JPH0822680B2 - Vehicle height adjustment device - Google Patents
Vehicle height adjustment deviceInfo
- Publication number
- JPH0822680B2 JPH0822680B2 JP60077046A JP7704685A JPH0822680B2 JP H0822680 B2 JPH0822680 B2 JP H0822680B2 JP 60077046 A JP60077046 A JP 60077046A JP 7704685 A JP7704685 A JP 7704685A JP H0822680 B2 JPH0822680 B2 JP H0822680B2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- oil
- valve
- vehicle height
- oil chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Axle Suspensions And Sidecars For Cycles (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、油圧緩衝装置の油圧減衰器を利用した車両
の車高調整装置に関するものであり、停車中は車高を下
げ、走行中は車高を高くするための車高２段階調整装置
について、油圧減衰器の伸縮動作を利用して油圧減衰器
を伸長させて車高を高くし、また任意に車高を低い位置
に変更することができるようにすることによって、例え
ば走行中は車高を高くすることが望ましいオフロード自
動二輪車について、車高を低くしてその乗り降りを楽に
するために利用して有効なものである。Description: TECHNICAL FIELD The present invention relates to a vehicle height adjusting device for a vehicle that uses a hydraulic damper of a hydraulic shock absorber, and reduces the vehicle height while the vehicle is stopped and while the vehicle is running. Regarding a vehicle height two-stage adjusting device for increasing vehicle height, using a telescopic operation of the hydraulic damper to extend the hydraulic damper to increase the vehicle height, and to arbitrarily change the vehicle height to a lower position. By making it possible, for example, for an off-road motorcycle in which it is desirable to increase the vehicle height while traveling, the present invention is effectively used to lower the vehicle height and make it easier to get on and off.
例えば自動二輪車等の車両において、走行中の油圧減
衰器の伸縮動作を利用して当該油圧減衰器を伸長させて
車高を適宜無段階に調整できるようにしたものがある
（例えば特開昭59-147135号公報）。その機構の概要は
油圧減衰器のシリンダ１（第７図、第８図参照、以下、
この項において同じ）のプランジャ杆２に対する往復動
作によって吐出される作動油がプランジャ杆２の通油路
３、プランジャ杆２の上端に配置された逆止弁11、流入
路10を経て、ばね５のばね座７を移動させる作動油室９
に導かれ、作動油室９から流出路15を経て戻される。こ
の流入路10と流出路15との間に多段可変絞り弁16が配置
されている。For example, in a vehicle such as a motorcycle, there is one in which the hydraulic attenuator is extended by utilizing the expanding and contracting operation of the hydraulic attenuator during traveling so that the vehicle height can be adjusted appropriately steplessly (for example, JP-A-59). -147135 publication). The outline of the mechanism is described in the cylinder 1 of the hydraulic damper (see FIGS. 7 and 8 below,
The same applies in this section) The hydraulic oil discharged by the reciprocating motion with respect to the plunger rod 2 passes through the oil passage 3 of the plunger rod 2, the check valve 11 arranged at the upper end of the plunger rod 2, the inflow passage 10, and then the spring 5 Oil chamber 9 for moving the spring seat 7 of
And is returned from the hydraulic oil chamber 9 through the outflow passage 15. A multistage variable throttle valve 16 is arranged between the inflow passage 10 and the outflow passage 15.
このものは重い荷物を搭載する場合、２人乗りをする
場合等、車体にかかる荷重が重くなり、車高が下がった
場合に、油圧減衰器に組み込まれているポンプによって
作動油を吐出し、その吐出油によって油圧緩衝装置の緩
衝ばねのばね座７を下げ（第７、８図においてばね座７
を左方向に移動させ）、これによって油圧減衰器のシリ
ンダ１を押し出して油圧減衰器を伸長させるものであ
り、この多段可変絞り弁16の絞りを強くすることによっ
て、上記ばね座７の位置を下げると共に油圧減衰器の特
性を堅くして、その荷重の増加に対応するものである。
このものは、上記ポンプの通油路３とばね座７を押し下
げる作動油室９とを流入路10を介して常時連通させ、多
段可変絞り弁16を介して流出路15に連通させているもの
であるから、自動二輪車が停止して油圧減衰器の伸縮動
作が停止すると、上記ポンプのポンピング動作も停止
し、ばね座７を押し下げる作動油室９内の作動油が上記
絞り弁16を経て戻されるので、自然に車高が下がり、ま
た、ポンプによって吐出される作動油量と上記作動油室
９から上記絞り弁16を経て戻される油量との差によって
常時車高は変動する。したがって、これはその機構上車
高を高い位置に固定することはできない。This one discharges hydraulic oil by the pump built into the hydraulic attenuator when the load applied to the vehicle body becomes heavy and the vehicle height decreases, such as when carrying heavy luggage, when carrying two passengers, The discharged oil lowers the spring seat 7 of the buffer spring of the hydraulic shock absorber (see FIGS. 7 and 8).
Is moved to the left), thereby pushing out the cylinder 1 of the hydraulic damper to extend the hydraulic damper, and by strengthening the throttle of the multistage variable throttle valve 16, the position of the spring seat 7 is changed. It lowers the pressure and strengthens the characteristics of the hydraulic damper to cope with the increase of the load.
This is one in which the oil passage 3 of the above-mentioned pump and the hydraulic oil chamber 9 for pushing down the spring seat 7 are always communicated with each other through the inflow passage 10 and are communicated with the outflow passage 15 through the multistage variable throttle valve 16. Therefore, when the motorcycle is stopped and the expansion / contraction operation of the hydraulic damper is stopped, the pumping operation of the pump is also stopped, and the hydraulic oil in the hydraulic oil chamber 9 that pushes down the spring seat 7 is returned via the throttle valve 16. As a result, the vehicle height naturally decreases, and the vehicle height constantly fluctuates due to the difference between the amount of hydraulic oil discharged by the pump and the amount of oil returned from the hydraulic oil chamber 9 through the throttle valve 16. Therefore, this cannot fix the vehicle height to a high position because of its mechanism.
したがって、所定の高い位置と所定の低い位置とに車
高を任意に選択することはできない。Therefore, the vehicle height cannot be arbitrarily selected between the predetermined high position and the predetermined low position.
ところで、オフロード用の自動二輪車等の荒れ地を走
行する車両については、油圧減衰器の緩衝特性を変える
ことなく車高を極端に高くすることが望まれる場合があ
る。このために車高を極端に高くすると乗り降りに不便
を来すことになる。したがって、油圧減衰器の緩衝特性
に影響を与えることなく、所定の高い位置と低い位置と
の２段階に車高を調整するという要求には上記従来技術
は応えることができない。By the way, for a vehicle such as an off-road motorcycle that travels in a wasteland, it may be desired to make the vehicle height extremely high without changing the cushioning characteristics of the hydraulic damper. For this reason, if the vehicle height is made extremely high, it will be inconvenient to get on and off. Therefore, the above prior art cannot meet the demand for adjusting the vehicle height in two steps of a predetermined high position and a predetermined low position without affecting the cushioning characteristics of the hydraulic damper.
本発明は、油圧緩衝装置の油圧減衰器の伸縮動作によ
るポンピング作用を利用して当該油圧減衰器を伸長させ
て車高を調整するについて、上記要求に応えられるよう
にすることをその目的とし、そのために油圧減衰器の緩
衝特性に影響を与えることなく、所定の高い位置と低い
位置とに車高を任意に選択し、その位置に固定できるよ
うに、上記ばね座を押し下げるシリンダへの作動油の給
排機構を工夫することをその課題とするものである。An object of the present invention is to extend the hydraulic damper to adjust the vehicle height by utilizing the pumping action by the expansion and contraction operation of the hydraulic damper of the hydraulic shock absorber, and to make it possible to meet the above-mentioned request. Therefore, the hydraulic oil to the cylinder that pushes down the spring seat so that the vehicle height can be arbitrarily selected and fixed at a predetermined high position and low position without affecting the damping characteristics of the hydraulic damper. The problem is to devise a feeding / discharging mechanism.
上記課題解決のために講じた手段はつぎの要素（イ）
〜（ハ）によって構成されるものである。The measures taken to solve the above problems are the following elements (a)
~ (C).
（イ） 油圧減衰器の蓋体に第２の逆止弁と、外部より
強制的に開閉される調整弁とを設け、当該逆止弁と調整
弁の一次側とを介して油圧減衰器のプランジャ杆の通油
路を油圧減衰器のばね座の作動油室に連通させ、調整弁
の二次側を油圧減衰器のシリンダの油室に連通させたこ
と、 （ロ） 油圧減衰器の蓋体に第１の逆止弁と戻し弁体と
からなる戻し弁を設け、当該戻し弁を介してプランジャ
杆の通油路と油圧減衰器のシリンダの油室とを連通させ
たこと、 （ハ） 上記ばね座の移動により傾斜カムによって戻し
弁を進退させて、ばね座が上限に到達したときに上記第
１の逆止弁を解放させて戻し弁体によってプランジャ杆
の油通路とシリンダの油室とを連通させるように戻し弁
を開閉すること。(A) A second check valve and a regulating valve that is forcibly opened and closed from the outside are provided on the lid of the hydraulic attenuator, and the hydraulic attenuator is provided via the check valve and the primary side of the regulating valve. The oil passage of the plunger rod was connected to the hydraulic oil chamber of the spring seat of the hydraulic attenuator, and the secondary side of the adjusting valve was connected to the oil chamber of the cylinder of the hydraulic attenuator. A return valve including a first check valve and a return valve body is provided in the body, and the oil passage of the plunger rod and the oil chamber of the cylinder of the hydraulic damper are communicated with each other via the return valve. ) The return valve is advanced and retracted by the inclined cam by the movement of the spring seat, and when the spring seat reaches the upper limit, the first check valve is released and the return valve body allows the oil passage of the plunger rod and the oil of the cylinder to be released. Open and close the return valve to establish communication with the chamber.
上記調整弁は外部より強制的に開閉される開閉弁であ
り、任意に開閉操作される。調整弁を車高を高くする位
置、すなわち閉弁位置にシフトさせると、第２の逆止弁
（吐出弁）を介して油圧減衰器のプランジャ杆の通油路
に連通したその一次側と、油圧減衰器のシリンダの油室
に連通したその二次側との連通が断たれているので、油
圧減衰器のポンプからプランジャ杆の通油路に吐出され
た作動油がばね座の作動油室に流入し、ばね座を押し下
げて油圧減衰器を伸長させて車高を高くする。このと
き、上記戻し弁の第１の逆止弁は閉じているので、プラ
ンジャ杆の通油路と油圧減衰器のシリンダの油室とを連
通させる通路は遮断され、速やかにばね座は押し下げら
れる。ばね座が所定の位置まで押し下げられると、ばね
座に連動する傾斜カムによって上記戻し弁の第１の逆止
弁（吸入弁）が開き、プランジャ杆の通油路と油圧緩衝
器のシリンダの油室とを連通させるので、上記ポンプか
らプランジャ杆の通油路に吐出された作動油は第１の逆
止弁を経て圧力が実質ゼロで油圧減衰器のシリンダの油
室に戻される。したがって、ばね座が所定の位置に押し
下げられて後は、上記ポンプは無負荷状態になる。それ
ゆえ、ポンプ負荷により油圧減衰器の緩衝特性が影響さ
れる（堅くなる）ことはない。The adjusting valve is an opening / closing valve that is forcibly opened / closed from the outside and is arbitrarily opened / closed. When the adjusting valve is shifted to a position where the vehicle height is increased, that is, a valve closing position, the primary side of the hydraulic damping device, which communicates with the oil passage of the plunger rod of the hydraulic damper via the second check valve (discharge valve), Since the communication with the secondary side of the cylinder of the hydraulic damper is cut off, the hydraulic oil discharged from the pump of the hydraulic damper to the oil passage of the plunger rod is the hydraulic chamber of the spring seat. And the spring seat is pushed down to extend the hydraulic damper and raise the vehicle height. At this time, since the first check valve of the return valve is closed, the passage that connects the oil passage of the plunger rod and the oil chamber of the cylinder of the hydraulic damper is shut off, and the spring seat is quickly pushed down. . When the spring seat is pushed down to a predetermined position, the first check valve (suction valve) of the return valve is opened by the inclined cam that interlocks with the spring seat, and the oil passage of the plunger rod and the oil of the cylinder of the hydraulic shock absorber are opened. Since it communicates with the chamber, the hydraulic oil discharged from the pump to the oil passage of the plunger rod is returned to the oil chamber of the cylinder of the hydraulic damper at substantially zero pressure via the first check valve. Therefore, after the spring seat is pushed down to a predetermined position, the pump becomes unloaded. Therefore, the damping characteristics of the hydraulic damper are not affected (stiffened) by the pump load.
調整弁を車高を低くする位置にシフトさせると、油圧
減衰器のプランジャ杆の通油路およびばね座の作動油室
に連通した調整弁の一次側が油圧減衰器のシリンダの油
室に連通した二次側に連通するので、プランジャ杆の通
油路に吐出された作動油と共に、ばね座の作動油室の作
動油が調整弁を通って油圧減衰器のシリンダの油室に戻
される。したがって、ばね座が緩衝器の緩衝ばねによっ
て押し上げられ、車高は下がる。ばね座が押し上げられ
ると、その傾斜カムによって戻し弁の第１の逆止弁が再
び閉じられ、戻し弁によるプランジャ杆の通油路と油圧
減衰器のシリンダの油室との連通は遮断される。この状
態では、プランジャ杆の通油路は調整弁を介して油圧減
衰器のシリンダの油室に連通するので、上記ポンプは無
負荷状態になり、したがって、ポンプ負荷によって油圧
減衰器の緩衝特性が影響されることない。When the control valve was shifted to a position where the vehicle height was lowered, the primary side of the control valve, which communicated with the oil passage of the plunger rod of the hydraulic damper and the hydraulic oil chamber of the spring seat, communicated with the oil chamber of the cylinder of the hydraulic damper. Since it communicates with the secondary side, the hydraulic oil in the hydraulic oil chamber of the spring seat is returned to the hydraulic chamber of the cylinder of the hydraulic damper together with the hydraulic oil discharged to the oil passage of the plunger rod. Therefore, the spring seat is pushed up by the buffer spring of the shock absorber, and the vehicle height is lowered. When the spring seat is pushed up, the first check valve of the return valve is closed again by the inclined cam, and the communication between the oil passage of the plunger rod and the oil chamber of the cylinder of the hydraulic damper is closed by the return valve. . In this state, the oil passage of the plunger rod communicates with the oil chamber of the cylinder of the hydraulic attenuator via the adjusting valve, so that the pump is in a no-load state, and therefore, the buffer load of the hydraulic attenuator varies depending on the pump load. Not affected.
以上のとおり調整弁を車高を高くする位置、車高を低
くする位置のいずれかに選択することによって、車高を
所定の高さ、あるいは所定の低さに任意に切り換えるこ
とができる。As described above, the vehicle height can be arbitrarily switched to a predetermined height or a predetermined low value by selecting the adjusting valve to either the position for increasing the vehicle height or the position for decreasing the vehicle height.
自動二輪車の車体フレーム11の後部に枢支されたリヤ
アーム15の後端において後輪19が車軸を介して軸支され
ている。油圧緩衝装置17がリヤアーム15とフレーム11と
の間にリンク機構21を介して配置されている。A rear wheel 19 is pivotally supported at the rear end of a rear arm 15 pivotally supported on the rear part of a body frame 11 of a motorcycle through an axle. A hydraulic shock absorber 17 is arranged between the rear arm 15 and the frame 11 via a link mechanism 21.
油圧緩衝装置17は油圧減衰器27と緩衝ばね29とを有す
る。油圧減衰器27において、シリンダ31の内部の油室30
に作動油Ｏが充填されている。このシリンダ31にピスト
ン杆35が連結されたピストン33が摺動自在に嵌合されて
いる。シリンダ31の頭部開口に蓋体37が嵌着されてお
り、この蓋体37がシリンダ31の取付ブラケットを兼ねて
いる。The hydraulic shock absorber 17 has a hydraulic damper 27 and a shock absorbing spring 29. In the hydraulic damper 27, the oil chamber 30 inside the cylinder 31
Is filled with hydraulic oil O. A piston 33 in which a piston rod 35 is connected to the cylinder 31 is slidably fitted. A lid 37 is fitted in the head opening of the cylinder 31, and the lid 37 also serves as a mounting bracket for the cylinder 31.
支持筒41は、シリンダ31の周囲に遊嵌した状態で蓋体
37に固定されている。また、筒状のばね座43はシリンダ
31および支持筒41に摺動自在に嵌挿されている。このば
ね座43は、ピストン杆35のブラケット45の反対側におい
て前記緩衝ばね29を支えるものである。作動油室47は、
支持筒の内側に形成されており、この作動油室47内の油
圧を変化させることにより、ばね座43を緩衝ばね29に抗
して押し下げて油圧減衰器27を伸長させてリヤアーム15
とフレーム11との間隔を増大させ、車高を高くする。な
お、先端下面にテーパ（傾斜カム）49aを有する受止片4
9は、ばね座43に一体形成されており、この受止片49は
じね座43と共に摺動し、その内側において後記する戻し
弁体61の外端面に当接している。The support cylinder 41 is a lid body that is loosely fitted around the cylinder 31.
It is fixed at 37. In addition, the cylindrical spring seat 43 is a cylinder.
It is slidably fitted into the support tube 31 and the support tube 41. The spring seat 43 supports the buffer spring 29 on the side of the piston rod 35 opposite to the bracket 45. The hydraulic oil chamber 47 is
It is formed inside the support cylinder, and by changing the hydraulic pressure in the hydraulic oil chamber 47, the spring seat 43 is pushed down against the buffer spring 29 to extend the hydraulic attenuator 27 to extend the rear arm 15.
And the frame 11 are increased to increase the vehicle height. The receiving piece 4 having a taper (inclined cam) 49a on the lower surface of the tip
9 is integrally formed with the spring seat 43, and the receiving piece 49 slides together with the spring seat 43 and contacts the outer end surface of the return valve body 61, which will be described later, inside thereof.
ポンプ室51はピストン杆35の先端から軸方向に形成さ
れている。また、プランジャ杆53の後端が蓋体37に嵌着
されており、プランジャ杆53の先端部は前記ピストン杆
35のポンプ室51に密に摺動自在に嵌挿されている。通油
路55がプランジャ杆53の軸芯に形成されており、この通
油路55が前記ピストン杆35のポンプ室51と連通してい
る。小蓋体57が前記蓋体37に嵌着し、この小蓋体57が前
記プランジャ杆53の通油路55を閉止している。蓋体37に
設けられた嵌挿孔59が底部において前記プランジャ杆53
の通油路55と連通している。嵌挿孔59に遊嵌されている
戻し弁体61の内端が、戻し弁の第１の逆止弁（吸入弁、
以下同じ）69に対するストッパ63よりも突出していて、
この内端面に第１の逆止弁69の弁板が圧縮ばね71によっ
て圧接されている。蓋体37に通油路65が形成されてお
り、戻し弁の戻し弁体61にＬ字状の貫通孔67が設けられ
ている。このＬ字状の貫通孔67と前記嵌挿孔59の底部の
通油路との連通を第１の逆止弁69によって遮断してお
り、Ｌ字状の貫通孔67が蓋体37の通油路65とを連通して
いる。なお、通油路65は貫通孔67と共にポンプの吸入孔
として機能し、圧縮ばね71によって閉弁方向に付勢され
た第１の逆止弁69がポンプの吸入弁として機能する。The pump chamber 51 is formed in the axial direction from the tip of the piston rod 35. Further, the rear end of the plunger rod 53 is fitted to the lid body 37, and the tip end portion of the plunger rod 53 is the piston rod.
It is densely slidably fitted in the pump chamber 51 of 35. An oil passage 55 is formed in the shaft center of the plunger rod 53, and this oil passage 55 communicates with the pump chamber 51 of the piston rod 35. The small lid 57 is fitted on the lid 37, and the small lid 57 closes the oil passage 55 of the plunger rod 53. A fitting insertion hole 59 provided in the lid 37 has a plunger rod 53 at the bottom.
It communicates with the oil passage 55 of. The inner end of the return valve body 61 loosely fitted in the fitting insertion hole 59 is the first check valve (suction valve,
The same applies hereinafter) 69 than the stopper 63,
The valve plate of the first check valve 69 is pressed against the inner end surface by a compression spring 71. An oil passage 65 is formed in the lid body 37, and an L-shaped through hole 67 is provided in the return valve body 61 of the return valve. The communication between the L-shaped through hole 67 and the oil passage at the bottom of the fitting insertion hole 59 is blocked by the first check valve 69, and the L-shaped through hole 67 communicates with the lid 37. It communicates with the oil passage 65. The oil passage 65 functions as a suction hole of the pump together with the through hole 67, and the first check valve 69 biased in the valve closing direction by the compression spring 71 functions as a suction valve of the pump.
通油路55の後端部に形成される細径部72はポンプの吐
出口として機能し、圧縮ばね75によって閉弁方向に付勢
された第２の逆止弁（吐出弁）73がポンプの吐出弁とし
て機能する。そして、蓋体37と小蓋体57との間に形成さ
れている油溜り室76がプランジャ杆53の透孔を介して、
第２の逆止弁73の二次側（下流側）と連通している。The small diameter portion 72 formed at the rear end portion of the oil passage 55 functions as a discharge port of the pump, and the second check valve (discharge valve) 73 biased by the compression spring 75 in the valve closing direction is used as the pump. Function as a discharge valve. Then, the oil sump chamber 76 formed between the lid body 37 and the small lid body 57 is inserted through the through hole of the plunger rod 53,
It communicates with the secondary side (downstream side) of the second check valve 73.
蓋体37に穿たれた孔に栓体81、83を嵌着していて、こ
れにより調整弁の二次側油室77、一次側油室79を形成し
ており、これらの油室77、79は連通孔85によって連通さ
れている。栓体81、83および連通孔85に対して調整弁体
87が摺動自在に嵌挿されている。なお、上記調整弁体87
は栓体81、83に対しては密に遊嵌され、連通孔85に対し
てはシール部材89によって密に嵌合されていて、これに
よって連通孔85による二次側油室77と一次側油室79との
連通が遮断される。電磁アクチュエータ91はブラケット
93を介してシリンダ31に固定されており、このアクチュ
エータ91の操作杆95は前記調整弁体87と連結されてお
り、電磁アクチュエータ91によって調整弁体87が操作さ
れる。Plugs 81 and 83 are fitted into the holes formed in the lid 37, thereby forming a secondary oil chamber 77 and a primary oil chamber 79 of the regulating valve. These oil chambers 77, 79 communicates with each other through a communication hole 85. Adjustment valve body for the plug bodies 81, 83 and the communication hole 85
87 is slidably inserted. The adjusting valve body 87
Is tightly loosely fitted in the plugs 81 and 83, and tightly fitted in the communication hole 85 by a seal member 89, whereby the secondary oil chamber 77 and the primary side by the communication hole 85 are formed. The communication with the oil chamber 79 is cut off. Electromagnetic actuator 91 is a bracket
It is fixed to the cylinder 31 via 93, and the operating rod 95 of this actuator 91 is connected to the adjusting valve body 87, and the adjusting valve body 87 is operated by the electromagnetic actuator 91.
なお、設定車速になったら自動的にスイッチが入って
電磁アクチュエータ91が作動するようにしておくと、上
記車速に達したとき、調整弁体87が押し出され、これに
よってシリンダ31の油室30に連通した前記二次側油室77
と一次側油室79との連通が遮断されるので、ポンプから
の吐出油が一次側油室79から通油路101を経て作動油室4
7に圧入される。このためにばね座43が押し下げられ、
これによって車高が高くなる。また、設定車速以下にな
るとスイッチが自動的に切れるようにしておくと、調整
弁体87が引かれて、一次側油室79を二次側油室77に連通
させるので、作動油室47内の作動油が一次側油室79、通
路103を経てシリンダ31の油室30に戻され、車高が下げ
られる。すなわち、これによって車速に応答して自動的
に車高が高められ、または低められる。When the vehicle speed reaches the set vehicle speed, the electromagnetic actuator 91 is automatically turned on so that the adjusting valve body 87 is pushed out when the vehicle speed reaches the above-mentioned vehicle speed. The secondary side oil chamber 77 in communication
Since the communication between the primary side oil chamber 79 and the primary side oil chamber 79 is cut off, the discharge oil from the pump passes from the primary side oil chamber 79 through the oil passage 101 to the hydraulic oil chamber
Pressed into 7. For this reason, the spring seat 43 is pushed down,
This increases the vehicle height. If the switch is automatically turned off when the vehicle speed falls below the set vehicle speed, the adjustment valve body 87 is pulled to connect the primary side oil chamber 79 to the secondary side oil chamber 77. Is returned to the oil chamber 30 of the cylinder 31 through the primary oil chamber 79 and the passage 103, and the vehicle height is lowered. That is, this automatically increases or decreases the vehicle height in response to the vehicle speed.
手元スイッチで電磁アクチュエータ91を作動させて操
作杆95を押し出すようにしておけば、任意に車高を高く
し、または低くすることができる。The vehicle height can be arbitrarily increased or decreased by operating the electromagnetic actuator 91 with the hand switch to push out the operating rod 95.
さらに、操作杆95を常に引く方向に付勢しておけば、
通常は車高が下がり、電磁アクチュエータ91を作動させ
て操作杆95を押すことによって車高を高められるように
することができる。したがって、走行する場所、車速に
応じて必要なときだけ任意に車高を高くすることができ
る。Furthermore, if you push the operating rod 95 in the direction that you pull it all the time,
Normally, the vehicle height is lowered, and the vehicle height can be increased by operating the electromagnetic actuator 91 and pushing the operating rod 95. Therefore, the vehicle height can be arbitrarily increased only when necessary according to the place to travel and the vehicle speed.
なお、通油路99、101が蓋体に形成されていて、その
うち通油路99は、一次側油室79と前記油溜り室76とを連
通させ、通油路101は一次側油室79とばね座43の作動油
室47とを連通させている。さらに、通油路101はプラン
ジャ杆53の通油路55と共に圧油をばね座43の作動油室47
に供給する通油路となる。また、第６図において、蓋体
37に形成された通油路103は二次側油室77と前記シリン
ダ31内の油室30とを連通し、後記するようにばね座43の
作動油室47内の油を油室30に戻す通油路となる。Incidentally, oil passages 99, 101 are formed in the lid, of which the oil passage 99 communicates the primary side oil chamber 79 and the oil reservoir chamber 76, and the oil passage 101 is the primary side oil chamber 79. And the hydraulic oil chamber 47 of the spring seat 43 communicate with each other. Further, the oil passage 101, together with the oil passage 55 of the plunger rod 53, supplies pressure oil to the hydraulic oil chamber 47 of the spring seat 43.
It becomes an oil passage to supply to. Further, in FIG. 6, the lid body
The oil passage 103 formed in 37 communicates the secondary side oil chamber 77 with the oil chamber 30 in the cylinder 31, and as described later, the oil in the hydraulic oil chamber 47 of the spring seat 43 is fed to the oil chamber 30. It becomes an oil passage to return.
次いで上記実施例の作動について説明する。 Next, the operation of the above embodiment will be described.
上記アクチュエータ91を作動させ、操作杆95により調
整弁体87を押し出して車高をアップする位置に選択する
と、二次側油室77と一次側油室79との連通が遮断され
る。この状態で油圧減衰器27のピストン33が往復動し、
プランジャ杆53がポンプ室51内で往復動してポンピイン
グ作用をすると、その油室30の作動油Ｏが通油路65、戻
し弁体61の貫通孔67、戻し弁の第１の逆止弁69、嵌挿孔
59の底部とプランジャ杆53の通油路55を経てポンプ室51
に吸い込まれる。そして、油圧減衰器27が圧縮されたと
き、ポンプ室から吐出された作動油は通油路55、細径部
72、第２の逆止弁73、油溜り室76、通油路99を経て一次
側油室79に入り、その後、通油路101を経て作動室47に
入って、ばね座43を下方（第１図において右方向）に移
動させて、緩衝ばね29を押し下げる。これによってフレ
ーム11とリヤアーム15との間の間隔が押し広げられ車高
が高くなる。ばね座43が所定の位置まで下降すると、こ
れと共に受止片49の端部の傾斜部（傾斜カム）49aが下
降し、戻し弁体61は作動油圧によって外方向（第１図に
おいて上方）に付勢されているので、受止片49の端部の
傾斜カム49aの斜面に沿って戻し弁体61が押し出され
る。このとき、第１の逆止弁69の弁板は圧縮ばね71によ
って閉弁方向に付勢されているので、戻し弁体61に追従
して外方向に移動するが、やがてストッパー63に当接す
る。第１の逆止弁69の弁板がストッパー63に当接する
と、それ以上戻し弁体61の移動に追従することができ
ず、第１の逆止弁69の弁板が戻し弁体61の端面から離間
し、貫通孔67の端部開口が解放される。このために貫通
孔67はプランジャ杆53の通油路55と連通し、ポンプの吐
出油は油圧が実質上ゼロのままで油室30に戻される。し
たがって、その後はポンプはアンロードされる。この状
態では作動油室47と通油路55とは第２の逆止弁73は逆止
弁であるので、作動油室47から通油路55への戻りはな
く、したがって、ばね座43はその位置に固定される。そ
れゆえ、車高は高いままに保持される。When the actuator 91 is operated and the operating rod 95 pushes out the adjusting valve body 87 to select the position where the vehicle height is increased, the communication between the secondary side oil chamber 77 and the primary side oil chamber 79 is cut off. In this state, the piston 33 of the hydraulic damper 27 reciprocates,
When the plunger rod 53 reciprocates in the pump chamber 51 to perform a pumping action, the hydraulic oil O in the oil chamber 30 causes the oil passage 65, the through hole 67 of the return valve body 61, and the first check valve of the return valve. 69, insertion hole
Pump chamber 51 through the bottom of 59 and oil passage 55 of plunger rod 53
Is sucked into. When the hydraulic attenuator 27 is compressed, the hydraulic oil discharged from the pump chamber flows through the oil passage 55, the small diameter portion.
72, the second check valve 73, the oil sump chamber 76, and the oil passage 99 into the primary oil chamber 79, and then the oil passage 101 into the working chamber 47 to move the spring seat 43 downward ( (FIG. 1 rightward), and the buffer spring 29 is pushed down. As a result, the space between the frame 11 and the rear arm 15 is widened to increase the vehicle height. When the spring seat 43 is lowered to a predetermined position, the inclined portion (inclined cam) 49a at the end of the receiving piece 49 is also lowered, and the return valve body 61 is moved outward (upward in FIG. 1) by the hydraulic pressure. Since it is biased, the return valve body 61 is pushed out along the slope of the inclined cam 49a at the end of the receiving piece 49. At this time, since the valve plate of the first check valve 69 is urged in the valve closing direction by the compression spring 71, it moves outward following the return valve body 61, but eventually contacts the stopper 63. . When the valve plate of the first check valve 69 comes into contact with the stopper 63, it is impossible to follow the movement of the return valve body 61 any more, and the valve plate of the first check valve 69 moves to the return valve body 61. The end portion opening of the through hole 67 is released away from the end face. Therefore, the through hole 67 communicates with the oil passage 55 of the plunger rod 53, and the oil discharged from the pump is returned to the oil chamber 30 while the hydraulic pressure remains substantially zero. Therefore, the pump is then unloaded. In this state, since the second check valve 73 for the hydraulic oil chamber 47 and the oil passage 55 is a check valve, there is no return from the hydraulic oil chamber 47 to the oil passage 55, and therefore the spring seat 43 is It will be fixed in that position. Therefore, the vehicle height is kept high.
上記アクチュエータ91を作動させて操作杆95によって
調整弁体87を引くと、二次側油室77と一次側油室79とが
連通する（第４図、第５図、第６図）。これにより、ば
ね座43の作動油室47は一次側油室79、二次側油室77、通
油路103を介してシリンダ31の油室30に連通するので、
作動油室47の作動油は速やかに油室30に戻り、ばね座43
は左方に戻り、車高は下がる。この状態ではポンプ室51
からの吐出油は一次側油室79から二次側油室77に入り、
通油路103を経てシリンダ31の油室30に戻るので、ポン
プ吐出圧は実質上ゼロである。なお、符号13はエンジ
ン、39はリザーブタンクである。When the actuator 91 is operated and the adjusting valve body 87 is pulled by the operating rod 95, the secondary side oil chamber 77 and the primary side oil chamber 79 communicate with each other (FIGS. 4, 5, and 6). As a result, the hydraulic oil chamber 47 of the spring seat 43 communicates with the oil chamber 30 of the cylinder 31 via the primary oil chamber 79, the secondary oil chamber 77, and the oil passage 103.
The hydraulic oil in the hydraulic oil chamber 47 immediately returns to the oil chamber 30, and the spring seat 43
Returns to the left and the vehicle height decreases. In this state, the pump chamber 51
The oil discharged from the primary oil chamber 79 enters the secondary oil chamber 77,
Since it returns to the oil chamber 30 of the cylinder 31 via the oil passage 103, the pump discharge pressure is substantially zero. Reference numeral 13 is an engine and 39 is a reserve tank.
本発明の上記課題を解決した発明は未だ公知ではな
い。したがって、上記課題を解決して従来技術の上記問
題を解消したこと自体が本発明特有の効果である。The invention which solves the above-mentioned problems of the present invention is not yet known. Therefore, solving the above problems and solving the above problems of the prior art is an effect peculiar to the present invention.
すなわち、油圧減衰器のポンピング動作による吐出油
を利用して、手元操作、あるいは自動操作によって調整
弁を開閉操作することによって、車高を所定の高さまで
任意に高めてその位置に保持することができ、また、車
高を所定の低い高さまで下げ、その低い位置に保持する
ことができる。That is, by using the discharged oil by the pumping operation of the hydraulic attenuator, the vehicle height can be arbitrarily raised to a predetermined height and held at that position by opening or closing the adjusting valve by hand operation or automatic operation. In addition, the vehicle height can be lowered to a predetermined low height and held at the low position.
そして、車高を高くする時間は一瞬であるから、その
後は油圧減衰器のポンプをアンロードするので、このも
ののポンピング動作によって油圧減衰器の緩衝特性に影
響を及ぼす（堅くなる）ことはない。車高が低げられた
状態においても同様にポンピング動作によって油圧減衰
器の緩衝特性が影響されることはない。Since the vehicle height is raised for a moment, the pump of the hydraulic attenuator is unloaded after that, so the pumping operation of the hydraulic attenuator does not affect (stiffen) the damping characteristics of the hydraulic attenuator. Similarly, even when the vehicle height is lowered, the pumping action does not affect the damping characteristic of the hydraulic damper.
そして、この車高調整は車体にかかる荷重の大小に無
関係に行なわれるので、車高を下げて乗り降りを容易に
し、路面の状態等を勘案して車高を高くしたいときは走
行中に所定の高さまで車高を高くすることができる。Since this vehicle height adjustment is performed regardless of the magnitude of the load applied to the vehicle body, when it is desired to lower the vehicle height to facilitate getting on and off and to increase the vehicle height in consideration of the road surface condition, etc. The vehicle height can be increased to the height.
高い位置の車高は、ばね座と連動する傾斜カム49aに
よって制御される戻し弁（実施例における「第１の逆止
弁69」と「戻し弁体61」とからなる弁であって、吸入弁
の機能とアンロード弁の機能とを有するもの）の開閉に
よって規定されるものであるから、その設定機構が極め
て単純であり、また、車高を高い位置に保持する機構は
第２の逆止弁、調整弁（開閉弁）、戻し弁であるから、
車高の高低調整のための油圧回路を極めて単純に構成す
ることができる。これも本発明の大きな利点である。The vehicle height at the high position is a return valve (a valve including the "first check valve 69" and the "return valve body 61" in the embodiment, which is controlled by an inclined cam 49a that works in conjunction with a spring seat, and The function of the valve and the function of the unload valve) are defined by opening and closing, and therefore the setting mechanism is extremely simple, and the mechanism for holding the vehicle height at a high position is the second reverse. Since it is a stop valve, adjustment valve (open / close valve), and return valve,
The hydraulic circuit for adjusting the height of the vehicle can be constructed extremely simply. This is also a great advantage of the present invention.
第１図は実施例の要部断面図、第２図は第１図の実施例
を適用した自動二輪車の側面図、第３図は第１図の実施
例の正面図、第４図は第１図のIV-IV断面図、第５図は
第４図のＶ−Ｖ断面図、第６図は第４図のVI-VI断面
図、第７図は従来技術の一部断面図、第８図は第７図の
一部拡大図である。 Ｏ……作動油、11……車体（フレーム） 17……油圧緩衝装置、27……油圧減衰器 29……緩衝ばね、30……シリンダの油室 31……シリンダ、33……ピストン 35……ピストン杆、47……作動油室 49……受止片、49a……傾斜カム 51……ポンプ室、53……プランジャ杆 61……戻し弁体 55、99、101……圧油を供給する通油路 65、67……作動油を補給する通油路、圧油の戻し通路、
69……第１の逆止弁 73……第２の逆止弁、79……一次側油室 77……二次側油室、87……調整弁体FIG. 1 is a sectional view of an essential part of the embodiment, FIG. 2 is a side view of a motorcycle to which the embodiment of FIG. 1 is applied, FIG. 3 is a front view of the embodiment of FIG. 1, and FIG. 1 is a sectional view taken along line IV-IV, FIG. 5 is a sectional view taken along line VV of FIG. 4, FIG. 6 is a sectional view taken along line VI-VI of FIG. 4, and FIG. FIG. 8 is a partially enlarged view of FIG. 7. O …… Operating oil, 11 …… Vehicle (frame) 17 …… Hydraulic shock absorber, 27 …… Hydraulic attenuator 29 …… Buffer spring, 30 …… Cylinder oil chamber 31 …… Cylinder, 33 …… Piston 35… … Piston rod, 47 …… Operating oil chamber 49 …… Reception piece, 49a …… Inclined cam 51 …… Pump chamber, 53 …… Plunger rod 61 …… Return valve body 55, 99, 101 …… Supply pressure oil Oil passages 65, 67 ... Oil passages for supplying hydraulic oil, pressure oil return passages,
69 …… First check valve 73 …… Second check valve, 79 …… Primary oil chamber 77 …… Secondary oil chamber, 87 …… Adjusting valve body
Claims (1)
るポンピング作用を利用して当該油圧減衰器を伸長させ
て車高を調整する車両の車高調整装置において、 油圧減衰器の蓋体に第２の逆止弁と、外部より強制的に
開閉される調整弁とを設け、当該逆止弁と調整弁の一次
側とを介して油圧減衰器のプランジャ杆の通油路を油圧
減衰器のばね座の作動油室に連通させ、調整弁の二次側
を油圧減衰器のシリンダの油室に連通させ、 油圧減衰器の蓋体に第１の逆止弁と戻し弁体とからなる
戻し弁を設け、当該戻し弁を介してプランジャ杆の通油
路と油圧減衰器のシリンダの油室とを連通させ、 上記ばね座の移動により傾斜カムによって戻し弁を進退
させて、ばね座が上限に到達したときに上記第１の逆止
弁を解放させて戻し弁体によってプランジャ杆の油通路
とシリンダの油室とを連通させるように戻し弁を開閉す
る車両の車高調整装置。1. A vehicle height adjusting device for a vehicle, wherein a hydraulic damping device of a hydraulic shock absorber is expanded / contracted to adjust a vehicle height by utilizing a pumping action of the hydraulic damping device. A second check valve and a regulating valve that is forcibly opened and closed from the outside are provided, and the oil passage of the plunger rod of the hydraulic attenuator is connected to the hydraulic attenuator via the check valve and the primary side of the regulating valve. To the hydraulic oil chamber of the spring seat, the secondary side of the regulating valve to the oil chamber of the cylinder of the hydraulic attenuator, and the lid of the hydraulic attenuator consisting of the first check valve and the return valve body. A return valve is provided, and the oil passage of the plunger rod and the oil chamber of the cylinder of the hydraulic damper are communicated with each other through the return valve, and the movement of the spring seat advances and retracts the return valve by the inclined cam. When the upper limit is reached, the first check valve is released and the return valve disc is used to plan. Vehicle height adjusting device for a vehicle for opening and closing the so return valve so as to communicate with the oil chamber of the oil passage and the cylinder of catcher rod.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60077046A JPH0822680B2 (en) | 1985-04-11 | 1985-04-11 | Vehicle height adjustment device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60077046A JPH0822680B2 (en) | 1985-04-11 | 1985-04-11 | Vehicle height adjustment device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61235285A JPS61235285A (en) | 1986-10-20 |
| JPH0822680B2 true JPH0822680B2 (en) | 1996-03-06 |
Family
ID=13622832
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60077046A Expired - Fee Related JPH0822680B2 (en) | 1985-04-11 | 1985-04-11 | Vehicle height adjustment device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0822680B2 (en) |
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| JP2508600Y2 (en) * | 1989-10-27 | 1996-08-28 | スズキ株式会社 | Height adjustment device for motorcycles |
| JP2508602Y2 (en) * | 1989-11-01 | 1996-08-28 | スズキ株式会社 | Height adjustment device for motorcycles |
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| JPS58110386A (en) * | 1981-12-24 | 1983-06-30 | 株式会社昭和製作所 | Front fork with antidive mechanism |
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| JPS601089A (en) * | 1983-06-16 | 1985-01-07 | 株式会社昭和製作所 | Self-levelling damper for two-wheel barrow |
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1985
- 1985-04-11 JP JP60077046A patent/JPH0822680B2/en not_active Expired - Fee Related
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