JPH0557443B2 - - Google Patents
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- Publication number
- JPH0557443B2 JPH0557443B2 JP16446286A JP16446286A JPH0557443B2 JP H0557443 B2 JPH0557443 B2 JP H0557443B2 JP 16446286 A JP16446286 A JP 16446286A JP 16446286 A JP16446286 A JP 16446286A JP H0557443 B2 JPH0557443 B2 JP H0557443B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- small diameter
- diameter hole
- oil chamber
- inflow
- 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
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- 238000004891 communication Methods 0.000 claims description 10
- 230000000694 effects Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Landscapes
- Servomotors (AREA)
- Lift Valve (AREA)
- Safety Valves (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は流量制御弁に係り、特に、本願出願人
の先願（特願昭61−11709号、特願昭61−11710
号、特願昭61−31699号、特願昭61−31700号）に
係る各装置の主弁として最適に採用し得る流量制
御弁に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a flow rate control valve, and in particular, the present invention relates to a flow rate control valve, and in particular, the present invention relates to a flow rate control valve.
The present invention relates to a flow control valve that can be optimally adopted as a main valve of various devices related to Japanese Patent Application No. 61-31699 and Japanese Patent Application No. 61-31700).
本願出願人は、上記した先願、例えば特願昭61
−11709号にて、第５図に例示する装置を提案し
た。
The applicant of this application has filed the above-mentioned earlier application, for example, Japanese Patent Application No. 61
In No. 11709, we proposed the device illustrated in FIG.
第５図に示す装置は、主弁１０、第１パイロツ
ト弁２０及び第２パイロツト弁３０によつて構成
されている流量制御装置であり、主弁１０は弁本
体１１と、この弁本体１１内に上下方向（軸方
向）へ摺動自在に嵌挿した弁体１２と、この弁体
１２を下方へ付勢するばね１３を主要構成部材と
している。弁本体１１は、大径孔１１ａの上下両
側に同一径の小径孔１１ｂ，１１ｃをそれぞれ同
軸的に設けてなり下方の段部に弁座１１ｄを形成
してなる段付内孔を有するとともに、流入路Ｐ１
が連通する環状溝１１ｅや流出路Ｐ２が連通する
環状溝１１ｆを有している。 The device shown in FIG. 5 is a flow control device composed of a main valve 10, a first pilot valve 20, and a second pilot valve 30. The main components are a valve body 12 that is slidably inserted in the vertical direction (axial direction), and a spring 13 that biases the valve body 12 downward. The valve body 11 has a stepped inner hole in which small diameter holes 11b and 11c of the same diameter are coaxially provided on both upper and lower sides of a large diameter hole 11a, and a valve seat 11d is formed in a lower step. Inflow path P1
It has an annular groove 11e with which it communicates and an annular groove 11f with which the outflow path P2 communicates.
弁体１２は、大径溝１１ａ内に圧力バランスさ
れた状態（上下両端部に作用する流入路Ｐ１内の
圧力が常に相殺される状態）にて摺動自在に嵌挿
されてテーパ面１２ａ１にて弁座１１ｄに着座し
たり離脱して流入路Ｐ１と流出路Ｐ２間を連通遮
断するポペツト弁部１２ａと、同ポペツト弁部１
２ａの下側に設けられて下方の小径孔１１ｂ内に
延び同小径孔１１ｂとの間に流出路Ｐ２が常時連
通する油室Ｐ１を形成する連結部１２ｂと、同連
結部１２ｂの下側に設けられて下方の小径孔１１
ｂに摺動自在に嵌挿され同小径孔１１ｂ端に油室
Ｒ２を形成するピストン部１２ｃを一体的に備え
るとともに、ポペツト弁部１２ａの上側に設けら
れて上方の小径孔１１ｃに摺動自在に嵌挿され同
小径孔１１ｃ端に油室Ｒ３を形成する小径筒部１
２ｄを一体的に備えている。しかして、油室Ｒ２
は第１パイロツト弁２０に接続されるとともに第
２パイロツト弁３０の第１切換弁３１に接続さ
れ、また油室Ｒ３は絞り１４を介して流入路Ｐ１
に接続されるとともに、第２パイロツト弁３０の
第２切換弁３２に接続されている。 The valve body 12 is slidably inserted into the large-diameter groove 11a in a pressure-balanced state (a state in which the pressure in the inflow path P1 acting on both the upper and lower ends is always canceled out) and is inserted into the tapered surface 12a1. a poppet valve portion 12a that seats on or leaves the valve seat 11d to cut off communication between the inflow path P1 and the outflow path P2, and the poppet valve portion 1
A connecting part 12b that is provided on the lower side of the connecting part 2a and forms an oil chamber P1 that extends into the lower small diameter hole 11b and has an outflow passage P2 communicating with the small diameter hole 11b at all times; A lower small diameter hole 11 is provided.
It is integrally provided with a piston portion 12c that is slidably inserted into the small diameter hole 11b and forms an oil chamber R2 at the end of the small diameter hole 11b, and is provided above the poppet valve portion 12a and is slidable into the upper small diameter hole 11c. A small-diameter cylindrical portion 1 that is fitted into the small-diameter hole 11c and forms an oil chamber R3 at the end of the small-diameter hole 11c.
2d is integrally provided. However, oil chamber R2
is connected to the first pilot valve 20 and to the first switching valve 31 of the second pilot valve 30, and the oil chamber R3 is connected to the inlet passage P1 via the throttle 14.
It is connected to the second switching valve 32 of the second pilot valve 30.
第１パイロツト弁２０は、供給路Ｐ３を通して
導入された圧油を所定値に減圧する減圧弁２１
と、この減圧弁２１から絞り２２を通して油室Ｒ
２に付与されるパイロツト圧を電流付与値に応じ
て比例制御する電流制御リリーフ弁２３によつて
構成されている。第２パイロツト弁３０は、油室
Ｒ２に付与されるパイロツト圧により作動を制御
される第１切換弁３１と、この第１切換弁３１に
よつて作動を制御される第２切換弁３２によつて
構成されている。第１切換弁３１は、油室Ｒ２か
ら通路Ｐ４を通して付与されるパイロツト圧が設
定値未満であるとき図示のように非作動状態にあ
つて供給路Ｐ３と第２切換弁３２の接続を断ちま
たパイロツト圧が設定値以上であるとき作動状態
となつて供給路Ｐ３を第２切換弁３２に接続させ
る。第２切換弁３２は、第１切換弁３１によつて
供給路Ｐ３に接続されたとき作動して油室Ｒ３に
連通する通路Ｐ５とリザーバＴに連通する戻り路
Ｐ６を連通させ、また第１切換弁３１によつて供
給路Ｐ３との接続を断たれて戻り路Ｐ６に接続さ
れたとき図示のように非作動となつて油室Ｒ３に
連通する通路Ｐ５と戻り路Ｐ６の連通を遮断す
る。 The first pilot valve 20 is a pressure reducing valve 21 that reduces the pressure of the pressure oil introduced through the supply path P3 to a predetermined value.
The pressure reducing valve 21 passes through the throttle 22 to the oil chamber R.
The current control relief valve 23 proportionally controls the pilot pressure applied to the valve 2 in accordance with the current applied value. The second pilot valve 30 includes a first switching valve 31 whose operation is controlled by the pilot pressure applied to the oil chamber R2, and a second switching valve 32 whose operation is controlled by the first switching valve 31. It is structured as follows. When the pilot pressure applied from the oil chamber R2 through the passage P4 is less than the set value, the first switching valve 31 is in an inoperable state as shown in the figure and disconnects the supply path P3 from the second switching valve 32. When the pilot pressure is equal to or higher than the set value, it is activated and connects the supply path P3 to the second switching valve 32. The second switching valve 32 operates when connected to the supply path P3 by the first switching valve 31, and connects the passage P5 communicating with the oil chamber R3 and the return path P6 communicating with the reservoir T. When the switching valve 31 disconnects the supply path P3 and connects it to the return path P6, it becomes inactive as shown in the figure, cutting off communication between the path P5 communicating with the oil chamber R3 and the return path P6. .
上記のように構成した流量制御装置において
は、主弁１０の弁体１２におけるポペツト弁部１
２ａに流入路Ｐ１内圧力が常に相殺されるように
作用し、また同ポペツト弁部１２ａとピストン部
１２ｃに流出路Ｐ２内圧力が常に相殺されるよう
に作用するため、如何なる状態においても流入路
Ｐ１内圧力や流入路Ｐ２内圧力の変動によつて主
弁１０の弁体１２が軸方向へ押動されることはな
い。 In the flow control device configured as described above, the poppet valve portion 1 of the valve body 12 of the main valve 10
2a so that the pressure inside the inflow path P1 always cancels out, and the poppet valve part 12a and the piston part 12c act so that the pressure inside the outflow path P2 always cancels out, so the inflow path The valve body 12 of the main valve 10 is not pushed in the axial direction due to fluctuations in the pressure inside P1 or the pressure inside the inflow path P2.
また第１パイロツト弁２０におけるリリーフ弁
２３への電流付与値が設定値未満であつて油室Ｒ
２に付与されるパイロツト圧が設定値未満である
場合には、図示のごとく、第２パイロツト弁３０
における第１切換弁３１が非作動状態にあつて供
給路Ｐ３と第２切換弁３２の接続を断つており、
第２切換弁３２が非作動状態にあつて油室Ｒ３と
戻り路Ｐ６の連通を遮断している。このため、主
弁１０の弁体１２は流入路Ｐ１から絞り１４を通
して油室Ｒ３に付与される油圧及びばね１３の作
用によりポペツト弁部１２ａを弁座１１ｄに着座
させており、流入路Ｐ１と流出路Ｐ２の連通が適
確に遮断されている。 Also, if the value of the current applied to the relief valve 23 in the first pilot valve 20 is less than the set value, the oil chamber R
If the pilot pressure applied to the second pilot valve 30 is less than the set value, the second pilot valve 30
The first switching valve 31 is in an inoperable state and disconnects the supply path P3 from the second switching valve 32;
The second switching valve 32 is in a non-operating state, cutting off communication between the oil chamber R3 and the return path P6. Therefore, the valve body 12 of the main valve 10 seats the poppet valve portion 12a on the valve seat 11d by the action of the spring 13 and the hydraulic pressure applied to the oil chamber R3 from the inflow path P1 through the throttle 14. Communication of the outflow path P2 is appropriately blocked.
しかして、第１パイロツト弁２０におけるリリ
ーフ弁２３への電流付与値を設定値以上として油
室Ｒ２に付与されるパイロツト圧を設定値以上と
すると、第２パイロツト弁３０における第１切換
弁３１が作動して供給路Ｐ３を第２切換弁３２に
接続するため、第２切換弁３２が作動して油室Ｒ
３を戻り路Ｐ６に連通させる。このため、油室Ｒ
３内の油圧は略ゼロとなり、主弁１０の弁体１２
は油室Ｒ２内のパイロツト圧（第１パイロツト弁
２０によつて設定値以上の或る値に設定されてい
る）による押圧力とばね１３の作用力がバランス
する位置にて保持され流入路Ｐ１から流出路Ｐ２
へ流れる流量が規定される。したがつて、第１パ
イロツト弁２０におけるリリーフ弁２３への電流
付与値を変えて油室Ｒ２に付与されるパイロツト
圧を変えることにより、主弁１０の弁体１２の位
置を調整でき、流入路Ｐ１から流出路Ｐ２へ流れ
る流量を調整することができる。 Therefore, when the value of current applied to the relief valve 23 in the first pilot valve 20 is made equal to or more than the set value and the pilot pressure given to the oil chamber R2 is made equal to or more than the set value, the first switching valve 31 in the second pilot valve 30 becomes more than the set value. The second switching valve 32 operates to connect the supply path P3 to the second switching valve 32, and the second switching valve 32 operates to connect the supply path P3 to the second switching valve 32.
3 is communicated with the return path P6. For this reason, oil chamber R
3 becomes almost zero, and the valve body 12 of the main valve 10
is maintained at a position where the pressing force due to the pilot pressure in the oil chamber R2 (set to a certain value higher than the set value by the first pilot valve 20) and the acting force of the spring 13 are balanced, and the inflow path P1 Outflow path P2
The flow rate flowing to is specified. Therefore, by changing the value of current applied to the relief valve 23 in the first pilot valve 20 and changing the pilot pressure applied to the oil chamber R2, the position of the valve body 12 of the main valve 10 can be adjusted, and the inflow path The flow rate flowing from P1 to outflow path P2 can be adjusted.
以上の説明から明らかなように、上記した流量
制御装置の主弁１０は、ポペツト弁としての機
能、すなわち流入路Ｐ１と流出路Ｐ２間の連通を
適確に遮断する（洩れなく遮断する）機能を備え
ながら、油室Ｒ２に付与されるパイロツト圧に応
じて流入路Ｐ１から流出路Ｐ２に流れる流量を容
易かつ正確に調整できる利点を備えている。 As is clear from the above description, the main valve 10 of the flow rate control device described above has the function of a poppet valve, that is, the function of appropriately blocking communication between the inflow path P1 and the outflow path P2 (blocking without leakage). However, it has the advantage that the flow rate flowing from the inflow path P1 to the outflow path P2 can be easily and accurately adjusted in accordance with the pilot pressure applied to the oil chamber R2.
ところで、上記した流量制御装置の主弁１０に
おいては、弁体１２のポペツト弁部１２ａにおけ
るテーパ面１２ａ１の頂角θが弁座１１ｄへの適
確なシート性を確保する必要性から所定角（通常
40〜60度）に限定されるため、ポペツト弁部１２
ａの軸方向ストロークに対する可変絞り部の流路
面積（当該弁の流量を規定する開口面積）の変化
率が大きく、同流路面積を所望の値に設定しづら
いといつた問題がある。
By the way, in the main valve 10 of the flow control device described above, the apex angle θ of the tapered surface 12a1 in the poppet valve portion 12a of the valve body 12 is set at a predetermined angle ( usually
40 to 60 degrees), the poppet valve part 12
There is a problem in that the rate of change in the flow path area (opening area that defines the flow rate of the valve) of the variable restrictor with respect to the axial stroke of a is large, and it is difficult to set the flow path area to a desired value.
また、ポペツト弁部１２ａのテーパ面１２ａ１
と弁座１１ｄ間に形成される可変絞り部を流れる
圧油により大きなフローフオースが発生して弁体
１２が軸方向へ押動されることがあるため、折角
設定した上記流路面積が影響を受けることがあ
る。 Further, the tapered surface 12a1 of the poppet valve portion 12a
A large flow force may be generated by the pressure oil flowing through the variable restrictor formed between the valve seat 11d and the valve seat 11d, and the valve body 12 may be pushed in the axial direction. Sometimes.
本発明は上記した問題を解決するために、上記
した主弁１０として採用し得る流量制御弁を、
大径孔の両側に同一径の小径孔をそれぞれ同軸
的に設けてなり、一方の小径孔と前記大径孔間の
段部に弁座を形成するとともに、同弁座の前記大
径孔側に第１流入出路を接続し、また一方の小径
孔の中間部に第２流入出路を接続してなる弁本体
と、
前記大径孔内に前記第１流入出路から受ける圧
力が常に相殺される状態にて嵌挿されてテーパ面
にて前記弁座に着座したり離脱して前記両流入出
路間を連通遮断するポペツト弁部と、同ポペツト
弁部の一側に設けられて前記一方の小径孔に摺動
自在に嵌挿されるスプール部と、同スプール部の
一側に設けられて前記一方の小径孔内に延び同小
径孔との間に前記第２流入出路に連通する第１油
室を形成する連結部と、同連結部の一側に設けら
れて前記一方の小径孔に摺動自在に嵌挿され同小
径孔端にパイロツト圧が付与される第２油室を形
成するピストン部を一体的に備えるとともに、前
記ポペツト弁部の他側に設けられて前記他方の小
径孔に摺動自在に嵌挿され同小径孔端に前記両流
入出路のうち流入路となる流路に絞りを介して常
に接続されるとともに戻り路に選択的に接続され
る第３油室を形成する小径部を一体的に備え、ま
た前記スプール部の外周に前記第３油室側への軸
方向移動によつて前記ポペツト弁部のテーパ面と
弁座間に形成される流路面積より流路面積が常に
小さい可変絞り部を前記大径孔及び一方の小径孔
内壁とにより構成する切欠を備える弁体と、
同弁体を前記第２油室に向けて付勢するばねを
具備する構成とした。
In order to solve the above-described problems, the present invention provides a flow control valve that can be adopted as the main valve 10 described above, in which a large-diameter hole and small-diameter holes of the same diameter are coaxially provided on both sides of the large-diameter hole, and one small-diameter hole is provided. A valve seat is formed in a stepped portion between the large diameter hole and a first inflow/outflow passage is connected to the large diameter hole side of the valve seat, and a second inflow/outflow passage is connected to an intermediate portion of one of the small diameter holes. a valve body that is fitted into the large-diameter hole in such a manner that pressures received from the first inflow and outflow passages are always canceled out, and seated on the valve seat on a tapered surface, and separated from the valve seat so that both the inflow and outflow passages are connected to each other; a poppet valve portion that disconnects communication between the outlet passages; a spool portion provided on one side of the poppet valve portion and slidably inserted into the small diameter hole of the one said spool portion; a connecting portion that extends into one of the small diameter holes and forms a first oil chamber communicating with the second inflow/output passage between the small diameter holes; A piston is integrally provided with a second oil chamber that is movably inserted into the small diameter hole and applies pilot pressure to the end of the small diameter hole, and is provided on the other side of the poppet valve part and connected to the other small diameter hole. A third oil chamber is formed at the end of the small diameter hole by being slidably inserted therein and always connected to the inflow path of the two inflow and outflow paths via a throttle and selectively connected to the return path. A small diameter portion is integrally provided, and the flow path area is smaller than the flow path area formed between the tapered surface of the poppet valve portion and the valve seat by axial movement toward the third oil chamber on the outer periphery of the spool portion. The valve body is provided with a notch that forms a variable throttle portion that is always small by the large diameter hole and the inner wall of one of the small diameter holes, and a spring that biases the valve body toward the second oil chamber. .
本発明による流量制御弁においては、第２油室
にパイロツト圧が付与されて弁体がばねに抗して
軸方向へ移動することにより、流入路と流出路が
ポペツト弁部のテーパ面と弁座間に形成される流
路、弁体のスプール部に設けた切欠と弁本体の大
径孔及び一方の小径孔内壁とにより構成される可
変絞り部、及び第１油室を通して連通して、ポペ
ツト弁部のテーパ面と弁座間に形成される流路が
前記可変絞り部の流路面積より流路面積が常に大
きい単なる通路として機能し、流入路から流出路
へ流れる流量が流路面積の最も小さい可変絞り部
にて規定される。
In the flow control valve according to the present invention, by applying pilot pressure to the second oil chamber and moving the valve body in the axial direction against the spring, the inflow passage and the outflow passage are connected to the tapered surface of the poppet valve portion and the valve body. The flow path formed between the seats, the variable throttle section formed by the notch provided in the spool part of the valve body, the large diameter hole of the valve body, and the inner wall of one of the small diameter holes, and the first oil chamber communicate with each other to form a poppet. The flow path formed between the tapered surface of the valve portion and the valve seat functions as a simple passage whose flow path area is always larger than the flow path area of the variable throttle portion, and the flow rate from the inflow path to the outflow path is the largest of the flow path area. Defined by a small variable diaphragm.
しかして、スプール部に設けられる切欠は、そ
の形状を他のものに制約されることなく適宜に設
定可能であり、弁体の軸方向ストロークに対する
可変絞り部の流路面積の変化率を適宜に小さくす
ることができる。したがつて、可変絞り部の流路
面積を所望の値に設定しやすくすることができ
る。 Therefore, the shape of the notch provided in the spool part can be set as appropriate without being restricted by other things, and the rate of change in the flow path area of the variable throttle part with respect to the axial stroke of the valve body can be set as appropriate. Can be made smaller. Therefore, it is possible to easily set the flow path area of the variable throttle portion to a desired value.
また、本発明による流量制御弁においては、ポ
ペツト弁部のテーパ面と弁座間に形成される流路
が単なる通路として機能し、かつスプール部に設
けた切欠と弁本体の大径孔及び一方の小径孔内壁
とにより構成される可変絞り部にて流体が絞られ
るようにしたため、ポペツト弁部のテーパ面と弁
座間に形成される流路を流れる圧油により発生す
るフローフオースを殆ど無くすことができるとと
もに、可変絞り部を流れる圧油により発生するフ
ローフオースを第５図に示したものに比して小さ
なものとすることができて、弁体のフローフオー
スによる軸方向移動を小さくすることができ、所
望の値に設定した可変絞り部の流路面積がフロー
フオースの影響をさほど受けないようにすること
ができる。なお、本発明者の実験結果によれば、
本発明による流量制御弁において弁体に作用する
フローフオースは第５図に示した弁体に作用する
フローフオースの略半分になることが判明した。 Further, in the flow control valve according to the present invention, the flow path formed between the tapered surface of the poppet valve part and the valve seat functions as a mere passage, and the notch provided in the spool part and the large diameter hole of the valve body, and Since the fluid is throttled by the variable throttle section formed by the inner wall of the small diameter hole, it is possible to almost eliminate the flow force generated by the pressure oil flowing through the flow path formed between the tapered surface of the poppet valve section and the valve seat. At the same time, the flow force generated by the pressure oil flowing through the variable restrictor can be made smaller than that shown in FIG. The flow path area of the variable throttle section, which is set to the value of , can be made so that it is not so affected by the flow force. According to the inventor's experimental results,
It has been found that in the flow control valve according to the present invention, the flow force acting on the valve body is approximately half the flow force acting on the valve body shown in FIG.
以下に本発明の一実施例を図面に基づいて説明
する。
An embodiment of the present invention will be described below based on the drawings.
第１図は本発明による流量制御弁を示してい
て、同流量制御弁４０は、第１部材４１Ａ、第２
部材４１Ｂ及び第３部材４１Ｃからなる弁本体４
１と、この弁本体４１内に上下方向（軸方向）へ
摺動自在に嵌挿した弁体４２と、この弁体４２を
下方へ付勢するばね４３は主要構成部材としてい
る。弁本体４１は、大径孔４１ａの上下両側に同
一径の小径孔４１ｂ，４１ｃをそれぞれ同軸的に
設けてなり下方の段部に弁座４１ｄを形成してな
る段付内孔を有するとともに、弁座４１ｄに近接
する側の大径孔端に形成されて流入路Ｐ１１が連
通する環状溝４１ｅや、下方の小径孔４１ｂの中
間部に形成されて流出路Ｐ１２が連通する環状溝
４１ｆを有している。 FIG. 1 shows a flow control valve according to the present invention, and the flow control valve 40 includes a first member 41A, a second member 41A, and a second member 41A.
Valve body 4 consisting of member 41B and third member 41C
1, a valve body 42 that is slidably inserted into the valve body 41 in the vertical direction (axial direction), and a spring 43 that biases the valve body 42 downward. The valve body 41 has a stepped inner hole in which small diameter holes 41b and 41c of the same diameter are coaxially provided on both upper and lower sides of a large diameter hole 41a, and a valve seat 41d is formed in the lower step. It has an annular groove 41e formed at the end of the large diameter hole near the valve seat 41d and communicating with the inflow passage P11, and an annular groove 41f formed in the middle part of the lower small diameter hole 41b and communicating with the outflow passage P12. are doing.
弁体４２は、大径孔４１ａ内に圧力バランスさ
れた状態（上下両端部に作用する流入路Ｐ１１内
の圧力が常に相殺される状態）にて摺動自在に嵌
挿されてテーパ面４２ａ１にて弁座４１ｄに着座
したり離脱して流入路Ｐ１１と流出路Ｐ１２間を
連通遮断するポペツト弁部４２ａと、同ポペツト
弁部４２ａの下側に設けられて下方の小径孔４１
ｂに摺動自在に嵌挿されるスプール部４２ｂと、
同スプール部４２ｂの下側に設けられて小径孔４
１ｂ内に延び同小径孔４１ｂとの間に流出路Ｐ１
２に連通する第１油室Ｒ１１を形成する連結部４
２ｃと、同連結部４２ｃの下側に設けられて小径
孔４１ｂに摺動自在に嵌挿され同小径孔端にパイ
ロツト圧が付与される第２油室Ｒ１２を形成する
ピストン部４２ｄを一体的に備えるとともに、ポ
ペツト弁部４２ａの上側に設けられて上方の小径
孔４１ｃに摺動自在に嵌挿され同小径孔４１ｃ端
に絞り４４を介して環状溝４１ｅに常に接続され
るとともに戻り路Ｐ６に選択的に接続される第３
油室Ｒ１３（第２図参照）を形成する小径筒部４
２ｅを一体的に備えている。また弁体４２のスプ
ール部４２ｂの外周には、第３油室Ｒ１３側への
軸方向移動によつてポペツト弁部４２ａのテーパ
面４２ａ１と弁座４１ｄ間に形成される流路面積
より流路面積が常に小さい可変絞り部Ａを大径孔
４１ａの環状溝４１ｅ部分及び下方の小径孔内壁
４１ｂ１とにより構成する切欠４２ｂ１が設けら
れている。 The valve body 42 is slidably inserted into the large-diameter hole 41a in a pressure-balanced state (a state in which the pressure in the inflow path P11 acting on both the upper and lower ends is always canceled out) and is inserted into the tapered surface 42a1. A poppet valve portion 42a that seats on or leaves the valve seat 41d to cut off communication between the inflow path P11 and the outflow path P12, and a small diameter hole 41 provided below the poppet valve portion 42a.
a spool portion 42b that is slidably inserted into b;
A small diameter hole 4 is provided on the lower side of the spool portion 42b.
1b and between it and the same small diameter hole 41b.
Connecting portion 4 forming a first oil chamber R11 communicating with 2
2c and a piston part 42d that forms a second oil chamber R12 that is provided below the connecting part 42c and is slidably inserted into the small diameter hole 41b and applies pilot pressure to the end of the small diameter hole. In addition, it is provided on the upper side of the poppet valve portion 42a, and is slidably inserted into the upper small diameter hole 41c, and is always connected to the annular groove 41e via the throttle 44 at the end of the small diameter hole 41c, and also has a return path P6. a third selectively connected to
Small diameter cylindrical portion 4 forming oil chamber R13 (see Figure 2)
2e is integrally provided. Furthermore, a flow path is formed on the outer periphery of the spool portion 42b of the valve body 42 due to the flow path area formed between the tapered surface 42a1 of the poppet valve portion 42a and the valve seat 41d by the axial movement toward the third oil chamber R13. A notch 42b1 is provided that constitutes a variable throttle portion A whose area is always small by the annular groove 41e portion of the large diameter hole 41a and the lower small diameter hole inner wall 41b1.
上記のように構成した流量制御弁は、第２図に
例示したように、第２油室Ｒ１２を第１パイロツ
ト弁２０に接続するとともに第２パイロツト弁３
０の第１切換弁３１に接続し、また第３油室Ｒ１
３を第２パイロツト弁３０の第２切換弁３２に接
続することにより、流量制御装置の主弁として採
用される。なお、第１パイロツト弁２０及び第２
パイロツト弁３０の構成は第５図に示したものと
全く同じである。 As illustrated in FIG. 2, the flow rate control valve configured as described above connects the second oil chamber R12 to the first pilot valve 20 and connects the second oil chamber R12 to the second pilot valve 3.
0 and the third oil chamber R1.
3 is connected to the second switching valve 32 of the second pilot valve 30, it is used as the main valve of the flow control device. Note that the first pilot valve 20 and the second
The construction of the pilot valve 30 is exactly the same as that shown in FIG.
ところで、上記のように構成した流量制御弁に
おいては、第２油室Ｒ１２に付与されるパイロツ
ト圧による押圧力が小さく、しかも第３油室Ｒ１
３が戻り路Ｐ６との連通を遮断されておれば、弁
体４２は流入路Ｐ１１から絞り４４を通して第３
油室Ｒ１３に付与される油圧及びばね４３の作用
により上記したパイロツト圧による押圧力に抗し
てポペツト弁部４２ａを弁座４１ｄに着座させて
おり、流入路Ｐ１１と流出路Ｐ１２の連通が適確
に遮断されている。しかして、このときには、弁
体４２におけるポペツト弁部４２ａに流入路Ｐ１
１内圧力が常に相殺されるように作用し、またス
プール部４２ｂとピストン部４２ｄに流出路Ｐ１
２内圧力が常に相殺されるように作用するため、
流入路内圧力や流出路内圧力の変動によつて弁体
４２が軸方向べ押動されることはない。 By the way, in the flow control valve configured as described above, the pressing force due to the pilot pressure applied to the second oil sac R12 is small, and moreover, the pressing force applied to the second oil sac R12 is small.
3 is cut off from communication with the return path P6, the valve body 42 passes through the throttle 44 from the inflow path P11 to the third
The poppet valve portion 42a is seated on the valve seat 41d against the pressing force caused by the pilot pressure described above due to the hydraulic pressure applied to the oil chamber R13 and the action of the spring 43, and proper communication between the inflow path P11 and the outflow path P12 is established. It's definitely blocked. At this time, the inflow path P1 is connected to the poppet valve portion 42a of the valve body 42.
1 internal pressure is always canceled out, and an outflow path P1 is provided between the spool portion 42b and the piston portion 42d.
2 The internal pressures always act to cancel each other out, so
The valve body 42 is not pushed in the axial direction due to fluctuations in the pressure inside the inflow path or the pressure inside the outflow path.
また、第２油室Ｒ１２に付与されるパイロツト
圧による押圧力ばね４３の取付荷重より大きく、
しかも第３油室Ｒ１３が戻り路Ｐ６と接続されて
連通しておれば、第３油室Ｒ１３内の油圧は略ゼ
ロとなつていて、弁体４２は第２油室Ｒ１２内の
パイロツト圧による押圧力とばね４３の作用力が
バランスする位置まで押動されている。このた
め、流入路Ｐ１１と流出路Ｐ１２は、ポペツト弁
部４２ａのテーパ面４２ａ１と弁座４１ｄ間に形
成される流路、スプール部４２ｂに設けた切欠４
２ｂ１と大径孔４１ａの環状溝４１ｅ部分及び下
方の小径孔内壁４１ｂ１とにより構成される可変
絞り部Ａ及び第１油室Ｒ１１を通して連通してい
て、ポペツト弁部４２ａのテーパ面４２ａ１と弁
座４１ｄ間に形成される流路が可変絞り部Ａの流
路面積より流路面積が常に大きい単なる通路とし
て機能し、流入路Ｐ１１から流出路Ｐ１２へ流れ
る流量が流路面積の最も小さい可変絞り部Ａにて
規定される。したがつて、第２油室Ｒ１２に付与
されるパイロツト圧を変えることにより、弁体４
２の位置を調整できて可変絞り部Ａでの絞り量を
調整でき、流入路Ｐ１１から流出路Ｐ１２へ流れ
る流量を調整することができる。 Also, the mounting load of the pressing force spring 43 due to the pilot pressure applied to the second oil chamber R12 is greater than the mounting load.
Moreover, if the third oil chamber R13 is connected and communicated with the return path P6, the oil pressure in the third oil chamber R13 is approximately zero, and the valve body 42 is controlled by the pilot pressure in the second oil chamber R12. It is pushed to a position where the pressing force and the acting force of the spring 43 are balanced. Therefore, the inflow path P11 and the outflow path P12 are a flow path formed between the tapered surface 42a1 of the poppet valve portion 42a and the valve seat 41d, and a notch 4 formed in the spool portion 42b.
2b1 and the annular groove 41e portion of the large diameter hole 41a and the lower small diameter hole inner wall 41b1 communicate through the variable throttle part A and the first oil chamber R11, and the tapered surface 42a1 of the poppet valve part 42a communicates with the valve seat. The flow path formed between 41d functions as a simple passage whose flow path area is always larger than the flow path area of the variable throttle section A, and the flow rate flowing from the inflow path P11 to the outflow path P12 is the variable throttle section with the smallest flow path area. Specified in A. Therefore, by changing the pilot pressure applied to the second oil chamber R12, the valve body 4
2 can be adjusted, the amount of throttling in the variable throttle part A can be adjusted, and the flow rate flowing from the inflow path P11 to the outflow path P12 can be adjusted.
しかして、弁体４２のスプール部４２ｂに設け
られる切欠４２ｂ１は、その形状を他のものに制
約されることなく適宜に設定可能であり、弁体４
２の軸方向スロトークにする可変絞り部Ａの流路
面積の変化率を適宜に小さくすることができる。
したがつて、可変絞り部Ａの流路面積を所望の値
に設定しやすくすることができる。 Therefore, the shape of the notch 42b1 provided in the spool portion 42b of the valve body 42 can be set as appropriate without being restricted by other things, and
The rate of change in the flow path area of the variable throttle section A to achieve the second axial throat talk can be appropriately reduced.
Therefore, the flow path area of the variable throttle section A can be easily set to a desired value.
また、本実施例の流量制御弁においては、ポペ
ツト弁部４２ａのテーパ面４２ａ１と弁座４１ｄ
間に形成される経路が単なる通路として機能し、
かつスプール部４２ｂに設けた切欠４２ｂ１と大
径孔４１ａの環状孔４１ｅ部分及び下方の小径孔
内壁４１ｂ１とにより構成される可変絞り部Ａに
て流体が絞られるようにしたため、ポペツト弁部
４２ａのテーパ面４２ａ１と弁座４１ｄ間に形成
される流路を流れる圧油により発生するフローフ
オースを殆ど無くすことができるとともに、可変
絞り部Ａを流れる圧油により発生するフローフオ
ースを第５図に示したものに比して小さなものと
することができて、弁体４２のフローフオースに
よる軸方向移動を小さくすることができ、所望の
値に設定した可変絞り部Ａの流路面積がフローフ
オースの影響をさほど受けないようにすることが
できる。なお、本発明者の実験結果によれば、弁
体４２に作用するフローフオースは第５図に示し
た弁体１２に作用するフローフオースの略半分に
なることが判明した。 In addition, in the flow control valve of this embodiment, the tapered surface 42a1 of the poppet valve portion 42a and the valve seat 41d
The path formed between them functions simply as a passage,
In addition, since the fluid is throttled in the variable throttle part A formed by the notch 42b1 provided in the spool part 42b, the annular hole 41e portion of the large diameter hole 41a, and the lower small diameter hole inner wall 41b1, the poppet valve part 42a is The flow force generated by the pressure oil flowing through the flow path formed between the tapered surface 42a1 and the valve seat 41d can be almost eliminated, and the flow force generated by the pressure oil flowing through the variable throttle part A is shown in FIG. , the axial movement of the valve body 42 due to the flow force can be reduced, and the flow path area of the variable throttle section A, which is set to a desired value, is not affected by the flow force so much. You can avoid it. According to the experimental results of the present inventor, it has been found that the flow force acting on the valve body 42 is approximately half of the flow force acting on the valve body 12 shown in FIG.
第３図は本発明の他の実施例を示していて、同
図に示した流量制御弁においては、弁本体４１が
第１〜第４部材４１Ａ〜４１Ｄによつて構成され
ていて、第４部材４１Ｄに弁座４１ｄが形成され
ている。このため、第４部材４１Ｄの材質を例え
ば鉄として弁座４１ｄの耐久性向上を図ることが
できる。また、弁本体４１の第２部材４１Ｂと第
４部材４１Ｄが一体的に結合された状態に第１部
材４１Ａ内に組付けられており、第２部材４１Ｂ
と第４部材４１Ｄ内には弁体４２とばね４３が予
め組込まれている。このため、この流量制御弁に
おいては、組付性がよいといつた利点やばね４３
の取付荷重を予め調整することができるといつた
利点がある。なお、その他の構成は第１図に示し
た流量制御弁の構成と実質的に同じである。ま
た、第３図に示した実施例の作用・効果は上述し
た第１図及び第２図にて示した実施例の作用・効
果と実質的に同じであるため、その説明は省略す
る。 FIG. 3 shows another embodiment of the present invention, and in the flow control valve shown in the same figure, the valve body 41 is constituted by first to fourth members 41A to 41D, and the fourth A valve seat 41d is formed on the member 41D. Therefore, the durability of the valve seat 41d can be improved by using iron as the material of the fourth member 41D, for example. Further, the second member 41B and the fourth member 41D of the valve body 41 are assembled into the first member 41A in an integrally coupled state, and the second member 41B
A valve body 42 and a spring 43 are installed in advance in the fourth member 41D. For this reason, this flow control valve has the advantages of easy assembly and the spring 43
The advantage is that the mounting load can be adjusted in advance. Note that the other configurations are substantially the same as the configuration of the flow control valve shown in FIG. Further, since the functions and effects of the embodiment shown in FIG. 3 are substantially the same as those of the embodiment shown in FIGS. 1 and 2 described above, their explanation will be omitted.
なお、上記した実施例においては、第２図にて
示したように、第３油室Ｒ１３を絞り４４を介し
て環状溝４１ｅに連通させて、環状溝４１ｅに接
続された流路を流入路Ｐ１１とするとともに環状
溝４１ｆに接続された流路を流出路Ｐ１２とした
が、第３油室Ｒ１３を絞り４４を介して環状溝４
１ｆに連通させて、環状溝４１ｆに接続された流
路を流入路とするとともに環状溝４１ｅに接続さ
れた流路を流出路としても、上記実施例と同様の
作用・効果が期待できる。また、上記実施例にお
いては、弁本体４１の大径孔４１ａの下端部に環
状溝４１ｅを形成して、この環状溝４１ｅに流入
路Ｐ１１を連通させたが、第４図にて示したよう
に、大径孔４１ａを環状溝４１ｅの径まで大きく
して同大径孔４１ａに流入路Ｐ１１を連通させる
ようにしても、上記実施例と同様の作用・効果が
期待できる。 In the above embodiment, as shown in FIG. 2, the third oil chamber R13 is communicated with the annular groove 41e through the throttle 44, and the flow path connected to the annular groove 41e is connected to the inflow path. P11 and the flow path connected to the annular groove 41f was defined as the outflow path P12, but the third oil chamber R13 is connected to the annular groove 4 through the throttle 44.
1f and the flow path connected to the annular groove 41f is used as the inflow path, and the flow path connected to the annular groove 41e is used as the outflow path, the same effects and effects as in the above embodiment can be expected. Further, in the above embodiment, an annular groove 41e is formed at the lower end of the large diameter hole 41a of the valve body 41, and the inflow passage P11 is communicated with the annular groove 41e. Furthermore, even if the large-diameter hole 41a is enlarged to the diameter of the annular groove 41e and the inflow passage P11 is communicated with the large-diameter hole 41a, the same functions and effects as in the above embodiment can be expected.
第１図は本発明による流量制御弁の一実施例を
示す要部拡大断面図、第２図は第１図に示した流
量制御弁を主弁として構成した流量制御装置の一
例を示す全体構成図、第３図は本発明による流量
制御弁の他の実施例を示す要部拡大断面図、第４
図は本発明による流量制御弁の変形例を主弁とし
て構成した流量制御装置を示す全体構成図、第５
図は特願昭61−11709号にて提案した流量制御装
置の一例を示す全体構成図である。
符号の説明、４０……流量制御弁（主弁）、４
１……弁本体、４１ａ……大径孔、４１ｂ，４１
ｃ……小径孔、４１ｄ……弁座、４２……弁体、
４２ａ……ポペツト弁部、４２ａ１……テーパ
面、４２ｂ……スプール部、４２ｂ１……切欠、
４２ｃ……連結部、４２ｄ……ピストン部、４２
ｅ……小径部、４３……ばね、４４……絞り、Ａ
……可変絞り部、Ｐ１１……流入路（第１流入出
路）、Ｐ１２……流出路（第２流入出路）、Ｐ６…
…戻り路、Ｒ１１……第１油室、Ｒ１２……第２
油室、Ｒ１３……第３油室。
FIG. 1 is an enlarged cross-sectional view of essential parts showing an embodiment of a flow control valve according to the present invention, and FIG. 2 is an overall configuration showing an example of a flow control device configured with the flow control valve shown in FIG. 1 as a main valve. FIG. 3 is an enlarged cross-sectional view of main parts showing another embodiment of the flow control valve according to the present invention, and FIG.
Figure 5 is an overall configuration diagram showing a flow control device in which a modification of the flow control valve according to the present invention is used as the main valve.
The figure is an overall configuration diagram showing an example of a flow rate control device proposed in Japanese Patent Application No. 11709/1983. Explanation of symbols, 40...Flow rate control valve (main valve), 4
1...Valve body, 41a...Large diameter hole, 41b, 41
c...Small diameter hole, 41d...Valve seat, 42...Valve body,
42a...poppet valve part, 42a1...tapered surface, 42b...spool part, 42b1...notch,
42c...Connection part, 42d...Piston part, 42
e...Small diameter part, 43...Spring, 44...Aperture, A
...Variable throttle part, P11...Inflow path (first inflow/output path), P12...Outflow path (second inflow/output path), P6...
...Return path, R11...First oil chamber, R12...Second
Oil chamber, R13...3rd oil chamber.
Claims (1)
軸的に設けてなり、一方の小径孔と前記大径孔間
の段部に弁座を形成するとともに、同弁座の前記
大径孔側に第１流入出路を接続し、また一方の小
径孔の中間部に第２流入出路を接続してなる弁本
体と、 前記大径孔内に前記第１流入出路から受ける圧
力が常に相殺される状態にて嵌挿されてテーパ面
にて前記弁座に着座したり離脱して前記両流入出
路間を連通遮断するポペツト弁部と、同ポペツト
弁部の一側に設けられて前記一方の小径孔に摺動
自在に嵌挿されるスプール部と、同スプール部の
一側に設けられて前記一方の小径孔内に延び同小
径孔との間に前記第２流入出路に連通する第１油
室を形成する連結部と、同連結部の一側に設けら
れて前記一方の小径孔に摺動自在に嵌挿され同小
径孔端にパイロツト圧が付与される第２油室を形
成するピストン部を一体的に備えるとともに、前
記ポペツト弁部の他側に設けられて前記他方の小
径孔に摺動自在に嵌挿され同小径孔端に前記両流
入出路のうち流入路となる流路に絞りを介して常
に接続されるとともに戻り路に選択的に接続され
る第３油室を形成する小径部を一体的に備え、ま
た前記スプール部の外周に前記第３油室側への軸
方向移動によつて前記ポペツト弁部のテーパ面と
弁座間に形成される流路面積より流路面積が常に
小さい可変絞り部を前記大径孔及び一方の小径孔
内壁とにより構成する切欠を備える弁体と、 同弁体を前記第２油室に向けて付勢するばねを
具備してなる流量制御弁。[Scope of Claims] 1 Small diameter holes of the same diameter are coaxially provided on both sides of a large diameter hole, and a valve seat is formed in the step between one of the small diameter holes and the large diameter hole, and A valve body having a first inflow/outflow passage connected to the large diameter hole side of the seat and a second inflow/outflow passage connected to an intermediate portion of one of the small diameter holes; a poppet valve portion that is inserted into the valve seat in a state where the pressures received are always canceled out and seats on the valve seat with a tapered surface, and separates from the valve seat to cut off communication between the two inflow and outflow passages, and one side of the poppet valve portion. a spool portion provided on one side of the spool portion and slidably inserted into the one small diameter hole; and a second inflow/outflow path provided on one side of the spool portion and extending into the one small diameter hole between the second small diameter hole. a connecting portion forming a first oil chamber communicating with the first oil chamber; and a second connecting portion provided on one side of the connecting portion and slidably inserted into the one small diameter hole and applying pilot pressure to the end of the small diameter hole. A piston part that forms an oil chamber is integrally provided, and the piston part is provided on the other side of the poppet valve part and is slidably inserted into the other small diameter hole, and the inflow and outflow passages are connected to the end of the small diameter hole. It is integrally provided with a small diameter portion forming a third oil chamber that is always connected to the flow path via a throttle and selectively connected to the return path, and the third oil chamber is provided on the outer periphery of the spool portion. A variable throttle portion whose flow path area is always smaller than the flow path area formed between the tapered surface of the poppet valve portion and the valve seat by axial movement toward the chamber side is formed between the large diameter hole and the inner wall of one of the small diameter holes. A flow control valve comprising: a valve body having a notch; and a spring urging the valve body toward the second oil chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16446286A JPS6319405A (en) | 1986-07-11 | 1986-07-11 | Flow control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16446286A JPS6319405A (en) | 1986-07-11 | 1986-07-11 | Flow control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6319405A JPS6319405A (en) | 1988-01-27 |
| JPH0557443B2 true JPH0557443B2 (en) | 1993-08-24 |
Family
ID=15793631
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16446286A Granted JPS6319405A (en) | 1986-07-11 | 1986-07-11 | Flow control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6319405A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2577225B2 (en) * | 1987-06-23 | 1997-01-29 | 株式会社小松製作所 | Flow control valve |
| JPH01115001U (en) * | 1988-01-29 | 1989-08-02 |
-
1986
- 1986-07-11 JP JP16446286A patent/JPS6319405A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6319405A (en) | 1988-01-27 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |