JPS6144002Y2 - - Google Patents
Info
- Publication number
- JPS6144002Y2 JPS6144002Y2 JP1980144492U JP14449280U JPS6144002Y2 JP S6144002 Y2 JPS6144002 Y2 JP S6144002Y2 JP 1980144492 U JP1980144492 U JP 1980144492U JP 14449280 U JP14449280 U JP 14449280U JP S6144002 Y2 JPS6144002 Y2 JP S6144002Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- hydraulic
- counterbalance
- relief valve
- 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
- 230000007935 neutral effect Effects 0.000 description 13
- 239000012530 fluid Substances 0.000 description 8
- 230000001133 acceleration Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
Description
【考案の詳細な説明】
本考案は、主にシヨベル、クレーンの慣性体旋
回系の液圧駆動装置のブレーキ回路に関するもの
である。[Detailed Description of the Invention] The present invention mainly relates to a brake circuit for a hydraulic drive device of an inertial body rotation system of a shovel or a crane.
この種の液圧駆動装置の慣性体制動過程におい
て、所定停止位置より手前で止まろうとする慣性
体を所定位置で停止させるべく少し加速操作を行
うと、カウンタバランス弁の応答遅れからブレー
キ側管路に瞬間的に異常な高圧（サージ圧）が発
生する。 In the inertial body movement process of this type of hydraulic drive device, if the inertial body that is about to stop before the predetermined stop position is slightly accelerated to stop at the predetermined position, the brake side pipe will be affected due to a delay in the response of the counterbalance valve. Abnormal high pressure (surge pressure) occurs momentarily.
これを説明する、第１図において、方向切換弁
１が位置Ａにあつてポンプ２からの吐出液が方向
切換弁１、カウンタバランス弁３の位置Ａ、主管
路４を経て油圧モータ５に流入し、油圧モータ５
からの排出液が主管路６、カウンタバランス弁
３、方向制御弁１を経てタンク７に還流して慣性
体（図示せず）がモータ５で駆動されている状態
から、方向切換弁１を中立位置に切換えると、ポ
ンプ２はタンク７に通じカウンタバランス弁３は
両端の圧力室がタンク７と連通して両端のばね８
により中立位置に切換わり、一方油圧モータ５は
慣性体の慣性力によりポンピングし、主管路４か
ら吸入したタンク側作動液を、カウンタバランス
弁３のチエツク弁でタンク側との連通を断たれた
主管路６へ排出するので、主管路６の液圧は急上
昇しその液圧が高圧設定のリリーフ弁９のセツト
圧を越えるとリリーフ弁９は開弁となり、リリー
フ弁９と油圧モータ５とを結ぶ閉回路を作動液が
循環し慣性体は急速に制動される。この制動過程
において、所定停止位置より手前で停止しようと
する慣性体の停止位置を補正すべく方向切換弁１
を中立位置から位置Ａに少しの間切換えて油圧モ
ータ５を加速すると、ポンプ液圧は最初カウンタ
バランス弁３の中立位置のチエツク弁、主管路４
を経て油圧モータ５に作用するが、ブレーキ側と
なる主管路６は最初カウンタバランス弁３の位置
Ａへの切換え遅れにより中立位置のチエツク弁で
ブロツクされたままとなるため、制御側主管路６
には高圧設定の残留ブレーキ圧に油圧モータ入口
圧力を加えたサージ圧が発生する。 To explain this, in FIG. 1, the directional control valve 1 is in position A, and the discharged liquid from the pump 2 flows into the hydraulic motor 5 through the directional control valve 1, the counterbalance valve 3 in position A, and the main pipe 4. and hydraulic motor 5
The discharged liquid flows back to the tank 7 through the main pipe 6, counterbalance valve 3, and directional control valve 1, and the inertial body (not shown) is driven by the motor 5, and then the directional control valve 1 is set to neutral. When switched to the position, the pump 2 communicates with the tank 7, the pressure chambers at both ends of the counterbalance valve 3 communicate with the tank 7, and the springs 8 at both ends communicate with the tank 7.
The hydraulic motor 5 was pumped by the inertial force of the inertial body, and the tank-side hydraulic fluid was sucked in from the main pipe 4, and communication with the tank side was cut off by the check valve of the counterbalance valve 3. Since the fluid is discharged to the main pipe 6, the hydraulic pressure in the main pipe 6 rises rapidly, and when the hydraulic pressure exceeds the set pressure of the relief valve 9, which is set to a high pressure, the relief valve 9 opens, and the relief valve 9 and the hydraulic motor 5 are connected to each other. The hydraulic fluid circulates through the closed circuit connecting the two, and the inertial body is rapidly braked. In this braking process, the directional control valve 1
When the hydraulic motor 5 is accelerated by switching from the neutral position to position A for a short period of time, the pump hydraulic pressure is initially applied to the neutral position check valve of the counterbalance valve 3 and the main line 4.
However, since the main line 6 on the brake side remains blocked by the check valve in the neutral position due to the delay in switching the counterbalance valve 3 to position A, the main line 6 on the control side
Surge pressure is generated by adding the hydraulic motor inlet pressure to the residual brake pressure set at high pressure.
本考案は前記の点に鑑みてなされたもので、前
記するように慣性体の制動過程において、方向切
換弁を加速位置に切換える操作（追代ち加速操
作）をしても制動側管路にサージ圧が発生しない
液圧駆動装置の提供を目的としている。 The present invention has been developed in view of the above points, and as mentioned above, during the braking process of the inertial body, even if the directional control valve is switched to the acceleration position (follow-up acceleration operation), the braking side pipe is The purpose is to provide a hydraulic drive device that does not generate surge pressure.
以下本考案の実施例を図面について説明する。
第２図において、１は方向切換弁、２はポンプ、
３はカウンタバランス弁、５は油圧モータ、７は
タンク、１０は主リリーフ弁である。１１、１１
はそれぞれ油圧モータ５を制動するためのベント
ポート付リリーフ弁、本実施例では差動形リリー
フ弁で、その圧力室１２、１２′は３位置４ポー
トパイロツト切換弁１３を介装したベント管路１
４、１４′によりカウンタバランス弁３の方向切
換弁１側の自身の差動形リリーフ弁の１次側通路
２０、２０′に接続する管路１５、１５′に接続さ
れている。パイロツト切換弁１３は、管路１５、
１５′が同圧のとき中立位置にあつてベント管路
１４、１４′をブロツクし、管路１５の圧が管路
１５′より高いとき位置Ａに、管路１５′の圧が管
路１５より高いとき位置Ｂに切換わり、位置Ａお
よび位置Ｂでは圧力室１２、１２′を管路１５、
１５′に連通する。 Embodiments of the present invention will be described below with reference to the drawings.
In Fig. 2, 1 is a directional valve, 2 is a pump,
3 is a counter balance valve, 5 is a hydraulic motor, 7 is a tank, and 10 is a main relief valve. 11, 11
are relief valves with vent ports for braking the hydraulic motor 5, and are differential type relief valves in this embodiment, and their pressure chambers 12 and 12' are vent pipes in which a 3-position, 4-port pilot switching valve 13 is interposed. 1
4 and 14', the counterbalance valve 3 is connected to conduits 15 and 15' which are connected to the primary passages 20 and 20' of its own differential relief valve on the directional control valve 1 side. The pilot switching valve 13 is connected to the pipe line 15,
15' is in the neutral position and blocks the vent lines 14, 14' when the pressure in line 15' is the same, and in position A when the pressure in line 15 is higher than that in line 15'. When the pressure is higher, it switches to position B, and in positions A and B, the pressure chambers 12, 12' are connected to the line 15,
15'.
前記差動形リリーフ弁の実施例を第３図につい
て説明すると、弁本体１６に嵌挿されたポペツト
１７は圧力室１２に内装されたばね１８で弁座１
９に押し当てられて１次側通路２０と２次側通路
２１の連通を断つと共に、閉弁時の弁座側受圧面
積A1を圧力室１２に位置する後端部の受圧面積
A2より大きく定め、一方、圧力室１２は絞り２
２を有する通孔２３により一次側通路２０に連通
すると共に、圧力室１２と絞り２２との間の通孔
に連通するベントポート２４にベント管路１４を
取付ける。なお、差動形リリーフ弁１１′は差動
形リリーフ弁１１と同じ構成であり、その構成部
分、部品を差動形リリーフ弁１１の対応部分、部
品と区別するため同符号に′を付す。 The embodiment of the differential relief valve will be explained with reference to FIG.
9 and cuts off the communication between the primary passage 20 and the secondary passage 21, and the pressure receiving area A 1 on the valve seat side when the valve is closed is changed to the pressure receiving area of the rear end located in the pressure chamber 12.
A is set larger than 2 , while the pressure chamber 12 is set to be larger than 2.
The vent conduit 14 is attached to a vent port 24 that communicates with the primary side passage 20 through a through hole 23 having a diameter of 2. The differential relief valve 11' has the same structure as the differential relief valve 11, and the same reference numerals are given the same reference numeral as '' to distinguish its constituent parts and parts from the corresponding parts and parts of the differential relief valve 11.
次に本実施例の作用につき説明する。第２図に
おいて、方向切換弁１を中立位置から位置Ａに切
換えてポンプ２からの作動液を方向切換弁１、管
路１５、カウンタバランス弁３を経て主管路４に
導くと、カウンタバランス弁３はスプール左端に
作用するパイロツト圧で位置Ａに切換わり、ポン
プ作動液は主管路４から油圧モータ５に流入し、
油圧モータ５からの排出液は主管路６、カウンタ
バランス弁３、方向切換弁１を経てタンク７に環
流し、慣性体（図示せず）は油圧モータ５で加速
せしめられる。この慣性体加速時、パイロツト切
換弁１３は管路１５のポンプ液圧により位置Ａに
切換わつているので、差動形リリーフ弁１１は、
圧力室１２と管路１５との連通によりポペツト１
７の前後にポンプ液圧が作用し、ばね１８の初期
セツト力をＦとするとセツト圧Ｆ／（A1−A2）の
高圧リリーフ弁となり、差動形リリーフ弁１１′
は、圧力室１２′が管路１５′に連通し１次側通路
２０′ともどもタンク７に通じるので、セツト圧
がＦ／A1の低圧設定となる。 Next, the operation of this embodiment will be explained. In Fig. 2, when the directional control valve 1 is switched from the neutral position to the position A and the working fluid from the pump 2 is guided to the main line 4 via the directional control valve 1, the line 15, and the counterbalance valve 3, the counterbalance valve 3 is switched to position A by the pilot pressure acting on the left end of the spool, and the pump working fluid flows into the hydraulic motor 5 from the main pipe 4.
The liquid discharged from the hydraulic motor 5 flows back into the tank 7 via the main pipe 6, the counterbalance valve 3, and the directional control valve 1, and the inertial body (not shown) is accelerated by the hydraulic motor 5. During this inertial body acceleration, the pilot switching valve 13 is switched to position A by the pump hydraulic pressure in the pipe line 15, so the differential relief valve 11 is
The poppet 1 is connected to the pressure chamber 12 and the pipe line 15.
Pump hydraulic pressure acts before and after 7, and if the initial setting force of the spring 18 is F, it becomes a high pressure relief valve with a setting pressure F/(A 1 - A 2 ), and the differential relief valve 11'
Since the pressure chamber 12' communicates with the conduit 15' and both the primary passage 20' and the tank 7, the set pressure is set to a low pressure of F/ A1 .
次に、慣性体を停止させるために方向切換弁１
を中立位置に切換えると、ポンプ２からの作動液
はタンク７に環流し、カウンタバランス弁３はス
プール両端の圧力室がタンク７と通じばね８によ
り中立位置に復帰する。一方、パイロツト切換弁
１３は、管路１５、１５′がタンク７と連通し同
圧となるので中立位置に切換わり、ベント管路１
４、１４′をブロツクする。油圧モータ５は慣性
体の慣性力によりポンピングし、タンク側作動液
を主管路４から吸入してカウンタバランス弁３の
中立位置のチエツク弁でタンク側との連通を断た
れた主管路６に排出するので、主管路６の液圧は
上昇する。この場合、差動形リリーフ弁１１は圧
力室１２と一次側通路２０が略タンク圧となつて
閉弁し、差動形リリーフ弁１１′は圧力室１２′と
一次側通路２０′が同圧となつてセツト圧がＦ／
（A1−A2）の高圧設定となる。主管路６の液圧が
このセツト圧を越えると、差動形リリーフ弁１
１′と油圧モータ５とを結ぶ閉回路を作動液が循
環し、慣性体は制動される。 Next, in order to stop the inertial body, the directional control valve 1
When the pump 2 is switched to the neutral position, the working fluid from the pump 2 flows back into the tank 7, and the pressure chambers at both ends of the spool of the counterbalance valve 3 communicate with the tank 7, and the spring 8 returns the counterbalance valve 3 to the neutral position. On the other hand, the pilot switching valve 13 is switched to the neutral position because the pipes 15 and 15' communicate with the tank 7 and have the same pressure, and the vent pipe 1 is switched to the neutral position.
Block 4 and 14'. The hydraulic motor 5 pumps by the inertial force of the inertial body, sucks the tank-side hydraulic fluid from the main pipe line 4, and discharges it to the main pipe line 6, which is disconnected from the tank side by the check valve in the neutral position of the counterbalance valve 3. Therefore, the hydraulic pressure in the main pipe line 6 increases. In this case, the differential relief valve 11 closes when the pressure chamber 12 and the primary passage 20 reach approximately the tank pressure, and the differential relief valve 11' closes when the pressure chamber 12' and the primary passage 20' reach the same pressure. So the set pressure is F/
The high pressure setting is (A 1 − A 2 ). When the hydraulic pressure in the main line 6 exceeds this set pressure, the differential relief valve 1
Hydraulic fluid circulates through a closed circuit connecting hydraulic motor 1' and hydraulic motor 5, and the inertial body is braked.
この制動過程において、慣性体の停止位置を補
正するため少しの間方向切換弁１を中立位置から
位置Ａに切換えて油圧モータ５を加速すると、応
答性の速いパイロツト切換弁１３は管路１５のポ
ンプ液圧で直ちに位置Ａに切換わる。これにより
差動形リリーフ弁１１は圧力室１２と一次側通路
２０にポンプ液圧をうけセツト圧がＦ／（A1−
A2）の高圧設定となるが、差動形リリーフ弁１
１′はその圧力室１２′がタンク７側と連通しセツ
ト圧はＦ／A1の低圧設定となるので、ブレーキ
側となる主管路６の液圧は油圧モータ５の加速圧
＋Ｆ／A1となり、従来のカウンタバランス弁３
の応答遅れによるサージ圧〔油圧モータ５の加速
圧＋Ｆ／（A1−A2）の発生を防止できる。 In this braking process, when the hydraulic motor 5 is accelerated by switching the directional control valve 1 from the neutral position to position A for a short time in order to correct the stop position of the inertial body, the pilot switching valve 13 with quick response is activated in the pipe line 15. Pump hydraulic pressure immediately switches to position A. As a result, the differential relief valve 11 receives pump hydraulic pressure in the pressure chamber 12 and the primary passage 20, and the set pressure becomes F/(A 1 -
A 2 ) high pressure setting is required, but differential relief valve 1
1', its pressure chamber 12' communicates with the tank 7 side and the set pressure is set to a low pressure of F/A 1 , so the hydraulic pressure in the main pipe line 6 on the brake side is equal to the acceleration pressure of the hydraulic motor 5 + F/A 1 Therefore, the conventional counterbalance valve 3
The generation of surge pressure [acceleration pressure of hydraulic motor 5 +F/(A 1 -A 2 )] due to delayed response can be prevented.
ついでカウンタバランス弁３が位置Ａに切換わ
ると、主管路６の液圧は略タンク圧にまで低下
し、慣性体は加速されることとなり、方向切換弁
１を中立位置に切換えると、再び慣性体は制動さ
れる。 Next, when the counterbalance valve 3 is switched to position A, the hydraulic pressure in the main line 6 drops to approximately the tank pressure, and the inertial body is accelerated. When the directional control valve 1 is switched to the neutral position, the inertial body is increased again. The body is braked.
なお、前記実施例においては、ブレーキ回路の
リリーフ弁に差動形リリーフ弁を使用したが、こ
の代にバランスピストン形リリーフ弁を用いても
同様の効果を得ることができる。 In the above embodiment, a differential type relief valve is used as the relief valve of the brake circuit, but the same effect can be obtained by using a balance piston type relief valve instead.
以上説明したように本考案においては、ブレー
キ回路のリリーフ弁のベントポートにベント管路
を取付け、このベント管路はその中間にパイロツ
ト切換弁を介装してカウンタバランス弁の方向切
換弁側の自身のリリーフ弁の１次側通路と接続す
る管路に接続し、パイロツト切換弁はそのパイロ
ツト圧をカウンタバランス弁の方向切換弁側両管
路よりとり両管路の圧力が等しいとき各ベント管
路をしや断し圧力が相違すると連通するようにし
ているので、制動側のリリーフ弁は制動時高圧設
定となり、制動時の追打ち加速操作で直ちに低圧
設定となる。従つて、慣性体を所定位置で停止さ
せるための追打ち加速操作によるサージ圧の発生
を確実に防止できる実益がある。 As explained above, in the present invention, a vent pipe is attached to the vent port of the relief valve of the brake circuit, and this vent pipe is connected to the directional switching valve side of the counterbalance valve by interposing a pilot switching valve in the middle. The pilot switching valve is connected to a pipe line that connects to the primary passage of its own relief valve, and the pilot switching valve receives its pilot pressure from both pipes on the directional switching valve side of the counterbalance valve, and when the pressure in both pipes is equal, Since the path is cut off and communication is established when the pressures are different, the relief valve on the braking side is set to a high pressure during braking, and is immediately set to a low pressure when an additional acceleration operation is performed during braking. Therefore, there is the practical benefit of reliably preventing the generation of surge pressure due to the additional acceleration operation for stopping the inertial body at a predetermined position.
第１図は従来の慣性体旋回系油圧回路図、第２
図は本考案の実施例の油圧回路図、第３図は差動
形リリーフ弁の一部切欠き縦断面図である。
１……方向切換弁、２……ポンプ、３……カウ
ンタバランス弁、５……油圧モータ、１１，１
１′……差動形リリーフ弁、１２，１２′……圧力
室、１３……パイロツト切換弁、１４，１４′…
…ベント管路、１７……ポペツト、１９……弁
座、２２……絞り、２４……ベントポート。
Figure 1 is a hydraulic circuit diagram of a conventional inertial body rotation system, Figure 2
The figure is a hydraulic circuit diagram of an embodiment of the present invention, and FIG. 3 is a partially cutaway longitudinal sectional view of a differential relief valve. 1...Directional switching valve, 2...Pump, 3...Counter balance valve, 5...Hydraulic motor, 11,1
1'... Differential relief valve, 12, 12'... Pressure chamber, 13... Pilot switching valve, 14, 14'...
...vent pipe line, 17...poppet, 19...valve seat, 22...throttle, 24...vent port.
Claims (1)
するカウンタバランス弁と液圧モータとを接続し
た両管路を向きを違えた二つのリリーフ弁でそれ
ぞれ接続してブレーキ回路を形成した液圧駆動装
置において、前記リリーフ弁は中間に３位置４ポ
ートパイロツト切換弁を介装したベント管路によ
りカウンタバランス弁の方向切換弁側の自身のリ
リーフ弁の一次側通路と接続する管路に接続し、
前記パイロツト切換弁はそのパイロツト圧をカウ
ンタバランス弁の方向切換弁側両管路よりとり両
管路の圧力が等しいとき各ベント管路を遮断し圧
力が相違すると連通するようにしたことを特徴と
する液圧駆動装置。 In a hydraulic drive device in which a brake circuit is formed by connecting both pipes, which connect a hydraulic motor and a counterbalance valve connected to a pump and a tank via a directional valve, with two relief valves in different directions. , the relief valve is connected to a conduit connected to the primary side passage of its own relief valve on the directional control valve side of the counterbalance valve by a vent conduit with a 3-position 4-port pilot switching valve interposed therebetween;
The pilot switching valve is characterized in that the pilot pressure is taken from both pipes on the directional switching valve side of the counterbalance valve, and when the pressures in both pipes are equal, each vent pipe is shut off, and when the pressures are different, they are communicated. Hydraulic drive device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980144492U JPS6144002Y2 (en) | 1980-10-09 | 1980-10-09 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980144492U JPS6144002Y2 (en) | 1980-10-09 | 1980-10-09 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5767101U JPS5767101U (en) | 1982-04-22 |
| JPS6144002Y2 true JPS6144002Y2 (en) | 1986-12-12 |
Family
ID=29504195
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980144492U Expired JPS6144002Y2 (en) | 1980-10-09 | 1980-10-09 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6144002Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007051689A (en) * | 2005-08-18 | 2007-03-01 | Tgk Co Ltd | Differential pressure regulating valve |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6113761Y2 (en) * | 1976-11-13 | 1986-04-28 | ||
| JPS5644881Y2 (en) * | 1977-01-06 | 1981-10-21 |
-
1980
- 1980-10-09 JP JP1980144492U patent/JPS6144002Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5767101U (en) | 1982-04-22 |
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