JPH0212134Y2 - - Google Patents
Info
- Publication number
- JPH0212134Y2 JPH0212134Y2 JP1982172824U JP17282482U JPH0212134Y2 JP H0212134 Y2 JPH0212134 Y2 JP H0212134Y2 JP 1982172824 U JP1982172824 U JP 1982172824U JP 17282482 U JP17282482 U JP 17282482U JP H0212134 Y2 JPH0212134 Y2 JP H0212134Y2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- hydraulic pressure
- spring
- piston member
- load
- 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
Links
- 239000012530 fluid Substances 0.000 claims description 4
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Landscapes
- Hydraulic Control Valves For Brake Systems (AREA)
Description
【考案の詳細な説明】
本考案は、積載荷重に応じてリヤホイールシリ
ンダへ供給する制動液圧の減圧開始点をＧボール
による制動減速度の検出で行なうようにした荷重
応答型液圧制御弁に関する。[Detailed description of the invention] The present invention is a load-responsive hydraulic pressure control valve that detects the braking deceleration using a G ball to determine the starting point for reducing the brake fluid pressure supplied to the rear wheel cylinder according to the load. Regarding.
従来の荷重応答型液圧制御弁としては、例えば
第１図に示すようなものがある。 As a conventional load-responsive hydraulic control valve, there is one shown in FIG. 1, for example.
第１図において、弁本体１内には、制御ピスト
ン２、ポペツト弁３、及び弁座４で成る液圧制御
機構が組み込まれ、また弁本体１の車体水平軸Ｘ
−Ｘに対する取付け角で定まる制動減速度が得ら
れたときに前進してバルブシート５の流路を閉じ
るＧボール６が設けられ、更にＧボール６により
封じ込められた液圧PGにより作動するアクチユ
エータピストン７が制御ピストン２を有する液圧
制御機構との間にスプリング８，９，９′の介在
をもつて配設されている。 In FIG. 1, a hydraulic control mechanism consisting of a control piston 2, a poppet valve 3, and a valve seat 4 is built into the valve body 1, and the valve body 1 has a horizontal axis X of the vehicle body.
- A G ball 6 is provided which moves forward to close the flow path of the valve seat 5 when a braking deceleration determined by the mounting angle with respect to An evaporator piston 7 is disposed between a hydraulic control mechanism having a control piston 2 and springs 8, 9, 9' interposed therebetween.
この荷重応答型液圧制御弁の動作は、制動減速
度が設定値に達すると、Ｇボール６の前進による
バルブシート５への当接で、そのときのマスタシ
リンダよりの液圧Ｐ１を液圧PGとしてアクチユ
エータピストン７側に封じ込め、この封じ込め液
圧PGに応じてアクチユエータピストン７はスプ
リング８，９，９′とバランスする位置に移動し、
スプリング９を介して制御ピストン２に対しリヤ
ホイールシリンダに供給している液圧Ｐ２の減圧
制御開始点（スプリツトポイント又は折れ点）を
設定する。この状態でマスタシリンダよりの液圧
Ｐ１がスプリツトポイントに達するとスプリング
９に抗して制御ピストン２が左側に動き、弁座４
に対するポペツト弁３の当接でリヤ液圧Ｐ２をカ
ツトし、カツト後にマスタ液圧Ｐ１が更に上昇す
ると制御ピストン２は押し戻されて再び流路を開
き、このような制御ピストン２の往復動の繰り返
しでリヤホイールシリンダに供給する液圧Ｐ２を
減圧制御し、急制動を行なつても後輪ロツクが起
き難いようにしている。 The operation of this load-responsive hydraulic pressure control valve is such that when the braking deceleration reaches a set value, the G ball 6 moves forward and contacts the valve seat 5, changing the hydraulic pressure P1 from the master cylinder at that time to the hydraulic pressure. The actuator piston 7 is sealed as PG on the side of the actuator piston 7, and in response to this sealed hydraulic pressure PG, the actuator piston 7 moves to a position where it balances with the springs 8, 9, 9'.
A pressure reduction control start point (split point or bending point) of the hydraulic pressure P2 supplied to the rear wheel cylinder is set for the control piston 2 via the spring 9. In this state, when the hydraulic pressure P1 from the master cylinder reaches the split point, the control piston 2 moves to the left against the spring 9, and the valve seat 4
When the poppet valve 3 comes into contact with the rear hydraulic pressure P2, the rear hydraulic pressure P2 is cut, and when the master hydraulic pressure P1 further increases after the cut, the control piston 2 is pushed back and opens the flow path again, and this reciprocating movement of the control piston 2 is repeated. The hydraulic pressure P2 supplied to the rear wheel cylinders is controlled to be reduced to prevent the rear wheels from locking even if sudden braking is performed.
しかしながら、このような従来の荷重応答型液
圧制御弁にあつては、アクチユエータピストン７
に対しスプリングを直接当接した構造としていた
ため、アクチユエータピストン７にはスプリング
の偏荷重が作用しており、この偏荷重でアクチユ
エータピストン７は液圧を受けたときにシリンダ
壁をこじつて動くこととなり、ピストンのこじり
による摺動抵抗の増大で封じ込め液圧に応じた減
圧制御点の設定にバラツキを起し、またアクチユ
エータピストン７に設けたシールの耐久性も悪化
し易いという問題点があつた。 However, in such a conventional load-responsive hydraulic control valve, the actuator piston 7
Since the spring is in direct contact with the actuator piston 7, an unbalanced load from the spring acts on the actuator piston 7, and this unbalanced load causes the actuator piston 7 to push against the cylinder wall when receiving hydraulic pressure. This causes the piston to move with difficulty, and the increased sliding resistance due to the piston's prying causes variations in the setting of the pressure reduction control point according to the containment fluid pressure, and also tends to deteriorate the durability of the seal provided on the actuator piston 7. There was a problem.
本考案は、このような従来の問題点に鑑みてな
されたもので、スプリングによる偏荷重を受けて
もアクチユエータピストンがこじりを起すことの
ない荷重応答型液圧制御弁を提供することを目的
とする。 The present invention was developed in view of these conventional problems, and aims to provide a load-responsive hydraulic control valve in which the actuator piston does not twist even when subjected to an uneven load due to a spring. purpose.
この目的を達成するため本考案は、アクチユエ
ータピストンを封じ込め液圧が作用するピストン
部材とスプリングを受着するロツド部材とに分離
し、ピストン部材の端部に形成した凹球部にロツ
ド部材に形成した凸球部を当接する構造とし、ス
プリング力をロツド部材を介してピストン部材の
中心軸線上に集中して掛けるようにしたものであ
る。 In order to achieve this objective, the present invention separates the actuator piston into a piston member on which hydraulic pressure acts and a rod member that receives a spring, and the rod member is attached to a concave sphere formed at the end of the piston member. The piston has a structure in which a convex spherical portion formed in the piston comes into contact with the piston, and the spring force is concentrated on the central axis of the piston member via the rod member.
以下、本考案の実施例を図面に基づいて説明す
る。 Hereinafter, embodiments of the present invention will be described based on the drawings.
第２図は本考案の一実施例を示した断面図であ
る。 FIG. 2 is a sectional view showing an embodiment of the present invention.
まず、構造を説明すると、弁本体１にはリヤホ
イールシリンダに供給する液圧Ｐ２を減圧制御す
るための制御ピストン２、ポペツト弁３及び弁座
４でなる液圧制御機構が設けられ、又車体水平軸
Ｘ−Ｘに対する取り付け角で定まる設定減速度が
得られたときに前進してバルブシート５に当接
し、アクチユエータピストンに液圧PGを封じ込
めるＧボール６′が設けられる。バルブシート５
よりの流路はアクチユエータピストンに連通さ
れ、この実施例において、アクチユエータピスト
ンは液圧PGが作用するピストン部材１０とロツ
ド部材１２とに分割されており、ピストン部材１
０はシール１４の嵌着によりシリンダ内に摺動自
在に設けられ、一方ロツド部材１２にはスプリン
グ８の一端が当接されると共にスプリング８の他
端はロツド部材１２の軸部に挿着したプレート１
６に当接され、このプレート１６に対し、スプリ
ング９，９′の一端が受着され、スプリング９の
他端は液圧制御機構の制御ピストン２との間に介
在されている。 First, to explain the structure, the valve body 1 is provided with a hydraulic pressure control mechanism consisting of a control piston 2, a poppet valve 3, and a valve seat 4 for reducing the hydraulic pressure P2 supplied to the rear wheel cylinder. A G ball 6' is provided which moves forward and comes into contact with the valve seat 5 when a set deceleration determined by the mounting angle with respect to the horizontal axis XX is obtained, thereby sealing the hydraulic pressure PG in the actuator piston. Valve seat 5
The second flow path communicates with the actuator piston, and in this embodiment, the actuator piston is divided into a piston member 10 on which hydraulic pressure PG acts and a rod member 12.
0 is slidably provided in the cylinder by fitting the seal 14, while one end of the spring 8 is in contact with the rod member 12, and the other end of the spring 8 is inserted into the shaft of the rod member 12. plate 1
One end of the spring 9, 9' is received by the plate 16, and the other end of the spring 9 is interposed between the spring 9 and the control piston 2 of the hydraulic pressure control mechanism.
ピストン部材１０はロツド側となる後端に凹球
部１１を形成しており、又ロツド部材１２の先端
には凸球部１３が一体に形成され、ピストン部材
１０の凹球部１１にロツド部材１２の凸球部１３
を当接させている。ここで、ピストン部材１０の
凹球部１１の底部を形成する球面の曲率半径Ｒに
対し、ピストン部材１２における凸球部１３の球
部曲率半径ｒはＲ＞ｒとなる関係に定められてお
り、ピストン部材１０の凹球部１１に対し、ロツ
ド部材の１２の凸球部１３の当接は、ほぼ点接触
となり、且つ当接位置はピストン部材１０の中心
軸線１５に調芯されている。 The piston member 10 has a concave spherical portion 11 formed at its rear end facing the rod, and a convex spherical portion 13 is integrally formed at the tip of the rod member 12. 12 convex sphere parts 13
are in contact with each other. Here, with respect to the radius of curvature R of the spherical surface forming the bottom of the concave spherical part 11 of the piston member 10, the radius of curvature r of the convex spherical part 13 in the piston member 12 is set in a relationship such that R>r. The twelve convex spherical portions 13 of the rod member contact the concave spherical portion 11 of the piston member 10 almost in point contact, and the abutment position is aligned with the central axis 15 of the piston member 10.
次に第２図に示した本考案のアクチユエータピ
ストン構造の作用を説明する。 Next, the operation of the actuator piston structure of the present invention shown in FIG. 2 will be explained.
まず、マスタシリンダからの液圧Ｐ１の上昇に
よる制動で制動減速度が設定値に達すると、Ｇボ
ール６′が前進してバルブシート５に当接し、ア
クチユエータピストンに対し液圧PGを封じ込め
る。このように液圧PGが封じ込められるまでの
マスタシリンダよりの液圧Ｐ１の上昇に応じてピ
ストン部材１０がロツド部材１２を介してスプリ
ング８，９及び９′を圧縮して移動するようにな
る。ピストン部材１０の移動によるスプリング８
〜９′の圧縮に対し、スプリング８〜９′のそれぞ
れは、所定のねじれ角をもつているため、圧縮に
よる軸方向のスプリング力に加えて横方向にずれ
ようとする反力を生じ、それが偏荷重としてロツ
ド部材１２に作用し、偏荷重を受けたロツド部材
１２は中心軸線１５に対し、僅かな傾きを持つよ
うになる。このロツド部材１２の傾きはピストン
部材１０の凹球部１１に当接した凸球部１３との
当接点を支点とした傾きとなり凹球部１３のピス
トン部材１０に対する当接位置が中心軸線１５か
ら外れることはない。従つてロツド部材１２がス
プリングの偏荷重で傾いてもピストン部材１０は
常に中心軸線１５においてスプリングのセツト荷
重を受けることとなり、液圧によりピストン部材
１０が移動しても、シリンダ壁との間にこじれを
起こさずＧボール６′の前進で液圧PGが封じ込め
られると、この封じ込め液圧PGに応じたピスト
ン部材１０の移動量で定まるスプリングの圧縮力
を液圧制御機構の制御ピストン２に与えることと
なり、封じ込め液圧PGに対応した正確な減圧制
御開始点を設定することが出来る。 First, when the braking deceleration reaches the set value due to braking due to an increase in the hydraulic pressure P1 from the master cylinder, the G ball 6' moves forward and comes into contact with the valve seat 5, sealing the hydraulic pressure PG against the actuator piston. . In this way, as the hydraulic pressure P1 from the master cylinder increases until the hydraulic pressure PG is contained, the piston member 10 compresses the springs 8, 9 and 9' via the rod member 12 and moves. Spring 8 due to movement of piston member 10
In response to compression of ~9', each of springs 8 to 9' has a predetermined torsion angle, so in addition to the axial spring force due to compression, a reaction force that tends to shift in the lateral direction is generated. acts on the rod member 12 as an unbalanced load, and the rod member 12 that has received the unbalanced load has a slight inclination with respect to the central axis 15. The inclination of the rod member 12 is such that the point of contact with the convex spherical part 13 in contact with the concave spherical part 11 of the piston member 10 is the fulcrum, and the position of contact of the concave spherical part 13 with respect to the piston member 10 is shifted from the central axis 15. It never comes off. Therefore, even if the rod member 12 is tilted due to the unbalanced load of the spring, the piston member 10 will always receive the set load of the spring at the center axis 15, and even if the piston member 10 moves due to hydraulic pressure, there will be no gap between it and the cylinder wall. When the hydraulic pressure PG is contained by the advance of the G ball 6' without twisting, a compressive force of the spring determined by the amount of movement of the piston member 10 according to this contained hydraulic pressure PG is applied to the control piston 2 of the hydraulic pressure control mechanism. Therefore, it is possible to set an accurate depressurization control start point corresponding to the containment hydraulic pressure PG.
以上の説明から明らかなように、本考案によれ
ば、スプリングによる荷重を常にアクチユエータ
ピストンの中心軸線に集中してかけることが出来
るので液圧の上昇でアクチユエータピストンが移
動してもシリンダ壁との間にこじれを起こさず、
設定減速度に達したときの封じ込め液圧に基づい
て液圧制御機構の減圧制御開始点を正確に設定す
ることが出来、又アクチユエータピストンがこじ
れを起さないことからアクチユエータピストンに
設けたシールの耐久性を向上することが出来ると
いう効果が得られる。 As is clear from the above explanation, according to the present invention, the load by the spring can always be concentrated on the center axis of the actuator piston, so even if the actuator piston moves due to an increase in hydraulic pressure. without causing any distortion between the cylinder wall and the cylinder wall.
The pressure reduction control start point of the hydraulic pressure control mechanism can be accurately set based on the containment hydraulic pressure when the set deceleration is reached, and since the actuator piston does not twist, it is possible to The effect is that the durability of the provided seal can be improved.
第１図は従来例を示した断面図、第２図は本考
案の一実施例を示した断面図である。
１：弁本体、２：制御ピストン、３：ポペツト
弁、４：弁座、５：バルブシート、６，６′：Ｇ
ボール、８，９，９′：スプリング、１０：ピス
トン部材、１１：凹球部、１２：ロツド部材、１
３：凸球部、１４：シール、１５：中心軸線、１
６：プレート。
FIG. 1 is a sectional view showing a conventional example, and FIG. 2 is a sectional view showing an embodiment of the present invention. 1: Valve body, 2: Control piston, 3: Poppet valve, 4: Valve seat, 5: Valve seat, 6, 6': G
Ball, 8, 9, 9': Spring, 10: Piston member, 11: Concave sphere, 12: Rod member, 1
3: Convex sphere, 14: Seal, 15: Center axis, 1
6: Plate.
Claims (1)
アクチユエータピストンへの制動液圧を封じ込
め、該封じ込め液圧によるアクチユエータピス
トンの移動で定まるスプリングの押圧で液圧制
御機構に対する減圧制御開始点を設定する荷重
応答型液圧制御弁において、 前記アクチユエータピストンを、封じ込め液
圧が作用するピストン部材と該ピストン部材の
押圧力を前記スプリングに伝達するロツド部材
とに分割し、前記ピストン部材の後端に形成し
た凹球部に前記ロツド部材の先端に形成した凸
球部を当接させたことを特徴とする荷重応答型
液圧制御弁。 (2) 前記ピストン部材の凹球部と前記ロツド部材
の凸球部の曲率が相異なる実用新案登録請求の
範囲第１項記載の荷重応答型液圧制御弁。[Claims for Utility Model Registration] (1) When the set deceleration is obtained, the braking fluid pressure to the actuator piston is sealed by the operation of the inertia valve, and the movement of the actuator piston is determined by the containment fluid pressure. In a load-responsive hydraulic control valve that sets a pressure reduction control start point for a hydraulic pressure control mechanism by the pressure of a spring, the actuator piston is confined by a piston member on which hydraulic pressure acts, and the pressing force of the piston member is controlled by the spring. A load-responsive hydraulic pressure control characterized in that the piston member is divided into a rod member that transmits the force to the piston member, and a convex spherical portion formed at the tip of the rod member is brought into contact with a concave spherical portion formed at the rear end of the piston member. valve. (2) The load-responsive hydraulic control valve according to claim 1, wherein the concave spherical portion of the piston member and the convex spherical portion of the rod member have different curvatures.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17282482U JPS5976462U (en) | 1982-11-15 | 1982-11-15 | Load responsive hydraulic control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17282482U JPS5976462U (en) | 1982-11-15 | 1982-11-15 | Load responsive hydraulic control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5976462U JPS5976462U (en) | 1984-05-24 |
| JPH0212134Y2 true JPH0212134Y2 (en) | 1990-04-05 |
Family
ID=30376628
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17282482U Granted JPS5976462U (en) | 1982-11-15 | 1982-11-15 | Load responsive hydraulic control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5976462U (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57104453A (en) * | 1980-12-22 | 1982-06-29 | Akebono Brake Ind Co Ltd | Decelerated speed detecting liquid pressure controller |
-
1982
- 1982-11-15 JP JP17282482U patent/JPS5976462U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57104453A (en) * | 1980-12-22 | 1982-06-29 | Akebono Brake Ind Co Ltd | Decelerated speed detecting liquid pressure controller |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5976462U (en) | 1984-05-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO1982000445A1 (en) | Vehicular suspension | |
| JPH01218948A (en) | Car load response type braking compensator | |
| USRE38327E1 (en) | Brake apparatus having an improved brake feel | |
| JP2001065542A (en) | Ball joint with supporting liner | |
| JPS5853620B2 (en) | Vehicle load sensing device | |
| JPH0212134Y2 (en) | ||
| US3695735A (en) | Braking pressure correcting valve control devices | |
| US4925251A (en) | Brake corrector subject to the load of a vehicle as a function of the seating of the latter | |
| US5302006A (en) | Brake regulator with lever and improved response time | |
| JPH032707B2 (en) | ||
| JPH07257132A (en) | Vehicle suspension device | |
| JPH08230633A (en) | Dual system type load-correspondent hydraulic control valve device | |
| JPH0216929Y2 (en) | ||
| JP2538670Y2 (en) | Load response type hydraulic controller | |
| JPS6228507Y2 (en) | ||
| JPS6444259U (en) | ||
| JP2514481Y2 (en) | Negative pressure booster | |
| GB1448910A (en) | Brake valve operating devices for fluid pressure control | |
| JP4331352B2 (en) | Installation method of load responsive brake fluid pressure control valve | |
| JPS6015500B2 (en) | Vehicle brake hydraulic control device | |
| JPH06135308A (en) | Valve mechanism | |
| JPH0226966U (en) | ||
| JPS63301160A (en) | Tandem type negative pressure booster | |
| JPS56103646A (en) | Mounted load response type braking liquid pressure control means for vehicle | |
| JPS5766058A (en) | Load sensing valve for car |