance, preferably magnetorheologic fluid, by varying the viscosity of which the rigidity of the functional element is arranged to be varied. In this way, simple, efficient and fast increase of rigidity is achieved.
  • the machine is supported on the mounting base in such a way that the functional element and the passive damper have a parallel influence on the motion between the mounting base and the machine. Therefore, the service life of the functional element is extended as a result of the load being shared. Moreover, it is easy to arrange for the passive damper to implement damping without an active damper when the vibration frequency is outside of a vibration frequency range comprising vibration peaks.
  • the determination of problematic rotational speeds and/or problematic vibration frequencies is performed at each instance of operation of the apparatus, preferably at the beginning of each instance of operation, by accelerating.
  • changes in circum- stances /load situation occurring between instances of operation will not have an adverse effect.
  • the determination of problematic rotational speeds and/or problematic vibration fre- quencies is performed at the beginning of each instance of operation of the apparatus (which comprises the aforesaid machine) by accelerating, e.g. by accelerating the machine with or without a load.
  • accelerating e.g. by accelerating the machine with or without a load.
  • rotational speed-specific problematic vibration frequencies are pre-determined, e.g. via acceleration of the machine, and during operation of the machine the vibration frequency pre-determined as being problematic for the current rotational speed is damped.
  • damping can always be applied to that vibration frequency which in the prevailing circumstances is the most problematic .
  • Fig. 1 represents an embodiment of the solution of the invention in diagrammatic and simplified side view
  • Fig. 2 represents the solution of Fig. 1 in diagrammatic and simplified top view
  • Fig. 3 represents a second embodiment of the solution of the invention in diagrammatic and simplified side view
  • Fig. 4 is block diagram of a solution according to the invention which uses one measuring sensor for each vibration damping functional element
  • Fig. 5 is a block diagram of a solution according to the invention which uses two measuring sensors for each vibration damping functional element .
  • Fig. 6 represents a third embodiment of the solution of the invention in diagrammatic and simplified side view
  • Fig. 7 represents a preferable procedure for activating a functional element.
  • Fig. 8 represents a second preferable procedure for activating a functional element.
  • Fig. 1 represents a side view and Fig. 2 a top view of an embodiment of the invention in diagrammatic an simplified form.
  • An elevator hoisting machine 3 is fitted on a machine bed 1 serving as a mounting element on a machine room floor 9 serv- ing as a mounting base.
  • the machine bed 1 comprises two transverse elements 2, on which the hoisting machine 3 with a drive sheave 4 is mounted by means of e.g. paw-like mounting elements 5.
  • Rotatably mounted on the machine bed 1 is also a diverting pulley 10, and a set of hoisting ropes 11 is ar- ranged to run at least over the drive sheave 4 and diverting pulley 10.
  • a functional element 6 is placed under each corner of the machine bed 1, i.e. under either end of both transverse elements 2. Placed at the corners of the machine bed 1 are also measuring means 7, 7' arranged to measure the vibration caused by the hoisting machine 3.
  • the measuring means 7, 7' are e.g. acceleration sensors. Fitted beside each functional element 6 under the machine bed 1 on the machine room floor 9 is one acceleration sensor 7, and one accelera- tion sensor 7' is fitted on the machine bed 1 above each functional element 6.
  • each functional element 6 two acceleration sensors are provided for each functional element 6, the first one of these sensors being arranged to measure the motion of the floor 9 and the second one to measure the motion of the machine bed 1, so that is possible to calculate the difference between the motion of the machine bed and the motion of the floor 9 at all four corners.
  • the arrangement additionally comprises a control system 8, which is connected both to the measuring means 7, 7' and to the functional elements 6.
  • the control system 8 is arranged to receive measurement results from the measuring means 7, 7' and to calculate and transmit on the basis of the results instructions of action to each functional element 6, which in- structions may be mutually different if necessary.
  • the functional element 6 is a motion resisting element, and thus it does not produce any motion itself.
  • the functional element 6 consists of a cylindrical cham- ber with a vertically movable piston fitted in it.
  • the cylinder contains magnetorheologic fluid, and the cylinder is provided with coils fitted to produce an electromagnetic field.
  • the viscosity of the fluid in the cylinder can be adjusted by controlling the magnetic field, the mobility of the piston being thereby varied. The greater the viscosity of the fluid, the more does the piston resist vertical motion and the less does it move vertically.
  • control system 8 is arranged to adjust the rigidity of the functional elements 6 between the machine room floor 9 and the machine bed 1 in a suitable manner on the basis of the measurement results obtained from the measuring means 7, 7'.
  • the variation of the internal rigidity of the functional elements 6 thus achieved is utilized to damp the vibration caused by the hoisting machine 3 when the elevator car is moving.
  • Fig. 3 presents a side view of the hoisting machine of an elevator without machine room in which the arrangement of the invention is applied.
  • the hoisting machine 3 together with a drive sheave 4 is fitted by means of a mounting element 13 on a guide rail 12 serving as a mounting base.
  • a functional element 6 Secured to the guide rail 12 below the mounting element 13 is a functional element 6 and below the latter is an acceleration sensor attached to the guide rail 12 and serving as a measuring means 7.
  • Another acceleration sensor serving as a measuring means 7' is attached to the mounting element 13 above the functional element 6.
  • the mounting element 13 and together with it the hoisting machine 3 are fitted to be vertically movable along the guide rail 12 above the functional element 6 within the limits permitted by the functional element 6.
  • the functional element 6 and the measuring means 7, 7' are connected to a control system 8, which, similarly to the above- described embodiment, is arranged to issue instructions of action based on the measurement results obtained from the measuring means 7, 7' to the functional element 6 to damp the vibration caused by the hoisting machine 3.
  • the idea of the invention is thus to damp the vibration caused by the hoisting machine 3 while the elevator car is moving, by controlling the supporting force between the hoisting machine 3 and the mounting base 9, 12 by means of at least one functional element 6.
  • the functional elements 6 are arranged to be rigidified whenever the vertical direction of vibration is substantially away from a balanced state.
  • This solution differs from active vibration damping in that here no motion opposite to the direction of motion of the vibration is produced, but only the rigidity of the structure of the functional element is varied in order to prevent the piston of the functional element from moving in the direction of vibration and thus at the same time to prevent motion caused by the hoisting machine 3 in the direction of vibration.
  • Fig. 4 presents a simplified block diagram showing how the invention can be arranged to work when each functional element 6 is controlled on the basis of the meas- urement result provided by only one sensor (7 or 7') .
  • the presence of a number of sensors, especially the presence of a sensor both in conjunction with the mounting base and in conjunction with the hoisting machine is preferable, because this makes it possible to establish the rela- tive speed of the hoisting machine and the mounting base, e.g. by calculating the difference value between the measurement results.
  • FIG. 5 presents a simplified diagram of the invention when each functional element 6 is controlled on the basis of the measurement results obtained from two sensors.
  • the control unit 8 performs a comparison between the measurement result obtained from the measuring means 7 con- nected to the mounting base and the measurement result obtained from the measuring means 7 ' connected to the hoisting machine and controls the functional element 6 on the basis of the comparison result.
  • the sensor 7 measuring the vibration of the mounting base is placed in the vi- cinity of the functional element 6 controlled on the basis of the measurement result provided by the sensor 7 in question.
  • this sensor 7 is placed at a distance below 50 cm from the functional element 6.
  • the preferable disposition of the sensors 7,7' relative to each other is visualized by depicting the sensor (s) near the functional element 6.
  • the noise and vibration caused by an elevator hoisting machine is reduced e.g. by suspending the hoisting machine 3 on the mounting base 9,12 via the said at least one functional element 6 and exerting an effect on the functional element 6 on the basis of the measurement results obtained from the measuring means 7, 7'. This can be done e.g. in the manner described elsewhere by varying the rigidity of the functional element 6.
  • the elevator comprises measuring means 7 measur- ing the vibration of the mounting base 9,12 and measuring means 7' measuring the vibration of the hoisting machine 3
  • the measurement result obtained from the measuring means 7 of the mounting base and the measurement result obtained from the measuring means 7' of the hoisting machine are compared to each other and the functional element 6 is controlled on the basis of the comparison result.
  • the rigidity of the functional element 6 is preferably increased when vibration occurs in a direction away from a balanced state. This is preferably done by feeding current from the control system 8 to the functional element 6 containing magnetorheologic substance when the speed of the vibrating motion is at a maximum.
  • Fig. 6 presents an embodiment of the invention, which corresponds to the embodiment in Fig. 1 in other respects except that the arrangement comprises in addition to the functional element 6 a passive damper 14, via which the hoisting machine 3 is supported on the mounting base (9,12) .
  • the damper 14 is preferably an elastomer body, such as e.g. a rubber body, but it could also be some other type of structure, e.g. a hydraulic spring.
  • the functional element 6 and the passive damper 14 are arranged to exert a parallel influence on the motion between the mounting base (9,12) and the hoisting machine 3. It is preferable to arrange for the passive damper 14 to bear most of the load imposed on the mounting base by the hoisting machine 3 and machine bed 1.
  • the service life of the functional element 6 can be considerably increased, because the load applied to it can be easily arranged to be sufficiently small.
  • a parallel arrangement permits the functional element to be arranged to complement the damping effect of the passive damper especially at frequencies that are too difficult for a rubber damper.
  • the damping effect of the functional element can only be turned on when certain vibra- tion frequencies and/or rotational speeds occur, but at other times the functional element can be kept inactive. By operating the functional element only according to need, its service life can be considerably extended. Also, if desirable, the damping function can be employed at night time only, which is when the noise produced by vibration causes the most disturbance .
  • dampers 6 and 14 When the dampers 6 and 14 are arranged to exert a damping ef- feet in parallel, the relative motion between the hoisting machine and mounting base can be easily caused to be transmitted substantially in its entire extent to both dampers 6 and 14, whereas if the dampers were series-connected, e.g. placed one upon the other, then, due to the elasticity of the rubber damper, the motion transmitted to the functional element would have an extent differing from the extent of the relative motion between the hoisting machine and mounting base.
  • a parallel arrangement saves space, among other things, and allows optimization of the damping properties of the dampers independently of each other.
  • Fig. 7 visualizes a preferable procedure for utilizing the functional element 6.
  • the graph A represents the reciprocating vibrating motion s relative to time t .
  • the balanced motional state occurs at the level of the time axis t.
  • the functional element is rigidified when the distance of the vibrating motion from the balanced state exceeds a given predetermined limit, i.e. in this figure when the motion from the balanced state ex- ceeds the limit value Ll. After this, the rigidification is interrupted by deactivating the functional element until the distance of vibration from the balanced state again exceeds a given predetermined limit.
  • the deactivation can be done as visualized by the figure when the distance from the balanced state returns to a point below the limit value, but in some cases it may be preferable to deactivate the functional element already at the peak point pi or after it, e.g. between the peak point pi and the limit value. It is obvious that the limit values for different directions of motion may be of different magnitude.
  • Fig. 8 visualizes another advantageous procedure for utilizing the functional element.
  • the graph B represents the motional speed of vibration v relative to time t.
  • the motional speed is zero at the level of the time axis t in the figure.
  • the functional element is rigidified when the absolute value of the speed of the vibrating motion exceeds a given predetermined limit. After this, the stiffening of the functional element is inter- rupted by deactivating the functional element until the absolute value of the speed of vibration again exceeds a given predetermined limit. The deactivation can be done as visualized by the figure when the absolute value of the speed returns to a point below the limit value.
  • the functional element 6 is used for active damping of vibration on the basis of previously acquired information regarding problematic frequency ranges, especially frequency ranges in which there occur vibration peaks.
  • problematic frequency ranges especially frequency ranges in which there occur vibration peaks.
  • the functional element 6 is used in this embodiment to damp one vibration frequency which has been pre-determined as being problematic, e.g. producing a vibration peak, the greatest vibration amplitude, noise or, say, a problematic resonance in its vicinity.
  • the damping effect of the functional element can be applied to damping vibration of that frequency which causes the most problems for the environment or the machine itself.
  • the functional element can also be used for active damping based on other criteria, e.g. on the basis of the rotational speed of the machine so that active damping by means of the functional element is not started until the rotational speed of the machine reaches a rotational speed range that has been found to be problematic. In this way, the service life of the functional element can be extended.
  • control based on rotational speed can also be so implemented that the most problematic vibration frequencies specific to rotational speeds can be defined beforehand, allowing a predetermined problematic frequency to be selected for the current rotational speed as the vibration frequency to be damped. Thus, when the rotational speed changes, the frequency to be damped can be changed. It is thus always possible damp that vibration frequency which is the most problematic in the prevailing circumstances.
  • vibrations of different frequencies are gener- ated by means of the machine, observing the frequencies at which there appear problems as mentioned above, and information regarding the problematic frequencies is stored in memory, for which purpose the control system 8 may comprise a memory.
  • the generation of vibrations of different frequencies can be effected by means of the machine by accelerating the rotational speed of the machine.
  • the vibration frequency having caused the most problems is selected and, during normal operation, vibration of this frequency is damped. Damping is preferably applied to the frequency having produced the highest vibration peak.
  • the damping of vibration is effected by exerting an influence on the functional element by varying the rigidity of the functional element on the basis of vibration measurement.
  • the functional element is preferably rigidified when the vibration occurs in a direction away from the balanced state.
  • the instant of rigidification of the functional element can also be so defined that it will occur when the absolute value of the speed of the vibrating motion exceeds a given predetermined limit.
  • the instant of ri- gidification of the functional element can also be so defined that it will occur when the distance of the vibrating motion from the balanced state exceeds a given predetermined limit.
  • the functional element is of a type described elsewhere in the application, but preferably it contains magnetorheologic fluid, by varying the viscosity of which the rigidity of the functional element is arranged to be varied. After the functional element 6 has been stiffened, the stiffening is interrupted, whereafter the element is stiffened again, preferably according to Fig. 7 or 8.
  • the aforesaid machine may be the machine of any apparatus .
  • the method comprises generation of vibration at different frequencies by accelerating the velocity of the elevator car, and observing frequencies at which problems as mentioned above, such as e.g. vibration peaks, appear.
  • the invention can also be applied in such a way that, if in connection with normal operation of the machine, e.g. in the case of an elevator, during constant-speed travel, there appears substantial vibration in a frequency range in which or in the vicinity of which a vibration peak has been observed, then a functional element is put into operation to damp the vibration frequency in question e.g. in the manner visualized in Fig. 7 or 8.
  • the exertion of an influence on the functional element is started by altering the rigidity of the functional element on the basis of vibration measurement at a frequency suited to the vibration frequency in question.
  • the functional element can be put into operation either from an idle state or by altering its damping frequency if the element is already damping.
  • the vibration frequency to be damped is advantageously changed during travel when it is detected that vibration begins to intensify at a frequency more problematic than the frequency currently being damped .
  • the machine can be accelerated in order to determine problematic rotational speeds, by increasing the rotational speed of the machine and at the same time measuring the influence of rotational speed on vibration or on an effect resulting from vibration, e.g. measuring the noise produced, the vibration amplitude, or the like. If the influence of rotational speed on vibration or on an effect resulting from vibration exceeds a predetermined limit value, then the rotational speed range in question is stored in memory to make it possible to activate the functional element when the rotational speed is in the problematic range in question during normal operation of the machine.
  • the aforesaid acceleration for determining problematic rota- tional speeds and/or problematic vibration frequencies can be performed in connection with the installation of the apparatus or via acceleration in connection with normal operation of the machine.
  • the aforesaid acceleration can be performed already at factory or when the rotational speed of the automobile motor is accelerated during idling or during travel when the driving speed is accelerated.
  • problematic rotational speeds and/or vibration frequencies can be determined during normal operation e.g. in connection with the initial acceleration.
  • the aforesaid acceleration for determining problematic rotational speeds and/or problematic vibration frequencies can be performed separately each time the apparatus is used.
  • the vibration-eliminating functional element of the invention may also be of a different type besides that described above.
  • the compensating device used as a functional element may be any mechanical, hydraulic or e.g. electro-mechanical device whose rigidity can be varied to damp vibration.
  • the rigidity of a hydraulic device could be varied e.g. by controlling the pressure of the hydraulic fluid.
  • the functional element could also be a solenoid damper wherein a solenoid is arranged to resist the motion of the hoisting machine. In this case, the rigidity of the functional element can be controlled by adjusting the current fed to the solenoid.
  • the functional ele- ment could also be a frictional damper wherein the motion of the hoisting machine is resisted by friction either directly or indirectly.
  • the intensity of the friction can be controlled e.g. by means of an adjustable-force solenoid which presses a friction piece against a part attached to the hoisting machine or machine bed. In this way, the resistance to the vibrating motion can be controlled.
  • the vibration can be measured in other ways, e.g. mechanically, optically, electrically, and so on.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Cage And Drive Apparatuses For Elevators (AREA)
  • Elevator Control (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

L'invention porte sur un agencement pour réduire la vibration et le bruit provoqués par la machine de levage d'un ascenseur, ledit ascenseur comprenant au moins une machine de levage (3) disposée sur une base de montage (9, 12), une poulie d'entraînement (4) reliée à la machine de levage (3), des moyens de mesure (7, 7') pour la mesure de vibration et au moins un élément fonctionnel (6) pour amortir la vibration. La rigidité de chaque élément fonctionnel (6) est apte à varier en fonction des résultats de mesure obtenus à partir des moyens de mesure (7, 7').
PCT/FI2009/000103 2008-12-11 2009-12-10 Agencement et procédé pour réduire le bruit et la vibration provoqués par une machine de levage d'ascenseur, et procédé pour réduire le bruit et la vibration provoqués par une machine WO2010066939A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FI20080653 2008-12-11
FI20080653A FI20080653L (fi) 2008-12-11 2008-12-11 Järjestely ja menetelmä hissin nostokoneiston aiheuttaman melun ja värähtelyn vähentämiseksi
FI20090055 2009-02-16
FI20090055A FI20090055A0 (fi) 2008-12-11 2009-02-16 Järjestelmä ja menetelmä hissin nostokoneiston aiheuttaman melun ja värähtelyn vähentämiseksi ja menetelmä koneiston aiheuttaman melun ja värähtelyn vähentämiseksi

Publications (2)

Publication Number Publication Date
WO2010066939A1 true WO2010066939A1 (fr) 2010-06-17
WO2010066939A8 WO2010066939A8 (fr) 2010-07-22

Family

ID=40240513

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FI2009/000103 WO2010066939A1 (fr) 2008-12-11 2009-12-10 Agencement et procédé pour réduire le bruit et la vibration provoqués par une machine de levage d'ascenseur, et procédé pour réduire le bruit et la vibration provoqués par une machine

Country Status (2)

Country Link
FI (2) FI20080653L (fr)
WO (1) WO2010066939A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106064779A (zh) * 2015-04-20 2016-11-02 株式会社日立制作所 电梯

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6296088B1 (en) * 1997-02-24 2001-10-02 Lord Corporation Magnetorheological fluid seismic damper
US20030160369A1 (en) * 2002-01-11 2003-08-28 Laplante John A. Semi-active shock absorber control system
WO2005044710A1 (fr) * 2003-10-08 2005-05-19 Otis Elevator Company Guidage d'ascenseur a galets avec amortisseur a rigidite variable
US20060173592A1 (en) * 2001-07-30 2006-08-03 Gade Prasad V Control of magnetorheological mount
US20070144842A1 (en) * 2003-08-20 2007-06-28 Reactec Ltd Vibration control system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6296088B1 (en) * 1997-02-24 2001-10-02 Lord Corporation Magnetorheological fluid seismic damper
US20060173592A1 (en) * 2001-07-30 2006-08-03 Gade Prasad V Control of magnetorheological mount
US20030160369A1 (en) * 2002-01-11 2003-08-28 Laplante John A. Semi-active shock absorber control system
US20070144842A1 (en) * 2003-08-20 2007-06-28 Reactec Ltd Vibration control system
WO2005044710A1 (fr) * 2003-10-08 2005-05-19 Otis Elevator Company Guidage d'ascenseur a galets avec amortisseur a rigidite variable

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106064779A (zh) * 2015-04-20 2016-11-02 株式会社日立制作所 电梯

Also Published As

Publication number Publication date
FI20090055A0 (fi) 2009-02-16
FI20080653L (fi) 2010-06-12
WO2010066939A8 (fr) 2010-07-22
FI20080653A0 (fi) 2008-12-11

Similar Documents

Publication Publication Date Title
CA2679474C (fr) Systeme et procede de reduction du balancement des cables d'ascenseurs
JP5530518B2 (ja) ロープ張力の調整によるロープの揺れの抑制
JP5341204B2 (ja) 振動ダンパを用いたエレベータかごの位置決め
JP3916295B2 (ja) エレベータ運動制御システムおよびアクティブエレベータヒッチ
EP2913289B1 (fr) Système élévateur
JP2006264983A (ja) 上下振動を補償するエレベータ
KR0182335B1 (ko) 엘리베이터의 제진장치
JPH06100273A (ja) エレベータの振動防止装置
JP2013095570A (ja) 制振装置を備えたエレベーター
JP2008168980A (ja) エレベータ乗りかごの縦振動抑制装置
JP2865949B2 (ja) エレベータの制振装置
US7543686B2 (en) Elevator with rollers having selectively variable hardness
JP2000219441A (ja) 制振装置
JP2899455B2 (ja) エレベータ
WO2010066939A1 (fr) Agencement et procédé pour réduire le bruit et la vibration provoqués par une machine de levage d'ascenseur, et procédé pour réduire le bruit et la vibration provoqués par une machine
EP1678068A1 (fr) Guidage d'ascenseur a galets avec amortisseur a rigidite variable
JP5528997B2 (ja) エレベータのかご室振動低減装置
JP2003104655A (ja) エレベータ装置
JPH09240930A (ja) エレベータの制御装置
JP6490201B2 (ja) リフティングシステム、電気的な検査のための方法、振動減衰器及び機械アセンブリ
JP5285583B2 (ja) エレベータ乗りかご用縦振動抑制装置
KR200427906Y1 (ko) 권상 로프식 엘리베이터 카의 진동 저감장치
JP4122761B2 (ja) エレベーター装置
JP2001247263A (ja) エレベータの振動抑制装置
WO2013158073A1 (fr) Actionneur intégré pour la commande de vibration d'un ascenseur

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09831512

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 09831512

Country of ref document: EP

Kind code of ref document: A1