GB2472626A - A generator set including a torsional vibration damper - Google Patents

A generator set including a torsional vibration damper Download PDF

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Publication number
GB2472626A
GB2472626A GB0914141A GB0914141A GB2472626A GB 2472626 A GB2472626 A GB 2472626A GB 0914141 A GB0914141 A GB 0914141A GB 0914141 A GB0914141 A GB 0914141A GB 2472626 A GB2472626 A GB 2472626A
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United Kingdom
Prior art keywords
springs
input
stiffness
engine
generator set
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Granted
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GB0914141A
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GB0914141D0 (en
GB2472626B (en
Inventor
Benjamin Chetwood Struve
Simon John Jayes
Andrea Ribichini
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Raicam Clutch Ltd
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Raicam Clutch Ltd
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Priority to GB0914141A priority Critical patent/GB2472626B/en
Publication of GB0914141D0 publication Critical patent/GB0914141D0/en
Publication of GB2472626A publication Critical patent/GB2472626A/en
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Publication of GB2472626B publication Critical patent/GB2472626B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • F16F15/12373—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/1213—Spiral springs, e.g. lying in one plane, around axis of rotation
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12306—Radially mounted springs
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/1333—Spiral springs, e.g. lying in one plane, around axis of rotation
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/13407—Radially mounted springs

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

A generator set (10) in which an internal combustion engine (11) is connected with an electrical generating machine (12). The set is operable in two modes, a generating mode when the engine drives the generating machine to generate electrical power and a starting mode in which the generating machine drives the engine to start the engine. A torsional vibration damper (14) connects the engine and the electrical generating machine, the vibration damper providing a lower torsional stiffness when the engine is driving the generating machine in generating mode than when the generator is driving the engine in starting mode.

Description

GENERATORS
This invention relates to generators and in particular generator sets, hereinafter referred to as of the type described", in which an internal combustion engine is connected with an electrical generating machine, the set being operable in two modes, a generating mode when the engine drives the generating machine to generate electrical power and a starting mode in which the generating machine drives the engine to start the engine.
Generator sets of the type described are used for many applications. For example, in the automotive sector a vehicle may be driven by one or more electric motors which receive power either directly from the electrical generating machine or from batteries or other storage devices which are charged by the electrical generating machine. In such an arrangement the electrical generating machine may also use stored electrical energy to apply a torque to the internal combustion engine to spin the engine up to its starting speed and thereafter the engine drives the generating machine to power the vehicle and to generate electrical energy which can also be stored. Such vehicle arrangements have overall control systems which stop and start the engine when further electrical power is required either to drive the vehicle or top-up the electrical energy storage devices.
Such generator sets use brush less technology to switch the direction of travel of current in rotor windings. Typically a rotary encoder measures the angular position of the rotor and feeds this information to an electronic control system which switches the current between the rotor windings using solid state devices. Such an arrangement for switching current in the rotor windings can be very efficient if the rotor rotates smoothly, however, if the rotor speed fluctuates, the control system cannot accurately predict the angular position of the rotor and the efficiency of the etectrical generating machine deteriorates.
It is therefore an object of the present invention to provide a generator set of the type described which is suitable for use in the above described vehicular application.
Thus according to the present invention there is provided a generator set of the type described having a torsional vibration damper which connects the engine and the electrical generating machine, the vibration dampel providing a lower torsional stiffness when the engine is driving the generating machine in generating mode than when the generator is driving the engine in starting mode.
By arranging that the torsional vibration damper has a lower stiffness when operating in the generating mode a low natural frequency of the system is ensured which is well below (e.g. half) the frequency of the fluctuating torque applied to the engine during generating. Similarly by arranging for the torsional vibration damper to have a higher stiffness when operating in the starting mode a higher natural frequency of the system is ensure which is well above (e.g. twice) the frequency of the fluctuating torque applied to the engine during start-up.
The torsional vibration damper may have an input member and an output member with spring members acting circumferentially between the input and output members which are compressed on relative rotation between the input and output members, the spring members being grouped together and connected with the input and output members so that relative rotation in one direction between the input and output members engages springs which provide a first lower total rotational stiffness and relative rotation between the input and output members in the opposite direction engages springs which provide a second higher total rotational stiffness.
The torsional vibration damper may have two tiers of springs acting circumferentially between the input and output members, a first tier of lower stiffness springs which are compressed in both directions of relative rotation of the input and output members and a second tier of higher stiffness springs which are only compressed during relative rotation of the input and output member during the starting mode of operation.
In such an arrangement, both tiers of springs may operate in two stages to give a two stage stiffness characteristic in both directions of relative rotation of the input and output members.
Alternatively, there may be two sets of springs acting between the input and output members, both sets of springs being compressed to give a higher stiffness in one direction of relative rotation between the input and output members, and only one set of springs being compressed to give a lower stiffness in the other direction of relative rotation between the input and output members.
The present invention will now be described, by way of example only, with reference to the accompanying drawings in which:-Figure 1 shows, diagrammatically, the general layout of a generator set in accordance with the present invention; Figure 2 shows the ideal characteristics for the torsional vibration damper of the generator set during engine start-up; Figure 3 shows the ideal characteristics for the damper during operation in its generating mode; Figure 4 shows the torque deflection curve for a first form of torsional vibration damper which uses two tiers of springs; Figure 5 shows a perspective cross sectional view through the two tier spring damper; Figure 6 shows a plan view of the high stiffness spring tier of the damper of figure 5; Figure 7 shows an external plan view of a second form of torsional vibration damper for use in the generator set; Figure 8 shows a section on the line A-A of figure 7; Figure 9 shows a view in the direction of the arrow B of figure 8 with an outer plate removed to show internal details of the damper, and Figure 10 shows the torque deflection curve for the damper of figures 7 to 9.
A generator set 10 in accordance with the present invention, shown in figure 1, comprises a combustion engine 11, for example a diesel engine, which drives an electrical generating machine 12 via a flywheel 13 and a torsional vibrating damper 14.
Typically such a generator set is used in automotive applications to drive a vehicle which is powered by one or more electric motors. These motors may, for example, receive power directly from the electrical generating machine or from batteries or other storage devices which are charged by the electrical generating machine 12.
Not only is the generator set used to generate electrical energy but it can also be used in reverse with the electrical generating machine 12 using stored electrical energy to apply torque to the internal combustion engine 11 in order to spin the engine up to its starting speed whereupon the engine starts to drive the generating set to generate further electrical energy which can again be stored. In such vehicle arrangements, an overall electrical power control system is provided which stops and starts the engine when further electrical power is required either to drive the vehicle or to top-up the electrical storage devices provided in the vehicle.
The generator set thus operates in two modes, the so-called "generating mode" when the engine drives the generating machine and the so-called "starting mode" when the generating machine drives the engine to start up the engine.
The electrical generating machine is supplied with the customary windings which are rotated in a magnetic field thus generating electrical current for charging the storage devices (e.g. batteries) of the vehicle. The direction of travel of current in the rotor windings is switched by a brushless switching arrangement having a rotary encoder which measures the angular position of the rotor windings and feeds this information to an electrical control system which switches the current between the rotor windings using solid state devices.
In accordance with the present invention, in order to ensure the smooth rotation of the rotor in both modes of operation of the generator set, the torsional vibration damper has a lower torsional stiffness when transmitting drive from the engine to the electrical generating machine than the torsional resistance provided by the damper when the electrical generating machine if starting the engine.
In a typical system the inertia of the rotating components within the engine is of the order of 0.05 kg.m2 and the inertia of the rotor in the electrical machine is of the order of 0.06 kg.m2. If the engine is a three cylinder unit operating on a four stroke cycle and runs at a constant speed of say 1500 rpm when in its generating mode (and assuming that there are three fluctuations in torque occurring in every two revolutions from the engine) the fluctuating torque applied to the engine inertia is predominantly of the order of 37.5 Hz. In order to avoid reaching the natural frequency of the system, the stiffness of the torsional vibration damper needs to be sufficiently stiff to ensure that the natural frequency of the system is significantly higher, for example twice, the forcing frequency (37.5Hz) applied to the engine. In order to reach this natural frequency of say 75 Hz is necessary for the stiffness of the torsional vibration damper in the generating mode to be approximately 6,000 Nm/rad or 105 Nm per degree.
This stiffness may be calculated as follows: The system having 2 inertias (i.e. the engine and the generator rotor), connected by a stiffness (i.e. the torsional damper), it has the same natural frequency as a system with a single equivalent inertia supported by the torsional damper stiffness. The value of this equivalent inertia is calculated as follows: lequivalent = (lengine * Igenerator) / (engine + Igenerator) The natural frequency of the system and the stiffness are linked by the equation: F = (1/2rr) * I(KdamperIlequivaIent) Therefore in the example quoted above, the equivalent inertia value is (0.05*0.06)/(0.05+0.06) = 0.027273 kg.m2, and consequently if the natural frequency is to be 75 Hz the stiffness is given from the equation:-Hz = (1121r) * I(Kdamper/0.027273).
This gives a stiffness of approximately 6000 Nm/rad.
Additionally it is desirable for the system to be highly damped in order to dissipate energy within the torsional damper. Figure 2 shows the relationship between the forcing frequency Fl applied to the engine and the systems natural frequency and shows that by having a highly damped system (see curve H) the forcing frequency applied to the engine can be kept well below the natural frequency of the system.
Conversely when the system is running in its generating mode, it is necessary for the natural frequency of the system to be much lower than the frequency at which the fluctuating torque is applied to the engine. For example, if the variables of the system remain as previously described it will be desirable for the natural frequency of the system to be significantly less than the forcing frequency to ensure that the rotors of the electrical generating machine are isolated from the vibrating engine.
Typically the arrangement will be set so that the natural frequency of the system is approximately half of the frequency applied to the engine i.e. 18.75Hz which necessitates a spring stiffness of approximately 375 Nm per rad or 6.6 Nm per degree (using the equations referred to above). When operating in generating mode, low damping is also desirable in order to ensure the most efficient vibration isolation at the electrical generating machine. Figure 3 shows the relationship between the forcing frequency F2 applied between the engine and the system's natural frequency using low damping (see curve L) in the torsional vibration damper. It can be seen that using such an operating characteristic the forcing frequency remains well above the systems natural frequency.
In order to achieve the above different torsional vibration damper characteristics when operating in the starting and generating modes it is necessary for torsional vibration damper 14 to have a highly asymmetric torque versus deflection characteristic. Figure 4 shows such toique versus deflection characteristic for one form of torsional vibration damper which is shown in figures 5 and 6.
As can be seen from figure 4, when the generator set is operating in its starting mode the torsional vibration damper applies a first level of resistance along the curved section OA and a second much higher level of torsional resistance along the second section AB of the curve. Similarly when the generator set is operating in its generating mode the relatively low (almost zero) resistance is applied on the first portion OC of the curve and a somewhat higher resistance is applied along the section CD of the curve.
This two stage stiffness characteristic can be achieved in a number of ways. For example, referring to figures 5 and 6, the torsional vibration damper may have an input member in the form of an outer annular member 15 which is bolted to the flywheel 13 of the generator set via holes 16. The torsional vibration damper also includes an output member in the form of a splined sleeve 17 which is connected with an input shaft 18 of the electrical generating machine 12. Acting between the outer annular member 15 and the sleeve 17 are two tiers of compression springs 19 and 20. Springs 19 form a higher stiffness tier of springs details of which are shown in figure 6. Springs 20 form a lower stiffness tier of springs which has a generally similar circumferential layout to that shown in figure 6 but which is connected with the output sleeve 17 in a different manner as will be discussed below.
Referring to the higher stiffness tier of springs 19 these act between axially spaced outer sheet metal plates 21 which are riveted together at 22.
Outer sheet metal members 21 have windows 23 which house the springs 19 and are also secured to the outer annular input member 15. An inner plate member 24 is connected at its inner periphery with output sleeve 17 via teeth 17a which engage circumferentially in extending slots 25 in the inner periphery of the plate 24. The springs 19 are of two types. There are two lower rate springs 1 9A at diametrically opposite positions and four higher rate springs 19B arranged circumferentially in pairs between the lower rate springs 19A. The lower rate springs 19A are located in windows 26 in the plate 24 which are substantially the same circumferential length as the springs 1 9A. The stiffer springs I 9B are located in windows 27 in plate 24 which are of a longer circumferential extent than the co-operating springs 1 9B.
Thus with the sleeve 16 in a position shown in figure 6, and with the sleeve being driven ant-clockwise during the starting mode of operation of the generator set the plate 24 is driven by the teeth 1 7a of the sleeve 17 which engage the ends 25a of the slots 25 in the inner periphery of the plate 24. Thus the lower stiffness springs are immediately compressed by the ends 26a of windows 26 contacting the adjacent end of the corresponding spring I 9A and the other end of the spring I 9A being contacted by one of the ends of the corresponding window 23 formed in the outer sheet metal members 21. Thus during the initial relative rotation of the sleeve 17 and the outer annular member 15 only the springs 1 9A are compressed contributing to the lower damping characteristic in the section OA of figure 4 which operates in the first 2° of relative rotation between sleeve 17 and outer member 15. Further relative rotation between sleeve 17 and outer member 15 causes the ends 27a of the windows 27 to abut the ends of the co-operating higher stiffness springs 1 9B so that these stiffer springs are then also compressed resulting in a higher overall stiffness from the high stiffness tier of springs 19 which contributes to the higher rate characteristic along the section AB of figure 4.
The low stiffness tier of the rotary damper provided by springs 20 is of a similar circumferential layout to that shown in figure 6 except that the teeth 17a on the sleeve 17 operate in slots 25 which have no circumferential clearance so that whichever direction the sleeve 17 is rotated relative to the outer annular member 15 the plate 24 of the lower stiffness tier is always driven by the sleeve 17. Thus during the operation of generating set in the starting mode the stiffness in sections OA and AB in the curve is also contributed to by two low stiffness springs 20 of the lower stiffness tier of the damper corresponding to the two first stage springs 1 9A of the higher stiffness tier and during the second stage AB of the starting mode of operation this stiffness is also contributed to by four further springs 20 of the low stiffness tier corresponding to the springs I 9B of the higher stiffness tier.
When the generator set is operating in the generating mode the higher stiffness tier of springs shown in figure 6 is not operative as the teeth 17a on sleeve 17 do not make contact with the ends 25b of slots 25 thus the stiffness in section OC of the curve is provided totally by the low stiffness spring pair from the low stiffness tier of springs corresponding to springs 19A and the stiffness in the second stage CD is provided by all six springs of the low stiffness tier which correspond to springs 19A and 1 9B of the higher stiffness tier.
Figures 7, 8 and 9 show details of an alternative form of torsional vibration damper which provides a single stage damping characteristic in the starting and generating modes. As can be best seen from figure 8, the flywheel 13 is connected with axially spaced outer sheet metal members 21 which are riveted together at 22 and secured to the flywheel by bolts 1 3a. The damper has outer lower stiffness springs 30 and inner lower stiffness springs 31 at diametrically opposite positions and which again act in windows 23 in the outer plates 21 and also in windows 26 in an inner plate 24 which is formed as an integral part of sleeve 17. As can be seen from figure 9, the windows 26 in inner plate 24 are the same length as the corresponding springs 30 and 31 so that these springs 30 and 31 will operate in both directions of relative rotation between the sleeve 17 and the flywheel 13 so that they operate in both the starting and generating modes of the generator set.
The torsional vibration damper 40 also includes stiffer outer springs 32 and stiffer inner springs 33 housed diametrically opposite each other these stiffer springs 32 and 33 are again housed in windows 23 in the outer plate 21 but are received in circumferentially longer windows 27 provided in the inner plate 24. Thus, when the inner plate 24 is rotated anti-clockwise relative to the outer plate 21 by the sleeve 17 during the starting mode of the operation of the generator set, the stiffer springs 32 I0 and 33 are compressed together with the lower stiffness springs 30 and 31 to provide the characteristic OX in figure 10, Conversely, in the generating mode of operation of the generator set, when the inner plate is effectively rotated clockwise relative to the outer plates 21, the ends 27a of the windows 27 will not contact the ends of the springs 32 and 33 so that the stiffer springs 32 and 33 do not contribute to the overall stiffness of the torsional vibration damper and the lower stiffness characteristic OY of figure 10 is produced. Thus the torsional vibration damper uses all the lower and higher stiffness springs 30 to 33 when operating in the starting mode and only the lower stiffness springs 30 and 31 when operating in the generating mode. A friction damper 35 may also be provided between the inner plate 24 and the outer plates 21 if the required damping charateristics require this.
As will be appreciated, the present invention thus provides a generator set which is particularly suitable for automotive applications since it overcomes the operating problems associated with torsional vibrations in the connection between the engine and the electrical generating machine.

Claims (6)

  1. CLAIMS1) A generator set of the type described having a torsional vibration damper which connects the engine and the electrical generating machine, the vibration damper providing a lower torsional stiffness when the engine is driving the generating machine in generating mode than when the generator is driving the engine in starting mode.
  2. 2) A generator set according to claim 1 in which the torsional vibration damper has an input member and an output member with spring members acting circumferentially between the input and output members which are compressed on relative rotation between the input and output members, the spring members being grouped together and connected with the input and output members so that relative rotation in one direction between the input and output members engages springs which provide a first lower total rotational stiffness and relative rotation between the input and output members in the opposite direction engages springs which provide a second higher total rotational stiffness.
  3. 3) A generator set according to claim 2 in which there are two tiers of springs acting circumferentially between the input and output members, a first tier of lower stiffness springs which are compressed in both directions of relative rotation of the input and output members and a second tier of higher stiffness springs which are only compressed during relative rotation of the input and output member during the starting mode of operation.
  4. 4) A generator set according to claim 3 in which both tiers of springs operate in two stages to give a two stage stiffness characteristic in both directions of relative rotation of the input and output members.
  5. 5) A generator set according to claim 2 in which there are two sets of springs acting between the input and output members, both sets of springs being compressed to give a higher stiffness in one direction of relative rotation between the input and output members, and only one set of springs being compressed to give a lower stiffness in the other direction of relative rotation between the input and output members.
  6. 6) A generator set constructed and arranged substantially as hereinbefore described with reference to and as shown in the accompanying drawings.
GB0914141A 2009-08-13 2009-08-13 Generators Expired - Fee Related GB2472626B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB0914141A GB2472626B (en) 2009-08-13 2009-08-13 Generators

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Application Number Priority Date Filing Date Title
GB0914141A GB2472626B (en) 2009-08-13 2009-08-13 Generators

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GB2472626A true GB2472626A (en) 2011-02-16
GB2472626B GB2472626B (en) 2014-12-17

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1047023A (en) * 1962-08-17 1966-11-02 Borg Warner Vibration damper assembly
GB2044396A (en) * 1979-02-23 1980-10-15 Ferodo Sa Clutch torsion damping device
US4747800A (en) * 1984-07-31 1988-05-31 Kabushiki Kaisha Daikin Seisakusho Damper disc with serial torsion springs
GB2341913A (en) * 1998-05-07 2000-03-29 Luk Lamellen & Kupplungsbau Torsional vibration absorber

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1047023A (en) * 1962-08-17 1966-11-02 Borg Warner Vibration damper assembly
GB2044396A (en) * 1979-02-23 1980-10-15 Ferodo Sa Clutch torsion damping device
US4747800A (en) * 1984-07-31 1988-05-31 Kabushiki Kaisha Daikin Seisakusho Damper disc with serial torsion springs
GB2341913A (en) * 1998-05-07 2000-03-29 Luk Lamellen & Kupplungsbau Torsional vibration absorber

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Publication number Publication date
GB0914141D0 (en) 2009-09-16
GB2472626B (en) 2014-12-17

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