CN202208289U - Electric power-assisting device - Google Patents
Electric power-assisting device Download PDFInfo
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- CN202208289U CN202208289U CN201120231440XU CN201120231440U CN202208289U CN 202208289 U CN202208289 U CN 202208289U CN 201120231440X U CN201120231440X U CN 201120231440XU CN 201120231440 U CN201120231440 U CN 201120231440U CN 202208289 U CN202208289 U CN 202208289U
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Abstract
The utility model provides an electric power-assisting device capable of regulating a springset load of an input rod when forked connector is in adjustment in a starting process of a system. In the starting process of the system, the electric power-assisting device utilizes a thrust from an electric motor (33) and based on a stroke checking value to assist an operation force of a driver. The electric power-assisting device is provided with a forked connector (12) combined with a braking pedal (10); the input rod (15) connecting with a forked connector threaded part (82) of the forked connector in a threaded manner; a flange (60) connecting with the input rod (15) in a threaded manner through a flange threaded part (83); a main piston arranged on an outer periphery position of the flange (60); a pair of springs (61, 62) installed in an axial gap between a recess (54a) of the main piston and the flange; and a groove part and a projecting part arranged between the main piston and the flange. The groove part and the projecting part are not combined in an embedded manner before the system starts. And the groove part and the projecting part splines the flange and are combined in the embedded manner in the starting process of the system.
Description
Technical field
The utility model relates to a kind of electric booster, and it utilizes electric actuator that driver's operation power is assisted as electric booster braking device etc. and use.
Background technology
Current; Known a kind of electric booster; It utilizes stroke sensor to detect the driver's operation amount; Thrust to the main piston effect will utilize the ball-screw conversion based on the motor torque of this detected value after and through pedal operation to the thrust that applies of input bar, the pedal force of chaufeur is assisted (for example, with reference to patent documentation 1).
Patent documentation 1: TOHKEMY 2007-112426 communique
The utility model content
But; In the prior electric work-saving device; In system's starting, the forked element of sustain pedal is adjusted, pedal position is under the situation of operable position, become the state that makes main piston move the operational ton detected value of stroke sensor through this forked element adjustment.Therefore, have following problems, that is, the flange of input bar and the gap value of main piston change, and can't correctly adjust spring assembly (springset) load of input bar.
The utility model is conceived to the problems referred to above and proposes, and its purpose is, a kind of electric booster is provided, and when it carries out the forked element adjustment in system's starting, can correctly adjust the spring assembly load of input bar.
To achieve these goals; The electric booster of the utility model is in system's starting; Utilize stroke sensor that chaufeur is detected to the operational ton that operating pedal applies, utilize thrust, driver assistance person's operating effort from electric actuator based on the stroke detection value.
This electric booster has: forked element, input bar, flange, piston element, a pair of spring and flange inserted structure.
Said forked element and said operating pedal carry out keying and close, the operating effort that input applies to said operating pedal.
Said input bar carries out screw thread with the forked element threaded portion of said forked element and combines, and transmits the operating effort that applies to said operating pedal, and, rotation when adjusting in the position of carrying out said forked element.
Said flange combines with said input bar screw thread via the flange threaded portion, protrudes to periphery from said input bar.
Said piston element is configured in the circumferential position of said flange, transmits the thrust and auxiliary thrust of pedal operation.
Said a pair of spring is installed in the recess and the endplay between the said flange of said piston element, with the center position pretension of said flange to said recess.
Said flange inserted structure is arranged between said piston element and the said flange, and is not chimeric at system's prestart, in system's starting that said flange spline is chimeric.
The effect of utility model
The position adjustment of forked element is carried out the input bar rotation that utilizes the forked element threaded portion to combine with the forked element screw thread.Flange also utilizes the flange threaded portion to combine with this input bar screw thread.
When adjusting owing to the position that makes input bar rotation carrying out forked element at system's prestart; Piston element and flange are not chimeric; So invariant positionization of input bar and flange; As long as do not utilize hill holder etc. that position adjustment stroke is applied restriction, then the endplay amount of piston element and flange does not change.
In system starting, make the rotation of input bar and when carrying out the position adjustment of forked element, utilize the flange inserted structure, make flange and piston element spline chimeric.Therefore, utilize the rotation of input bar that flange is moved, and owing to be in system's starting,, piston element is moved so utilize based on thrust from electric actuator from the stroke detection value of stroke sensor.As noted above, move together through making flange and piston element, thereby the endplay amount of piston element and flange is not changed.
Its result when in system's starting, carrying out the forked element adjustment, can correctly adjust the spring assembly load of input bar.
Description of drawings
Fig. 1 is the whole section-drawing of the electric booster braking device (example of electric booster) of expression embodiment 1.
Fig. 2 is the control system block diagram of control system in the electric booster braking device of expression embodiment 1.
Fig. 3 is the skeleton diagram of the forked element adjustment structure in the electric booster braking device of expression embodiment 1.
Fig. 4 is the D-D line section-drawing of Fig. 3 of the forked element adjustment structure in the electric booster braking device of expression embodiment 1.
Fig. 5 is the pressure balanced scheme drawing that is used for the electric booster braking device of illustrative embodiment 1.
Fig. 6 is the instruction diagram that utilizes the constant power operated control that the controller in the electric booster braking device of embodiment 1 carries out; (a) the auxiliary stroke of expression is with respect to the characteristic data of input travel; (b) the expression relative shift is with respect to the characteristic data of input travel, and (c) expression hydraulic pressure is with respect to the characteristic data of input travel.
Fig. 7 is the forked element corrective action instruction diagram in the Comparative Examples, (a) expression prestart forked element overtime, and (b) forked element overtime in the expression starting is when (c) expression prestart forked element shortens, when (d) forked element shortens in the expression starting.
Fig. 8 is the forked element corrective action instruction diagram in the electric booster braking device of embodiment 1; (a) expression prestart forked element overtime; (b) forked element overtime in the expression starting is when (c) expression prestart forked element shortens, when (d) forked element shortens in the expression starting.
The specific embodiment
Below, based on embodiment 1 shown in the drawings, the optimal way of the electric booster of realizing the utility model is described.
(embodiment 1)
At first, description architecture.
Fig. 1 is the whole section-drawing of the electric booster braking device (example of electric booster) of expression embodiment 1.Below, based on Fig. 1, integral structure is described.
The electric booster braking device of embodiment 1 is as shown in Figure 1, has: pedal operation unit 1, Electric booster unit 3 and main hydraulic cylinder unit 5.Above-mentioned pedal operation unit 1 applies piston thrust through the pedal operation of chaufeur.Above-mentioned Electric booster unit 3 applies piston thrust through motor torque.Above-mentioned main hydraulic cylinder unit 5 is transformed to main hydraulic pressure and secondary hydraulic pressure with the total thrust of 2 kinds of piston thrusts.
Above-mentioned pedal operation unit 1 is as shown in Figure 1, has: brake pedal 10, forked element pin 11, forked element 12, pedal-rod 13, union lever 14, input bar 15 and stroke sensor 16.
Above-mentioned brake pedal 10, upper end are supported on the instrument carrier panel 17 rotationally, and central portion is installed on the forked element 12 via forked element pin 11.That is, if chaufeur applies pedal force, then pedal force transmits to input bar 15 via pedal-rod 13 and union lever 14, make input bar 15 to the left of Fig. 1 to producing stroke.In addition, input bar 15 is to be through to the state configuration of main hydraulic cylinder unit 5 via Electric booster unit 3.
Above-mentioned stroke sensor 16 is potentiometers that input bar 15 is detected with respect to the absolute displacement amount of instrument carrier panel 17 (below be called " input absolute displacement detected value A ").The trip sensor 16 is installed in the car body lateral bracket 18 that is set in instrument carrier panel 17 sides and is set between the bar lateral bracket 19 of input bar 15 sides, utilizes built-in spring to remain elongation state.
Above-mentioned Electric booster unit 3 is as shown in Figure 1, has: servo-unit housing 30, case lid 31, electrical motor stay bearing plate 32, electrical motor 33 (electric actuator), motor reel 34, rotary transfer machine 35, bearing 36, ball screw framework 37, ring-type guide portion 38, vibrating part 39 and tubular guide portion 40.
Above-mentioned servo-unit housing 30, above-mentioned case lid 31 and above-mentioned electrical motor stay bearing plate 32 are the stationary parts that are fixed on the instrument carrier panel 17.
Above-mentioned electrical motor 33 is fixed on the electrical motor stay bearing plate 32, utilizes controller 70, and control law according to the rules carries out drive controlling, and this controller 70 is transfused to the detection information from stroke sensor 16 and relative displacement transducer 41.
Above-mentioned rotary transfer machine 35 be with from the rotation of electrical motor 33 to mechanism that ball screw framework 37 transmits.This rotary transfer machine 35 has: the 1st belt wheel 35a, and it is installed on the motor reel 34; The 2nd belt wheel 35b, it is installed on the nut part 37a of ball screw framework 37; And driving band 35c, it is erected at two belt wheel 35a, 35b is last.
Above-mentioned ball screw framework 37 is with from the electrical motor rotary torque of electrical motor 33 via rotary transfer machine 35 transmission, is transformed to the mechanism of axial piston thrust.This ball screw framework 37 has: nut part 37a, and it transmits the electrical motor rotary torque; And cannulated threaded axle 37b, it screws togather via ball and nut part 37a.Nut part 37a utilizes ring-type guide portion 38 and retreating of limit axial is mobile.Cannulated threaded axle 37b utilizes the rotation of nut part 37a and advances mobilely vertically, makes the chimeric vibrating part 39 that is fixed on its leading section push main piston 54 (piston element).In the chimeric fixedly tubular of the rearward end guide portion 40 of cannulated threaded axle 37b, it carries out sliding guidance to input bar 15.
In addition, on the input bar 15 of the center shaft that runs through this Electric booster unit 3, be provided with relative displacement transducer 41, its relative shift to input bar 15 and main piston 54 detects.
Above-mentioned main hydraulic cylinder unit 5 is as shown in Figure 1, has: liquid reserve tank the 50, the 1st hydraulic actuating cylinder housing the 51, the 2nd hydraulic actuating cylinder housing 52, port hydraulic actuating cylinder (port cylinder) 53, main piston 54 (piston element) and auxiliary piston 55.
Above-mentioned liquid reserve tank 50 is casings of savings braking liquid, is fixed on the 2nd hydraulic actuating cylinder housing 52.And when non-brake operating, the liquid chamber in the liquid reserve tank 50 is communicated with the main hydraulic pressure chamber 56 that is formed by main piston 54 and by the secondary hydraulic pressure chamber 57 that auxiliary piston 55 forms via pressure-reduction outlet 58,59.When brake operating, utilize the stroke of main piston 54 and auxiliary piston 55, with being communicated with and the cut-out that is communicated with of liquid chamber that liquid reserve tank 50 is interior and secondary hydraulic pressure chamber 57 of the liquid chamber in the liquid reserve tank 50 and main hydraulic pressure chamber 56.And, main hydraulic pressure and secondary hydraulic pressure are risen with piston thrust.
Above-mentioned main piston 54 when brake operating, via be arranged on input on the bar 15 flange 60 and with the spring 61,62 of flange 60 to the center position pretension, the pedal operation through chaufeur applies piston thrust.And, apply piston thrust by motor torque via vibrating part 39.In addition, in Fig. 1, the 63rd, the retracing spring of vibrating part 39, the 64th, the retracing spring of main piston 54.
Above-mentioned auxiliary piston 55 via the leading section of input bar 15, is applied piston thrust and is applied piston thrust by motor torque by the pedal operation of chaufeur when brake operating.In addition, in Fig. 1, the 63rd, the retracing spring of auxiliary piston 55.
Fig. 2 is the control system block diagram of control system in the electric booster braking device of expression embodiment 1.Below, based on Fig. 2, the structure of control system is described.
Above-mentioned controller 70 is as shown in Figure 2 to have memory device 71, in this memory device 71, stores: have the s operation control content program, use input travel and relative shift corresponding and the displacement of targets amount estimated performance data represented and input travel-hydraulic characteristic data etc. with it.And controller 70 is except memory device 71, and as shown in Figure 2 also have: differential circuit 72, displacement of targets amount setting apparatus 73, subtraction circuit 74 and controller 75.
72 pairs in above-mentioned differential circuit carries out differential by stroke sensor 16 detected absolute displacement amounts, computation speed V (below be called speed signal V).Above-mentioned displacement of targets amount setting apparatus 73 is accepted the input from the speed signal V of differential circuit 72 and the detection signal of stroke sensor 16 (input absolute displacement detected value A), target setting displacement C (relative shift), and with its input subtraction circuit 74.Above-mentioned subtraction circuit 74 deducts by relative displacement transducer 41 detected relative shifts (relative displacement detected value B) (C-B), and obtains deviation from the displacement of targets amount C by 73 outputs of displacement of targets amount setting apparatus.The supplying electric current of supplying with to electrical motor 33 is obtained in the input of the deviation that above-mentioned controller 75 is accepted to be obtained by subtraction circuit 74, and the drive division of electrical motor 33 is controlled.
In addition; Utilize controller 70; As shown in Figure 2 electrical motor 33 and transmission mechanism (rotary transfer machine 35 and ball screw framework 37) are controlled with this in proper order, utilized the action of cannulated threaded axle 37b and the spring force of retracing spring 61, make main piston 54 displacements (advance and retreat).And,, adjust main hydraulic pressure and secondary hydraulic pressure with the displacement and the displacement addition of importing bar 15 of main piston 54.At this moment, utilize the difference (relative displacement detected value B) between the displacement of displacement and stroke sensor 16 of 41 pairs of main pistons 54 of relative displacement transducer to detect.Should detect data (relative displacement detected value B) to controller 70 feedbacks, and in the control of electrical motor 33, use.
Promptly; Controller 70 is corresponding with the detection signal (input absolute displacement detected value A) of stroke sensor 16; Setting makes the relative displacement relation between input bar 15 and the main piston 54 become variable displacement of targets amount C; Based on the detection signal (relative displacement detected value B) of relative displacement transducer 41, electrical motor 33 is controlled, so that the relation of the relative displacement between input bar 15 and the main piston 54 (relative displacement detected value B) becomes above-mentioned displacement of targets amount C.In addition, the setting of displacement of targets amount C is to use the displacement of targets amount estimated performance data of obtaining in advance to carry out.
In addition; Controller 70 is through executive routine, for example carries out constant power operated control, variable power operated control, rises to (jump in) control, co-operative control is controlled, regenerated to braking aux. controls, enhancing (build up), subtract power operated control, backlash reduces control etc.
Fig. 3 is the skeleton diagram of the forked element adjustment structure in the electric booster braking device of expression embodiment 1.Fig. 4 is the D-D line section-drawing of Fig. 3 of the forked element adjustment structure in the electric booster braking device of expression embodiment 1.Below, based on Fig. 3 and Fig. 4, forked element adjustment structure is described.
The electric booster braking device of embodiment 1 is as noted above; In system's starting; Utilize stroke sensor 16 to detect the operational ton that chaufeur applies brake pedal 10 (operating pedal); Utilization is assisted the operating effort of chaufeur based on the thrust from electrical motor 33 (electric actuator) of stroke detection value.
In above-mentioned electric booster braking device; As forked element adjustment structure, have: forked element 12, input bar 15, flange 60, main piston 54 (piston element), a pair of spring 61,62, slot part 80 (flange inserted structure) and salient 81 (flange inserted structure).In addition, so-called input bar 15 comprises the pedal-rod 13 and union lever 14 that are wholely set.
Above-mentioned forked element 12 closes via forked element pin 11 and brake pedal 10 keyings, the pedal force (operating effort) that input applies to brake pedal 10.
Above-mentioned input bar 15 combines with forked element threaded portion 82 screw threads of forked element 12, transmits the operating effort that applies to brake pedal 10, and rotation when the position adjustment of carrying out forked element 12.
Above-mentioned flange 60 combines with input bar 15 screw threads via flange threaded portion 83, protrudes to periphery from input bar 15.Here, flange threaded portion 83 is that pitch is set at the threaded portion that equates at interval with the pitch of forked element threaded portion 82 at interval.Thus, if make 15 rotations of input bar for the position adjustment of forked element 12, then flange 60 promptly, makes the interval of forked element 12 and flange 60 keep constant to identical direction mobile phase amount together.
Above-mentioned main piston 54 is configured in the circumferential position of flange 60, transmits the thrust and auxiliary thrust of pedal operation.This main piston 54 is through system's starting, and till the initial position, forward direction moves specified amount α from prestart initial position to starting.One of mobile reason as noted above is that slot part 80 is not chimeric at prestart with salient 81, utilizes system's starting to make slot part 80 and salient 81 splines chimeric.In addition, other reasons is, through having the gap that in system's starting, main piston 54 is returned slightly, thereby prevents knock (slapping sound) etc.
Above-mentioned a pair of spring 61,62 is installed among the recess 54a and the endplay between the flange 60 of main piston 54, with the center position pretension of flange 60 to the recess 54a of main piston 54.
Above-mentioned slot part 80 and above-mentioned salient 81 are arranged between main piston 54 and the flange 60, are not chimeric at system's prestart, the flange inserted structure that flange 60 splines are chimeric in system's starting.In more detail; Above-mentioned slot part 80 moves (specified amount α) this point when utilizing main piston 54 to start in system with above-mentioned salient 81; The system's prestart that is positioned at the prestart initial position at main piston 54 is not chimeric; The system that is arranged in the starting initial position at main piston 54 starts, and makes flange 60 splines chimeric.The slot part 80 keyway structures that utilize as shown in Figure 4 are arranged on the peripheral part of flange 60.Salient 81 as shown in Figure 3 being arranged on the main piston 54, be configured in the endplay with the position of brake pedal 10 near the endplay of side on.
Below, illustration.
The effect of the electric booster braking device of embodiment 1 is divided into " corrective action of main hydraulic cylinder hydraulic pressure and constant power operated control effect ", " the forked element corrective action in the Comparative Examples ", " the forked element corrective action among the embodiment 1 " and describes.
[corrective action of main hydraulic cylinder hydraulic pressure and constant power operated control effect]
When adjustment main hydraulic cylinder hydraulic pressure, the displacement of main piston 54 (advance and retreat) to be carried out with the displacement addition of input bar 15, this hydraulic pressure adjustment is according to being undertaken by the equilibrium of pressure relation of following formula (1) expression.
Pb＝(Fi-K×ΔX)/Ai＝(Fb+K×ΔX)/Ab …(1)
Here, each key element in the pressure balance type (1) is as shown in Figure 5, for
Pb: main hydraulic pressure
Fi: the thrust of brake operating input
Fb: servo-unit thrust
Ai: the compression area of input bar 15
Ab: the compression area of main piston 54
K: the spring constant of spring 61,62
Δ X: the relative shift between input bar 15 and the main piston 54.
In addition, the displacement of input bar 15 is made as Xi, the displacement of main piston 54 is made as Xb, relative shift Δ X is defined as Δ X=Xi-Xb.Therefore, Δ X is 0 at the center position place that relatively moves, and on the direction that main piston 54 is retreated with respect to input bar 15, for just, is negative at its opposite sense.In addition, the sliding resistance of in pressure balance type (1), ignoring sealing member.In this pressure balance type (1), servo-unit thrust Fb can infer according to the current value of electrical motor 33.
On the other hand, power-assisted is expressed as following formula (2) than α.
α＝Pb×(Ab+Ai)/Fi …(2)
Therefore, if the Pb substitution of above-mentioned pressure balance type (1) is somebody's turn to do in (2) formula, then power-assisted is expressed as formula (3) than α, that is,
α＝(1-K×ΔX/Fi)×(Ab/Ai+1)…(3)。
Carry out at the electric booster braking device that utilizes embodiment 1 based on the testing result of stroke sensor 16, (controlled reset) being controlled in the rotation of electrical motor 33, so that relative shift Δ X becomes 0 under the situation of constant power operated control (example of control).Like this, power-assisted becomes α=Ab/Ai+1 than α, ground identical with vacuum booster unit, utilize between the compression area Ai of compression area Ab and input bar 15 of main piston 54 area than and confirm (Fig. 5) uniquely.
Relative therewith, X is set at negative specified value with the relative shift Δ, makes relative shift Δ X become the afore mentioned rules value.That is, the rotation of electrical motor 33 is controlled, with along with input bar 15 moves to the direction that increases brake fluid pressure, to compare the absolute displacement quantitative change that makes main piston 54 big with the absolute displacement amount of input bar 15.According to this control, power-assisted becomes (1-K * Δ X/Fi) size doubly than α, that is, the power-assisted variable ratio, electric actuator 53 works as the power-assisted source, can realize that pedal force reduces significantly.
Constant power operated control makes input bar 15 and main piston 54 displacement integratedly (with relative displacement is that 0 mode is carried out displacement, so that main piston 54 is in above-mentioned center position with respect to input bar 15 all the time).Being made as transverse axis if will import the stroke (input travel) of bar 15, the stroke of main piston 54 (auxiliary stroke) is made as the longitudinal axis, then is to make auxiliary stroke become the control method of the characteristic shown in the solid line of Fig. 6 (a).In addition, through carrying out this control, shown in Fig. 6 (c), be accompanied by input the advancing of bar 15, the hydraulic pressure that is produced by main hydraulic cylinder 2 is with 2 curves, 3 curves, or compound etc. with high order curve more and these curves and repeatedly curve-like that obtain becomes greatly.
If input travel is made as transverse axis; Relative shift between input bar 15 and the main piston 54 is made as the longitudinal axis; Then can the characteristic of the constant power operated control of being represented by the characteristic data shown in the characteristic data shown in Fig. 6 (a) and Fig. 6 (c) be showed with the displacement of targets amount estimated performance data shown in Fig. 6 (b).Solid line among Fig. 6 (b) is the relative shift between input bar 15 and the main piston 54.If shown in the solid line of Fig. 6 (b), electrical motor 33 is controlled, so that the relative shift between input bar 15 and the main piston 54 is always 0, then can obtain the hydraulic characteristic shown in Fig. 6 (c).
[the forked element corrective action in the Comparative Examples]
To only have the forked element threaded portion, and the feature structure that does not have an embodiment 1 is the structure example as a comparison of flange threaded portion, slot part and salient, based on Fig. 7, the forked element corrective action in this Comparative Examples is described.
(a) prestart forked element overtime
System's prestart with the forked element position when prolonging the side adjustment owing to be system's prestart, main piston keeps stopping at the state of normal place.And, owing to the pedal hill holder makes forked element can't be to prolonging side shifting, replacing makes flange march forward to the left of Fig. 7 (a).
At this prestart forked element overtime, flange is made as δ by the endplay amount of pretension when the middle position of main piston recess, the amount of movement that prolongs in the side adjustment is made as X.In the case, prolong the adjusted endplay amount of side (gap value) shown in Fig. 7 (a), for gap value=(δ+X), the spring assembly load of input bar becomes big, can't correctly adjust the spring assembly load.
(b) forked element overtime in the starting
In system starting with the forked element position when prolonging the side adjustment, though be in system's starting, under the situation of Comparative Examples, main piston keeps stopping at the state of normal place.And, owing to the pedal hill holder makes forked element can't be to prolonging side shifting, replacing makes flange march forward to the left of Fig. 7 (b).
Forked element overtime in this starting is made as δ with flange by the endplay amount of pretension when the middle position of main piston recess, and the amount of movement that prolongs in the side adjustment is made as X.In the case, prolong the adjusted endplay amount of side (gap value) shown in Fig. 7 (b), identical ground with prestart forked element overtime is for gap value=(δ+X), make the spring assembly load of input bar become big can't correctly adjust the spring assembly load.
When (c) the prestart forked element shortens
System's prestart with the forked element position when shortening the side adjustment owing to be system's prestart, main piston keeps stopping at the state of normal place.And the position relation of flange and main piston remains unchanged, and only forked element is with respect to importing bar to shortening side shifting.
When this prestart forked element shortens, flange is made as δ by the endplay amount of pretension when the middle position of main piston recess, the amount of movement that shortens in the side adjustment is made as X.In the case, shorten the adjusted endplay amount of side (gap value) shown in Fig. 7 (c), be gap value=δ, can correctly adjust the spring assembly load of input bar.
When (d) forked element shortens in the starting
In system starting with the forked element position when shortening the side adjustment owing to be in system's starting, thus with shortening amount as amount of pedal operation, main piston shown in Fig. 7 (d), corresponding with shortening amount and from normal place left direction advance.And forked element is with respect to importing bar to shortening side shifting.
When forked element shortens in this starting, flange is made as δ by the endplay amount of pretension when the middle position of main piston recess, the amount of movement that shortens in the side adjustment is made as X.In the case, shorten the adjusted endplay amount of side (gap value) shown in Fig. 7 (d), for gap value=(δ-X), the spring assembly load of input bar is diminished can't end and really adjust the spring assembly load.
Shown in as described above, in Comparative Examples, when shortening except the prestart forked element, can't correctly adjust the spring assembly load.In other words, no matter be at system's prestart or in system's starting, all can't the forked element position be adjusted to the prolongation side, and the forked element position also is limited to system's prestart when shortening the side adjustment.
[the forked element corrective action among the embodiment 1]
Requirement under at least a state of the system in these two kinds of state of the system, can be carried out the prolongation side adjustment of forked element position and shorten the side adjustment in system's prestart and system's starting.Below, based on Fig. 8, the forked element corrective action among the embodiment 1 that reflects this point is described.
(a) prestart forked element overtime
System's prestart with the forked element position when prolonging the side adjustment because main piston 54 keeps stopping at the state of prestart initial position, slot part 80 is in non-chimerism with salient 81.And, owing to the pedal hill holder makes forked element 12 can't be to prolonging side shifting, the flange 60 that replaces marches forward to the left of Fig. 8 (a).
At this prestart forked element overtime; Flange 60 is made as δ by the endplay amount of pretension when the middle position of the recess 54a of main piston 54; The amount of movement that prolongs in the side adjustment is made as X, the difference of initial position in the prestart initial position of main piston 54 and the starting is made as specified amount α.The adjusted endplay amount of the prestarting prolongation side of this system (gap value) is gap value=(δ+α+X) shown in Fig. 8 (a).And, if system starting then through making main piston 54 move specified amount α, thereby becomes gap value=(δ+X).Therefore, the spring assembly load of input bar 15 becomes big, can't correctly adjust the spring assembly load.
(b) forked element overtime in the starting
In system starting with the forked element position when prolonging the side adjustment, because main piston 54 is arranged in the starting initial position that prestart initial position and specified amount α addition are obtained, so slot part 80 and salient 81 become the spline chimerism.If make 15 rotations of input bar for the adjustment of forked element position, then forked element 12 can't move because of the pedal hill holder, keeps the halted state of forked element 12 and flange 60 obviously.That is, even make 15 rotations of input bar, the forked element 12 that combines via forked element threaded portion 82 also keeps constant at interval with the setting of the flange that combines via flange threaded portion 83 60.And; Because main piston 54 is arranged in the starting initial position, the position adjustment of beginning forked element 12 even make 15 rotations of input bar, the position of forked element 12 (=travel position) also do not change; So do not carry out aux. controls, still keep initial position in the starting.That is, flange 60 can not change relative position relation with main piston 54.
Forked element overtime in this starting is made as δ with flange 60 by the endplay amount of pretension when the middle position of the recess 54a of main piston 54.In this system's starting, because the relative position relation of flange 60 and main piston 54 does not change,, be gap value=δ so prolong the adjusted endplay amount of side (gap value) shown in Fig. 8 (b), can correctly adjust the spring assembly load of input bar 15.
When (c) the prestart forked element shortens
System's prestart with the forked element position when shortening the side adjustment because main piston 54 keeps stopping at the state of prestart initial position, slot part 80 is in non-chimerism with salient 81.And the position relation of flange 60 and main piston 54 is kept intact, and only forked element 12 is with respect to importing bar 15 to shortening side shifting.
When this prestart forked element shortens; Flange 60 is made as δ by the endplay amount of pretension when the middle position of the recess 54a of main piston 54; The amount of movement that shortens in the side adjustment is made as X, the difference of initial position in the prestart initial position of main piston 54 and the starting is made as specified amount α.In the case, shorten the adjusted endplay amount of side (gap value) shown in Fig. 8 (c), be gap value=(δ+α).And,, can correctly adjust the spring assembly load of input bar 15 if system starting then through making main piston 54 move specified amount α, thereby becomes gap value=δ.
When (d) forked element shortens in the starting
In system starting with the forked element position when shortening the side adjustment, because main piston 54 is arranged in the starting initial position that prestart initial position and specified amount α addition are obtained, so slot part 80 and salient 81 become the spline chimerism.If make 15 rotations of input bar for the adjustment of forked element position, then forked element 12 is to shortening side shifting, flange 60 itself and setting between the forked element 12 are kept at interval constant in, to the left of Fig. 8 (d) to mobile.And; Because main piston 54 is in initial position in the starting before shortening adjustment; The position adjustment of beginning forked element 12 if make 15 rotations of input bar; Then the position of forked element 12 (=travel position) changes, thus carry out aux. controls, make main piston 54 from starting initial position to the left of Fig. 8 (d) to moving.That is, for forked element 12, flange 60 and main piston 54, relative position relation does not change, to the left of Fig. 8 (d) to moving.
When forked element shortens in this starting, flange 60 is made as δ by the endplay amount of pretension when the middle position of the recess 54a of main piston 54, the amount of movement that shortens in the side adjustment is made as X.In this system's starting; Because the relative position relation of forked element 12, flange 60 and main piston 54 does not change; So shorten the adjusted endplay amount of side (gap value) shown in Fig. 8 (d), be gap value=δ, can correctly adjust the spring assembly load of input bar 15.
Shown in as described above, in embodiment 1, except prestart forked element overtime, can correctly adjust the spring assembly load.In other words, in system's starting, can the forked element position be adjusted to the prolongation side, and can be with the forked element position to shortening the side adjustment.In addition, for the forked element position is adjusted to the shortening side, can in system's prestart and system's starting, carry out under any state of the system in these two kinds of state of the system.
Below, description effect.In the electric booster braking device of embodiment 1, can obtain the following effect of enumerating.
(1) a kind of electric booster braking device (electric booster); It is in system's starting; Utilize 16 pairs of chaufeurs of stroke sensor to detect to the operational ton that operating pedal (brake pedal 10) applies; Utilization is assisted the operating effort of chaufeur based on the thrust from electric actuator (electrical motor 33) of stroke detection value, and it has:
Forked element 12, itself and aforesaid operations pedal (brake pedal 10) carry out keying and close, the operating effort that input applies to above-mentioned operating pedal (brake pedal 10);
Piston element (main piston 54), it is configured in the circumferential position of above-mentioned flange 60, transmits the thrust and auxiliary thrust of pedal operation;
A pair of spring 61,62, it is installed among the recess 54a and the endplay between the above-mentioned flange 60 of above-mentioned piston element (main piston 54), with the center position pretension of above-mentioned flange 60 to above-mentioned recess 54a; And
Flange inserted structure (slot part 80, salient 81), it is arranged between above-mentioned piston element (main piston 54) and the above-mentioned flange 60, and is not chimeric at system's prestart, in system's starting that above-mentioned flange 60 splines are chimeric.
Therefore, when in system's starting, carrying out the forked element adjustment, can correctly adjust the spring assembly load of input bar 15.
(2) above-mentioned piston element (main piston 54) is to utilize system starting from prestart initial position to starting, to move the parts of specified amount α till the initial position along working direction; Above-mentioned flange inserted structure is not chimeric at system's prestart that above-mentioned piston element (main piston 54) is positioned at the prestart initial position; The system that is arranged in the starting initial position at above-mentioned piston element (main piston 54) starts, and above-mentioned flange 60 splines are chimeric.Therefore; On the basis of the effect of (1); Move such simple structure through utilizing piston element (main piston 54) to be accompanied by system starting, thus can obtain not chimeric at system's prestart, in system starts the flange inserted structure that flange 60 splines are chimeric.
(3) above-mentioned flange inserted structure has: slot part 80, and it is arranged on the above-mentioned flange 60; And salient 81, it is arranged on the above-mentioned piston element (main piston 54), is configured in the above-mentioned endplay and the position of aforesaid operations pedal (brake pedal 10) near the endplay of side.Therefore, on the basis of the effect of (2), through only appending slot part 80 and salient 81, thus can obtain at system's prestart not chimeric, reliably that flange 60 splines are chimeric flange inserted structure in system's starting.
More than, based on embodiment 1, the electric booster of the utility model has been described, but concrete structure is not limited to present embodiment 1, only otherwise break away from the related utility model purport of each claim item of claims, then allow the design-calculated change and append etc.
In embodiment 1,, show the example of main piston set in the brake equipment that the brake fluid pressure of 2 systems is controlled as piston element.But,, also can be the piston that the hydraulic pressure etc. to 1 system is controlled as piston element.
In embodiment 1, as the flange inserted structure, show and utilize main piston 54 and system to start moving of accompanying, not chimeric at system's prestart, the structure example that flange 60 splines are chimeric in system's starting.But, as the flange inserted structure, also can be following flange inserted structure, that is, adopt the piston element that can not be accompanied by system's starting and move, in system's starting, use actuator that flange is carried out the chimeric action of spline.
In embodiment 1,, show and use through main piston 54 and system starting moving and the chimeric slot part 80 of spline and the example of salient 81 together as the flange inserted structure.But,, also can adopt through piston element and system starting moving and the chimeric spline tooth of spline or the example of other inserted structures together as the flange inserted structure.
In embodiment 1, show the example of electric booster, but electric booster can be used as the auxiliary use of the driver's operation systems such as power-transfer clutch outside the brake system as the electric booster braking device of the auxiliary use of brake system.In addition,, show the example that uses electrical motor, but also can use the actuator outside the electrical motor such as screw actuator as electric actuator.
Claims (3)
1. electric booster, it utilizes stroke sensor that chaufeur is detected to the operational ton that operating pedal applies in system's starting, utilizes the thrust from electric actuator based on the stroke detection value, the operating effort of chaufeur is assisted,
It is characterized in that having:
Forked element, itself and said operating pedal carry out keying and close, the operating effort that input applies to said operating pedal;
The input bar, it carries out screw thread with the forked element threaded portion of said forked element and combines, transmits the operating effort that applies to said operating pedal, and, rotate when adjusting in the position of carrying out said forked element;
Flange, it combines with said input bar screw thread via the flange threaded portion, protrudes to periphery from said input bar;
Piston element, it is configured in the circumferential position of said flange, transmits the thrust and auxiliary thrust of pedal operation;
A pair of spring, it is installed in the recess and the endplay between the said flange of said piston element, with the center position pretension of said flange to said recess; And
The flange inserted structure, it is arranged between said piston element and the said flange, and is not chimeric at system's prestart, in system's starting that said flange spline is chimeric.
2. electric booster according to claim 1 is characterized in that,
Said piston element is to utilize system starting from prestart initial position to starting, to move the parts of specified amount till the initial position along working direction,
Said flange inserted structure, the system's prestart that is positioned at the prestart initial position at said piston element is not chimeric, and the system that is arranged in the starting initial position at said piston element starts, and said flange spline is chimeric.
3. electric booster according to claim 2 is characterized in that,
Said flange inserted structure has: slot part, and it is arranged on the said flange; And salient, it is arranged on the said piston element, is configured in the said endplay and the position of said operating pedal near the endplay of side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010147655A JP5640498B2 (en) | 2010-06-29 | 2010-06-29 | Electric booster |
| JP2010-147655 | 2010-06-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202208289U true CN202208289U (en) | 2012-05-02 |
Family
ID=45598779
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201120231440XU Expired - Lifetime CN202208289U (en) | 2010-06-29 | 2011-06-29 | Electric power-assisting device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5640498B2 (en) |
| CN (1) | CN202208289U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107444381A (en) * | 2016-04-15 | 2017-12-08 | 株式会社万都 | The brake pressure control apparatus and method of electric booster braking system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101636832B1 (en) * | 2014-06-24 | 2016-07-06 | 주식회사 만도 | Apparatus for controlling electronic booster and method for controlling thereof |
| DE102014226255A1 (en) * | 2014-12-17 | 2016-06-23 | Volkswagen Aktiengesellschaft | Electromechanical brake booster |
| WO2020170509A1 (en) * | 2019-02-22 | 2020-08-27 | 本田技研工業株式会社 | Hydraulic actuator structure and saddle type vehicle |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11287272A (en) * | 1998-03-31 | 1999-10-19 | Tokico Ltd | Disc brake |
| JP5182678B2 (en) * | 2005-06-30 | 2013-04-17 | 日立オートモティブシステムズ株式会社 | Electric booster |
| JP2009208523A (en) * | 2008-03-01 | 2009-09-17 | Nissan Motor Co Ltd | Electric brake booster |
-
2010
- 2010-06-29 JP JP2010147655A patent/JP5640498B2/en not_active Expired - Fee Related
-
2011
- 2011-06-29 CN CN201120231440XU patent/CN202208289U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107444381A (en) * | 2016-04-15 | 2017-12-08 | 株式会社万都 | The brake pressure control apparatus and method of electric booster braking system |
| CN107444381B (en) * | 2016-04-15 | 2020-02-28 | 株式会社万都 | Brake pressure control device and method of electric power-assisted brake system |
| US10857986B2 (en) | 2016-04-15 | 2020-12-08 | Mando Corporation | Apparatus and method for controlling braking pressure of powered booster brake system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012011814A (en) | 2012-01-19 |
| JP5640498B2 (en) | 2014-12-17 |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20120502 |