JPH0356782A - Flow control valve - Google Patents
Flow control valveInfo
- Publication number
- JPH0356782A JPH0356782A JP19294789A JP19294789A JPH0356782A JP H0356782 A JPH0356782 A JP H0356782A JP 19294789 A JP19294789 A JP 19294789A JP 19294789 A JP19294789 A JP 19294789A JP H0356782 A JPH0356782 A JP H0356782A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- valve body
- steps
- flow control
- gap
- 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.)
- Pending
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 46
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 238000011144 upstream manufacturing Methods 0.000 abstract description 4
- 238000010276 construction Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000009499 grossing Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 239000006228 supernatant Substances 0.000 description 1
Landscapes
- Details Of Valves (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は給湯器より出湯する湯等の流量を調整制御する
水量制御弁において、流通音の発生を小さくしたＸｉ音
の小さい弁の構造に関するものである，
従来の技術
一般に袷湯器は第５図に示す如く、熱交ｌＡ器八から出
湯する湯の設定湯温を一定に保つために流量の流れ過ぎ
を押える水量制御弁Ｂが給湯器の出湯路Ｃに設けられて
いる．Ｄは水量センサ、Ｅは湯温検知のサーミスタであ
る。このような水量制御弁Ｂを使用した水量制御装置を
第６図に示し、そして第７図は水量制御弁の断面図であ
る．この装置はモータＩが回転することにより歯車２と
連動して歯車３が回転し、内側にネジを有する軸受４と
周動ずることにより軸５が前後に動く．それに伴い軸５
の先に取り付いている弁体６が動き、弁受７との隙間９
の面積を変えることにより流量を調整する。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a water flow control valve that adjusts and controls the flow rate of hot water, etc. discharged from a water heater, and relates to a structure of a valve with low noise, which reduces the generation of flow noise. Conventional technology In general, as shown in Figure 5, in a water heater, a water flow control valve B is installed in the water heater to prevent excessive flow in order to keep the set temperature of hot water constant from the heat exchanger IA. It is installed at hot spring path C. D is a water flow sensor, and E is a thermistor for detecting water temperature. A water flow control device using such a water flow control valve B is shown in FIG. 6, and FIG. 7 is a sectional view of the water flow control valve. In this device, when a motor I rotates, a gear 3 rotates in conjunction with a gear 2, and a shaft 5 moves back and forth by rotation with a bearing 4 having a screw inside. Along with this, axis 5
The valve body 6 attached to the tip of moves and the gap 9 between the valve receiver 7 and
Adjust the flow rate by changing the area of the
そして、元水圧が高い場合は弁体６と弁受７の隙間９を
小さくして流量を調整するため、特に大流量を流す場合
は隙間９を通過する水は高速度となる。When the source water pressure is high, the flow rate is adjusted by reducing the gap 9 between the valve body 6 and the valve seat 7, so that the water passing through the gap 9 has a high velocity especially when a large flow rate is flowing.
発明が解決しようとする課題
第７図に示す従来例のように単純に弁体６と弁受７の隙
間９の面積を変えて流量を調整する構戒では従来の技術
で記載した様に高水圧で大流量を流す場合、隙間９をｉ
１遇する水は高速度になり、噴流の衝突によって第６図
の如くキャビテーシタン泡８が発生し、大きな遣水騒音
が発生するという課題を有していた．
本発明は、上記課題を解消するもので、弁体、弁受前後
の高差圧を小さ＜シ゛ζ、噴流の衝突を緩和することに
よりキ＋ビテーシゴン泡の発生を少なくし、低騒音化を
はかることを目的とする．課題を解決するための手段
前記目的を達威するために本発明の水量制御弁は第１手
段として多数段の隙間によって隙間面積を絞るものであ
る．
また、本発明の第２手段は弁体と弁受の相対向する面の
距離を長くして、大きな面で隙間面積を絞るものである
．
さらに本発明の第３手段は弁体と弁受の相対向する面の
距離を長くして、隙間面積を大きな面で絞るとともに、
弁受側の対向面の一部に窪みを設けて抵抗をつけるもの
である。Problems to be Solved by the Invention In the conventional example shown in FIG. 7, in which the flow rate is adjusted by simply changing the area of the gap 9 between the valve body 6 and the valve seat 7, the flow rate is increased as described in the conventional technology. When flowing a large flow rate with water pressure, the gap 9 should be
The problem is that the flowing water has a high velocity, and the collision of the jets generates cavity bubbles 8 as shown in Figure 6, causing a large water spray noise. The present invention solves the above-mentioned problems by reducing the high differential pressure between the valve body and the valve seat, reducing the collision of jets, thereby reducing the generation of air bubbles and reducing noise. The purpose is to measure. Means for Solving the Problems In order to achieve the above object, the water flow control valve of the present invention, as a first means, narrows the gap area by using multiple stages of gaps. Moreover, the second means of the present invention is to increase the distance between the opposing surfaces of the valve body and the valve receiver, thereby narrowing down the gap area on the larger surface. Furthermore, the third means of the present invention is to increase the distance between the facing surfaces of the valve body and the valve seat, thereby narrowing the gap area to a large surface, and
A depression is provided in a part of the opposing face on the valve receiving side to provide resistance.
さらに本発明の第４手段は弁受に相対向する面の弁体の
弁角度を６０″〜７０°にして、かつその後の形状をな
めらかにし、また弁受の入口側の弁角度を９０＠にした
後にストレート部を設け、出口側の弁角度を６０’〜７
０°と末広がりにするとともに弁体の外径と弁受の内径
差を０。３〜１．０ｍと微小にするものである。Furthermore, the fourth means of the present invention is to set the valve angle of the valve element on the surface facing the valve receiver to 60'' to 70°, and to make the subsequent shape smooth, and to set the valve angle on the inlet side of the valve receiver to 90°. After that, a straight part is installed, and the valve angle on the outlet side is set to 60' to 7.
It widens toward the end at 0°, and the difference between the outer diameter of the valve body and the inner diameter of the valve seat is minutely reduced to 0.3 to 1.0 m.
作用
上記の第１手段では多数段の絞りにより隙間での局部的
な高差圧が小さくなり、隙間を通遇する水の流速が小さ
くなる．
また、第２手段では弁体、弁受の相対向する大きな面で
絞ることにより隙間での局部的な高差圧が小さくなり、
隙間を通過する水の流速が小さくなる。Effect: In the first means described above, the local high differential pressure in the gap is reduced by multiple stages of throttling, and the flow rate of water passing through the gap is reduced. In addition, in the second means, the local high differential pressure in the gap is reduced by squeezing the opposing large surfaces of the valve body and valve seat.
The flow rate of water passing through the gap is reduced.
さらに、第３手段では弁体、弁受の相対向する大きな面
で絞るとともに、弁受の窪みによる抵抗により隙間での
局部的な高差圧が小さくなり隙間を通過する水の流速が
小さくなる。Furthermore, in the third means, the valve body and the valve seat are narrowed by the opposing large surfaces, and the local high differential pressure in the gap is reduced due to the resistance due to the depression of the valve seat, and the flow rate of water passing through the gap is reduced. .
さらに、第４手段では弁体の人口から入った水は徐々に
絞られた後弁受のストレート部で整流され、出口部から
徐々に末広がりに開放されることにより噴流の衝突を緩
和する．
実施例
以下第１図〜第４図にしたがい本発明の各実施例を説明
する．第６図に示す水量制御装置の水量制御弁Ｂにおき
かえて使用するものである．第１図は第１の実施例を示
し、軸５に固定した弁体６１は上清から下流に向って径
小になる略円錐台形状をなし、外周面６１ａをほぼ等間
隔に２段階にわたり、しだいに径小にして段差をつけて
いる。Furthermore, in the fourth means, the water that enters through the valve body is gradually squeezed and then rectified in the straight part of the valve receiver, and is gradually released from the outlet part in a widening direction, thereby alleviating the impact of the jet flow. EXAMPLES Below, each example of the present invention will be explained according to FIGS. 1 to 4. This is used in place of water flow control valve B of the water flow control device shown in Figure 6. FIG. 1 shows a first embodiment, in which a valve body 61 fixed to the shaft 5 has a substantially truncated conical shape whose diameter decreases from the supernatant toward the downstream, and extends over the outer circumferential surface 61a in two stages at approximately equal intervals. , the diameter is gradually reduced and steps are added.
また、弁体６ｌに相対向して隙間９１ （絞り流路）を
形威する弁受７ｌの内周面７１ａも弁体６ｌと同様に段
差をつけている．したがって、高水圧の状態で入った水
は矢印のように弁体６１と弁受７ｌの相対向する面の隙
間９１で多数段に絞られることにより、水は絞りと開放
を数回繰り返して徐々に減圧され隙間９１を通遇する流
速が小さくなり、噴疏の衝突が緩和され、キャビテーシ
ジン泡の発生を押えることができる．
また低水圧の状態では軸５を左方へ移動させて、弁体６
１と弁受７１の隙間９１を大きくすることにより圧力損
失を小さくして、大流量を確保する．第２図は本発明の
第２の実施例を示し、弁体６１の外周面６ｌｂと弁受７
１の内周面７ｌｂは、ともに上流から下流に向ってスト
レートに径がしだいに小さくせしめて隙間９１の長さを
充分にとってある．したがって、高水圧の状態で入った
矢印の水は弁体６ｌと弁受７１の相対向する面（外周面
６ｌｂ、内周面７ｌｂ）の長い距離で絞られることによ
り、徐々に減圧され隙間９１を通過する流速が小さくな
り、噴流の衝突が緩和され、キャビテーシ吋ン泡の発生
を押えることができる．
また低水圧の状態では第１実施例と同様に、大流量を確
保できる．
第３図は本発明の第３の実施例を示し、上記した第２実
施例と相違するのは弁受７１の内周面７１ｃの途中に周
囲全体にわたり窪み１０を設けた点で、それ以外は同一
構造である．したがって、高水圧の状態で入った矢印の
水は弁体６１と弁受７ｌの相対向する面の長い距離で絞
られるとともに弁受７１の内周面７１ｃの窪み１０によ
る抵抗により、徐々に減圧され隙間９ｌを通過する流速
が小さくなり、噴流の衝突が緩和され、キャビテーシッ
ン泡の発生を押えることができる．
また低水圧の状態では第１実施例と同様に、大流量を確
保できる．
第４図は本発明の第４の実施例を示し、弁体６ｌ１は上
流側より下流側にかけて次第に径大になる傾斜外面６１
１ ａと径が変化しない等径外面６１ｌｂと上流より下
流に向けて弁角度６０〜７０＠でしだい径小にした外周
面６１１ ｃとからなる形状にしている．また、弁受７
ｌは内周面を弁角度９０°の部分とこれに続くストレー
ト部ｌ１で構或する．したがって、高水圧の状態で入っ
た水は弁角度６０′″〜７０°の弁体６１１と弁角度７
１ａを９０度にした弁受７１を通遇することにより、徐
々に絞られた後弁受７１のストレート部ｌ１で整流され
、弁体６１１のなめらかな形状と弁受７１の弁開度７ｌ
ｂを６０゜〜７０＠の末広がりにして流れが開放される
ことにより噴流の衝突が緩和され、キャビテーシッン泡
の発生を押さえることができる．
また低水圧の状態では第１実施例と同様に、大流量を確
保できる．
発明の効果
以上説明したように本発明によれば次のような作用効果
を期待できる．
請求項１によれば、元水圧が高い場合、流水に弁体と弁
受の相対向する面の間にできた絞り流路で数段にわたっ
て絞りと開放を繰り返す作用を与えることによって、減
圧の効果が大きく、キャビテーシッン泡の発生を防ぎ、
騒音の発生が非常に小さくできる．
また、請求項２．３においては弁体と弁受の相対向する
面により形威される絞り流路が大きな面で絞り徐々に減
圧するので、キャビテーシｊン泡の発生を押え、騒音の
低下に効果がある．また形状も簡易であるので低コスト
にすることができる．さらに請求項４によれば、水の流
れをなめらかにすることにより、噴流の衝突が緩和され
、キャビテーション泡の発生を押え、騒音の低下に効果
がある．
さらに請求項ｌ〜４によれば低水圧の状態では弁体と弁
受の間に形威される絞り流路を大きくすることにより圧
力損失を小さくして大ｔｌＬＩが確保できる．Further, the inner circumferential surface 71a of the valve seat 7l, which faces the valve element 6l and forms a gap 91 (throttled flow path), is also stepped in the same way as the valve element 6l. Therefore, the water that enters under high water pressure is squeezed in multiple stages through the gap 91 between the facing surfaces of the valve body 61 and the valve receiver 7l as shown by the arrow, and the water gradually repeats squeezing and opening several times. The pressure is reduced, the flow velocity passing through the gap 91 is reduced, the impact of the blow canal is alleviated, and the generation of cavity siding bubbles can be suppressed. In addition, in a state of low water pressure, the shaft 5 is moved to the left and the valve body 6 is
By enlarging the gap 91 between 1 and the valve receiver 71, pressure loss is reduced and a large flow rate is ensured. FIG. 2 shows a second embodiment of the present invention, in which the outer peripheral surface 6lb of the valve body 61 and the valve seat 7
The diameter of the inner circumferential surface 7lb of both cases gradually decreases in a straight line from upstream to downstream to provide a sufficient length of the gap 91. Therefore, the water indicated by the arrow that enters under high pressure is squeezed over a long distance between the opposing surfaces (outer circumferential surface 6 lb, inner circumferential surface 7 lb) of the valve body 6l and the valve receiver 71, and the pressure is gradually reduced and the pressure is gradually reduced to the gap 91. The flow velocity passing through the jet is reduced, the collision of the jets is alleviated, and the generation of cavitation bubbles can be suppressed. Also, in a state of low water pressure, a large flow rate can be ensured as in the first embodiment. FIG. 3 shows a third embodiment of the present invention, which is different from the second embodiment described above in that a recess 10 is provided in the middle of the inner circumferential surface 71c of the valve receiver 71 over the entire circumference. have the same structure. Therefore, the water indicated by the arrow that enters under high water pressure is squeezed by the long distance between the facing surfaces of the valve body 61 and the valve receiver 7l, and the pressure is gradually reduced due to the resistance caused by the depression 10 on the inner circumferential surface 71c of the valve receiver 71. The flow velocity passing through the gap 9l is reduced, the collision of the jets is relaxed, and the generation of cavitation bubbles can be suppressed. Also, in a state of low water pressure, a large flow rate can be ensured as in the first embodiment. FIG. 4 shows a fourth embodiment of the present invention, in which the valve body 6l1 has an inclined outer surface 61 whose diameter gradually increases from the upstream side to the downstream side.
1a, an outer surface 61lb whose diameter does not change, and an outer peripheral surface 611c whose diameter gradually decreases from upstream to downstream at a valve angle of 60 to 70@. Also, Benke 7
1 has an inner peripheral surface consisting of a portion with a valve angle of 90° and a straight portion l1 following this. Therefore, the water entering under high pressure is transferred to the valve body 611 with a valve angle of 60'' to 70° and the valve angle 7.
By passing the valve holder 71 with angle 1a at 90 degrees, the flow is gradually narrowed down and then rectified by the straight part 11 of the valve holder 71, resulting in the smooth shape of the valve body 611 and the valve opening degree 7l of the valve holder 71.
By widening b to 60° to 70° and opening the flow, the collision of jets is alleviated, and the generation of cavitation bubbles can be suppressed. Also, in a state of low water pressure, a large flow rate can be ensured as in the first embodiment. Effects of the Invention As explained above, according to the present invention, the following effects can be expected. According to claim 1, when the source water pressure is high, the pressure is reduced by giving the flowing water the effect of repeatedly throttling and opening in several stages in the throttling channel formed between the facing surfaces of the valve body and the valve seat. It is highly effective and prevents cavitation bubbles from forming.
Noise generation can be extremely reduced. In addition, in claim 2.3, the throttle flow path formed by the opposing surfaces of the valve body and the valve seat is throttled by a large surface and the pressure is gradually reduced, suppressing the generation of cavitation bubbles and reducing noise. It is effective. Also, since the shape is simple, costs can be reduced. Furthermore, according to claim 4, by smoothing the flow of water, the collision of jets is alleviated, the generation of cavitation bubbles is suppressed, and noise is reduced. Furthermore, according to claims 1 to 4, in a state of low water pressure, by enlarging the throttle flow path formed between the valve body and the valve seat, pressure loss can be reduced and a large tLI can be ensured.
Claims (4)
える弁体を有し、この弁体の外周面である傾き形状部に
ほぼ等間隔の多数段を設け、かつ弁体と相対向する弁受
の傾き形状部にも弁体の多数段と同間隙、同数の段を設
けてこの弁体と弁受けの間に絞り流路を多数段有する水
量制御弁。(1) It has a valve body that changes its opening area with the valve seat by moving its position, and has multiple stages at approximately equal intervals on the slanted outer circumferential surface of the valve body, and faces opposite to the valve body. The water flow control valve has the same number of stages with the same gaps as the multiple stages of the valve body in the inclined shape part of the valve body, and has multiple stages of throttling channels between the valve body and the valve base.
える弁体を有し、この弁体の外周面に一定距離を有する
傾き面を設け、かつ弁体と相対向する弁受にも同角度で
一定距離を有する傾き面を有する水量制御弁。(2) It has a valve body that changes its opening area with the valve receiver by moving its position, and an inclined surface with a certain distance is provided on the outer circumferential surface of the valve body, and also on the valve receiver that faces the valve body. A water flow control valve with inclined surfaces having the same angle and a certain distance.
える弁体を有し、この弁体の外周面に一定距離を有する
傾き面を設け、かつ弁体と相対向する弁受に同角度で一
定距離を有する傾き面と傾き面の一部に窪みを有する水
量制御弁。(3) It has a valve body whose opening area with respect to the valve seat can be changed by moving the position, and an inclined surface having a certain distance is provided on the outer peripheral surface of this valve body, and the valve body facing the valve body has the same slope. A water flow control valve having an inclined surface having a certain distance in angle and a depression in a part of the inclined surface.
える弁体を有し、この弁体の外周面に弁角度６０゜〜７
０゜の傾き面とその後になめらかな形状の面を有すると
ともに、弁体と相対向する弁受けに弁角度９０゜の傾き
面、ストレート面、及び出口側に弁角度６０゜〜７０゜
の末広がりの傾きを有し、かつ弁体の外径を弁受けの内
径より０．３〜１．０ｍｍ大きくした水量制御弁。(4) It has a valve body that changes its opening area with the valve receiver by moving its position, and the outer peripheral surface of this valve body has a valve angle of 60° to 7.
It has a 0° inclined surface and a smooth surface after that, a 90° inclined surface on the valve receiver facing the valve body, a straight surface, and a flared end with a valve angle of 60° to 70° on the outlet side. A water flow control valve having an inclination of 0.3 to 1.0 mm, and the outer diameter of the valve body is 0.3 to 1.0 mm larger than the inner diameter of the valve receiver.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19294789A JPH0356782A (en) | 1989-07-25 | 1989-07-25 | Flow control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19294789A JPH0356782A (en) | 1989-07-25 | 1989-07-25 | Flow control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0356782A true JPH0356782A (en) | 1991-03-12 |
Family
ID=16299661
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19294789A Pending JPH0356782A (en) | 1989-07-25 | 1989-07-25 | Flow control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0356782A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005351605A (en) * | 2004-06-14 | 2005-12-22 | Daikin Ind Ltd | Expansion valve and refrigeration device |
| US10302201B2 (en) | 2017-08-30 | 2019-05-28 | Sun Hydraulics, Llc | Enhancement of valve flow and pressure characteristics in valves and hydraulic systems |
| US11054046B2 (en) | 2016-12-30 | 2021-07-06 | Parker-Hannifin Corporation | Valve with gradual flow area changes |
-
1989
- 1989-07-25 JP JP19294789A patent/JPH0356782A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005351605A (en) * | 2004-06-14 | 2005-12-22 | Daikin Ind Ltd | Expansion valve and refrigeration device |
| US11054046B2 (en) | 2016-12-30 | 2021-07-06 | Parker-Hannifin Corporation | Valve with gradual flow area changes |
| US10302201B2 (en) | 2017-08-30 | 2019-05-28 | Sun Hydraulics, Llc | Enhancement of valve flow and pressure characteristics in valves and hydraulic systems |
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