WO2005119100A1 - System for limiting a force load - Google Patents
System for limiting a force load Download PDFInfo
- Publication number
- WO2005119100A1 WO2005119100A1 PCT/NO2005/000191 NO2005000191W WO2005119100A1 WO 2005119100 A1 WO2005119100 A1 WO 2005119100A1 NO 2005000191 W NO2005000191 W NO 2005000191W WO 2005119100 A1 WO2005119100 A1 WO 2005119100A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- signal
- piston
- regulator
- gear lever
- force
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/04—In which the ratio between pump stroke and motor stroke varies with the resistance against the motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7053—Double-acting output members
- F15B2211/7054—Having equal piston areas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/76—Control of force or torque of the output member
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
- F16H2061/301—Hydraulic or pneumatic motors or related fluid control means therefor for power assistance, i.e. servos with follow up action
-
- 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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
- F16H2061/301—Hydraulic or pneumatic motors or related fluid control means therefor for power assistance, i.e. servos with follow up action
- F16H2061/302—Hydraulic or pneumatic motors or related fluid control means therefor for power assistance, i.e. servos with follow up action with variable force amplification, e.g. force is depending on selected gear or on actuator force (non-linear amplification)
Definitions
- the invention relates to a system for ensuring that the total force acting on a shifting mechanism that is used to change the gear ratio in a gearbox does not exceed a predetermined value.
- the gear shifting mechanisms such as the shift forks and the synchronisation mechanisms in manual gearboxes, are constructed so as to be able to withstand the forces to which they are subjected when operated manually.
- the forces employed by the driver when he operates the gear lever are transmitted by, for example, a mechanical or hydraulic transmission to the gear shifting mechanism in the gearbox.
- One approach in order to solve this problem is to obtain a condition-controlled limit to the assistance system power supply, the controlling conditions for limiting the power supply being set according to parameters such as the tolerance limit of the gear shifting mechanism etc.
- This can be solved by introducing a reducer which can work together with the servomechanism and which is capable of providing an altered power supply to the servomechanism.
- a system is provided to ensure that the total force acting on the gear shifting mechanism does not exceed a predetermined value. It is presupposed in this connection that the force transmitted from the gear lever to the gear shifting mechanism receives power assistance from an assistance system.
- the system is provided so that a first limit value is used to control the power assistance having a positive value, and that a second limit value is used to control the power assistance having a negative value.
- the power assistance provided by the assistance system has a value that holds the total force acting on the gear shifting mechanism constant or reduces the total force acting on the gear shifting mechanism, when the gear lever force is equal to or greater than a limit value (hereinafter referred to as the second limit value).
- the limit value is adjusted according to the durability of the gear shifting mechanism that is to be used and the other individual properties of the system. If the invention is to be used in a gear shifting mechanism which requires large forces to effect a shift of the gear ratio, an assistance system is used which provides power assistance that makes it easier for the driver to change gear, typically a so- called servo system.
- the system according to the invention as disclosed in independent patent claim 2 will have a two-part function wherein: - the power assistance provided by the assistance system has a value which increases the total force acting on the gear shifting mechanism, when the gear lever force is increased within a range in which the gear lever force is equal to or greater than the first limit value and less than the second limit value; and wherein - the power assistance provided by the assistance system has a value which holds the total force acting on the gear shifting mechanism constant or reduces the total force acting on the gear shifting mechanism, when the gear lever force is equal to or greater than the second limit value.
- the system may also be controlled by setting the limit values for the total force acting on the gear shifting mechanism.
- signal transmission is used below to describe the power transmission that takes place in the gear shifting system between the gear lever mechanism and the gear shifting mechanism and the assistance system, respectively.
- transmission of signals in this connection is meant transmission of information about which input conditions apply to the gear shifting mechanism and the assistance system.
- the signal that is transmitted between the gear lever mechanism and the gear shifting mechanism and the assistance system, respectively may thus be of different types. It may be a combined force and motion signal via a rod or cable, for example, if the gear shifting system is mechanical.
- the signal transmission may also be in the form of a pressure signal, for example, if the gear shifting system is a hydraulic system.
- the pressure signal transmission may, of course, also be carried out by pressure mediums other than hydraulic, for example, pneumatic.
- the signal transmission may be in the form of an electric, optical or electromagnetic signal. It should be mentioned that this same term “signal transmission” will also be used to describe the transmission of pressure, force and voltage conditions between other components in the system.
- a power-providing device for example, a servomechanism
- the signal is transmitted from the gear lever to the power- providing device, and depending upon the value of the signal, power assistance is transmitted to the gear shifting mechanism.
- a signal can be transmitted from the assistance system which represents power assistance to a power-providing device that is connected to the gear shifting mechanism.
- a signal that corresponds to the signal from the gear lever or that is derived from this signal is transmitted to a reducer that is provided so that, depending on the value of the incoming signal, it can adjust the value of a power supply to which the reducer is connected.
- This may be a power supply of different kinds such as pressurised fluid, a voltage source etc.
- the reducer can transmit a power supply to the servomechanism, or may alternatively transmit a signal that represents a power supply, for example, if the power supply is of a kind that must be converted in order to be compatible with the servomechanism.
- the reducer comprises at least one measuring unit and at least one regulator,
- the measuring unit receives the signal from the gear lever, or the signal that is derived from the gear lever's signal, and controls the regulator on the basis of this signal.
- the signal from the gear lever represents a value that is equal to or greater than the second limit value
- the measuring unit controls the regulator so that the signal from the reducer to the servomechanism is or represents a reduced power supply.
- the signal that is transmitted to the servomechanism from the reducer represents the power supply that the regulator receives from a source.
- the signal from the gear lever represents a value that is equal to or greater than the second limit value
- the power supply from the source is reduced in the regulator, and the value of the signal that is transmitted to the servomechanism from the reducer is reduced correspondingly.
- the power supply can be provided by a pressurised fluid
- the regulator is made having a inlet for conducting the pressurised fluid from the source to a cavity in the regulator.
- a preloaded regulator piston which is made having a bore for conducting the fluid to an outlet.
- the piston causes the opening of an exhaust port when moved in the direction of its preloading force.
- the exhaust port in the regulator is opened for discharge of fluid from the regulator and the pressure of the fluid that is passed out of the outlet is thus reduced in accordance with the value of the signal from the gear lever.
- the measuring unit controls the regulator so that a force is provided in the regulator which counteracts/is greater than the preloading of the regulator piston, and optionally the preloading of the regulator piston valve seat that closes the exhaust port, the piston thereby opening for discharge of fluid through the exhaust port.
- the force that is provided in the regulator can be produced in different ways, and the measuring unit's control of the regulator can also be effected in different ways.
- the measuring unit comprises two preloaded pistons that are arranged in the cavity of the measuring unit.
- the piston rod of the first piston is placed in a though-going bore that extends through the second piston and the piston rod of the second piston.
- the signal from the gear lever represents a value that is equal to or greater than the second limit value
- a force against one of the two pistons is provided which counteracts/is greater than the sum of the preloading of the piston in question, the preloading of the regulator piston and optionally the preloading of the valve seat.
- the piston of the first measuring unit is displaced into abutment against the regulator piston which is also displaced so that the exhaust port is opened.
- the force exerted against one of the two pistons will be provided by the supply of fluid to the measuring unit in response to the gear lever force.
- fluid On movement of the gear lever in one direction, fluid is transferred to the measuring unit so that it exerts pressure against the piston face of the first piston.
- fluid On movement of the gear lever in the other direction, fluid is transferred to a space between the first and the second piston in the measuring unit so that the fluid exerts pressure against the piston face of the second piston.
- the reducer may, in a preferred embodiment, comprise two regulators and one measuring unit that is disposed between the two regulators.
- the measuring unit comprises two preloaded slides that are placed in a cavity in the measuring unit. Movement of the gear lever with a force that is equal to or greater than the second limit value in one direction or the other results in a force being exerted against one of the two slides that is greater than, the sum of the preloading of the slide in question, the preloading of a valve arranged in the cavity of the measuring unit, the preloading of the regulator piston in question, and optionally the preloading of the regulator piston valve seat. This results in an opening of the exhaust port with subsequent pressure regulation of the power supply into the servomechanism.
- Figure 1 shows the forces that arise in the gear shifting mechanism according to the prior art.
- Fig. 2 shows the forces that arise in the gear shifting mechanism according to the solution principle that forms the basis for the invention.
- Fig. 3 shows a block diagram of the solution principle according to the invention.
- Fig. 4 shows the invention used in a hydraulic gear shifting system.
- Fig. 5 shows a reducer that is used in the system in Figure 4.
- Figs. 6, 7 and 8 show the invention used in a mechanical gear system.
- the horizontal axis shows the force that the driver exerts on the gear lever.
- the vertical axis shows the force that is applied to the gear shifting mechanism.
- a standard system without power assistance from an assistance system will give a force on the gear selector mechanism in the gearbox as a function of the driver's force on the gear lever. This situation is shown by curve 2, where it is seen that the force acting on the gear selector mechanism increases proportionally with the driver's force on the gear lever.
- Curve 5 shows an example of how the power assistance from the assistance system will work. At low gear lever forces, the power assistance from the assistance system will increase as a function of the gear lever forces, and when maximum power assistance from the assistance system has been reached, the curve will flatten out and indicate constant supplementary power to the gear selector mechanism in the gearbox.
- the total force that acts on the gear selector mechanism in the gearbox is shown by curve 6.
- This curve is the resultant of the gear lever force shown by curve 2 and the power assistance from the assistance system shown by curve 5.
- Curve 1 shows the maximum force that the synchronisation rings of the gearbox can withstand.
- This area is indicated by the reference numeral 7 in Figure 1.
- the aim of the present invention is to provide a system which, with the aid of suitable means, ensures that the total force acting on the gear mechanism is maintained below the maximum tolerance value.
- FIG. 2 A solution principle for such a system is shown in Figure 2.
- the horizontal axis shows the force that the driver exerts on the gear lever.
- the vertical axis shows the force that is applied to the gear shifting mechanism.
- Curve 2 shows, as in Figure 1 , a standard system without power assistance from an assistance system which will provide a force on the gear selector mechanism in the gearbox as a function of the driver's force on the gear lever.
- Curve 3 shows an example of a solution in which desired protection against overloading of the gear shifting mechanism is introduced by adjusting the power assistance from an assistance system. As curve 3 illustrates, this is done by reducing the power assistance from the assistance system when the gear lever force reaches a certain limit value.
- This solution principle results in the gear shifting mechanism being loaded with the resultant (illustrated by curve 4) of the gear lever force (illustrated by curve 2) and the power assistance from the assistance system (illustrated by curve). It is seen from Fig. 2 that at low gear lever forces, the power assistance from the assistance system will increase as a function of the gear lever forces.
- the power assistance from the assistance system has a magnitude that increases the total force acting on the gear shifting mechanism when the gear lever force is increased within a range in which the gear lever force is equal to or greater than a first limit value and less than a second limit value. Also, the power assistance from the assistance system has a magnitude that holds the total force acting on the gear shifting mechanism constant, or reduces the total force acting on the gear shifting mechanism, when the gear lever force is equal to or greater than the second limit value.
- the value of the maximum total force allowed on the gear shifting mechanism, and the first and second limit values may vary depending on what type of system is used.
- the second limit value of the gear lever force will be in the range where it is seen that the power assistance from the assistance system has a reducing effect (see curve 2) on the total force shown by curve 4.
- the first limit value of the gear lever force will also be less than the second limit value, and in the example shown in Figure 2, the first limit value will be found in the range in which the power assistance from the assistance system (curve 2) begins to make a positive contribution to the total force on the gear shifting mechanism (curve 4).
- Arrow 6a illustrates the force that the driver applies to the gear lever.
- the gear lever mechanism transfers the driver's force load on the gear lever to a signal 6b.
- the signal 6b may be a combined force and motion via rod or cable or the like. Optionally, it may be a hydraulic or pneumatic pressure or an electrical signal.
- the signal from the gear lever mechanism will actuate the gearbox gear shifting mechanism 3 directly by signal 6c.
- a servo assistance is included in the assistance system, and the signal from the gear lever mechanism controls a servomechanism 2.
- the servomechanism provides power assistance, represented as signal 2a, to the gearbox gear shifting mechanism.
- Signal 2a and signal 6c represent the total force applied to the gear shifting mechanism in the gearbox.
- the servomechanism 2 receives a signal 5b which is or represents a power supply.
- the signal 5b may, for example, be a pneumatic or hydraulic pressure, or alternatively a voltage supply signal.
- the assistance system further comprises a reducer which is shown within the marked area 1.
- the reducer comprises a regulator 5 and a measuring unit 4 which receives desired gear change force signal from the gear lever mechanism via signal 6b.
- the measuring unit 4 controls the regulator 5 which is provided so that a power supply 5a can be adjusted to a desired level 5b, depending on the input signal 6b to the measuring unit 4.
- a power source provides the power supply 5a, the power source, for example, being an air pressure supply, supply of hydraulic pressure, voltage supply etc. If the signal 6b is greater than or equal to the first limit value, the power supply 5b that is delivered to the servomechanism 2 will essentially correspond to the power supply 5a into the regulator.
- the servomechanism provides power assistance which increases the total force on the gear shifting mechanism, and which thus makes changing gear easier for the driver of the vehicle. If the signal 6b is equal to or exceeds the second limit value, the measuring unit 4 will control the regulator so that the power supply 5a to the regulator is adjusted down in the regulator, and a reduced power supply 5b to the servomechanism is obtained. It is thus ensured that the power assistance 2a provided by the servomechanism to the gear shifting mechanism is limited when the force on the gear lever is greater than the second limit value. Thus, it is ensured that the total force on ' the gear shifting mechanism is maintained at less than or equal to a pre-set value, thereby avoiding a possible overloading of the shifting mechanism.
- the solution principle illustrated in Fig. 3 is, in Fig. 4, implemented in a hydraulic gear shifting system with pneumatic servo assistance.
- the reducer 1 is shown made having a regulator part 5, here shown as a pneumatic pressure reduction valve 5, which is controlled by a hydraulic measuring unit 4.
- a hydraulic measuring unit 4 a hydraulic measuring unit 4
- other types of fluid may also be used as pressure medium in the regulator, and for that matter also in the measuring unit.
- the detailed construction of the reducer is shown most clearly in Figure 5. This embodiment of the solution principle will be described below with reference to both Figure 4 and Figure 5.
- the measuring unit 5 is comprised of a cavity 12 that is formed in the reducer 1 , where in the cavity 12 there is arranged a first preloaded piston 13 and a second preloaded piston 14. It is seen from Figures 4 and 5 that the first piston 13 is arranged with its piston rod projecting through a bore in the second piston 14, so that the ends of the piston rods of both pistons are placed at a similar distance from the regulator piston 15. It is also seen in Figures 4 and 5 that the first and the second piston 13, 14 are preloaded by springs 13a, 14a.
- the servomechanism 2 comprises a valve unit and a servo actuator. If the gear lever is moved in the direction of the arrow A, hydraulic fluid is transferred through the lines 10 to the servomechanism 2 and to the area of the cavity that is above the piston face of the piston 13b. If the gear lever is moved in the direction of the arrow B, hydraulic fluid is transferred through lines 1 1 to the servomechanism 2 and to the area that is above the piston face 14b of the second piston 14.
- the pressure that acts against the respective piston faces in each of the two cases is dependent upon the force that the driver exerts on the gear lever.
- the force that acts on the pistons 13 and 14 must have a magnitude and direction that are capable of overcoming the preloading force of the springs 13a and 14a, respectively.
- a fluid path is established from a source 16 to the valve unit that is connected to the servomechanism. Pressurised fluid is passed from the source 16 into an inlet 16a in the regulator and then through a bore 17 formed in the regulator piston 15, out through an outlet 21 and then into the valve unit. In this way, it is ensured that the servomechanism is supplied with a pressure substantially equivalent to the pressure of the fluid in the source 16.
- the pressure supply from the reducer 1 to the servomechanism 2 is determining for the power assistance provided by the servomechanism to the gear shifting mechanism 3.
- the pressure supply into the servomechanism 2 provides power assistance that helps to increase the total force acting on the gear shifting mechanism 3.
- the regulator piston 15 is shown preloaded by a spring 15a. If the force acting on one of the pistons 13, 14 is greater than the second limit value, this will result in the end of the associated piston rod being moved into abutment against the regulator piston 15. In this case, the piston 13 or 14 transfers a force to the regulator piston 15 which counteracts the preloading of the regulator piston 15. The regulator piston 15 is thus displaced downwards into abutment against the valve seat 19 of the regulator piston which is preloaded by a spring 19a, and furthermore the force is sufficient to counteract the preloading of the spring 19a so that the spring is compressed.
- valve seat 19 of the regulator piston is opened and this allows a discharge of fluid to the exhaust port 20.
- How large an opening is obtained when the valve seat 19 of the regulator piston is opened, and thus how much fluid is passed out of the fluid path between the source 16 and the valve unit, is therefore dependent upon the force acting on the piston faces 13b or 14b.
- Figures 6-8 the solution principle that is illustrated in Figure 3 is implemented in a mechanical gear shifting system with pneumatic servo assistance.
- Figure 6 shows an overview of the mechanical gear shifting system.
- the term "mechanical gear shifting system” is used here to mean a cable or rod transmission between gear lever and gearbox.
- Figures 7 and 8 show a reducer la for use in such a mechanical gear shifting system.
- the reducer l a comprises a measuring unit 4 that is disposed between two regulators 5a and 5b.
- the reducer's measuring unit in this case consists of a servo valve.
- the servo actuator is placed outside the reducer as in the embodiment in Figures 4-5.
- the term servomechanism 2 is used to refer to the servo actuator in the following.
- the regulators 5a, 5b essentially resemble the regulator shown in Figures 4 and 5. Therefore, to a large extent the same reference numerals have been used as for the regulator in Figure 4. It is seen that the measuring unit 4' has a different structure than the measuring unit shown in Figure 4.
- the measuring unit 4' is double acting (works in both directions) and comprises two slides 22a, 22b that are preloaded by springs 22e and 22d.
- the force from the gear lever is transferred to the servomechanism 2 and the reducer la by a balanced lever (not shown).
- the lever has a point of action in the measuring unit 4' of the reducer at an actuating pin 12 that exerts a force on one slide or the other.
- the force will act on either the slide 22a or the slide 22b.
- the descriptions of the mode of operation and the structure will thus be identical for both sides of the reducer.
- outlet 21 a, 21b for transfer of pressurised air to the servomechanism 2 is directly connected to the exhaust port 24 via exhaust port valve seat 26 and a bore 25 inside the slide 22a, 22b.
- the system as shown in Figures 7 and 8 is shown in its unloaded state.
- the measuring unit When the gear lever force is equal to or greater than the first limit value, but less than the second limit value, the measuring unit is activated in that the actuating pin 12 exerts a force that presses on one of the slides 22a, 22b and moves it down some distance so that the spring 22c, 22d which provides preloading of the slide 22a, 22b is compressed to a certain extent. This in turn means that the force required to move the slide is a function of spring stiffness and movement path. When the slide 22a, 22b is moved some distance, the exhaust port valve seat 26 will seal against the valve 27. This means that the outlet 21 to the servomechanism is no longer vented to the exhaust port 24.
- valve 27 which in turn compresses the valve spring 28, and also opens for passage of fluid through the supply valve seat 29.
- the fluid from the source will be passed in through the inlet 16a, 16b, through the bore 17 in the regulator piston 15, then through duct 23 and then into the supply valve seat 29 via slots in the valve seat 30 where the valve seat 30 rests against the regulator piston 15. These slots are not shown in the drawing.
- the fluid passage that is produced by the valve 27 being moved in the direction of the supply valve seat 29, is facilitated either in that there is a possibility for movement of the valve 27 relative to a pin 31 that is received in a recess in the valve 27 and the regulator piston 15, or that the valve 27 and the pin 31 are moved relative to the regulator piston 15.
- the valve 27, the connecting pin 31 and the regulator piston 15 are moved downwards together, the distance between the regulator piston valve seat 19 and the regulator piston 15 permitting this without it resulting in the opening of the regulator piston valve seat 19.
- Fluid will thus flow out to the servomechanism 2 and make it easier for the driver to move it.
- the servomechanism 2 moves towards the position indicated by the gear lever, the distance between desired position (the gear lever) and real position (servomechanism 2) will be reduced, and the lever mechanism that couples the regulator to the servomechanism 2 will ensure that once desired position has been reached, the displacement of the slide 22a, 22b is drawn back towards its original position. In this way, the described valve mechanism will act as a position regulator.
- the regulator piston 15 can be actuated by the pin 31 that is received in a recess in the valve 27, the pin 31 also optionally being fastened to the valve.
- the pin 31 is not fixed in the regulator piston 15, but can be moved independently thereof.
- the valve 27 moves as a result of the fact that the force exerted on the gear lever represents a counter-force that is greater than the preloading of the slide spring 22c, 22d.
- the top part of the regulator piston 15 may be supplied with pressurised fluid via the duct 23.
- the supply from the source that is brought in through the inlet 16a, 16b comes into the regulator piston 15 to a cavity halfway between two slide seals as shown in Figures 6 and 7.
- the net force from the supply from the source against the regulator piston 15 is virtually zero.
- the underside of the large piston area of the regulator piston 15 is vented to exhaust port 20 via duct 32, so that there is never a build-up of pressure there.
- the servomechanism 2 will use some of the air from the outlet 21a or 21b, and thus the air pressure above the regulator piston 15 will drop, and the piston will be pushed back by the spring 15a until the regulator piston 15 is lifted from the regulator piston valve seat 19 and again lets fluid into the measuring unit/servo valve. (The same applies in the case of the embodiment shown in Figs. 4 and 5).
- the regulator part 5 is actuated in order to obtain a down regulation of the pressure of the fluid that is passed into the servomechanism 2.
- the regulator piston 5 is pressed even further down, and the regulator piston valve seat 19 is pressed downwards in that the spring 19a is compressed.
- the fluid that is passed into the servo valve/measuring unit 4' through duct 23 will then be vented to the exhaust port 20.
- a balance between the pressure on the upper side of the regulator piston 15, the force the driver exerts on the gear lever mechanism that is transferred by the actuating pin 12 and the counter-force from the spring to the regulator piston ensures that the unit pin 31 , the regulator piston 15, the regulator piston 15 spring, the regulator piston valve seat 19 and the associated spring 19 together work as a pressure regulator and regulate down the supply pressure that is to be delivered to the servo valve/measuring unit 4'.
- the drawing off of fluid via the exhaust port 20, and the subsequent reduced pressure in fluid that is then passed to the servomechanism 2 through the outlet 21a, 21b, will result in the total force acting on the gear shifting mechanism being held constant or reduced.
- the pressure regulation of the fluid that is delivered to the measuring unit/servo valve and thence to the servomechanism 2 is so adapted that when the force that the driver exerts on the gear mechanism in excess of an initial dead band increases, the pressure of the fluid into the servo valve will drop proportionally. This means that the greater the force with which the driver changes gear, the smaller the servo boost the servo valve contributes, when the gear lever force is above the second limit value. This will continue until the servo unit is no longer capable of providing power assistance. In this way, the total force acting on the gear shifting mechanism from the servomechanism 2 and the gear lever force will be prevented from exceeding a predetermined maximum value.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007514963A JP2008501904A (en) | 2004-06-04 | 2005-06-06 | System to limit power load |
DE112005001257T DE112005001257T5 (en) | 2004-06-04 | 2005-06-06 | System for limiting a force load |
BRPI0512195-7A BRPI0512195A (en) | 2004-06-04 | 2005-06-06 | a system to ensure that the total force acting on the gear change mechanism does not exceed a predetermined value |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE0401455A SE528347C2 (en) | 2004-06-04 | 2004-06-04 | System to ensure that the total force acting on a switching mechanism does not exceed a predetermined value |
SE0401455-1 | 2004-06-04 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005119100A1 true WO2005119100A1 (en) | 2005-12-15 |
Family
ID=32653552
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NO2005/000191 WO2005119100A1 (en) | 2004-06-04 | 2005-06-06 | System for limiting a force load |
Country Status (6)
Country | Link |
---|---|
JP (1) | JP2008501904A (en) |
CN (1) | CN100552269C (en) |
BR (1) | BRPI0512195A (en) |
DE (1) | DE112005001257T5 (en) |
SE (1) | SE528347C2 (en) |
WO (1) | WO2005119100A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007101754A1 (en) * | 2006-02-14 | 2007-09-13 | Zf Friedrichshafen Ag | Shifting device for a variable-speed vehicle transmission |
EP1632697A3 (en) * | 2004-09-03 | 2007-10-10 | Zf Friedrichshafen Ag | Characteristic of a power assist unit for a gear shift device |
WO2008043690A1 (en) * | 2006-10-12 | 2008-04-17 | Zf Friedrichshafen Ag | Servo assistance device for motor vehicle variable-speed transmission |
EP1947372A1 (en) | 2007-01-18 | 2008-07-23 | Kongsberg Automotive AS | A gear shift system with a power assistance system |
EP1975472A1 (en) | 2007-03-26 | 2008-10-01 | Kongsberg Automotive AS | Mechanical shift servo reduction |
DE102007048400A1 (en) * | 2007-06-06 | 2008-12-11 | Zf Friedrichshafen Ag | Switching device for motor vehicle gearbox |
EP2068044A3 (en) * | 2007-12-06 | 2011-08-03 | ZF Friedrichshafen AG | Servo assistance device for motor vehicle variable-speed transmission |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007026421A1 (en) * | 2007-06-06 | 2008-12-11 | Zf Friedrichshafen Ag | Servo assistance unit |
DK2143936T3 (en) | 2008-07-07 | 2016-03-21 | Siemens Ag | Wind turbine comprising a main bearing, and method for the replacement of the main bearing |
CN106863356B (en) * | 2017-02-27 | 2019-03-19 | 湖北工业大学 | A kind of constant force output actuator |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2223881A1 (en) | 1972-05-17 | 1973-12-13 | Knorr Bremse Gmbh | SERVO CONTROL DEVICE |
GB2127180A (en) * | 1982-09-16 | 1984-04-04 | Teleflex Morse Ltd | Power assistance device |
DE3410802A1 (en) * | 1983-04-07 | 1984-10-11 | Steyr-Daimler-Puch Ag, Wien | Shift device for gearbox of commercial vehicles |
DE19839854A1 (en) * | 1998-09-02 | 2000-03-09 | Zahnradfabrik Friedrichshafen | Switching device for motor vehicle gearbox |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03114665U (en) * | 1990-03-07 | 1991-11-26 |
-
2004
- 2004-06-04 SE SE0401455A patent/SE528347C2/en not_active IP Right Cessation
-
2005
- 2005-06-06 BR BRPI0512195-7A patent/BRPI0512195A/en not_active IP Right Cessation
- 2005-06-06 JP JP2007514963A patent/JP2008501904A/en active Pending
- 2005-06-06 CN CN 200580017871 patent/CN100552269C/en not_active Expired - Fee Related
- 2005-06-06 WO PCT/NO2005/000191 patent/WO2005119100A1/en active Application Filing
- 2005-06-06 DE DE112005001257T patent/DE112005001257T5/en not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2223881A1 (en) | 1972-05-17 | 1973-12-13 | Knorr Bremse Gmbh | SERVO CONTROL DEVICE |
GB2127180A (en) * | 1982-09-16 | 1984-04-04 | Teleflex Morse Ltd | Power assistance device |
DE3410802A1 (en) * | 1983-04-07 | 1984-10-11 | Steyr-Daimler-Puch Ag, Wien | Shift device for gearbox of commercial vehicles |
DE19839854A1 (en) * | 1998-09-02 | 2000-03-09 | Zahnradfabrik Friedrichshafen | Switching device for motor vehicle gearbox |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1632697A3 (en) * | 2004-09-03 | 2007-10-10 | Zf Friedrichshafen Ag | Characteristic of a power assist unit for a gear shift device |
WO2007101754A1 (en) * | 2006-02-14 | 2007-09-13 | Zf Friedrichshafen Ag | Shifting device for a variable-speed vehicle transmission |
WO2008043690A1 (en) * | 2006-10-12 | 2008-04-17 | Zf Friedrichshafen Ag | Servo assistance device for motor vehicle variable-speed transmission |
CN101523089A (en) * | 2006-10-12 | 2009-09-02 | 腓特烈斯港齿轮工厂股份公司 | Servo assistance device for motor vehicle variable-speed transmission |
JP2010506123A (en) * | 2006-10-12 | 2010-02-25 | ツェットエフ フリードリヒスハーフェン アクチエンゲゼルシャフト | Power assist device for automobile transmission |
US8074533B2 (en) | 2006-10-12 | 2011-12-13 | Zf Friedrichshafen Ag | Servo assistance device for motor vehicle variable-speed transmission |
EP1947372A1 (en) | 2007-01-18 | 2008-07-23 | Kongsberg Automotive AS | A gear shift system with a power assistance system |
EP1975472A1 (en) | 2007-03-26 | 2008-10-01 | Kongsberg Automotive AS | Mechanical shift servo reduction |
WO2008116531A1 (en) | 2007-03-26 | 2008-10-02 | Kongsberg Automotive As | Gear shift system |
DE102007048400A1 (en) * | 2007-06-06 | 2008-12-11 | Zf Friedrichshafen Ag | Switching device for motor vehicle gearbox |
US8578809B2 (en) | 2007-06-06 | 2013-11-12 | Zf Friedrichshafen Ag | Shifting device for a variable speed motor vehicle transmission |
EP2068044A3 (en) * | 2007-12-06 | 2011-08-03 | ZF Friedrichshafen AG | Servo assistance device for motor vehicle variable-speed transmission |
Also Published As
Publication number | Publication date |
---|---|
DE112005001257T5 (en) | 2007-05-16 |
JP2008501904A (en) | 2008-01-24 |
CN101014787A (en) | 2007-08-08 |
SE0401455L (en) | 2005-12-05 |
SE528347C2 (en) | 2006-10-24 |
SE0401455D0 (en) | 2004-06-04 |
BRPI0512195A (en) | 2008-02-19 |
CN100552269C (en) | 2009-10-21 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2005119100A1 (en) | System for limiting a force load | |
US7089733B1 (en) | Hydraulic control valve system with electronic load sense control | |
JP4712959B2 (en) | Load detection hydraulic controller for variable displacement pump | |
US6837045B2 (en) | Electrohydraulic lifting control device for industrial trucks | |
US4191094A (en) | Power drive unit | |
JPH0526955B2 (en) | ||
EP1674736A2 (en) | Hydraulic system for power assisted clutch actuation comprising an emergency release mechanism | |
US6601602B2 (en) | Pressure-control valve | |
CA2212155C (en) | Electro-pneumatic brake system and controller therefor | |
CN110901621B (en) | Control valve, electronically controllable brake system and method for controlling said system | |
CN110901620B (en) | Control valve, electronically controllable brake system and method for controlling said system | |
US4967554A (en) | Commonly-piloted directional control valve and load pressure signal line relieving switching valve | |
US4194364A (en) | Arrangement for controlling the operation of a fluid-displacement machine | |
US4669363A (en) | Hydraulic priority control means for at least two servo motors | |
US4960035A (en) | Control system for a hydraulic lift driven by a variable displacement pump | |
KR101740925B1 (en) | Hydraulic assembly comprising a variable displacement pump and a relief valve | |
US5720168A (en) | Control device for a hydraulic pump | |
DE3915919C2 (en) | Valve arrangement | |
WO2017112720A1 (en) | Apparatus for independently controlling seating forces in rotary valves | |
EP1947372A1 (en) | A gear shift system with a power assistance system | |
US4862691A (en) | Pump drive speed regulator with control-pressure-generating valve having spring biased by cam face on load directional control valve | |
JPS6014651A (en) | Variable pressure controller | |
EP4179209B1 (en) | Hydrostatic variable displacement axial piston unit and displacement volume setting device | |
EP0310733A1 (en) | Hydropneumatic actuator for automotive vehicles | |
JPH0735161Y2 (en) | Hydraulic pump controller for hydraulically driven vehicles |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KM KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NG NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 200580017871.3 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120050012573 Country of ref document: DE Ref document number: 2007514963 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 3689/KOLNP/2006 Country of ref document: IN |
|
RET | De translation (de og part 6b) |
Ref document number: 112005001257 Country of ref document: DE Date of ref document: 20070516 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase | ||
ENP | Entry into the national phase |
Ref document number: PI0512195 Country of ref document: BR |