JPH0366546B2 - - Google Patents
Info
- Publication number
- JPH0366546B2 JPH0366546B2 JP22252984A JP22252984A JPH0366546B2 JP H0366546 B2 JPH0366546 B2 JP H0366546B2 JP 22252984 A JP22252984 A JP 22252984A JP 22252984 A JP22252984 A JP 22252984A JP H0366546 B2 JPH0366546 B2 JP H0366546B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- screw
- thread
- valve stem
- stopper
- 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
- 239000000696 magnetic material Substances 0.000 claims description 2
- 230000001141 propulsive effect Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000005415 magnetization Effects 0.000 description 1
- 230000005405 multipole Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Landscapes
- Electrically Driven Valve-Operating Means (AREA)
- Magnetically Actuated Valves (AREA)
Description
〔産業上の利用分野〕
本発明は、ルームエアコンやカーエアコンなど
の冷凍サイクル中に用いられる電子制御膨張弁、
あるいは一般の産業分野でマイコンと組合せて使
用する比例制御弁として利用される電動弁に関す
るものである。
〔従来の技術の構成〕
ステツピングモータと弁を合せてマイコンによ
り制御する電動弁としてとくに構造が簡単で、か
つ廉価な物を提供するために第４図に示すような
構成の電動弁が実用化されている。
その構成・作動を第４図により詳細に説明する
と、弁軸１は先端から針状弁３、おねじ４、外周
多極着磁された円筒形の永久磁石からなるモータ
の回転子５の順に一体化して形成され、おねじ４
は、弁本体６に固定され中心にめねじ７を切つた
推進軸受８とはめあわされている。
モータの固定子５の外周は薄肉円筒状のケース
９でおおい、このケース９の外側には、モータの
固転子５に対応する位置にモータの固定子コイル
１０が固定されている。
ケース９は流体の出入口１１，１２と弁座２を
有する弁本体６にプラズマ溶接などにより気密的
に一体化され、ケース９の他端も蓋１３により密
閉化されている。
１４は比較的強力なコイルバネであり、弁軸１
のおねじ４後方の弁軸１太径部１ａと推進軸受８
の間で圧縮可能なようにはめこまれ、１５も同様
に強力なコイルバネで、弁軸１の最後端の段付部
１ｂにかめこみ固定され、弁軸１が蓋１３側へ移
動した時に、蓋１３の内面部に当たり、圧縮可能
なように構成されている。おねじ４、めねじ７で
構成される推進ねじ１６は、ねじ効率50％未満の
範囲で高い効率が得られるよう、たとえば２条ね
じなどで構成されている。
〔従来品の作動〕
以上のように構成された従来品においては、モ
ータの固定子コイル１０に所定量の通電をする
と、回転子５が回転し、おねじ４とめねじ７のね
じ作用により弁軸１は回転しながら前方（閉弁方
向）に移動してコイルバネ１４と推進軸受８面と
を当接させ、針状弁３が弁座２に着座して完全閉
弁することなく、針状弁３と弁座２間にきわめて
わずかな隙間を保つた状態で停止するようになつ
ている。このように、針状弁３と弁座２間に隙間
を設けているのは、ねじ部４，７間に強いねじつ
け摩擦力が発生し、次の開弁運動が不能になると
いつたことを避けるためである。
次に、弁軸１は後方（開弁方向）に移動し、コ
イルバネ１５と蓋１３内面が当接して、弁軸１の
直進運動が停止させられる。
〔発明が解決しようとする問題点〕
以上のように構成された従来の電動弁は、弁軸
１と回転子５が一体型で、かつ直進運動を直接停
止させる構造を採用するため、部品数が少なく、
かつ複雑な加工や調整を要しないきわめて廉価に
製造できるという利点を有しているが、反面、閉
弁時における弁軸の停止に際しては、おねじ４と
推進軸受のめねじ７がきつく咬み合い閉弁後の弁
軸１の逆方向起動（開弁５をスムーズに行えなか
つたり、あるいは全く再起動させることができな
いという欠点を有していた。
そこで、弁軸１の逆方向起動（開弁）をスムー
ズに行えるように、推進ねじのねじ効率が50％以
上の自然ゆるみねじを使うことが考えられるが、
これでは、固定子コイル１０への非通電時に流体
の流れによつて弁軸が回転してしまい電動弁の制
御が不可能となるので、実際には、２条ねじにし
て、ねじリードを大きくするなどの手段を用いて
ねじ効率を50％未満近づけるようにしている。し
かし、この場合にはねじ効率を上げる限度があつ
て、場合によつては弁軸１の逆方向起動（開弁）
をスムーズに行えなかつたり、また、ねじ作用に
よつて発生する弁軸１の推進力が小くなるという
欠点があつた。
なお、ここでねじ効率とねじの緩みの関係を、
ねじの理論面から説明する。
一般に、締付トルクT1に対する緩めトルクT2
の比率T2／T1×100（％）が小さいほどねじが緩
みやすく、またねじ効率ηが大きいほどねじが緩
みやすいと言われ、次の公式で表れる。
T1＝Ｆ｛De／２・tan（ρ＋β）｝×102 (1)
T2＝Ｆ｛De／２・tan（ρ−β）｝×102 (2)
η＝tan β／tan（ρ＋β）×100（％） (3)
Ｆ ：ねじ部にかかる軸力（Kg）
De：ねじの有効径（mm）
ρ ：ねじ面の摩擦相当角（゜）
ρ＝tan-1（μ／cos α）
μ ：ねじ面の摩擦係数…0.15とする。
β ：ねじのリード角（゜）
β＝tan-1（ｌ／π・De）
ｌ ：ねじのリード（mm）
ここで上式(1)〜(3)に、例えば
Ａ仕様：ねじM5×P0.8 JIS並目めじ
Ｂ仕様：ねじM5×P0.8×２条ねじ
の異なつたねじについて各値を計算すると、下表
に示すように、ねじ効率ηの高いＢ仕様の方が締
めトルク比T2／T1が小さくなり、弁軸の停止後
の逆方向への起動がスムーズに行える。
[Industrial Application Field] The present invention relates to an electronically controlled expansion valve used during the refrigeration cycle of room air conditioners, car air conditioners, etc.
Alternatively, it relates to an electric valve used as a proportional control valve in combination with a microcomputer in the general industrial field. [Constitution of conventional technology] In order to provide a particularly simple and inexpensive electric valve that combines a stepping motor and a valve and is controlled by a microcomputer, an electric valve having the configuration shown in Fig. 4 has been put into practical use. has been made into To explain the structure and operation in detail with reference to FIG. 4, the valve stem 1 is arranged in order from the tip: a needle valve 3, a male screw 4, and a motor rotor 5 consisting of a cylindrical permanent magnet with multi-pole magnetization on the outer periphery. Integrated and formed, male thread 4
is fitted with a propulsion bearing 8 which is fixed to the valve body 6 and has a female thread 7 cut in the center. The outer periphery of the stator 5 of the motor is covered with a thin cylindrical case 9, and a stator coil 10 of the motor is fixed to the outside of the case 9 at a position corresponding to the stator rotor 5 of the motor. The case 9 is hermetically integrated with a valve body 6 having fluid inlets and outlets 11 and 12 and a valve seat 2 by plasma welding or the like, and the other end of the case 9 is also hermetically sealed with a lid 13. 14 is a relatively strong coil spring, and the valve stem 1
male thread 4 rear valve shaft 1 large diameter portion 1a and propulsion bearing 8
Similarly, 15 is also a strong coil spring and is fixed to the stepped portion 1b at the rearmost end of the valve stem 1, so that when the valve stem 1 moves toward the lid 13, It corresponds to the inner surface of the lid 13 and is configured to be compressible. The propulsion screw 16 composed of the male thread 4 and the female thread 7 is composed of, for example, a double thread thread so as to obtain high efficiency within a range of less than 50% thread efficiency. [Operation of conventional product] In the conventional product configured as described above, when a predetermined amount of current is applied to the stator coil 10 of the motor, the rotor 5 rotates and the valve is opened by the screw action of the male screw 4 and the female screw 7. The shaft 1 moves forward (in the valve closing direction) while rotating and brings the coil spring 14 into contact with the propulsion bearing 8 surface. It is designed to stop with an extremely small gap maintained between the valve 3 and the valve seat 2. The reason why there is a gap between the needle valve 3 and the valve seat 2 is to avoid the possibility that a strong threading friction force will be generated between the threaded parts 4 and 7, making the next valve opening movement impossible. This is to avoid. Next, the valve stem 1 moves rearward (in the valve opening direction), and the coil spring 15 and the inner surface of the lid 13 come into contact with each other, and the linear motion of the valve stem 1 is stopped. [Problems to be solved by the invention] The conventional electric valve configured as described above has a structure in which the valve shaft 1 and the rotor 5 are integrated and directly stops linear motion, so the number of parts is reduced. There are few
It has the advantage that it can be manufactured at a very low cost without requiring complicated machining or adjustment. However, on the other hand, when the valve stem stops when closing the valve, the male thread 4 and the female thread 7 of the propulsion bearing mesh tightly. This had the disadvantage that the valve stem 1 could not be started in the reverse direction (valve opening 5) after closing the valve smoothly, or it could not be restarted at all. ), it is conceivable to use a self-loosening screw with a thread efficiency of 50% or more for the propulsion screw.
In this case, when the stator coil 10 is de-energized, the valve shaft rotates due to the flow of fluid, making it impossible to control the motor-operated valve. Therefore, in reality, a double thread thread is used to increase the thread lead. We are trying to bring the screw efficiency closer to less than 50% by using methods such as However, in this case, there is a limit to increasing screw efficiency, and in some cases, the valve shaft 1 may be started in the reverse direction (opening the valve).
This has disadvantages in that the valve shaft 1 cannot be moved smoothly and the propulsive force of the valve shaft 1 generated by the screw action is reduced. In addition, here, the relationship between screw efficiency and screw loosening is
I will explain from the theoretical side of screws. In general, the loosening torque T 2 for the tightening torque T 1
It is said that the smaller the ratio T 2 /T 1 ×100 (%), the easier the screw will loosen, and the larger the screw efficiency η, the easier the screw will loosen, and this is expressed by the following formula. T 1 =F{De/2・tan(ρ+β)}×10 2 (1) T 2 =F{De/2・tan(ρ−β)}×10 2 (2) η=tan β/tan(ρ+β )×100(%) (3) F: Axial force applied to the threaded part (Kg) De: Effective diameter of the thread (mm) ρ: Equivalent angle of friction on the threaded surface (°) ρ=tan -1 (μ/cos α ) μ: Coefficient of friction on the thread surface…0.15. β: Thread lead angle (°) β=tan -1 (l/π・De) l: Thread lead (mm) Here, in the above formulas (1) to (3), for example, A specification: thread M5 x P0 .8 JIS coarse thread B specification: When calculating each value for different screws (M5 x P0.8 x 2 threads), as shown in the table below, B specification with higher thread efficiency η has a higher tightening torque ratio. T 2 /T 1 becomes smaller, allowing smooth startup in the opposite direction after the valve stem has stopped.
本発明の電動弁の構造は、弁軸１を前後進させ
るためのおねじ４は、推進力を高くとれるように
すると共に、弁軸１の前後進を停止させるための
ねじを弁軸１の後端部に一体的に設け、このねじ
を、ねじ効率＞50％で自然にゆるむねじを設けた
ものである。
即ち、非磁性体からなるケース９外周部に固定
したモータの固定子コイル１０への通電により、
ケース内に収納したおねじ４を有する弁軸１と一
体的に形成したモータの回転子５を回転させ、こ
の回転をめねじ７を切た推進軸受８により弁軸１
の直進運動に変換することによつて弁座２の開口
度を制御する電動弁において、弁軸１の最後端に
ねじ効率50％以上のストツパーボルト１７を弁軸
１と一体に設け、このストツパーボルト１７に、
中心のめねじをはさんで対称位置に設けた２個の
貫通孔１８ａを有するストツパーナツト１８をね
じ込むと共にその後端には当て板２１を固定し、
一方、蓋１３の内面に固定した２本のピン２０を
前記ストツパーナツトの２個の貫通孔１８ａに挿
入したことを特徴とする電動弁の構造である。
〔作 用〕
本発明は、弁軸１を前後進させるためのおねじ
４の他に、弁軸１の前後進を停止させるためのね
じを弁軸１の後端部に一体的に設けられているか
ら、弁軸１に設けられた針状弁３が弁座２に着座
し完全閉弁する手前で、ストツパーナツト１８の
背が当て板２１に当たり、弁軸１の回転・直進運
動が停止する。この時にねじの締付力は、ねじ効
率ηが50％以上のものを使用している停止用ねじ
１９部だけにはたらき、従来のように、閉弁時に
おける弁軸の停止に際して、おねじ４と推進軸受
のめねじ７がきつく咬み合うようなことがないの
で、閉弁後の弁軸１の逆方向起動（開弁）をスム
ーズに行うことができる。
また、弁軸１の開弁後においては、弁軸１のス
トツパーボルト１７前方の太径部１ａ面に当た
り、弁軸１の回転・直進運動が停止し、閉弁停止
時と同様に作用する。
〔実施例〕
本発明の構成を第１図〜第３図によつて説明す
る。第１図、第２図において同一番号を符したも
のは従来品と同等のはたらきをする部品であり、
これらの詳細な説明は省略する。
本発明の従来品との相違点を以下に説明する
と、
本発明におけるおねじ４とめねじ７による推進
ねじ１６は、ねじ効率50％未満（例えば、
M4P0.75×１条ねじ）のものを使用し、ねじの緩
みが起きにくいものにしている。このわけは、同
一モータの出力トルクであつても、推進ねじ１６
部で推進力に変換され、流体力に打勝つて弁軸１
が前後進するのに必要な推進力を大きくするため
である。
また、弁軸１の最後端には、弁軸１と一体的に
ねじ効率50％以上（例えば、M3.5×P1.0×２条
ねじ）のストツパーボルト１７が設けられてい
る。そして、このストツパーボルト１７には、中
心のめねじをはさんで対称位置に設けた２個の貫
通孔１８ａを有するストツパーナツト１８をねじ
込むと共に、その後端にストツパーボルト１７の
外径より大なる当て板２１がかしめなどの法によ
つて固定されている。
一方、蓋１３の内には、ストツパーナツト１８
の２個の貫通孔１８ａと対応する位置に同一ピツ
チで孔１８ａの径より小さい径の２本のピン２０
が圧入などにより固定され、この２本のピン２０
が前記ストツパーナツト１８の２個の貫通孔１８
ａ内に通されている。
なお、前記ピン２０が挿入される貫通孔１８ａ
にかえて、図示しないが縦方向の切り溝を設けて
もよい。また、推進ねじ１６と停止用ねじ１９の
ねじ巻き方向は右、左いずれでもよい。
次に、本発明の働きを、推進ねじリードl1＜停
止用ねじリードl2とし同方向ねじの場合について
説明する。
固定子コイル１０に一定量閉方向に回転るよう
通電されると、モータの回転子５および弁軸１は
一体的に回転し、推進ねじの作用で１回転につき
弁軸１はリードl1分前進する。
一方、ストツパーナツト１８は、ピン２０によ
り回転を止められているためストツパーボルト１
７に対してはリードl2分、ピン２０に対しては
（l2−l1）分後方移動する。
そして、弁軸１が所定量閉弁方向に回転して針
状弁３が弁座２完全に着座する手前で、ストツパ
ーナツト１８の背面が当て板２１に当たり、弁軸
１の回転・直進運動が停止する。この状態が第１
図に示すものである。
なお、弁軸１の移動量とストツパーナツト１８
の移動量との関係についけは、弁軸１がｎ回転
し、（ｎ×l1）分弁軸が前進した距離と、ストツ
パーナツト１８がｎ×（l2−l1）分、ピン２０上を
滑つて当て板２１に当たる距離が等しくなるよう
にしてある。
そして、弁軸１の回転・直進運動が停止する際
のねじの締付力は、ねじ効率ηが50％以上のもの
を使用している停止用ねじ１９部だけにはたら
き、従来のように、閉弁時における弁軸の停止に
際して、おねじ４と推進軸受のめねじ７がきつく
咬み合うようなことがないので、閉弁後の弁軸１
の逆方向起動（開弁）をスムーズに行うことがで
きる。また、停止用ねじ１９部が強力にねじ込め
ばねじ込むほど、ストツパーナツト１８が当て板
２１に当つた時の反力はねじが緩む方向の力とし
て作用することになり、次の開く方向への運動に
は支障をきたさない。
続いて開弁方向への通電が固定子コイル１０に
なされると、ストツパーナツト１８はすみやかに
当て板２１面から離れ、弁軸１は後方向へ回転・
直進しストツパーナツト１８は前方向へピン２０
に沿つて摺動し、ついには第２図に示すように弁
軸１のストツパーボルト１７前方の太径部１ａ面
に当たり、閉弁停止と同様ストツパーナツト１８
の直進・弁軸１の回転・直進運動が停止する。
〔発明の効果〕
以上、説明したごとく、従来品においては推進
用と直進停止用の双方の機能を持つていたねじを
推進だけのねじ部と直進停止のためだけのねじ部
それぞれに分割して、弁軸１上に別々設けたこと
により各機能に即したねじ形状を選択でき、その
結果
(1) 弁軸１を前後進させるためのおねじ４の他
に、弁軸１の前後進を停止させるためのねじを
弁軸１の後端部に一体的に設けられているか
ら、弁軸１の回転・直進運動が停止する際のね
じの締付力は、ねじ効率ηが50％以上のものを
使用している停止用ねじ１９部だけにはたらく
ので、停止後の逆方向への再起動がスムーズ行
える。
２ 弁軸１を推進力を高くでき、モータの小形化
や人力電流の低減ができる。
といつた効果が得られ産業上有益な発明である。
The structure of the electrically operated valve of the present invention is such that the male thread 4 for moving the valve stem 1 back and forth allows a high propulsive force to be obtained, and the screw for stopping the valve stem 1 from moving back and forth. This screw is integrally provided at the rear end, and this screw is provided with a screw that loosens naturally when the screw efficiency is >50%. That is, by energizing the stator coil 10 of the motor fixed to the outer periphery of the case 9 made of a non-magnetic material,
A rotor 5 of a motor integrally formed with a valve shaft 1 having a male thread 4 housed in a case is rotated, and this rotation is transferred to the valve shaft 1 by a propulsion bearing 8 having a female thread 7.
In a motor-operated valve that controls the opening degree of the valve seat 2 by converting it into a linear motion, a stopper bolt 17 with a thread efficiency of 50% or more is provided integrally with the valve shaft 1 at the rear end of the valve shaft 1. To stopper bolt 17,
A stopper nut 18 having two through holes 18a provided at symmetrical positions across the center female thread is screwed in, and a backing plate 21 is fixed to the rear end.
On the other hand, this electric valve structure is characterized in that two pins 20 fixed to the inner surface of the lid 13 are inserted into two through holes 18a of the stopper nut. [Function] In addition to the external thread 4 for moving the valve stem 1 back and forth, the present invention has a screw integrally provided at the rear end of the valve stem 1 to stop the valve stem 1 from moving back and forth. Therefore, before the needle valve 3 provided on the valve stem 1 seats on the valve seat 2 and is completely closed, the back of the stopper nut 18 hits the backing plate 21, and the rotational and linear movement of the valve stem 1 stops. . At this time, the tightening force of the screw acts only on the 19 stop screws that have a screw efficiency η of 50% or more. Since the female thread 7 of the propulsion bearing does not mesh tightly, the valve shaft 1 can be smoothly started in the reverse direction (opening the valve) after the valve is closed. In addition, after the valve stem 1 is opened, it hits the large diameter portion 1a in front of the stopper bolt 17 of the valve stem 1, and the rotational and linear movement of the valve stem 1 is stopped, acting in the same manner as when the valve is closed and stopped. . [Example] The structure of the present invention will be explained with reference to FIGS. 1 to 3. Components with the same numbers in Figures 1 and 2 are parts that function in the same way as conventional products.
Detailed explanations of these will be omitted. The differences between the present invention and conventional products will be explained below.
M4P0.75 x 1 thread thread) is used to make it difficult for the screw to come loose. This is because even if the output torque of the same motor is the same, the propulsion screw 16
It is converted into propulsive force at the valve shaft 1, which overcomes the fluid force.
This is to increase the propulsive force required to move forward and backward. Further, at the rearmost end of the valve stem 1, a stopper bolt 17 with a thread efficiency of 50% or more (for example, M3.5×P1.0×2 thread thread) is provided integrally with the valve stem 1. Then, a stopper nut 18 having two through holes 18a provided at symmetrical positions across the central female thread is screwed into this stopper bolt 17, and a stopper nut 18 having a diameter larger than the outside diameter of the stopper bolt 17 is screwed into the rear end. The backing plate 21 is fixed by caulking or other methods. On the other hand, inside the lid 13 is a stopper nut 18.
Two pins 20 with the same pitch and a diameter smaller than the diameter of the holes 18a are placed at positions corresponding to the two through holes 18a.
are fixed by press fitting etc., and these two pins 20
are the two through holes 18 of the stopper nut 18.
It is passed through a. Note that the through hole 18a into which the pin 20 is inserted is
Alternatively, although not shown, vertical grooves may be provided. Further, the winding direction of the propulsion screw 16 and the stop screw 19 may be either right or left. Next, the operation of the present invention will be described in the case where the propulsion screw lead l 1 <the stopping screw lead l 2 and screws in the same direction. When the stator coil 10 is energized to rotate by a certain amount in the closing direction, the rotor 5 of the motor and the valve shaft 1 rotate integrally, and the valve shaft 1 has a lead l of 1 minute per rotation due to the action of the propulsion screw. Advance. On the other hand, since the stopper nut 18 is prevented from rotating by the pin 20, the stopper bolt 1
For pin 20, it moves backward by lead l 2 minutes, and for pin 20 it moves backward by (l 2 −l 1 ). Then, before the valve stem 1 rotates a predetermined amount in the valve-closing direction and the needle valve 3 is completely seated on the valve seat 2, the back of the stopper nut 18 hits the backing plate 21, and the rotation and linear movement of the valve stem 1 stops. do. This state is the first
This is shown in the figure. In addition, the amount of movement of the valve stem 1 and the stopper nut 18
Regarding the relationship between the amount of movement of The distance between the two sliders and the contact plate 21 is made equal. Then, the tightening force of the screw when the rotation and linear movement of the valve stem 1 is stopped acts only on the stop screw 19, which uses screw efficiency η of 50% or more, and as in the conventional case, When the valve stem stops when the valve is closed, the male thread 4 and the female thread 7 of the propulsion bearing do not mesh tightly, so the valve stem 1 after the valve closes
The reverse direction start (valve opening) can be performed smoothly. In addition, the more strongly the stopper screw 19 is screwed in, the more the reaction force when the stopper nut 18 hits the backing plate 21 will act as a force in the direction of loosening the screw, which will prevent the next movement in the opening direction. does not cause any hindrance. Subsequently, when the stator coil 10 is energized in the valve opening direction, the stopper nut 18 immediately separates from the backing plate 21 surface, and the valve shaft 1 rotates rearward.
Go straight and the stopper nut 18 will move forward to the pin 20
Finally, as shown in Fig. 2, the valve shaft 1 hits the large diameter portion 1a in front of the stopper bolt 17, and the stopper nut 18
The linear movement of the valve stem 1 and the rotation and linear movement of the valve stem 1 stop. [Effects of the Invention] As explained above, the screw, which had the functions of both propulsion and straight-line stopping in conventional products, is divided into a screw part only for propulsion and a threaded part only for straight-line stopping. By providing separate threads on the valve stem 1, it is possible to select the thread shape that suits each function.As a result, (1) In addition to the external thread 4 for moving the valve stem 1 forward and backward, Since the screw for stopping is integrally provided at the rear end of the valve stem 1, the tightening force of the screw when the rotational/linear motion of the valve stem 1 is stopped has a screw efficiency η of 50% or more. Since it works only on the stopping screw 19 that is used, restarting in the opposite direction after stopping can be performed smoothly. 2. The driving force of the valve shaft 1 can be increased, the motor can be made smaller, and the human power current can be reduced. This is an industrially useful invention with the following effects.
第１図は本発明の一実施例で閉弁状態を示す縦
断面図、第２図は第１図の実施例で開弁状態を示
す縦断面図、第３図は停止用ねじ部を示す斜視
図、第４図は従来の縦断面図。
１……弁軸、２……弁座、３……針状弁、４…
…おねじ、５……モータの回転子、６……弁本
体、７……めねじ、８……推進軸受、９……ケー
ス、１０……モータの固定子コイル、１１１２…
…出入口、１３……蓋、１４１５……コイルバ
ネ、１６……推進ねじ、１７……ストツパーボル
ト、１８……ストツパーナツト、１９……停止用
ねじ、２０……ピン、２１……当て板、１ａ……
弁軸の太径部、１ｂ……弁軸の段付部、１８ａ…
…ストツパーナツトの外周孔。
Fig. 1 is a longitudinal sectional view showing an embodiment of the present invention in a valve closed state, Fig. 2 is a longitudinal sectional view showing the embodiment of Fig. 1 in an open state, and Fig. 3 shows a stop screw part. A perspective view, and FIG. 4 is a conventional longitudinal sectional view. 1... Valve stem, 2... Valve seat, 3... Needle valve, 4...
... Male thread, 5 ... Motor rotor, 6 ... Valve body, 7 ... Female thread, 8 ... Propulsion bearing, 9 ... Case, 10 ... Motor stator coil, 1112 ...
... Doorway, 13 ... Lid, 1415 ... Coil spring, 16 ... Propulsion screw, 17 ... Stopper bolt, 18 ... Stopper nut, 19 ... Stopping screw, 20 ... Pin, 21 ... Backing plate, 1a ……
Large diameter part of the valve stem, 1b...Stepped part of the valve stem, 18a...
...Peripheral hole of stopper nut.
Claims (1)
モータの固定子コイル１０への通電により、ケー
ス内に収納したおねじ４を有する弁軸１と一体的
に形成したモータの回転子５を回転させ、この回
転をめねじ７を切つた推進軸受８により弁軸１の
直進運動に変換することによつて弁座２の開口度
を制御する電動弁において、弁軸１の最後端にね
じ効率50％以上のストツパーボルト１７を弁軸１
と一体的に設け、このストツパーボルト１７に、
中心のめねじをはさんで対称位置に設けた２個の
貫通孔１８ａを有するストツパーナツト１８をね
じ込むと共にその後端には当て板２１を固定し、
一方、蓋１３の内面に固定した２本のピン２０を
前記ストツパーナツトの２個の貫通孔１８ａに挿
入したことを特徴とする電動弁の構造。1 By energizing the stator coil 10 of the motor fixed to the outer periphery of the case 9 made of a non-magnetic material, the rotor 5 of the motor, which is integrally formed with the valve shaft 1 having the male thread 4 housed inside the case, is rotated. In this electric valve, the degree of opening of the valve seat 2 is controlled by converting this rotation into a linear movement of the valve stem 1 using a propulsion bearing 8 with a female thread 7. 50% or more of the stopper bolt 17 is attached to the valve stem 1
Provided integrally with this stopper bolt 17,
A stopper nut 18 having two through holes 18a provided at symmetrical positions across the central female thread is screwed in, and a backing plate 21 is fixed to the rear end.
On the other hand, the electric valve structure is characterized in that two pins 20 fixed to the inner surface of the lid 13 are inserted into the two through holes 18a of the stopper nut.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22252984A JPS61103077A (en) | 1984-10-23 | 1984-10-23 | Constitution of motor-operated valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22252984A JPS61103077A (en) | 1984-10-23 | 1984-10-23 | Constitution of motor-operated valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61103077A JPS61103077A (en) | 1986-05-21 |
| JPH0366546B2 true JPH0366546B2 (en) | 1991-10-17 |
Family
ID=16783856
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22252984A Granted JPS61103077A (en) | 1984-10-23 | 1984-10-23 | Constitution of motor-operated valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61103077A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0613125U (en) * | 1991-12-18 | 1994-02-18 | 富士通テン株式会社 | Vertical mounting electronic components |
| JP4550528B2 (en) | 2004-09-01 | 2010-09-22 | 株式会社不二工機 | Motorized valve |
| JP5649365B2 (en) * | 2010-08-11 | 2015-01-07 | 三菱電機株式会社 | Air conditioner |
| JP6175715B2 (en) * | 2013-11-29 | 2017-08-09 | 株式会社テージーケー | Stepping motor driven control valve |
-
1984
- 1984-10-23 JP JP22252984A patent/JPS61103077A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61103077A (en) | 1986-05-21 |
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