WO2012046492A1 - ステアリング装置の設計支援装置及びステアリング装置設計支援方法 - Google Patents
ステアリング装置の設計支援装置及びステアリング装置設計支援方法 Download PDFInfo
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- WO2012046492A1 WO2012046492A1 PCT/JP2011/066982 JP2011066982W WO2012046492A1 WO 2012046492 A1 WO2012046492 A1 WO 2012046492A1 JP 2011066982 W JP2011066982 W JP 2011066982W WO 2012046492 A1 WO2012046492 A1 WO 2012046492A1
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- allowable
- reference point
- phase angle
- yoke
- allowable range
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
- B62D1/20—Connecting steering column to steering gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/15—Vehicle, aircraft or watercraft design
Definitions
- the present invention relates to a steering device design support device and a steering device design support method for supporting the design of a vehicle steering device.
- the steering device transmits the movement of the steering shaft that is rotated by the operation of the steering wheel to the pinion shaft that is the input shaft of the steering gear.
- the direction of the wheel is changed by the transmitted movement of the steering gear.
- the rotating shaft of the steering shaft and the shaft of the pinion shaft cannot be provided on the same straight line. Therefore, an intermediate shaft is provided between the steering shaft and the steering gear via the universal joint, and the end of the intermediate shaft and the steering shaft are coupled. Moreover, the end part of the intermediate shaft and the end part of the pinion shaft are coupled via a universal joint. Due to the presence of the two universal joints and the intermediate shaft, power is transmitted between the steering shaft that does not exist on the same straight line and the input shaft of the steering gear.
- the intermediate shaft is arranged in a three-dimensional space between the steering shaft and the pinion shaft. Since the angular speed of rotation of the steering shaft and the pinion shaft is constant, the intermediate shaft module is arranged according to the angle formed by the rotating shaft of the steering shaft and the rotating shaft of the intermediate shaft, the shaft of the steering gear, and the intermediate shaft. It is necessary to arrange so that the angle formed with the rotation axis of the shaft is equal.
- a steering device that steers the wheels of a vehicle has been designed using simulation technology. For example, there are techniques described in Patent Document 1 to Patent Document 3.
- the present invention has been made in view of the above, and provides a design support device and a steering device design support method for a steering device that support the design of a steering device having an intermediate shaft that fits within a predetermined allowable torque fluctuation.
- the purpose is to do.
- a steering device design support device of the present invention includes a steering mechanism having a column yoke, a slide tube yoke, a slide shaft yoke, and a pinion side yoke.
- a steering device design support apparatus comprising: coordinates of a handle position reference point of a handle; coordinates of a first universal joint reference point connecting the column yoke and the slide tube yoke; the slide shaft yoke and the pinion Storage means for storing the coordinates of the second universal joint reference point connecting the side yoke, the coordinates of the steering gear reference point, the allowable torque fluctuation rate, and the phase angle allowable error;
- the handle position reference point coordinates, the first Reference point placement means for placing coordinates of a universal joint reference point, coordinates of the second universal joint reference point, and coordinates of the steering gear reference point, and the second from the first universal joint reference point
- a reference axis calculating means for calculating a reference axis passing through the universal joint reference point, a straight line from the handle position reference point to the first joint reference point when viewed from the reference axis, and the reference axis from the reference axis
- the permissible range determination means includes a permissible tolerance of the phase angle tolerance within a permissible range of the permissible torque fluctuation rate in each of the upper, middle, and lower stages of the tilt operation. It is preferable to determine whether a condition including the range is satisfied. According to the present invention, the designer can be assisted in designing in consideration of the tilt operation.
- an input means for accepting a change in the allowable torque fluctuation rate or the phase angle allowable error, an allowable range allowed by the allowable torque fluctuation rate, and an allowable range allowed by the phase angle allowable error Display means for displaying the information, wherein the storage means stores the allowable torque fluctuation rate or the phase angle allowable error received by the input means, and the allowable range determination means is the storage means.
- the display means calculates the allowable range of the allowable torque fluctuation rate calculated by the allowable range determination means, and the previous value calculated by the allowable range determination means. It is preferable to simultaneously display the allowable tolerance range of the phase angle tolerance. Thus, by simultaneously displaying the allowable range allowed by the allowable torque fluctuation rate and the allowable range allowed by the phase angle allowable error, it is possible to assist the designer to grasp intuitively.
- the display screen continuously changes in accordance with at least one of the allowable torque fluctuation rate or the phase angle allowable error that has been accepted, and the design support device for the steering device is intuitively understood by the designer. Can help.
- the permissible range determining unit is configured to display the display unit when a condition that the permissible range permitted by the phase angle permissible error is not included in the permissible range permitted by the permissible torque fluctuation rate is satisfied. Is preferably highlighted. According to the present invention, the designer can clearly recognize that the condition is not satisfied without reading a number or the like.
- the permissible range judging means creates a combination of conditions in which the permissible range permitted by the permissible torque fluctuation rate includes the permissible range permitted by the phase angle permissible error as a condition establishment table. It is preferable.
- the design support device for a steering device according to the present invention can clarify an allowable range by creating a condition satisfaction table.
- storage means for storing a mass-produced product data table, the handle position reference point coordinates, the coordinates of the first universal joint reference point, and the coordinates of the second universal joint reference point And a component condition calculation means for obtaining a part condition from the coordinates of the steering gear reference point, and a part selection means for selecting a mass production part from the mass production data table based on the part condition and the condition establishment table. It is preferable. According to the present invention, the designer can reduce the labor for selecting parts.
- the component selecting means selects the column yoke, the slide tube yoke, the slide shaft yoke, and the pinion side yoke, and the first universal joint reference in a three-dimensional space.
- a connection point between the column yoke and the slide tube yoke is disposed at a point
- a connection point between the slide shaft yoke and the pinion side yoke is disposed at the second universal joint reference point. According to the present invention, the designer can easily grasp the selected part.
- a steering apparatus design support method of the present invention includes a steering mechanism including a column yoke, a slide tube yoke, a slide shaft yoke, and a pinion side yoke.
- a steering device design support method in which a computer supports the design of the device, comprising: coordinates of a handle position reference point of a handle; and coordinates of a first universal joint reference point connecting the column yoke and the slide tube yoke; A storage step for storing coordinates of a second universal joint reference point connecting the slide shaft yoke and the pinion side yoke, coordinates of a steering gear reference point, an allowable torque variation rate, and a phase angle allowable error; , Tertiary where the front and rear, up and down and left and right direction of the vehicle are defined A reference point arrangement step for arranging the handle position reference point coordinates, the coordinates of the first universal joint reference point, the coordinates of the second universal joint reference point, and the coordinates of the steering gear reference point in space.
- a reference axis calculating step for calculating a reference axis passing through the second universal joint reference point from the first universal joint reference point, and the first joint reference from the handle position reference point as viewed from the reference axis.
- An allowable range determination step for determining whether a condition that the allowable range includes the allowable range of the phase angle allowable error is satisfied. And having a, the. According to the present invention, the designer is assisted to facilitate the design of a steering apparatus having an intermediate shaft that can be accommodated within a predetermined allowable torque fluctuation.
- the allowable range that the phase angle allowable error allows is within the allowable range that the allowable torque fluctuation rate allows in all of the upper, middle, and lower stages of the tilt operation. It is preferable to determine whether the included conditions are satisfied. According to the present invention, the designer can be assisted in designing in consideration of the tilt operation.
- a desirable mode of the present invention includes a display step for displaying an allowable range allowed by the allowable torque fluctuation rate calculated in the allowable range determining step and an allowable range allowed by the phase angle allowable error.
- the allowable torque fluctuation rate is changed based on the changed allowable torque fluctuation rate.
- At least one of an allowable range of the phase angle allowable error is calculated based on the allowable range of the allowable phase angle or the changed phase angle allowable error, and the display step includes the allowable range calculated in the allowable range determining step.
- Allowable range of torque fluctuation rate and allowable range of the phase angle allowable error calculated in the allowable range determination step It is preferable to simultaneously display.
- the display screen continuously changes in accordance with at least one of the allowable torque fluctuation rate or the phase angle allowable error that has been accepted, and the steering device design support method allows the designer to grasp intuitively. Can help.
- the allowable range determining step when the condition that the allowable range allowed by the phase angle allowable error is not included in the allowable range allowed by the allowable torque fluctuation rate is emphasized in the display step. It is preferable to display. According to the present invention, the designer can clearly recognize that the condition is not satisfied without reading a number or the like.
- the allowable range can be clarified by creating the condition establishment table.
- a storage step for storing a mass-produced product data table, the handle position reference point coordinates, the coordinates of the first universal joint reference point, the coordinates of the second universal joint reference point, A component condition calculating step for obtaining a component condition from the coordinates of the steering gear reference point; and a component selecting step for selecting a mass-produced component from the mass-produced product data table based on the component condition and the condition establishment table.
- the designer can reduce the labor for selecting parts.
- the column yoke, the slide tube yoke, the slide shaft yoke, and the pinion side yoke are selected and used as the first universal joint reference point in a three-dimensional space. It is preferable that a connection point between the column yoke and the slide tube yoke is disposed, and a connection point between the slide shaft yoke and the pinion side yoke is disposed at the second universal joint reference point. According to the present invention, the designer can easily grasp the selected part.
- the designer is assisted to facilitate the design of a steering device having an intermediate shaft that can be accommodated within a predetermined allowable torque fluctuation.
- FIG. 1 is a diagram illustrating a configuration of a design support apparatus for a steering apparatus according to the present embodiment.
- FIG. 2 is an explanatory diagram schematically illustrating the vehicle.
- FIG. 3 is a diagram illustrating an example of an intermediate shaft module.
- FIG. 4 is a view showing an example of a slide tube yoke used for the intermediate shaft module.
- FIG. 5 is a view showing an example of a slide shaft yoke used in the intermediate shaft module.
- FIG. 6 is a diagram showing an interposing state of the cross shaft excluding the bearing used in the intermediate shaft module.
- FIG. 7 is a diagram illustrating an example of a cross shaft excluding a bearing used in an intermediate shaft module.
- FIG. 8 is a diagram illustrating an example of a column yoke.
- FIG. 9 is a diagram illustrating an example of the pinion side yoke.
- FIG. 10 is an explanatory view for explaining the relationship between the pinion side yoke of the steering gear module and the cross shaft free joint.
- FIG. 11 is an explanatory view illustrating the relationship between the pinion side yoke and the cross shaft free joint excluding the bearing.
- FIG. 12A is a diagram illustrating an example of an image in which four reference points are arranged in a three-dimensional space.
- 12B is an explanatory diagram illustrating a projection plane viewed in the direction of the arrow VJ on the reference axis S in FIG. 12A (viewed on the GJ-HJ axis).
- FIG. 13 is a flowchart showing a processing procedure of the steering apparatus design support apparatus.
- FIG. 13 is a flowchart showing a processing procedure of the steering apparatus design support apparatus.
- FIG. 14 is a flowchart for explaining details of a processing procedure of the steering apparatus design support apparatus.
- FIG. 15 is a diagram illustrating an example of the design information input screen.
- FIG. 16 is a diagram illustrating an example of another design information input screen.
- FIG. 17 is a diagram illustrating an example of a tilt coordinate display screen.
- FIG. 18 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- FIG. 19 is a diagram illustrating an example of an output display screen that displays the calculation result of the phase angle ⁇ .
- FIG. 20 is a diagram illustrating an example of an output display screen that displays the calculation results of the component conditions.
- FIG. 21 is a diagram illustrating an example of an input display screen displaying torque calculation conditions.
- FIG. 22 is a diagram showing an example of an output display screen for explaining the torque fluctuation rate-phase angle curve.
- FIG. 23 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 24 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 25 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 26 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 27 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 28 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 29 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 30 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 31 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 32 is a diagram showing an example of an output display screen showing a torque fluctuation rate-phase angle curve under a predetermined condition.
- FIG. 33 is a diagram showing an example of outputting a establishment table of the relationship of allowable range ⁇ > allowable range ⁇ .
- FIG. 34 is a flowchart for explaining details of a processing procedure of the steering device design support apparatus 1.
- FIG. 35 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- FIG. 36A is a diagram of an example of a mass production part data table.
- FIG. 36-2 is a diagram of an example of a mass production part data table.
- FIG. 36C is a diagram of an example of the mass production part data table.
- FIG. 37 is an explanatory view illustrating a planar cross section of the bearing.
- FIG. 38 is an explanatory diagram for explaining an assembled state of the bearing.
- FIG. 39 is a diagram illustrating an example of a mass production part data table.
- FIG. 40 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- FIG. 41 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- FIG. 42 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- FIG. 43 is a flowchart for explaining a modification of the present embodiment.
- FIG. 1 is a diagram illustrating a configuration of a design support device for a steering device according to an embodiment.
- the steering device design support apparatus 1 includes an input device 2, a display device 3, a control device 4, and an external storage device 5.
- the input device 2 is a mouse, a keyboard, or the like, and is an input unit that receives an input operation and a selection operation of a designer who is a user and outputs an input signal to the control device 4.
- the display device 3 is a display means for displaying an image such as a CRT (Cathode Ray Tube) or a liquid crystal display.
- the control device 4 is a computer such as a personal computer (PC), and includes an input interface 4a, an output interface 4b, a CPU (Central Processing Unit) 4c, a ROM (Read Only Memory) 4d, and a RAM (Random Access Memory). 4e and an internal storage device 4f.
- the input interface 4a, output interface 4b, CPU 4c, ROM 4d, RAM 4e, and internal storage device 4f are connected by an internal bus.
- the input interface 4a receives an input signal from the input device 2 and outputs it to the CPU 4c.
- the output interface 4 b receives an image signal from the CPU 4 c and outputs it to the display device 3.
- the ROM 4d stores programs such as BIOS (Basic Input Output System).
- BIOS Basic Input Output System
- the internal storage device 4f is, for example, an HDD or a flash memory, and stores an operating system program and application programs.
- the CPU 4c implements various functions by executing programs stored in the ROM 4d and the internal storage device 4f while using the RAM 4e as a work area.
- the external storage device 5 is an HDD (Hard Disk Drive), a server, or the like.
- the external storage device 5 is connected to the control device 4 via a network such as a LAN. Note that the external storage device 5 may be installed at a location away from the control device 4.
- an existing module database that stores information on components that constitute the steering and have a production record is stored.
- FIG. 2 is a block diagram showing a schematic configuration of the steering device mounted on the vehicle.
- the vehicle 100 includes a steering device 102, a steering mechanism 103 of the steering device 102, a control unit 104, an ignition switch 105, a battery 106, and a vehicle speed sensor 107.
- vehicle 100 has various components that normally pass as a vehicle, such as an engine and wheels.
- a steering device 102 shown in FIG. 2 is an electric power steering device.
- the steering device 102 includes a steering wheel (steering wheel) 110 operated by a driver, a steering shaft 120 that transmits rotation input from the steering wheel 110, torque input to the steering shaft 120, and a rotation angle of the steering shaft 120.
- a torque sensor 130 to be detected and an auxiliary steering mechanism 140 for assisting the rotation of the steering shaft 120 based on the torque detected by the torque sensor 130 are provided.
- the steering device 102 detects the steering torque generated in the steering shaft 120 by the torque sensor 130 when the handle 110 is operated. Further, the steering device 102 assists the steering force of the steering wheel 110 by controlling the drive of the electric motor 160 by the control unit 104 based on the detected signal to generate an auxiliary steering torque.
- a steering shaft 120 connected to the handle 110 has an input shaft 120a and a column output shaft 120b on which a driver's steering force acts, and a torque sensor 130 and a reduction gear are provided between the input shaft 120a and the column output shaft 120b.
- a box 150 is interposed. The steering force transmitted to the column output shaft 120 b of the steering shaft 120 is transmitted to the steering mechanism 103.
- the torque sensor 130 detects the steering force transmitted to the input shaft 120a via the handle 110 as a steering torque.
- the auxiliary steering mechanism 140 is connected to the column output shaft 120b of the steering shaft 120 and transmits auxiliary steering torque to the column output shaft 120b.
- the auxiliary steering mechanism 140 includes a reduction gear box 150 connected to the column output shaft 120b, and an electric motor 160 connected to the reduction gear box 150 and generating auxiliary steering torque.
- the steering shaft 120, the torque sensor 130, and the reduction gear box 150 constitute a column, and the electric motor 160 applies auxiliary steering torque to the column output shaft 120b of the column. That is, the electric power steering apparatus in this embodiment is a column assist type.
- the steering mechanism 103 of the steering device 102 includes a universal joint 20, an intermediate shaft module 10, a universal joint 30, a pinion shaft 60, a steering gear 61, and a tie rod 70.
- the steering force transmitted from the steering device 102 to the steering mechanism 103 is transmitted to the intermediate shaft module 10 via the universal joint 20, further transmitted to the pinion shaft 60 via the universal joint 30, and transmitted to the pinion shaft 60.
- the steering force thus transmitted is transmitted to the tie rod 70 via the steering gear 61 and steers a steered wheel (not shown).
- the steering gear 61 is configured as a rack and pinion type having a pinion 61a connected to the pinion shaft 60 and a rack 61b meshing with the pinion 61a. It has been converted.
- a control unit (ECU, Electronic Control Unit) 104 controls driving of the vehicle 100 such as an electric motor 160 and an engine.
- the control unit 104 is supplied with power from the battery 106 when the ignition switch 105 is in an on state.
- the control unit 104 calculates an assist steering command value of the assist command based on the steering torque Q detected by the torque sensor 130 and the traveling speed V detected by the vehicle speed sensor 107, and based on the calculated assist steering command value.
- the supply current value to the electric motor 160 is controlled.
- the steering device 102 of this embodiment is provided with a tilt mechanism and a telescopic mechanism.
- the tilt position of the handle 110 and the position of the handle 110 in the longitudinal direction of the vehicle body are freely set.
- the handle position reference point H moves.
- the handle position reference point H is located on the axis T of the rotation center of the steering shaft 120.
- the connection reference point HJ of the universal joint 20 where the column output shaft 120b of the steering shaft 120 is connected to the intermediate shaft module 10 is located on the axis T of the rotation center of the steering shaft 120.
- the connection reference point HJ of the universal joint 20 connects the intermediate shaft module 10 and the universal joint 20.
- connection reference point HJ of the universal joint 20 is located on the reference axis S at the center of rotation of the intermediate shaft module 10.
- the connection reference point GJ of the universal joint 30 at which the intermediate shaft module 10 is connected to the pinion shaft 60 is located on the reference axis S at the rotation center of the intermediate shaft module 10.
- the connection reference point GJ of the universal joint 30 is located on the rotation center axis R of the pinion shaft 60.
- a steering gear reference point GC which is an intersection of the pinion shaft 60 and the steering gear 61, is also located on the rotation center axis R of the pinion shaft 60.
- FIG. 3 is a diagram illustrating an example of a connection state between the universal joint and the intermediate shaft module.
- FIG. 4 is an explanatory view for explaining a slide tube yoke which is a component of the intermediate shaft module.
- FIG. 5 is an explanatory diagram for explaining a slide shaft yoke that is a component of the intermediate shaft module.
- FIG. 6 is an explanatory view for explaining the relationship between the intermediate shaft module and the cross shaft free joint.
- FIG. 7 is a view showing an example of a cross joint free joint used in the intermediate shaft module.
- FIG. 8 is an explanatory diagram for explaining a column yoke connected to the column output shaft.
- FIG. 9 is an explanatory diagram for explaining the pinion side yoke.
- FIG. 10 is an explanatory diagram for explaining the relationship between the pinion-side yoke connected to the pinion shaft and the cross shaft free joint.
- FIG. 11 is an explanatory view illustrating the relationship between the pinion side yoke and the cross shaft free joint.
- the intermediate shaft module 10 is disposed between the column yoke 21 connected to the column output shaft 120 b of the steering shaft 120 and the pinion side yoke 31 connected to the pinion shaft 60.
- the intermediate shaft module 10 includes a slide tube yoke 11 and a slide shaft yoke 14.
- one end of the slide tube yoke 11 is U-shaped, and a pair of opposing arm portions 12 and 12 are provided.
- the arm portions 12, 12 are provided with a pair of bearing holes 13, 13 provided facing the arm portions 12, 12.
- the swing axis STC connecting the center of the bearing holes 13 and 13 is orthogonal to the axis ST serving as the rotation center of the slide tube yoke 11.
- the intersection of the swing axis STC and the axis ST is the intersection HJs.
- the other end of the slide tube yoke 11 can be connected to the slide shaft yoke 14.
- one end of the slide shaft yoke 14 is U-shaped, and a pair of opposing arm portions 15 and 15 are provided.
- the arm portions 15, 15 are provided with a pair of bearing holes 16, 16 provided to face the arm portions 15, 15.
- the swing axis SSC connecting the hole centers of the bearing holes 15, 15 is orthogonal to the axis SS serving as the rotation center of the slide tube yoke 11.
- the intersection of the swing axis SSC and the axis SS is an intersection GJs.
- the other end of the slide shaft yoke 14 can be connected to the slide tube yoke 11.
- the end of the slide shaft yoke 14 and the slide tube yoke 11 are fitted together.
- the shaft ST that is the rotation center of the slide tube yoke 11 shown in FIG. 4 and the axis SS that is the rotation center of the slide shaft yoke 14 shown in FIG. 5 are fitted so as to coincide with each other, and the intermediate shaft module 10 shown in FIG.
- the axis S is the center of rotation.
- a cross shaft free joint 41 and a cross shaft free joint 51 are combined with the intermediate shaft module 10.
- the joints 44 (54), 45 (55), 46 (56), and 47 (57) are arranged every 90 degrees on the body 43 (53).
- the joint 44 (54) and the joint 45 (55) are disposed on the coaxial line along the axis Y.
- the joint 46 (56) and the joint 47 (57) are arranged on the coaxial line along the axis X.
- the intersection point O between the axis X and the axis Y is the center of the cross shaft free joint 41 (51), which is the operation center of the free joint. Since the cruciform free joint 51 is the same as the cruciform free joint 41, the corresponding reference numerals are shown in parentheses and the description thereof is omitted.
- the cross shaft free joint 41 is interposed between the pair of arm portions 12 and 12. More specifically, the joints 44 and 45 of the cross shaft free joint 41 are inserted into the bearing holes 13 and 13 through bearings described later.
- the cross shaft free joint 51 is interposed between the pair of arm portions 15 and 15. More specifically, the joints 54 and 55 of the cross shaft free joint 51 are inserted into the bearing holes 16 and 16 through bearings described later.
- the cross shaft free joint 41 is interposed so that the intersection point O of the cross shaft free joint 41 coincides with the intersection point HJs of FIG.
- the cross shaft free joint 51 is interposed such that the intersection point O of the cross shaft free joint 51 coincides with the intersection point GJs of FIG.
- the X axis of the cross shaft free joint 41 is arranged in a direction orthogonal to the column output axis and is directed in the direction of the axis XH.
- the X axis of the cross shaft free joint 51 is arranged in a direction orthogonal to the pinion shaft and is directed in the direction of the axis XG.
- the column yoke 21 connected to the column output shaft 120b of the steering shaft 120 has a U-shaped end, and a pair of opposed arm portions 22 and 22 are provided.
- the axis serving as the rotation center of the column output shaft 120b of the steering shaft 120 is an axis T.
- the arm portions 22 and 22 are provided with a pair of bearing holes 23 and 23 provided to face the arm portions 22 and 22.
- the swing axis CJC connecting the hole centers of the bearing holes 23 and 23 is orthogonal to the axis T serving as the rotation center of the column yoke 21.
- the intersection of the swing axis CJC and the axis T is an intersection HJc.
- the column yoke 21 is provided with a pinch bolt hole 24 into which a pinch bolt for attaching to the column output shaft 120b is inserted.
- the pinion side yoke 31 connected to the pinion shaft 60 has a U-shaped end portion and is provided with a pair of opposing arm portions 32 and 32.
- An input shaft serving as a rotation center of the steering gear is an axis R.
- the arm portions 32, 32 are provided with a pair of bearing holes 33, 33 provided to face the arm portions 32, 32.
- the swing axis GJC connecting the hole centers of the bearing holes 33 and 33 is orthogonal to the axis R serving as the rotation center of the pinion side yoke 31.
- the intersection of the swing axis GJC and the axis R is the intersection GJg.
- the pinion side yoke 31 is provided with a pinch bolt hole 34 into which a pinch bolt for attaching to the pinion shaft 60 is inserted.
- joints 46 and 47 of the cross shaft free joint 41 shown in FIG. 6 are inserted into bearing holes 23 and 23 of the column yoke 21 shown in FIG.
- the cross shaft free joint 41 is interposed so that the intersection point O of the cross shaft free joint 41 coincides with the intersection point HJc of FIG.
- the universal joint 20 is formed through the cross shaft free joint 41 so that the joint angle between the steering shaft 120 and the column output shaft 120b of the steering shaft 120 can be freely changed.
- the intersection point O of the cross shaft free joint 41 coincides with the intersection point HJs of FIG. 4 and the intersection point HJc of FIG. 8, and is set as a reference point HJ of the universal joint 20.
- joints 56 and 57 of the cross shaft free joint 51 shown in FIG. 6 are inserted into bearing holes 33 and 33 of the pinion side yoke 31 shown in FIG.
- the cross shaft free joint 51 is interposed so that the intersection point O of the cross shaft free joint 51 coincides with the intersection point GJg of FIG.
- the universal joint 30 is formed through which the joint angle between the steering shaft 120 and the pinion shaft 60 can be freely changed via the cross shaft free joint 51.
- the intersection point O of the cross shaft free joint 51 coincides with the intersection point GJs of FIG. 5 and the intersection point GJg of FIG. 10, and becomes the reference point GJ of the universal joint 30.
- the distance between the reference point HJ of the universal joint 20 and the reference point GJ of the universal joint 30 is referred to as a joint length W.
- the joint length W can be changed by changing the position where the slide shaft yoke 14 and the slide tube yoke 11 are fitted together.
- FIG. 12A shows a steering wheel reference point H, a reference point HJ for the universal joint 20, a reference point GJ for the universal joint 30, and a steering gear reference point GC in a three-dimensional space. It is explanatory drawing which showed this relationship. Since the angular velocity of rotation of the steering shaft and the pinion shaft is constant, the joint angle ⁇ h formed by the reference axis S and the axis T at the reference point HJ is formed by the reference axis S and the axis R at the reference point GJ. It is necessary to design it equal to the joint angle ⁇ g.
- FIG. 12A shows a steering wheel reference point H, a reference point HJ for the universal joint 20, a reference point GJ for the universal joint 30, and a steering gear reference point GC in a three-dimensional space. It is explanatory drawing which showed this relationship. Since the angular velocity of rotation of the steering shaft and the pinion shaft is constant, the joint angle ⁇ h formed by the reference axis S and the axis T at the reference
- FIG. 12-2 is an explanatory diagram for explaining a projection plane viewed in the direction of the arrow VJ on the reference axis S in FIG. 12-1 (viewed on the GJ-HJ axis).
- the angle formed between the projection line of the axis R and the projection line of the axis T that intersect with the reference axis S is the phase angle ⁇ .
- FIG. 13 is a flowchart showing a processing procedure of the steering device design support apparatus 1.
- the control device 4 of the steering device design support device 1 starts designing the steering mechanism 103 of the steering device 102 (step S200).
- step S300 the design support apparatus 1 calculates an allowable range of parts of the steering mechanism 103 of the steering apparatus 102 in a three-dimensional space.
- step S400 the design support apparatus 1 selects the intermediate shaft module component and the universal joint component based on the determined reference point information.
- step S500 when it is determined that the selected part interferes with other parts in the vehicle 1, the design support apparatus 1 restarts the processing procedure from before step S400.
- the steering device design support apparatus 1 ends the process (step S600).
- the control device 4 of the steering device design support device 1 starts calculation of the allowable range of the components of the steering mechanism 103 (step S301).
- the control device 4 of the steering device design support device 1 receives vehicle design information from the input device 2.
- the design information is a constraint condition of the vehicle 100, for example.
- the control device 4 of the design support device 1 stores the input vehicle constraint conditions in the external storage device 5 or the internal storage device 4f.
- the control device 4 of the design support device 1 reads the stored vehicle constraint conditions from the external storage device 5 or the internal storage device 4f, and stores and holds them in the RAM 4e (step S310).
- the design support apparatus 1 includes an external storage device 5, an internal storage device 4f, or a RAM 4e as storage means.
- the control device 4 of the design support apparatus 1 can directly store and hold the input vehicle constraint conditions in the RAM 4e.
- the constraint conditions of the vehicle 100 are the steering wheel reference point H, the reference point HJ of the universal joint 20 that is the first joint reference point, the reference point GJ of the universal joint 30 that is the second joint reference point, and the steering gear reference point GC.
- the control device 4 of the steering device design support device 1 receives four reference points from the input device 2 such as a handle position reference point H, a universal joint 20 reference point HJ, a universal joint 30 reference point GJ, and a steering gear reference point GC. Each coordinate is input and stored in the RAM 4e.
- the control device 4 of the steering device design support device 1 causes the display device 3 to display the coordinates of the four reference points on the design information input screen.
- FIG. 15 is a diagram showing an example of the design information input screen.
- An input field for receiving input of the steering gear reference point GC (X coordinate, Y coordinate, Z coordinate) is displayed. The designer inputs the coordinates (X coordinate, Y coordinate, Z coordinate) of four reference points in each input field.
- the control device 4 of the steering device design support device 1 stores the coordinates of the four reference points input in the input fields in the RAM 4e.
- the control device 4 of the steering device design support device 1 stores the coordinates of the four reference points in the external storage device 5 or the internal storage device 4f.
- the control device 4 of the steering device design support device 1 uses the stored coordinates of the four reference points. It may be read out and stored in the RAM 4e.
- FIG. 16 is a diagram showing an example of another design information input screen for tilt and telescopic information.
- an input field for accepting an input of a distance from the handle position reference point H an input field for accepting an input of a distance (height) from the column output axis, and a tilt amount (tilt increase UP amount). , Tilt DOWN amount) and an input column for receiving telescopic amounts (telescopic contraction amount, telescopic expansion amount) respectively.
- FIG. 17 is a tilt coordinate display screen 502 showing an example of tilt UP coordinate data and tilt DOWN coordinate data displayed on the display device 3 by the control device 4 of the steering device design support apparatus 1.
- the control device 4 of the design support device 1 for the steering device starts calculation of the allowable range (step S310), and enters the three-dimensional space in which the front and rear, the top and bottom, and the left and right directions of the vehicle are defined.
- a reference point is arranged (step S320).
- the control device 4 arranges a steering wheel reference point H, a reference point HJ of the universal joint 20, a reference point GJ of the universal joint 30, and a steering gear reference point GC in a three-dimensional space.
- the spatial arrangement of points is displayed on the display device 3.
- PV is a Pivot point (tilt point) serving as a fulcrum for the tilt operation.
- FIG. 18 is a diagram illustrating an example of an output display screen 503 for reference points and reference axes arranged in a three-dimensional space.
- the CPU 4c of the control device 4 serves as a reference axis calculation means in a three-dimensional space, the axis T connecting the handle position reference point H and the reference point HJ of the universal joint 20, the reference point HJ of the universal joint 20 and the universal joint 30.
- the reference axis S connecting the reference point GJ and the axis R connecting the reference point GJ of the universal joint 30 and the steering gear reference point GC are calculated.
- the control device 4 of the steering device design support device 1 outputs the axis T, the reference axis S, and the axis R to the display device 3 (step S339).
- the CPU 4c of the control device 4 of the steering device design support apparatus 1 serves as a phase angle calculation means, as viewed from the reference axis S (GJ-HJ axis) viewed in the direction of the arrow VJ on the reference axis S in FIG.
- An angle formed by the projection line of the axis R and the projection line of the axis T intersecting with the reference axis S on the joint plane), that is, a so-called phase angle ⁇ is calculated (step S340).
- the control device 4 of the steering device design support device 1 outputs the calculation result of the phase angle ⁇ to the display device 3 (step S349).
- FIG. 19 is a diagram illustrating an example of an output display screen 504 that displays the calculation result of the phase angle ⁇ .
- the output display screen 504 includes a phase angle calculated value display screen 505 that displays a calculated value of the phase angle ⁇ and an angle drawing screen 506 that displays the phase angle ⁇ on the joint plane.
- FIG. 20 is a diagram illustrating an example of an output display screen 504 that displays the calculation results of the component conditions.
- the output display screen 504 has a component condition data table 507 that displays calculated values of component condition data.
- the CPU 4c of the control device 4 stores the component condition data in the external storage device 5 or the internal storage device 4f.
- FIG. 21 is a diagram illustrating an example of an input display screen displaying torque calculation conditions.
- the CPU 4c of the control device 4 receives the torque calculation condition 509 on the input screen 508 as shown in FIG. 21 from the input device 2 via the input interface 4a.
- the input torque calculation condition 509 includes phase angle tolerance, allowable torque fluctuation rate, input torque, intermediate torque (inter-joint torque in the middle tilt stage), and intermediate torque (inter-joint torque) during tilt UP and DOWN. Is included.
- an allowable joint play condition 512 for example, 1 minute (') is input to the input screen 508 from the input device 2 via the input interface 4a.
- the allowable joint backlash condition 512 is determined by the environmental conditions of the vehicle.
- the phase angle tolerance is a range of phase angle deviation caused by a manufacturing error.
- the torque fluctuation rate is a torque fluctuation when the vehicle is steered. A large torque fluctuation rate affects the steering feeling of the steering wheel. Therefore, it is preferable that the torque fluctuation rate is small.
- the control device 4 of the design support apparatus 1 stores the input torque calculation condition 509 and the allowable joint backlash condition 512 in the external storage device 5 or the internal storage device 4f.
- the control device 4 of the design support device 1 reads the stored torque calculation condition 509 from the external storage device 5 or the internal storage device 4f, and stores and holds it in the RAM 4e.
- the control device 4 of the design support apparatus 1 can directly store and hold the input torque calculation condition 509 in the RAM 4e.
- the calculation condition of the torque fluctuation rate-phase angle curve is detected.
- calculation of the torque fluctuation rate will be described.
- the rotation angle ⁇ 1 on the axis S is shown in the equation (1).
- Equation (2) is derived by differentiating both sides of equation (1) with time and calculating the angular velocity.
- Equation (3) is derived.
- the torque fluctuation rate (%) is the ratio between the input torque Tin and the output torque Tout, and this ratio is the reciprocal of the angular velocity ratio, so the torque fluctuation rate Tr is expressed by the equation (5).
- the CPU 4c of the control device 4 calculates the torque fluctuation rate-phase angle curve based on the calculation conditions according to the above formulas (5) and (6).
- FIG. 22 is a diagram showing an example of an output display screen for explaining the torque fluctuation rate-phase angle curve.
- FIG. 22 shows a torque fluctuation rate-phase angle curve with the torque fluctuation rate on the vertical axis and the phase angle on the horizontal axis.
- the torque fluctuation rate-phase angle curves Lup, Lmd, and Ldw of the upper tilt stage, the middle tilt stage, and the lower tilt stage are calculated by the CPU 4 c of the control device 4.
- the torque fluctuation rate-phase angle curve Lmd in the middle stage of the tilt has the minimum torque fluctuation rate when the phase angle is ⁇ . As shown in FIG.
- the angle values are set as TQ1 and TQ2, and the phase angle range from TQ1 to TQ2 is set as an allowable range ⁇ .
- the range of phase angle deviation caused by manufacturing error is defined as an allowable range ⁇ .
- the phase angle is ⁇
- the minimum and maximum values of the phase angle whose phase angle is most shifted within the allowable range ⁇ are the torque fluctuation rate-phase angle curves Lup, Lmd
- the points having the largest torque fluctuation rate given to Ldw are PH1 and PH2.
- the allowable range ⁇ is given as a range of phase angle deviation caused by a manufacturing error in a mass-produced part of the intermediate shaft module 10 having an allowable torque fluctuation rate of 10%, for example, the allowable range ⁇ is the phase angle ⁇ ⁇ 7 °.
- the minimum phase angle ⁇ -7 ° and the maximum phase angle ⁇ + 7 ° of the phase angle are given to the torque fluctuation rate-phase angle curves Lup, Lmd, Ldw of the upper tilt stage, the middle tilt stage, and the lower tilt stage, and the most torque It can be seen that the torque fluctuation rate of PH1 and PH2 showing a large fluctuation rate has an allowable torque fluctuation rate smaller than 10%, for example. Further, among the torque fluctuation rate-phase angle curve values Lup, Lmd, and Ldw of the upper tilt stage, the middle tilt stage, and the lower tilt stage when the allowable torque fluctuation rate is 10%, for example, the value of the phase angle closest to the phase angle ⁇ is TQ1.
- the allowable range ⁇ includes the range of the phase angle ⁇ ⁇ 7 ° which is the allowable range ⁇ . Therefore, the allowable range allowed by the phase angle allowable error is included in the allowable range allowed by the allowable torque fluctuation rate.
- the upper limit line line passing through TQ1 and TQ2 moves up and down, for example, in FIG. It moves along the direction of the arrow F shown.
- the CPU 4c of the control device 4 detects the input of the phase angle allowable error and the allowable torque fluctuation rate from the input device 2 as input means via the input interface 4a on the input screen 508 as shown in FIG. For example, the CPU 4c of the control device 4 detects an input value in which a designer directly inputs a numerical value as shown in an input / output screen 508 as shown in FIG.
- the CPU 4c of the control device 4 stores the values of the phase angle allowable error and the allowable torque fluctuation rate in the external storage device 5 or the internal storage device 4f.
- the CPU 4c of the control device 4 reads the stored phase angle allowable error and allowable torque fluctuation rate from the external storage device 5 or the internal storage device 4f, and stores and holds them in the RAM 4e.
- the CPU 4c of the control device 4 can directly store and hold the input phase angle allowable error and allowable torque fluctuation rate values in the RAM 4e.
- the CPU 4c of the control device 4 may detect, for example, the input of the up / down change value input in the arrow direction of the allowable torque fluctuation rate or the phase angle allowable error on the value change screen 510.
- the CPU 4c of the control device 4 stores the input phase angle allowable error or allowable torque fluctuation rate value in the external storage device 5 or the internal storage device 4f.
- the CPU 4c of the control device 4 reads the stored phase angle allowable error and allowable torque fluctuation rate from the external storage device 5 or the internal storage device 4f, and stores and holds them in the RAM 4e.
- the CPU 4c of the control device 4 allows the allowable range ⁇ of the allowable torque fluctuation rate based on the changed allowable torque fluctuation rate. Based on the changed phase angle tolerance, at least one allowable range ⁇ allowed by the phase angle tolerance is calculated.
- the CPU 4c of the control device 4 causes the display device 3 as a display unit to simultaneously display the allowable range ⁇ allowed by the allowable torque fluctuation rate and the allowable range ⁇ allowed by the phase angle allowable error.
- the CPU 4c of the control device 4 increases or decreases by a predetermined range from the initial value when the initial values of the allowable torque fluctuation rate and the phase angle allowable error are given to the external storage device 5 or the internal storage device 4f.
- the values of the phase angle allowable error and the allowable torque fluctuation rate can be directly stored in the RAM 4e.
- FIG. 23 to 27 show that when the allowable range ⁇ is ⁇ ⁇ 7 °, the torque fluctuation rate is changed from 10% to 3%, and the allowable range of the allowable torque fluctuation rate and the allowable tolerance of the phase angle are allowed. It is an example of the display screen which compares the magnitude relationship with a range (step S369).
- FIG. 23 shows an allowable range in which the allowable torque fluctuation rate is allowed by the phase angle ⁇ corresponding to 10% of the torque fluctuation rate.
- the allowable range ⁇ is an allowable range allowed by the phase angle allowable error and is ⁇ ⁇ 7 °.
- FIG. 24 shows an allowable range in which the allowable torque fluctuation rate is allowed by the phase angle ⁇ corresponding to 8% of the torque fluctuation rate.
- the allowable range ⁇ is an allowable range allowed by the phase angle allowable error and is ⁇ ⁇ 7 °.
- FIG. 25 shows an allowable range in which the allowable torque fluctuation rate is allowed by the phase angle ⁇ corresponding to 6% of the torque fluctuation rate.
- the allowable range ⁇ is an allowable range allowed by the phase angle allowable error and is ⁇ ⁇ 7 °.
- FIG. 26 shows an allowable range in which the allowable torque fluctuation rate is allowed by the phase angle ⁇ corresponding to 4% of the torque fluctuation rate.
- the allowable range ⁇ is an allowable range allowed by the phase angle allowable error and is ⁇ ⁇ 7 °.
- the allowable range ⁇ is an allowable range allowed by the phase angle allowable error and is ⁇ ⁇ 7 °.
- the allowable range ⁇ corresponding to the torque fluctuation rate of 10% to 4% includes the allowable range ⁇ .
- the torque fluctuation rate is 10% to 4%
- the relationship of allowable range ⁇ > allowable range ⁇ is established.
- the torque fluctuation rate is 3%
- the allowable range ⁇ cannot include ⁇ ⁇ 7 ° of the allowable range ⁇ .
- the torque fluctuation rate is 3%
- the relationship of allowable range ⁇ > allowable range ⁇ is not established.
- the failure is highlighted as shown by the hatched portion in order to clearly indicate the failure state. The designer can clearly recognize that the condition does not hold.
- the establishment display of the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ may be highlighted such that establishment is displayed in green and failure is displayed in red.
- the display screen of the display device 3 continuously changes as shown in FIGS. The designer can clearly recognize that the condition is not satisfied without reading the numbers.
- the display screen changes continuously according to the allowable torque fluctuation rate for which the change has been accepted, and the steering device design support device 1 can assist the designer to grasp intuitively.
- FIGS. 28 to 32 when the torque fluctuation rate is 5%, the allowable range ⁇ allowed by the phase angle tolerance is changed from ⁇ ⁇ 7 ° to ⁇ ⁇ 11 °, and the phase corresponding to the torque fluctuation rate of 5% is obtained.
- This is an example of a display screen that compares the magnitude relationship between the allowable range ⁇ that is a corner and the allowable range ⁇ (step S369).
- FIG. 28 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 7 °.
- FIG. 28 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 7 °.
- FIG. 29 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 8 °.
- FIG. 30 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 9 °.
- FIG. 31 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 10 °.
- FIG. 32 shows the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ where the torque fluctuation rate is 5% and the allowable range ⁇ is ⁇ ⁇ 11 °.
- the CPU 4c of the control device 4 compares the magnitude relationship between the allowable range ⁇ and the allowable range ⁇ from the allowable torque fluctuation rate and the phase angle allowable error as an allowable range determining means. First, the CPU 4c of the control device 4 calculates the allowable range ⁇ and the allowable range ⁇ from the allowable torque fluctuation rate and the phase angle allowable error. Then, the CPU 4c of the control device 4 calculates an allowable range where the allowable range ⁇ > the allowable range ⁇ is established. The CPU 4c of the control device 4 outputs the calculation result of the allowable range, for example, as a condition establishment table 511 that represents establishment as ⁇ and establishment as x as shown in FIG.
- the allowable range is clarified.
- the CPU 4 c of the control device 4 stores the condition establishment table 511 in the internal storage device 4 f or the external storage device 5. (Step S370). Then, the control device 4 of the steering device design support device 1 ends the allowable range calculation (step S380).
- step S401 the control device 4 of the steering device design support apparatus 1 starts component selection (step S401).
- the control device 4 reads the spatial arrangement data of the handle position reference point H, the universal joint 20 reference point HJ, the universal joint 30 reference point GJ, and the steering gear reference point GC into the three-dimensional space (step S410).
- step S410 the control device 4 includes a steering wheel position reference point H, a universal joint 20 reference point HJ, a universal joint 30 reference point GJ, and a steering gear reference in a three-dimensional space.
- a point GC is arranged (step S420).
- the CPU 4c of the control device 4 inquires as to whether there is a selection candidate in the mass production parts table as part condition calculation means (step S440).
- 36A, 36B, and 36C are diagrams illustrating an example of the mass production part data table.
- the mass production part data tables 701 and 711 shown in FIGS. 36A and 36B are data tables in which the tube length and the phase angle error are accumulated for each part, and are stored in the internal storage device 4f or the external storage device 5 in advance. It is remembered.
- 36-3 is a data table in which data of a target fitting length obtained by combining a slide tube yoke part and a slide shaft yoke part is stored, and is previously stored in the internal storage device 4f or the external storage device. 5 is stored.
- the data of the target fitting length is a target value, and is a value having an adjustment range (for example, 10 mm) before and after the target value.
- the joint length W between the HJGJ is determined by calculating the added value of the tube length of the slide tube yoke part and the tube length of the slide shaft yoke part and subtracting the fitting length from this added value. Is done.
- the CPU 4c of the control device 4 reads out the mass production part data tables 701, 711, and 721 exemplified in FIGS. 36-1, 36-2, and 36-3 to the RAM 4e, and stores and holds them (step S430).
- the CPU 4c of the control device 4 reads the component condition data table 507 obtained in step S350 described above from the external storage device 5 or the internal storage device 4f to the RAM 4e.
- the CPU 4c of the control device 4 selects a combination of a slide tube yoke part and a slide shaft yoke part that satisfies the condition of the joint length W between the HJGJs based on the part condition data table 507. For example, as shown in FIG.
- the joint length W is 291 mm.
- the CPU 4c of the control device 4 reads the value of the joint length W from the external storage device 5 or the internal storage device 4f into the RAM 4e.
- the CPU 4c of the control device 4 gives the read joint length W to mass production part data tables 701, 711, 721 as shown in FIGS. 36-1, 36-2 and 36-3, and satisfies the condition of the joint length W.
- the combination of the slide tube yoke part and the slide shaft yoke part is calculated. For example, since the joint length W is 291 mm in the part condition data table 507, the joint length W is set in the mass production part data tables 701, 711, 721 as shown in FIGS.
- a combination of a slide tube yoke part and a slide shaft yoke part that can be combined at 291 mm is selected.
- the X 3 selects the X 3 as a target fitting length 70 mm.
- Data fitting length is a target value, because the target value is a value that the adjustment range before and after as a reference to adjust the X 3, when a 69 mm, combined joint length W is 291mm is Selected. Since the range of the phase angle deviation caused by the manufacturing error is the phase angle error, it is preferable that the phase angle error is narrow when a plurality of combinations are possible.
- FIG. 37 is an explanatory view illustrating a planar cross section of the bearing.
- FIG. 38 is an explanatory diagram for explaining an assembled state of the bearing.
- the bearing 80 has a cylindrical cup-shaped outer ring 81 that fits and fits in the bearing hole, a needle 83 that is inserted into the inner circumference 811 of the outer ring 81, and an inner diameter ⁇ D1 into which, for example, the joint 46 of the cross shaft free joint 41 is inserted. Has an inner periphery. As shown in FIG.
- FIG. 39 is a diagram illustrating an example of a mass production part data table.
- the mass production part data table 702 is a data table storing the allowable joint backlash for each combination of parts and the friction amount corresponding to the allowable joint backlash, and is stored in the internal storage device 4f or the external storage device 5 in advance. . As shown in FIG. 39, in the mass-produced part data table 702, the allowable joint play amount and the friction amount corresponding to the allowable joint play amount are associated with each combination of parts.
- the CPU 4c of the control device 4 reads the mass production component data table 702 stored in the internal storage device 4f or the external storage device 5 to the RAM 4e, and stores and holds it. The CPU 4c selects a combination of the cross shaft free joint parts C1 and C2 and the bearing parts B1 and B2 shown in FIG. 39 according to the allowable joint backlash condition 512 on the input screen 508 shown in FIG.
- the CPU 4c of the control device 4 reads the condition establishment table 511 obtained in step S360 from the external storage device 5 or the internal storage device 4f into the RAM 4e, and stores and holds it.
- the CPU 4c of the control device 4 selects a phase angle allowable error that matches the phase angle error added to the condition establishment table 511 by the combination of the selected slide tube yoke and slide shaft yoke. For example, in the condition establishment table 511 shown in FIG.
- the phase angle allowable error ⁇ ⁇ 7 ° is inquired, and a combination with a torque fluctuation rate of 4% or more that satisfies the condition is selected. In general, a smaller torque fluctuation rate is preferable.
- the combination of the cross shaft free joint part and the bearing is selected according to the allowable joint play condition. Further, since the cross shaft free joint part and the bearing part are combined, for example, when the allowable joint backlash amount is 1 minute as in the combination of the cross shaft free joint part C2 and the bearing part B1, the friction amount is 0.005. It becomes. This reduces the amount of friction, but also increases backlash when steering the steering device, so parts are selected and combined according to the joint conditions required by the vehicle.
- the CPU 4c of the control device 4 inquires of the mass production part data table 702 about selection candidates based on the information in the part condition data table 507 and the condition establishment table 511 as part selection means (step S440). .
- the designer can reduce the labor of component selection.
- step S440, No If there is no mass-produced part in the mass-produced part data table 701 and the mass-produced part data table 702 that matches the part condition data table 507 obtained in step S350 (step S440, No), the mass-produced part cannot be selected and new part data is created. Need to do.
- the new part data is obtained, for example, by outputting the conditions in the part condition data table 507 (step S450).
- step S440, Yes When there are mass-produced parts that match the mass-produced part data table 507 in the mass-produced part data table 701 and the mass-produced part data table 702 (step S440, Yes), each part is placed in a three-dimensional space as shown in FIGS. Are arranged (step S460).
- FIG. 40 is an explanatory diagram showing an example in which mass-produced parts of the column yoke 21 are arranged at the reference point HJ of the universal joint 20 in a three-dimensional space.
- FIG. 41 is an explanatory diagram showing an example in which mass production parts of the slide tube yoke 11 are further arranged at the reference point HJ of the universal joint 20 in the three-dimensional space.
- FIG. 42 is an explanatory view showing an example in which mass production parts of the slide shaft yoke 14 and the pinion side yoke 31 are further arranged at the reference point GJ of the universal joint 30 in the three-dimensional space. Since the screen 602 shown in FIG. 40, the screen 603 shown in FIG. 41, and the screen 604 shown in FIG.
- the designer can visually determine the components in the three-dimensional space, the designer can have an arrangement image. In this embodiment, the designer can easily grasp the selected part.
- an instruction that allows the designer to change the direction of the pinch bolt holes 24 and 34 of the column yoke 21 and the pinion side yoke 31 to 180 ° reverse direction is given to the control device 4 via the input device 2 in consideration of the assembly direction. You may be able to do it.
- step S500 the process returns to the part selection step (step S400). If there is no interference, the control device 4 of the steering device design support device 1 ends the process (step S600). As described above, the designer is supported in the design of a steering apparatus having an intermediate shaft that can be accommodated within a predetermined allowable torque fluctuation.
- FIG. 43 is a flowchart for explaining a modification of the present embodiment.
- the procedure is the same, and a description thereof is omitted.
- the control device 4 when there is no component interference (step S500), the control device 4 creates a drawing (step S550). Information such as the selected part, reference point, reference axis, and phase is converted into a two-dimensional drawing. The converted drawing is displayed on the display device 3 (step S560), and the drawing is output to the external storage device 5 (step 570).
- the control device 4 of the steering device design support device 1 ends the process (step S600).
- the steering device design support device and the steering device design support method according to the present invention are useful for supporting the design of the steering device.
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Abstract
Description
2 入力装置
3 表示装置
4 制御装置
4a 入力インターフェース
4b 出力インターフェース
4c CPU
4d ROM
4e RAM
4f 内部記憶装置
5 外部記憶装置
10 インターミディエイトシャフトモジュール
11 スライドチューブヨーク
13,13,16,16,33,33 軸受孔
14 スライドシャフトヨーク
15,15,22,22 アーム部
21 コラムヨーク
23,23 軸受孔
31 ピニオン側ヨーク
32,32 アーム部
41,51 十字軸自由継手
43 胴部
44,45,46,47,54,55,56,57 継手
60 ピニオンシャフト
61b ラック
70 タイロッド
80 軸受
81 外輪
83 ニードル
103 操舵機構
105 イグニッションスイッチ
107 車速センサ
110 ハンドル
120a 入力軸
120b コラム出力軸
130 トルクセンサ
140 補助操舵機構
150 減速ギヤボックス
160 電動モータ
H ハンドル位置基準点
HJ ユニバーサルジョイントの基準点
GJ ユニバーサルジョイントの基準点
GC ステアリングギヤ基準点
Claims (14)
- コラムヨークと、スライドチューブヨークと、スライドシャフトヨークと、ピニオン側ヨークと、を有する操舵機構を含むステアリング装置の設計支援装置であって、
ハンドルのハンドル位置基準点の座標と、前記コラムヨークと前記スライドチューブヨークとを接続する第1のユニバーサルジョイント基準点の座標と、前記スライドシャフトヨークと前記ピニオン側ヨークとを接続する第2のユニバーサルジョイント基準点の座標と、ステアリングギヤ基準点の座標と、許容トルク変動率と、位相角許容誤差と、を記憶する記憶手段と、
車両の前後、上下及び左右方向が定められている3次元空間に、前記ハンドル位置基準点座標、前記第1のユニバーサルジョイント基準点の座標と、前記第2のユニバーサルジョイント基準点の座標と、前記ステアリングギヤ基準点の座標と、を配置する基準点配置手段と、
前記第1のユニバーサルジョイント基準点から前記第2のユニバーサルジョイント基準点を通る基準軸を算出する基準軸算出手段と、
前記基準軸上から視て前記ハンドル位置基準点から前記第1ジョイント基準点への直線と、前記基準軸上から視て前記第2ジョイント基準点から前記ステアリングギヤ基準点への直線との角度である位相角を算出する位相角算出手段と、
前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件成立の判断を行う許容範囲判断手段と、
を有することを特徴とするステアリング装置の設計支援装置。 - 前記許容範囲判断手段は、チルト動作の上段、中段、及び下段の各段階においてすべて前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件成立の判断を行うことを特徴とする請求項1に記載のステアリング装置の設計支援装置。
- 前記許容トルク変動率又は前記位相角許容誤差の変更を受け付ける入力手段と、前記許容トルク変動率の許容する許容範囲と、前記位相角許容誤差の許容する許容範囲とを表示する表示手段とをさらに含み、
前記記憶手段は、前記入力手段で変更を受け付けた、前記許容トルク変動率又は前記位相角許容誤差を記憶し、
前記許容範囲判断手段は、前記記憶手段で記憶している前記許容トルク変動率に基づいて前記許容トルク変動率の許容する許容範囲と、前記記憶手段で記憶している前記位相角許容誤差に基づいて前記位相角許容誤差の許容する許容範囲とを算出し、
前記表示手段は、前記許容範囲判断手段で算出した前記許容トルク変動率の許容する許容範囲と、前記許容範囲判断手段で算出した前記位相角許容誤差の許容する許容範囲とを同時表示する請求項1又は2に記載のステアリング装置の設計支援装置。 - 前記許容範囲判断手段は、前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件が成立しない場合に、前記表示手段に強調表示をさせることを特徴とする請求項3に記載のステアリング装置の設計支援装置。
- 前記許容範囲判断手段は、前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件の組み合わせを条件成立テーブルとして作成することを特徴とする請求項1から4のいずれか1項に記載のステアリング装置の設計支援装置。
- 量産品データテーブルを記憶する記憶手段と、
前記ハンドル位置基準点座標と、前記第1のユニバーサルジョイント基準点の座標と、前記第2のユニバーサルジョイント基準点の座標と、前記ステアリングギヤ基準点の座標と、から部品条件を求める部品条件算出手段と、
前記量産品データテーブルから、前記部品条件及び前記条件成立テーブルを基準として量産部品を選定する部品選定手段を有することを特徴とする請求項5に記載のステアリング装置の設計支援装置。 - 前記部品選定手段は、前記コラムヨーク、前記スライドチューブヨーク、前記スライドシャフトヨーク、前記ピニオン側ヨークと、を選定し、
3次元空間の前記第1のユニバーサルジョイント基準点に、前記コラムヨークと前記スライドチューブヨークとの接続点を配置し、前記第2のユニバーサルジョイント基準点に、前記スライドシャフトヨークと前記ピニオン側ヨークとの接続点を配置することを特徴とする請求項6に記載のステアリング装置の設計支援装置。 - コラムヨークと、スライドチューブヨークと、スライドシャフトヨークと、ピニオン側ヨークと、を有する操舵機構を含むステアリング装置の設計をコンピュータが支援するステアリング装置設計支援方法であって、
ハンドルのハンドル位置基準点の座標と、前記コラムヨークと前記スライドチューブヨークとを接続する第1のユニバーサルジョイント基準点の座標と、前記スライドシャフトヨークと前記ピニオン側ヨークとを接続する第2のユニバーサルジョイント基準点の座標と、ステアリングギヤ基準点の座標と、許容トルク変動率と、位相角許容誤差と、を記憶する記憶ステップと、
車両の前後、上下及び左右方向が定められている3次元空間に、前記ハンドル位置基準点座標、前記第1のユニバーサルジョイント基準点の座標と、前記第2のユニバーサルジョイント基準点の座標と、前記ステアリングギヤ基準点の座標と、を配置する基準点配置ステップと、
前記第1のユニバーサルジョイント基準点から前記第2のユニバーサルジョイント基準点を通る基準軸を算出する基準軸算出ステップと、
前記基準軸上から視て前記ハンドル位置基準点から前記第1ジョイント基準点への直線と、前記基準軸上から視て前記第2ジョイント基準点から前記ステアリングギヤ基準点への直線との角度である位相角を算出する位相角算出ステップと、
前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件成立の判断を行う許容範囲判断ステップと、
を有することを特徴とするステアリング装置設計支援方法。 - 前記許容範囲判断ステップは、チルト動作の上段、中段、及び下段の各段階においてすべて前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件成立の判断を行うことを特徴とする請求項8記載のステアリング装置設計支援方法。
- 前記許容範囲判断ステップで算出する前記許容トルク変動率の許容する許容範囲と、前記位相角許容誤差の許容する許容範囲とを表示する表示ステップを含み、
前記許容範囲判断ステップは、前記記憶ステップにおいて記憶している前記許容トルク変動率と、前記位相角許容誤差と、の少なくとも1つが変更された場合、変更された前記許容トルク変動率に基づいて前記許容トルク変動率の許容する許容範囲又は変更された前記位相角許容誤差に基づいて前記位相角許容誤差の許容する許容範囲の少なくとも1つを算出し、
前記表示ステップは、前記許容範囲判断ステップで算出した前記許容トルク変動率の許容する許容範囲と、前記許容範囲判断ステップで算出した前記位相角許容誤差の許容する許容範囲とを同時表示する請求項8又は9に記載のステアリング装置設計支援方法。 - 前記許容範囲判断ステップにおいて、前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件が成立しない場合に、前記表示ステップにおいて強調表示を行うことを特徴とする請求項10に記載のステアリング装置設計支援方法。
- 前記許容範囲判断ステップは、前記許容トルク変動率の許容する許容範囲に前記位相角許容誤差の許容する許容範囲が含まれる条件の組み合わせを条件成立テーブルとして作成することを特徴とする請求項8から11のいずれか1項に記載のステアリング装置設計支援方法。
- 量産品データテーブルを記憶する記憶ステップと、
前記ハンドル位置基準点座標と、前記第1のユニバーサルジョイント基準点の座標と、前記第2のユニバーサルジョイント基準点の座標と、前記ステアリングギヤ基準点の座標と、から部品条件を求める部品条件算出ステップと、
前記量産品データテーブルから、前記部品条件及び前記条件成立テーブルを基準として量産部品を選定する部品選定ステップを有することを特徴とする請求項12に記載のステアリング装置設計支援方法。 - 前記部品選定ステップでは、前記コラムヨーク、前記スライドチューブヨーク、前記スライドシャフトヨーク、前記ピニオン側ヨークと、を選定し、
3次元空間の前記第1のユニバーサルジョイント基準点に、前記コラムヨークと前記スライドチューブヨークとの接続点を配置し、前記第2のユニバーサルジョイント基準点に、前記スライドシャフトヨークと前記ピニオン側ヨークとの接続点を配置することを特徴とする請求項13に記載のステアリング装置設計支援方法。
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