JPH023046B2 - - Google Patents
Info
- Publication number
- JPH023046B2 JPH023046B2 JP55078656A JP7865680A JPH023046B2 JP H023046 B2 JPH023046 B2 JP H023046B2 JP 55078656 A JP55078656 A JP 55078656A JP 7865680 A JP7865680 A JP 7865680A JP H023046 B2 JPH023046 B2 JP H023046B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- oil
- chamber
- piston
- hydraulic
- 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
- 230000001603 reducing effect Effects 0.000 abstract description 7
- 239000003921 oil Substances 0.000 description 31
- 238000005336 cracking Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
この発明は、回転軸および固定側部材にそれぞ
れ設けられた摩擦板に作用する押付力を、ばねと
油圧による力との釣合いで変化させる制動装置に
関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a braking device that changes the pressing force acting on friction plates provided on a rotating shaft and a stationary side member, depending on the balance between the forces caused by a spring and hydraulic pressure.
つぎに、この種の従来の制動装置の一例を第１
図により説明する。 Next, an example of this type of conventional braking device will be described below.
This will be explained using figures.
油圧モータの出力軸２は固定部材であるモータ
ケーシング１を貫通しており、モータケーシング
１の内部の室には、回転がわの摩擦板４、固定が
わの摩擦板５、両摩擦板４，５の結合、切離しを
行うばね８、ピストン７がおさめられている。摩
擦板４は出力軸２にその軸方向には移動できるが
出力軸２に対しては回転できないようにスプライ
ン構造により結合されており、摩擦板５はモータ
ケーシング１にその軸方向には移動できるがモー
タケーシング１に対しては回転できないようにス
プライン構造により結合されており、両摩擦板
４，５は交互に配置されている。モータケーシン
グ１の室の両がわの壁部には、それぞれオイルシ
ール１０，３が取付けられている。ピストン７の
外壁面部とモータケーシング１の室の壁面部との
間には油圧室９が設けられており、その油圧室９
には油路６が接続されている。 The output shaft 2 of the hydraulic motor passes through a motor casing 1, which is a fixed member, and the internal chamber of the motor casing 1 includes a friction plate 4 on the rotating side, a friction plate 5 on the fixed side, and both friction plates 4. , 5, and a piston 7 are housed therein. The friction plate 4 is connected to the output shaft 2 by a spline structure so that it can move in the axial direction but cannot rotate with respect to the output shaft 2, and the friction plate 5 can move in the axial direction to the motor casing 1. is connected to the motor casing 1 by a spline structure so as not to rotate, and both friction plates 4 and 5 are arranged alternately. Oil seals 10 and 3 are attached to the walls on both sides of the chamber of the motor casing 1, respectively. A hydraulic chamber 9 is provided between the outer wall surface of the piston 7 and the wall surface of the chamber of the motor casing 1.
An oil passage 6 is connected to.
この制動装置は、ばね８の力でピストン７を介
して両摩擦板４，５が押付けられることにより制
動作用が行われる。油路６から油圧室９に圧油を
供給し、ピストン７を介してばね８を押し縮め、
摩擦板４，５に作用する押付力を減少させれば制
動が解かれる。 This braking device performs a braking action by pressing both friction plates 4 and 5 through a piston 7 with the force of a spring 8. Supplying pressure oil from the oil passage 6 to the hydraulic chamber 9 and compressing the spring 8 via the piston 7,
The braking is released by reducing the pressing force acting on the friction plates 4 and 5.
第２図はピストン７に油路６からの圧油を供給
する複数の受圧ピストン１１を配置した従来の他
の制動装置を示し、同図中第１図と同じ符号をつ
けたものは、同じもの、もしくは相当するものを
表わす。この制動装置の作動は、さきに説明した
ものと同様である。 FIG. 2 shows another conventional braking device in which a plurality of pressure-receiving pistons 11 are arranged to supply pressure oil from an oil passage 6 to a piston 7. In the figure, the same reference numerals as in FIG. represents something or something equivalent. The operation of this braking device is similar to that previously described.
一般に、上述の制動装置における制動を解除す
る圧力は、油圧モータの最高使用圧力に対して非
常に小さな値を設定し1/10〜1/20以下になること
がある。油圧モータに作用する圧力で制動解除を
行う、いわゆるネガテイブブレーキ付油圧モータ
では、ピストン７の発生する押付力は、油圧モー
タが最高使用圧力で作用すると、ばね８を押し縮
めるのに必要な値の10〜20倍以上の大きな力とな
る。第４図のＡはその押付力の一例を表わす。同
図において、横軸は回路圧力を表わし、縦軸は押
付力を表わす。前記の大きな押付力に耐え得るた
めに、モータケーシング１等は大きな強度を要求
され、したがつて、大形で重いものになる。また
制動装置に作用する圧力を制限するため、減圧弁
を設けたものもあるが、それでは減圧弁の分、原
価が高くなり、また、減圧作用のための圧油の漏
れがあり、圧油の有効利用で問題がある。 Generally, the pressure for releasing the brake in the above-mentioned braking device is set to a very small value and may be 1/10 to 1/20 of the maximum working pressure of the hydraulic motor. In a hydraulic motor with a so-called negative brake, in which braking is released by the pressure applied to the hydraulic motor, the pressing force generated by the piston 7 is equal to the value necessary to compress the spring 8 when the hydraulic motor is applied at its maximum operating pressure. It becomes 10 to 20 times more powerful. A in FIG. 4 represents an example of the pressing force. In the figure, the horizontal axis represents circuit pressure, and the vertical axis represents pressing force. In order to withstand the above-mentioned large pressing force, the motor casing 1 and the like are required to have great strength, and therefore are large and heavy. In addition, some models are equipped with a pressure reducing valve to limit the pressure acting on the braking device, but this increases the cost due to the pressure reducing valve, and there is also a risk of leakage of pressure oil for the pressure reducing effect. There are problems with effective use.
この発明は、減圧弁を使用せずに、制動解除用
のピストンの押付力を制限できる制動装置を提供
することを目的とするもので、回転軸および固定
側部材にそれぞれ設けられた摩擦板に作用する押
付力を、ばねと油圧による力との釣合いで変化さ
せる制動装置において、油圧を前記押付力に変換
する第１、第２受圧手段を設け、予め設定された
所定の圧力以下で第１、第２受圧手段の両方に圧
油の供給油路を連通させる第１の切換位置と、予
め設定された所定の圧力以上で第１受圧手段に圧
油の供給油路を連通させると共に、第２受圧手段
を油タンクに連通させる第２の切換位置とを備え
た切換弁を、第１、第２受圧手段と圧油の供給油
路とに接続させたことを特徴とする制動装置。 An object of the present invention is to provide a braking device that can limit the pressing force of a piston for braking release without using a pressure reducing valve. A braking device that changes the applied pressing force in accordance with the balance between the force generated by the spring and the hydraulic pressure, is provided with first and second pressure receiving means that convert the hydraulic pressure into the pressing force, and the first pressure is lower than a predetermined pressure. , a first switching position in which the pressure oil supply passage is communicated with both of the second pressure receiving means; A braking device characterized in that a switching valve having a second switching position that communicates two pressure receiving means with an oil tank is connected to the first and second pressure receiving means and a pressure oil supply line.
以下、この発明の一実施態様を第３図および第
４図により説明する。第３図において、第１図お
よび第２図と同じ符号をつけたものは、同じも
の、もしくは相当するものを表わす。 Hereinafter, one embodiment of the present invention will be explained with reference to FIGS. 3 and 4. In FIG. 3, the same reference numerals as in FIGS. 1 and 2 represent the same or equivalent components.
ピストン７の外壁面部とモータケーシング１の
室の壁面部との間には、ピストン７の外周面部に
取付けたＯリング１７により液密に区分した第１
受圧手段である第１油圧室（以下油圧室という）
９と第２受圧手段である第２油圧室（以下油圧室
という）１２との二つの油圧室が設けられてい
る。油圧室９には供給油路（以下油路という）６
が接続され、油圧室１２には油路１６が接続され
ている。油路１６の途中には油圧室１２を油路６
または油タンクに通じさせる切換弁１４が設けら
れており、切換弁１４のパイロツト油路１５は油
路６に接続されている。切換弁１４にはスプール
を図示の位置に保つばね１４が取付けられてい
る。 Between the outer wall surface of the piston 7 and the wall surface of the chamber of the motor casing 1, there is a first section partitioned fluid-tightly by an O-ring 17 attached to the outer circumferential surface of the piston 7.
The first hydraulic chamber (hereinafter referred to as the hydraulic chamber) is a pressure receiving means.
Two hydraulic chambers are provided: a hydraulic chamber 9 and a second hydraulic chamber (hereinafter referred to as hydraulic chamber) 12 which is a second pressure receiving means. The hydraulic chamber 9 has a supply oil passage (hereinafter referred to as oil passage) 6.
is connected to the hydraulic chamber 12, and an oil passage 16 is connected to the hydraulic chamber 12. The hydraulic chamber 12 is connected to the oil passage 6 in the middle of the oil passage 16.
Alternatively, a switching valve 14 that communicates with the oil tank is provided, and a pilot oil passage 15 of the switching valve 14 is connected to the oil passage 6. A spring 14 is attached to the switching valve 14 to maintain the spool in the position shown.
制動装置の制動を解除する場合には油路６に圧
油を圧油源から給送する。最初切換弁１３はばね
１４の作用により図示の第１の切換位置に保たれ
ており、圧油は油路６を経て油圧室９に供給され
るとともに、切換弁１３、油路１６を経て油圧室
１２に供給される。両方の油圧室９，１２により
発生するピストン７の押付力がばね８を押し縮
め、制動を解除するのに必要な値F1になつた時
の圧力P1をクラツキング圧という。さらに圧力
が上昇し、油圧室９で発生する押付力がF1より
大きくなつたとき、この圧力をP2とする。ばね
１４はパイロツト油路１５からの圧力がP2に達
したとき切換弁１３が第３図の逆の位置である第
２の切換位置に切換えられるように設定されてい
る。したがつて、この時点で、油圧室１２は切換
弁１３を介して油タンクに連通し、押付力は発生
しない。このため、ピストン７の押付力は油圧室
９により発生する押付力Ｃとなる。圧力がさらに
上昇し、油圧モータの最高使用圧力に達した場合
でも、ピストン７の押付力は油圧室９により発生
するだけで、その値はF2となる。 When the brake of the brake device is released, pressure oil is supplied to the oil passage 6 from a pressure oil source. Initially, the switching valve 13 is kept at the first switching position shown in the figure by the action of the spring 14, and pressure oil is supplied to the hydraulic chamber 9 via the oil passage 6, and the hydraulic oil is supplied via the switching valve 13 and the oil passage 16 to the hydraulic pressure chamber 9. It is supplied to chamber 12. The pressure P 1 when the pressing force of the piston 7 generated by both hydraulic chambers 9 and 12 compresses the spring 8 and reaches the value F 1 necessary to release the brake is called cracking pressure. When the pressure further increases and the pressing force generated in the hydraulic chamber 9 becomes greater than F1 , this pressure is defined as P2 . The spring 14 is set so that when the pressure from the pilot oil line 15 reaches P2 , the switching valve 13 is switched to a second switching position, which is the opposite position in FIG. Therefore, at this point, the hydraulic chamber 12 communicates with the oil tank via the switching valve 13, and no pressing force is generated. Therefore, the pressing force of the piston 7 becomes the pressing force C generated by the hydraulic chamber 9. Even if the pressure increases further and reaches the maximum working pressure of the hydraulic motor, the pressing force of the piston 7 is only generated by the hydraulic chamber 9, and its value becomes F2 .
油路の圧力が低下した時は、圧力P2において
圧力室１２にも圧油が供給されるので、クラツキ
ング圧P1に下がるまで制動が作用することはな
い。 When the pressure in the oil passage decreases, pressure oil is also supplied to the pressure chamber 12 at pressure P2 , so braking is not applied until the pressure decreases to cracking pressure P1 .
なお、第４図の線Ｂはこの発明による押付力の
変化を示す。 Note that line B in FIG. 4 shows the change in pressing force according to the present invention.
円周上に油圧ピストン１１を配置した制動装置
では、それらのピストン１１を二群に区分し、上
記と同様な切換えを行うように構成すればよい。 In a braking device in which hydraulic pistons 11 are arranged on the circumference, the pistons 11 may be divided into two groups and configured to perform switching in the same manner as described above.
以上説明したこの発明によれば、減圧弁を設置
しないで制動解除用ピストンの押付力を容易に制
限でき、したがつて、制動装置を小形、軽量化す
ることができるとともに流体損失が非常に小さく
なる。また、油圧室のいずれかのシールが破損し
ても、残りの圧力室を利用して緊急の制動解除を
行うことができる。 According to the invention described above, the pressing force of the brake release piston can be easily limited without installing a pressure reducing valve, and therefore, the brake device can be made smaller and lighter, and the fluid loss is extremely small. Become. Furthermore, even if any of the seals in the hydraulic chambers is damaged, the remaining pressure chambers can be used to perform emergency brake release.
第１図、第２図はそれぞれ従来の制動装置を示
す断面側面図、第３図はこの発明の一実施態様を
示す断面側面図、第４図は制動装置における油圧
力とピストン押付力との関係を示す説明図であ
る。
１……モータケーシング、２……出力軸、４…
…摩擦板、５……摩擦板、６……供給油路、７…
…ピストン、８……ばね、９……油圧室、１２…
…油圧室、１３……切換弁、１４……ばね、１５
……パイロツト油路、１６……油路。
1 and 2 are cross-sectional side views showing a conventional braking device, FIG. 3 is a cross-sectional side view showing an embodiment of the present invention, and FIG. 4 is a diagram showing the relationship between hydraulic pressure and piston pressing force in the braking device. It is an explanatory diagram showing a relationship. 1...Motor casing, 2...Output shaft, 4...
...Friction plate, 5...Friction plate, 6...Supply oil path, 7...
...Piston, 8...Spring, 9...Hydraulic chamber, 12...
...Hydraulic chamber, 13...Switching valve, 14...Spring, 15
...Pilot oil road, 16...Oil road.
Claims (1)
た摩擦板に作用する押付力を、ばねと油圧による
力との釣合いで変化させる制動装置において、油
圧を前記押付力に変換する第１、第２受圧手段を
設け、予め設定された所定の圧力以下で第１、第
２受圧手段の両方に圧油の供給油路を連通させる
第１の切換位置と、予め設定された所定の圧力以
上で第１受圧手段に圧油の供給油路を連通させる
と共に、第２受圧手段を油タンクに連通させる第
２の切換位置とを備えた切換弁を、第１、第２受
圧手段と圧油の供給油路とに接続させたことを特
徴とする制動装置。1. In a braking device that changes the pressing force acting on friction plates provided on the rotating shaft and the stationary side member, depending on the balance between the force caused by the spring and the hydraulic pressure, first and second receiving pressures convert the hydraulic pressure into the pressing force. a first switching position in which the pressure oil supply passage is communicated with both the first and second pressure receiving means when the pressure is below a preset predetermined pressure; A switching valve having a second switching position that communicates the pressure oil supply passage with the pressure receiving means and a second switching position that communicates the second pressure receiving means with the oil tank is connected to the first and second pressure receiving means and the pressure oil supply passage. A braking device characterized in that it is connected to a road.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7865680A JPS576139A (en) | 1980-06-10 | 1980-06-10 | Braking system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7865680A JPS576139A (en) | 1980-06-10 | 1980-06-10 | Braking system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS576139A JPS576139A (en) | 1982-01-13 |
| JPH023046B2 true JPH023046B2 (en) | 1990-01-22 |
Family
ID=13667896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7865680A Granted JPS576139A (en) | 1980-06-10 | 1980-06-10 | Braking system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS576139A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101922524A (en) * | 2010-09-17 | 2010-12-22 | 中钢集团衡阳重机有限公司 | Enclosed multi-disc wet type braking device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5055930A (en) * | 1973-09-20 | 1975-05-16 | ||
| JPS533388B2 (en) * | 1973-10-04 | 1978-02-06 |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4057297A (en) * | 1976-06-28 | 1977-11-08 | Beck Henry E | Brake mechanism with spring applied fluid pressure released assembly |
-
1980
- 1980-06-10 JP JP7865680A patent/JPS576139A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5055930A (en) * | 1973-09-20 | 1975-05-16 | ||
| JPS533388B2 (en) * | 1973-10-04 | 1978-02-06 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS576139A (en) | 1982-01-13 |
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