JPH083682Y2 - Relief valve for brake circuit - Google Patents
Relief valve for brake circuitInfo
- Publication number
- JPH083682Y2 JPH083682Y2 JP1989011585U JP1158589U JPH083682Y2 JP H083682 Y2 JPH083682 Y2 JP H083682Y2 JP 1989011585 U JP1989011585 U JP 1989011585U JP 1158589 U JP1158589 U JP 1158589U JP H083682 Y2 JPH083682 Y2 JP H083682Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- main valve
- valve seat
- piston
- 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 - Lifetime
Links
- 230000001105 regulatory effect Effects 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 230000000903 blocking effect Effects 0.000 claims description 2
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002040 relaxant effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Safety Valves (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Description
【考案の詳細な説明】 〔産業上の利用分野〕 本考案は、油圧ショベルやクレーン等の慣性体（負
荷）の駆動装置に使用される、慣性体駆動時等の油圧の
昇圧を制御して、衝撃の発生を防止するブレーキ回路用
リリーフ弁に関するものである。[Detailed Description of the Invention] [Industrial field of application] The present invention controls boosting of hydraulic pressure when driving an inertial body (load) used in a drive device for an inertial body (load) such as a hydraulic excavator and a crane. The present invention relates to a relief valve for a brake circuit that prevents the occurrence of impact.
従来、ブレーキ回路用リリーフ弁は、第３図（特公昭
52−23034号）に開示されるものがある。Conventionally, a relief valve for a brake circuit is shown in Fig. 3
52-23034).
以下、このブレーキ回路用リリーフ弁１について説明
するが、このブレーキ回路用リリーフ弁１は、弁座筒50
を中心にして左右対象であるので、その右側の構成につ
いてのみ説明し、左側の構成は、同一番号にダッシュを
付けて示し、その詳細な説明を省く。Hereinafter, the relief valve 1 for the brake circuit will be described. The relief valve 1 for the brake circuit is a valve seat cylinder 50.
Since it is a left-right symmetry centering around, only the configuration on the right side will be described, and the configuration on the left side will be indicated by attaching the same number with a dash, and detailed description thereof will be omitted.
この、ブレーキ回路用リリーフ弁１は、弁本体３の中
央に配置された内孔２内に移動可能に弁座筒50を設け、
この弁座筒50には、クロスオーバ通路18が設けられてお
り、このクロスオーバ通路18の開口端に当接可能に絞り
孔22を有する主弁51が配置されている。この主弁51は、
ピストン52によって押圧される調圧バネ10が当接してい
る。このピストン52は、弁本体３との間に圧力室20を形
成してあり、この圧力室20は、主弁51とピストン52とに
摺動自在に嵌入し通路を有するロッド27で連結してあ
る。主弁51に作用する油圧は、このロッド27の通路を介
して伝達されるようになっている。The brake circuit relief valve 1 is provided with a valve seat cylinder 50 movably in an inner hole 2 arranged in the center of the valve body 3.
A crossover passage 18 is provided in the valve seat cylinder 50, and a main valve 51 having a throttle hole 22 is disposed so as to be able to come into contact with the open end of the crossover passage 18. This main valve 51
The pressure adjusting spring 10 pressed by the piston 52 is in contact. The piston 52 forms a pressure chamber 20 between the piston 52 and the valve body 3, and the pressure chamber 20 is slidably fitted into the main valve 51 and the piston 52 and connected by a rod 27 having a passage. is there. The hydraulic pressure acting on the main valve 51 is transmitted through the passage of the rod 27.
なお、ロッド27と主弁51の嵌入部で形成される圧力室
26の断面積は、クロスオーバ通路18の断面積より小さく
なっている。従って、主弁51は、クロスオーバ通路18と
圧力室26との受圧面積の差に作用する油圧による押圧力
が調圧バネ10の押圧力を超えると作動する構成である。The pressure chamber formed by the rod 27 and the fitting portion of the main valve 51.
The cross-sectional area of 26 is smaller than the cross-sectional area of the crossover passage 18. Therefore, the main valve 51 is configured to operate when the pressing force by the hydraulic pressure that acts on the difference in the pressure receiving area between the crossover passage 18 and the pressure chamber 26 exceeds the pressing force of the pressure adjusting spring 10.
次に、作動について説明する。 Next, the operation will be described.
第３図において切換弁７を切換位置7Aに操作すると、
ポンプ８からの油圧は、カウンターバランス弁６を通り
通路a1、a2を経て流入し、モータ５を矢印方向に回転さ
せようとする。このとき通路a1、a2の圧力は、負担Ｗの
大きさに応じた値まで上昇する。When the switching valve 7 is operated to the switching position 7A in FIG. 3,
The hydraulic pressure from the pump 8 flows through the counter balance valve 6 and the passages a 1 and a 2 to try to rotate the motor 5 in the arrow direction. At this time, the pressure in the passages a 1 and a 2 rises to a value according to the magnitude of the burden W.
また、このとき通路a1、a2に作用する油圧により弁座
筒50が左方向に移動させられクロスオーバ通路18の左端
の開口部が主弁51′に当接する。他方主弁51にはその全
断面積に油圧が作用するので、右方向に移動しクロスオ
ーバ通路18の右端と主弁51との間が大きく開き通路を形
成する。この通路からクロスオーバ通路18を介して作用
した油圧は、主弁51′の絞り孔22′ピストン27′の通路
を介して圧力室20′に作用する。At this time, the valve seat cylinder 50 is moved leftward by the hydraulic pressure acting on the passages a 1 and a 2, and the opening at the left end of the crossover passage 18 comes into contact with the main valve 51 ′. On the other hand, since the hydraulic pressure acts on the entire cross-sectional area of the main valve 51, the main valve 51 moves to the right and a large open passage is formed between the right end of the crossover passage 18 and the main valve 51. The hydraulic pressure acting from this passage through the crossover passage 18 acts on the pressure chamber 20 'through the passage of the throttle hole 22' piston 27 'of the main valve 51'.
このため、ピストン52′は、絞り孔22′の開口面積と
圧力室20′の容量によって決まる時間t2の間に調圧バネ
10′を圧縮する。従って、通路a1、a2の圧力は、作動の
時間（ｔ）と圧力（ｐ）の関係を示す第４図の特性曲線
c1に示すように、時間t2の間に圧力p1からp2に上昇す
る。この特性曲線c1は、回路に衝撃が発生しない限界に
設定してある。Therefore, the piston 52 ', the throttle hole 22' pressure adjusting during determined time t 2 by the capacity of the opening area and the pressure chamber 20 'springs
Compress 10 '. Therefore, the pressure in the passages a 1 and a 2 is the characteristic curve of FIG. 4 showing the relationship between the operating time (t) and the pressure (p).
As shown by c 1 , the pressure rises from p 1 to p 2 during time t 2 . This characteristic curve c 1 is set to the limit at which no shock is generated in the circuit.
従って、この従来のブレーキ回路用リリーフ弁１は、
通路a1、a2の圧力が特性曲線c1を越えて上昇しようとし
たとき主弁51′が弁座筒50から離座させられ通路a1、a2
の圧力上昇を制限する。このため、切換弁７の急激な操
作などにより通路a1、a2に大流量が供給されても、通路
a1、a2の油圧は、特性曲線c1に沿って上昇するものであ
るから、通路a1、a2内の急激な圧力上昇による衝撃を防
止するものである。Therefore, this conventional brake circuit relief valve 1 is
When the pressure in the passages a 1 and a 2 tries to rise above the characteristic curve c 1 , the main valve 51 ′ is separated from the valve seat cylinder 50 and the passages a 1 and a 2
Limit the pressure rise of. Therefore, even if a large flow rate is supplied to the passages a 1 and a 2 due to a sudden operation of the switching valve 7,
Since the hydraulic pressures of a 1 and a 2 increase along the characteristic curve c 1 , the hydraulic pressures in the passages a 1 and a 2 are prevented from being impacted by a sudden pressure increase.
上記したブレーキ回路用リリーフ弁の調圧バネは、第
４図の特性曲線c1に示すように設定圧を低圧p1から高圧
p2迄変化させる必要があるので、そのバネ定数の値を小
さくし、調圧バネの変位量を大きくする必要がある。従
って、調圧バネの長さは、衝撃防止の機能を持たない通
常のリリーフ弁の調圧バネの長さより長くなる。そし
て、このような調圧バネが２本同一軸線上に配置される
従来のブレーキ回路用リリーフ弁は、その軸方向に長く
なる欠点を有する。The pressure regulating spring of the relief valve for the brake circuit described above changes the set pressure from the low pressure p 1 to the high pressure as shown by the characteristic curve c 1 in FIG.
Since it is necessary to change up to p 2, it is necessary to reduce the value of the spring constant and increase the displacement amount of the pressure adjusting spring. Therefore, the length of the pressure adjusting spring is longer than the length of the pressure adjusting spring of a normal relief valve that does not have a function of preventing impact. The conventional relief valve for a brake circuit, in which two pressure adjusting springs are arranged on the same axis, has the drawback of being elongated in the axial direction.
本考案は、調圧バネを１本にすることで上記の問題点
を解決しようとするものである。The present invention is intended to solve the above problems by using only one pressure adjusting spring.
上記の課題を解決するための本考案の手段は、弁本体
中央に内孔と、この内孔と給排回路とを連通する通路と
が設けられ、前記内孔に摺動自在に弁座筒を挿入し、こ
の弁座筒の両端のそれぞれに当接可能に主弁を配置し、
この主弁の軸線方向に調圧バネとピストンを配置し、こ
のピストンがそのピストンに関連する主弁側の油圧によ
り主弁側に移動し調圧バネのバネ力を増加させる構成と
したブレーキ回路用リリーフ弁において、 前記弁座筒を２分割し、この２つの弁座筒間に１本の
調圧バネを配置し、前記弁座筒の一端の主弁に関連する
ピストンがこの主弁を介して前記弁座筒を調圧バネの圧
縮方向に押圧すると共に、前記弁座筒の他端の前記主弁
に関連するピストンがこの主弁を介して前記弁座筒の後
退位置を規制し、前記通路と前記内孔との間に、前記主
弁と前記弁座筒とにより連通又は遮断される油路と並列
に、通路から内孔への流れを阻止する逆止弁を設けたこ
とを特徴とするものである。Means for solving the above-mentioned problems is to provide an inner hole in the center of a valve body and a passage for communicating the inner hole with a supply / discharge circuit, and the valve seat cylinder is slidable in the inner hole. , And arrange the main valve so that it can contact each of both ends of this valve seat cylinder,
A brake circuit in which a pressure regulating spring and a piston are arranged in the axial direction of the main valve, and the piston moves to the main valve side by the hydraulic pressure of the main valve side associated with the piston to increase the spring force of the pressure regulating spring. In the relief valve for a vehicle, the valve seat cylinder is divided into two, and one pressure adjusting spring is arranged between the two valve seat cylinders, and a piston associated with the main valve at one end of the valve seat cylinder operates the main valve. The valve seat cylinder is pressed through in the compression direction of the pressure adjusting spring via the piston, and the piston associated with the main valve at the other end of the valve seat cylinder regulates the retracted position of the valve seat cylinder via the main valve. A check valve is provided between the passage and the inner hole in parallel with an oil passage communicated with or cut off by the main valve and the valve seat cylinder to prevent a flow from the passage to the inner hole. It is characterized by.
切換弁７の切換位置を切り換えると、通路a1,a2に圧
力が発生する。この圧力により前記弁座筒11の一端の主
弁19に関連するピストン15が主弁19を介して調圧バネ10
を圧縮方向に移動させる。前記弁座筒11′の一端の主弁
19′に関連するピストン15′は主弁19′を介して調圧バ
ネ10の端を規制する。これにより、圧力に応じて調圧バ
ネ10を圧縮しバネ力が増加し、リリーフ圧を増加させ
る。このリリーフ圧以上の油圧が通路a1,a2に発生する
と、弁座筒11が調圧バネ10のバネ力に抗して主弁19より
離座する。これにより内孔２に油が流入し、逆止弁23′
を経て通路b1,b2に油を流出させる。その結果、図４に
示すようなリリーフ特性が得られる。なお、通路b1,b2
に圧力が発生する場合も同様である。When the switching position of the switching valve 7 is switched, pressure is generated in the passages a1 and a2. Due to this pressure, the piston 15 associated with the main valve 19 at one end of the valve seat cylinder 11 passes through the main valve 19 and adjusts the pressure of the spring 10.
Is moved in the compression direction. Main valve at one end of the valve seat cylinder 11 '
The piston 15 'associated with 19' limits the end of the pressure regulating spring 10 via the main valve 19 '. As a result, the pressure adjusting spring 10 is compressed according to the pressure, the spring force increases, and the relief pressure increases. When the hydraulic pressure equal to or higher than the relief pressure is generated in the passages a1 and a2, the valve seat cylinder 11 is separated from the main valve 19 against the spring force of the pressure adjusting spring 10. As a result, oil flows into the inner hole 2 and the check valve 23 '
The oil is discharged to the passages b1 and b2 via the. As a result, relief characteristics as shown in FIG. 4 are obtained. In addition, passages b1, b2
The same applies when pressure is generated in the.
本考案の実施例を示す第１図について説明する。 An embodiment of the present invention will be described with reference to FIG.
なお、第１図から明らかなように、このブレーキ回路
用リリーフ弁１は、調圧バネ10を中心にして左右対称で
あるので、その右側の構成についてのみ説明し、左側の
構成は、同一番号にダッシュを付けて示し、その詳細な
省く。As is apparent from FIG. 1, the brake circuit relief valve 1 is symmetrical with respect to the pressure adjusting spring 10, so only the configuration on the right side will be described and the configuration on the left side will be the same. Show with a dash and omit that detail.
このブレーキ回路用リリーフ弁１は、弁本体３の内孔
２に調圧バネ10と、この調圧ばね10に当接し、揺動自在
に嵌入する弁座筒11、11′が設けてある。この、弁座筒
11は、その中心に絞り孔13を備え、その右側に主弁19が
当接する弁座13aを構成してあり、その右側には、ピス
トン型摺動体14が摺動自在に嵌入する筒体28を設けてあ
る。また、弁座筒11には、スリット12が設けてあり、内
孔２に流入した圧油は、自由に通過できるようになって
いる。The brake circuit relief valve 1 is provided with a pressure adjusting spring 10 in an inner hole 2 of a valve body 3 and valve seat cylinders 11 and 11 'which are in contact with the pressure adjusting spring 10 and are swingably fitted therein. This valve seat cylinder
The reference numeral 11 designates a valve seat 13a on the right side of which a throttle hole 13 is provided, and the main valve 19 abuts on the right side thereof. Is provided. Further, the valve seat cylinder 11 is provided with a slit 12 so that the pressure oil flowing into the inner hole 2 can freely pass therethrough.
主弁19は、内孔２とほぼ同径に形成した内孔2aに摺動
自在に嵌入するピストン15に一体的に形成された筒体の
形状であり、その先端が、前記弁座13aに当接しその内
部にクロスオーバ通路18を有する。主弁19のクロスオー
バ通路18は、通路17を介して通路a1、a2に連通すると共
に、絞り孔22を介して圧力室20に連通する。The main valve 19 is in the shape of a cylinder integrally formed with a piston 15 which is slidably fitted in an inner hole 2a formed to have substantially the same diameter as that of the inner hole 2, and the tip of the main valve 19 is attached to the valve seat 13a. It abuts and has a crossover passage 18 therein. The crossover passage 18 of the main valve 19 communicates with the passages a 1 and a 2 via the passage 17 and also communicates with the pressure chamber 20 via the throttle hole 22.
なお、第２図に示すように、主弁19の先端が弁座13a
に当接する当接部の直径d2は、圧力室26の内径の直径d1
より大きい直径となっており、弁座筒11の押圧力は当接
部と圧力室の受圧面積の差に作用する油圧力と調圧バネ
10のバネ力の差によるものとなる。従って、直径d2と直
径d1との差を小さくすると押圧力が小さくなる。As shown in FIG. 2, the tip of the main valve 19 has a valve seat 13a.
The diameter d 2 of the abutting portion that abuts against the inner diameter of the pressure chamber 26 is d 1
The pressure of the valve seat cylinder 11 has a larger diameter, and the pressing force of the valve seat cylinder 11 acts on the difference in the pressure receiving area between the contact portion and the pressure chamber.
This is due to the difference in spring force of 10. Therefore, when the difference between the diameter d 2 and the diameter d 1 is reduced, the pressing force is reduced.
また、主弁19の外周には、逆止弁23が摺動自在に配置
してあり、この逆止弁23で通路a1、a2から内孔２方向へ
の圧油の流通を阻止している。この逆止弁23は、内孔２
に摺動自在に嵌入する部分にスリット25を設けてあり、
ピストン15に一端が当接するスプリング24で内孔２の端
部で形成される弁座2cに押圧されている。Further, a check valve 23 is slidably arranged on the outer periphery of the main valve 19, and the check valve 23 prevents the flow of pressure oil from the passages a 1 and a 2 toward the inner hole 2. ing. This check valve 23 has an inner hole 2
The slit 25 is provided in the part that slidably fits into
A spring 24, one end of which abuts against the piston 15, is pressed against a valve seat 2c formed at the end of the inner hole 2.
以上の構成を有する実施例の作用について述べる。 The operation of the embodiment having the above configuration will be described.
第１図において、切換弁７を切換位置7Aに操作すると
ポンプ８からの油圧は、カウンターバランス弁６を介し
て通路a1、a2を経てモータ５に流入する。この時通路
a1、a2内の油圧は、通路17からクロスオーバ通路18に到
り、更に、絞り孔22を介して圧力室20に作用すると同時
に圧力室26に作用する。圧力室26に作用した油圧は、ピ
ストン型摺動体14を左方向で反対側のピストン型摺動体
14′に当接するまで押圧する。同時に圧力室20に流入す
る圧油によりピストン15が左の方向に作動しはじめる。In FIG. 1, when the switching valve 7 is operated to the switching position 7A, the hydraulic pressure from the pump 8 flows into the motor 5 via the counter balance valve 6 and the passages a 1 and a 2 . At this time the passage
The hydraulic pressures in a 1 and a 2 reach the crossover passage 18 from the passage 17 and further act on the pressure chamber 20 via the throttle hole 22 and simultaneously act on the pressure chamber 26. The hydraulic pressure acting on the pressure chamber 26 causes the piston type sliding body 14 to move to the left side in the opposite direction.
Press until it touches 14 '. At the same time, the pressure oil flowing into the pressure chamber 20 causes the piston 15 to start operating in the left direction.
ピストン型摺動体14が、ピストン型摺動体14′に当接
すると前述のように、調圧バネ10に作用する弁座筒11の
油圧による押圧力が圧力室26と弁座13aと主弁19との当
接部の受面積の差の小さな値となるので設定圧は、第４
図の圧力P1に示す値となる。そして、更に時間が経過す
るとピストン15が左へ移動する。このためピストン15の
移動により弁座筒11を介して調圧バネ10が圧縮されるの
で、その設定圧は、第４図の特性曲線c1に示すように順
次上昇する。この特性曲線c1は衝撃が生じない限界に設
定してある。When the piston type sliding body 14 comes into contact with the piston type sliding body 14 ', as described above, the pressing force by the hydraulic pressure of the valve seat cylinder 11 acting on the pressure adjusting spring 10 causes the pressure chamber 26, the valve seat 13a, and the main valve 19 to move. Since the difference in the receiving area of the contact portion with
It becomes the value indicated by pressure P 1 in the figure. Then, when the time further passes, the piston 15 moves to the left. For this reason, the pressure adjusting spring 10 is compressed by the movement of the piston 15 via the valve seat cylinder 11, so that the set pressure thereof sequentially increases as shown by the characteristic curve c 1 in FIG. This characteristic curve c 1 is set to the limit at which no impact occurs.
したがって、通路a1、a2の油圧の時間に対する上昇の
割合が、特性曲線c1をこえると弁座筒11が主弁19より離
座させられ、通路a1、a2の圧油が内孔２から逆止弁23′
を介して通路b1、b2放出され、油圧の上昇が制限され
る。Therefore, when the rate of increase of the hydraulic pressure in the passages a 1 and a 2 exceeds the characteristic curve c 1 , the valve seat cylinder 11 is separated from the main valve 19, and the pressure oil in the passages a 1 and a 2 is Check valve 23 'from hole 2
The passages b 1 and b 2 are discharged via the valve and the increase in hydraulic pressure is limited.
従って、油圧の急激な上昇による衝撃を防止すること
が出来る。Therefore, it is possible to prevent an impact due to a sudden increase in hydraulic pressure.
以上、切換弁７を切換位置7Bに操作すると、通路b1、
b2の油圧が、主弁19′と弁座筒11′と調圧バネ10とによ
って、通路a1、a2の作動と同様に第４図の特性曲線c1に
沿った値に制御され、油圧による衝撃を防止する。As described above, when the switching valve 7 is operated to the switching position 7B, the passage b 1 ,
The hydraulic pressure of b 2 is controlled by the main valve 19 ′, the valve seat cylinder 11 ′ and the pressure adjusting spring 10 to a value along the characteristic curve c 1 of FIG. 4 as in the operation of the passages a 1 and a 2 . , Prevents impact due to hydraulic pressure.
本考案は、弁座筒を２分割し、この２つの弁座筒の間
に１本の調圧バネに配置し、この２つの弁座筒の各々に
当接可能に配置した主弁を前記ピストンにより押圧する
構成としたものであるので、ブレーキ回路用リリーフ弁
の軸方向への寸法を調圧バネ一本分短縮することが出来
る。According to the present invention, the valve seat cylinder is divided into two, one pressure adjusting spring is arranged between the two valve seat cylinders, and the main valve arranged so as to be able to come into contact with each of the two valve seat cylinders is described above. Since the piston is pressed, the dimension of the brake circuit relief valve in the axial direction can be shortened by one pressure adjusting spring.
また、内孔と通路が接続する通路との間に通路から内
孔への流れを阻止する逆止弁を、主弁の外周に設けたも
のであるので、径方向の寸法が逆止弁の分だけ増加す
る。Further, since the check valve for blocking the flow from the passage to the inner hole is provided between the inner hole and the passage connecting the passage on the outer circumference of the main valve, the size in the radial direction is larger than that of the check valve. Increase by minutes.
従って、ブレーキ回路用リリーフ弁の形状を正方形に
近くすることができる。このため、油圧モータ等の円形
の機器と組み合わせ易くなる効果を有する。Therefore, the shape of the relief valve for the brake circuit can be made close to a square. Therefore, there is an effect that it is easy to combine with a circular device such as a hydraulic motor.
また、弁座筒を２分割しその間に調圧バネを設置する
構成であるので、調圧バネの設置部所が内孔の全体とす
ることができるので、調圧バネの設計のバネのコイル径
方向への制限が緩和され調圧バネの設計が容易になる効
果がある。In addition, since the valve seat cylinder is divided into two and the pressure adjusting spring is installed between them, the installation portion of the pressure adjusting spring can be the entire inner hole. Therefore, the coil coil of the pressure adjusting spring is designed. This has the effect of relaxing the restriction in the radial direction and facilitating the design of the pressure regulating spring.
第１図は、本考案の一実施例のブレーキ回路用リリーフ
弁の断面図、第２図は、弁座筒と主弁との関係を示す部
分断面図、第３図は、従来のブレーキ回路用リリーフ弁
の断面図、第４図は、ブレーキ回路用リリーフ弁の特性
曲線図である。 １…ブレーキ回路用リリーフ弁、２…内孔、３…弁本
体、５…モータ、６…カウンターバランス弁、７…切換
弁、８…ポンプ、10…調圧バネ、11…弁座筒、12…スリ
ット、13…絞り孔、14…ピストン型摺動体、15…ピスト
ン、17…通路、18…クロスオーバ通路、19…主弁、20…
圧力室、22…絞り孔、23…逆止弁、24…スプリング、25
…スリット、26…圧力室、27…ロッド、28…筒体。FIG. 1 is a sectional view of a relief valve for a brake circuit according to an embodiment of the present invention, FIG. 2 is a partial sectional view showing the relationship between a valve seat cylinder and a main valve, and FIG. 3 is a conventional brake circuit. FIG. 4 is a sectional view of the relief valve for a vehicle, and FIG. 4 is a characteristic curve diagram of the relief valve for a brake circuit. 1 ... Brake circuit relief valve, 2 ... Inner hole, 3 ... Valve body, 5 ... Motor, 6 ... Counter balance valve, 7 ... Switching valve, 8 ... Pump, 10 ... Pressure adjusting spring, 11 ... Valve seat cylinder, 12 … Slits, 13… Throttle holes, 14… Piston-type sliding bodies, 15… Pistons, 17… Passages, 18… Crossover passages, 19… Main valves, 20…
Pressure chamber, 22 ... Throttle hole, 23 ... Check valve, 24 ... Spring, 25
… Slits, 26… pressure chambers, 27… rods, 28… cylindrical bodies.
Claims (1)
とを連通する通路とが設けられ、前記内孔に摺動自在に
弁座筒を挿入し、この弁座筒の両端のそれぞれに当接可
能に主弁を配置し、この主弁の軸線方向に調圧バネとピ
ストンを配置し、このピストンがそのピストンに関連す
る主弁側の油圧により主弁側に移動し調圧バネのバネ力
を増加させる構成としたブレーキ回路用リリーフ弁にお
いて、 前記弁座筒を２分割し、この２つの弁座筒間に１本の調
圧バネを配置し、前記弁座筒の一端の主弁に関連するピ
ストンがこの主弁を介して前記弁座筒を調圧バネの圧縮
方向に押圧すると共に、前記弁座筒の他端の前記主弁に
関連するピストンがこの主弁を介して前記弁座筒の後退
位置を規制し、前記通路と前記内孔との間に、前記主弁
と前記弁座筒とにより連通又は遮断される油路と並列
に、通路から内孔への流れを阻止する逆止弁を設けたこ
とを特徴とするブレーキ回路用リリーフ弁。1. An inner hole is provided at the center of the valve body, and a passage for communicating the inner hole with the supply / discharge circuit is provided. A valve seat cylinder is slidably inserted into the inner hole. The main valve is placed so that it can contact each of both ends, and the pressure adjusting spring and the piston are placed in the axial direction of this main valve, and this piston moves to the main valve side by the hydraulic pressure of the main valve side related to the piston. In a relief valve for a brake circuit configured to increase the spring force of a pressure regulating spring, the valve seat cylinder is divided into two, and one pressure regulating spring is arranged between the two valve seat cylinders. A piston associated with the main valve at one end of the main valve presses the valve seat cylinder through the main valve in the compression direction of the pressure adjusting spring, and a piston associated with the main valve at the other end of the valve seat cylinder is connected to the main valve. A retracted position of the valve seat cylinder is regulated via a valve, and the main valve and the valve seat are provided between the passage and the inner hole. A relief valve for a brake circuit, characterized in that a check valve for blocking a flow from a passage to an inner hole is provided in parallel with an oil passage that is communicated with or cut off by a cylinder.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989011585U JPH083682Y2 (en) | 1989-01-31 | 1989-01-31 | Relief valve for brake circuit |
| KR1019890017084A KR0149159B1 (en) | 1989-01-31 | 1989-11-24 | Relief Valve for Brake Circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1989011585U JPH083682Y2 (en) | 1989-01-31 | 1989-01-31 | Relief valve for brake circuit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02102001U JPH02102001U (en) | 1990-08-14 |
| JPH083682Y2 true JPH083682Y2 (en) | 1996-01-31 |
Family
ID=11781984
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1989011585U Expired - Lifetime JPH083682Y2 (en) | 1989-01-31 | 1989-01-31 | Relief valve for brake circuit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH083682Y2 (en) |
| KR (1) | KR0149159B1 (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5944299B2 (en) * | 1975-08-11 | 1984-10-29 | 三菱瓦斯化学株式会社 | Method for producing adduct of aromatic dicarboxylic acid and alkylene oxide |
| JPS56167903A (en) * | 1980-05-24 | 1981-12-23 | Hitachi Constr Mach Co Ltd | Hydraulic circuit of brake for hydraulic motor |
-
1989
- 1989-01-31 JP JP1989011585U patent/JPH083682Y2/en not_active Expired - Lifetime
- 1989-11-24 KR KR1019890017084A patent/KR0149159B1/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02102001U (en) | 1990-08-14 |
| KR0149159B1 (en) | 1998-10-15 |
| KR900012027A (en) | 1990-08-02 |
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