JPH0313571Y2 - - Google Patents
Info
- Publication number
- JPH0313571Y2 JPH0313571Y2 JP8501286U JP8501286U JPH0313571Y2 JP H0313571 Y2 JPH0313571 Y2 JP H0313571Y2 JP 8501286 U JP8501286 U JP 8501286U JP 8501286 U JP8501286 U JP 8501286U JP H0313571 Y2 JPH0313571 Y2 JP H0313571Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- spring
- return
- check valve
- return side
- 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
- 238000002347 injection Methods 0.000 claims description 26
- 239000007924 injection Substances 0.000 claims description 26
- 239000000446 fuel Substances 0.000 claims description 18
- 230000007423 decrease Effects 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
Description
【考案の詳細な説明】
（産業上の利用分野）
この考案は、燃料噴射ポンプに用いられる送出
弁であつて特に等圧形のものに関する。[Detailed Description of the Invention] (Industrial Field of Application) This invention relates to a delivery valve used in a fuel injection pump, and particularly to an isobaric type.
（従来の技術）
等圧形送出弁は、例えば特開昭58−65966号公
報により公知となつている。これは、送出側逆止
弁と戻し側逆止弁とを有し、燃料噴射ポンプのプ
ランジヤにより高圧室の燃料の圧力が高まると送
出側逆止弁が開かれて燃料を送出する一方、噴射
終了後は戻し側逆止弁が開かれて噴射管内が所定
の残圧となるようにしたものである。(Prior Art) An equal pressure type delivery valve is known, for example, from Japanese Patent Application Laid-Open No. 58-65966. This has a check valve on the delivery side and a check valve on the return side. When the fuel pressure in the high pressure chamber is increased by the plunger of the fuel injection pump, the delivery side check valve is opened and fuel is sent out, while the injection After completion, the return side check valve is opened to maintain a predetermined residual pressure in the injection pipe.
（考案が解決しようとする問題点）
しかしながら、従来においては、戻し側逆止弁
には、ばね定数に一定のスプリングが用いられて
いたので、ポンプ回転数が増大し、噴射圧が高く
なつて噴射弁からの反射波が大きくなるのに従つ
て戻し側逆止弁のオーバーシユートが大きくな
り、その結果、ポンプ回転数が増大するにつれて
噴射管内の残圧が低くなり、噴射管内の残圧が低
くなり、噴射管内の残圧が変動するという問題点
があつた。(Problem to be solved by the invention) However, in the past, the return side check valve used a spring with a constant spring constant, so the pump rotation speed increased and the injection pressure increased. As the reflected wave from the injection valve increases, the overshoot of the return side check valve increases, and as a result, as the pump rotation speed increases, the residual pressure in the injection pipe decreases, and the residual pressure in the injection pipe decreases. There was a problem that the residual pressure inside the injection pipe fluctuated as the pressure became low.
そこで、この考案は、上記の問題点を解消し、
戻し側逆止弁のオーバーシユートを防ぎ、使用さ
れるポンプ回転数の全域で噴射管内の残圧を等し
く保持し、もつて噴射系の安定性と内燃機関の性
能向上を図ることができる等圧形送出弁を提供す
ることを課題としている。 Therefore, this idea solves the above problems and
It prevents the return side check valve from overshooting, maintains the residual pressure in the injection pipe equally over the entire pump rotation speed range, and thereby improves the stability of the injection system and the performance of the internal combustion engine. The objective is to provide a pressure-type delivery valve.
（問題点を解決するための手段）
しかして、戻し側逆止弁は所定のリフトから急
激に反発力が増大するので、噴射弁からの反射波
が大きくてもオーバーシユートを少なくすること
ができ、そのため上記課題を達成することができ
るものである。(Means for solving the problem) However, since the repulsive force of the return side check valve increases rapidly after a predetermined lift, it is difficult to reduce overshoot even if the reflected wave from the injection valve is large. Therefore, the above-mentioned problem can be achieved.
（実施例）
第１図において、等圧形送出弁は、弁ホルダ１
とこの弁ホルダ１の下部に挿入された弁座体２と
を有し、弁ホルダ１内に送出側逆止弁３が、弁座
体２内に戻し側逆止弁４がそれぞれ配置されてい
る。(Example) In Fig. 1, the isobaric type delivery valve has a valve holder 1
and a valve seat body 2 inserted into the lower part of the valve holder 1, a delivery side check valve 3 is disposed inside the valve holder 1, and a return side check valve 4 is disposed inside the valve seat body 2. There is.
送出側逆止弁３はポペツト状の送出側弁体５を
有し、該弁体５が弁ホルダ１との間に設けられた
送出側スプリング６に押圧されて、弁座体２の一
端に形成された送出側弁座面７に着座し、弁ホル
ダ１内に形成された出口側通路８から弁座体２に
形成された入口側通路９への燃料の逆流を阻止す
るようになつている。出口側通路８は噴射管を介
して燃料噴射弁に接続され、また、入口側通路９
は燃料噴射ポンプの高圧室に接続される。 The delivery side check valve 3 has a poppet-shaped delivery side valve body 5, and the valve body 5 is pressed by a delivery side spring 6 provided between the valve holder 1 and the valve seat body 2 at one end. The valve seats on the formed delivery side valve seat surface 7 and prevents the backflow of fuel from the outlet side passage 8 formed in the valve holder 1 to the inlet side passage 9 formed in the valve seat body 2. There is. The outlet side passage 8 is connected to a fuel injection valve via an injection pipe, and the inlet side passage 9 is connected to a fuel injection valve via an injection pipe.
is connected to the high pressure chamber of the fuel injection pump.
戻し側逆止弁４は球状の戻し側弁体１０を有
し、該弁体１０が前述した送出側弁体５の一端に
形成された戻し側弁座面１１に着座し、前述した
入口側通路９から送出側弁体５内に形成された戻
し通路１２への逆流を阻止するようになつてい
る。戻し通路１２は、オリフイス１３を介して前
述した出口側通路８に接続されている。上記戻し
側弁体１０には上部スプリング受け１４が当接
し、また、前述した弁座体２には下部スプリング
受け１５が固定されており、該スプリング受け１
４，１５の間に戻し側スプリング１６が弾装さ
れ、この戻し側スプリング１６により戻し側弁体
１０が上方へ押圧されている。 The return side check valve 4 has a spherical return side valve body 10, and the valve body 10 is seated on a return side valve seat surface 11 formed at one end of the above-mentioned delivery side valve body 5. It is designed to prevent backflow from the passage 9 to the return passage 12 formed in the delivery side valve body 5. The return passage 12 is connected to the aforementioned outlet passage 8 via an orifice 13. An upper spring receiver 14 is in contact with the return side valve body 10, and a lower spring receiver 15 is fixed to the aforementioned valve seat body 2.
A return side spring 16 is elastically mounted between 4 and 15, and the return side valve body 10 is pressed upward by the return side spring 16.
戻し側スプリング１６は例えば不等ピツチばね
から構成され、第２図に示すように、たわみδが
所定値δ1までは反発力Ｆのたわみδに対する変
化、即ち、ばね定数が小さいが、所定値δ1以上に
なると急激に大きくなる特性をもつているもので
ある。 The return side spring 16 is composed of an unequal pitch spring, for example, and as shown in FIG . It has the property of rapidly increasing when δ exceeds 1 .
上記構成において、燃料噴射ポンプのプランジ
が吐出行程に入ると、入口側通路９の燃料の圧力
が上昇し、送出側逆止弁３が開かれ、出口側通路
８から噴射管を介して燃料噴射弁へ送出される。
入口側通路９の燃料の圧力が低下すると送出側逆
止弁３が閉じられ、燃料の送出が終了する。ここ
で、噴射管内の圧力が所定値よりも高いと戻し側
逆止弁４が開かれ、戻し通路１２を介して一部の
燃料が入口側通路９へ戻される。この戻し側逆止
弁４が開かれる時には、戻し側弁体１０が戻し側
スプリング１６に抗してリフトするが、この戻し
側スプリング１６は第２図に示すような特性をも
つので、そのたわみδが所定値δ1になるまでは急
激なリフトを許す一方、所定値δ1を越すような外
力に対してはほとんどリフトしなくなる。 In the above configuration, when the plunge of the fuel injection pump enters the discharge stroke, the pressure of the fuel in the inlet side passage 9 increases, the delivery side check valve 3 is opened, and the fuel is injected from the outlet side passage 8 through the injection pipe. sent to the valve.
When the pressure of the fuel in the inlet side passage 9 decreases, the delivery side check valve 3 is closed, and the delivery of fuel is completed. Here, when the pressure inside the injection pipe is higher than a predetermined value, the return side check valve 4 is opened, and a part of the fuel is returned to the inlet side passage 9 via the return passage 12. When the return check valve 4 is opened, the return valve body 10 lifts against the return spring 16, but since the return spring 16 has the characteristics shown in FIG. While a rapid lift is allowed until δ reaches a predetermined value δ 1 , there is almost no lift in response to an external force that exceeds the predetermined value δ 1 .
即ち、この戻し側スプリング１６は、戻し側弁
体１０が所定のリフトに達したところで弾性的に
それ以上のリフトを阻止するストツパとしての機
能をもつており、このため、オーバーシユートを
少なくすることができるものである。 That is, the return side spring 16 has a function as a stopper that elastically prevents the return side valve body 10 from lifting further when it reaches a predetermined lift, and therefore reduces overshoot. It is something that can be done.
尚、この実施例においては、戻し側スプリング
として不等ピツチばねを用いたが、二重コイルば
ね等、第２図に示した特性を示すものであればよ
い。 In this embodiment, an unequal pitch spring is used as the return spring, but any spring having the characteristics shown in FIG. 2 may be used, such as a double coil spring.
（考案の効果）
以上述べたように、この考案によれば、燃料噴
射ポンプの等圧形送出弁において、戻し側スプリ
ングとしてばね定数が所定のたわみ以上で大とな
るものを用いたので、戻し側逆止弁のオーバーシ
ユートを少なくすることができ、使用されるポン
プ回転数の全域で噴射管内の残圧を等しく保持す
ることができ、このため、噴射系の安定性と内燃
機関の性能向上に寄与することができる。また、
戻し側スプリングはたわみの所定値までは、ばね
定数が小さくなつているので、長期の使用におけ
る戻し側スプリングのへたりによる設定圧低下の
割合を小さくすることができ、耐久性も向上させ
ることができるものである。(Effects of the invention) As described above, according to this invention, in the isobaric type delivery valve of the fuel injection pump, a spring whose spring constant becomes large when the deflection exceeds a predetermined value is used as the return side spring. Overshoot of the side check valve can be reduced, and the residual pressure in the injection pipe can be maintained equally over the entire range of pump rotation speeds used, thus improving the stability of the injection system and the performance of the internal combustion engine. can contribute to improvement. Also,
Since the spring constant of the return side spring is small until the deflection reaches a predetermined value, the rate of decrease in set pressure due to fatigue of the return side spring during long-term use can be reduced, and durability can also be improved. It is possible.
第１図はこの考案の実施例を示す断面図、第２
図は戻し側スプリングの特性を示す線図である。
３……送出側逆止弁、４……戻し側逆止弁、１
６……戻し側スプリング。
Figure 1 is a sectional view showing an embodiment of this invention, Figure 2 is a sectional view showing an embodiment of this invention.
The figure is a diagram showing the characteristics of the return side spring. 3... Delivery side check valve, 4... Return side check valve, 1
6...Return side spring.
Claims (1)
噴射ポンプの等圧形送出弁において、前記戻し
側逆止弁にばね定数が所定のたわみ以上で大と
なる戻し側スプリングを設けたことを特徴とす
る燃料噴射ポンプの等圧形送出弁。 ２ 戻し側スプリングは不等ピツチばねから構成
されたことを特徴とする実用新案登録請求の範
囲第１項記載の燃料噴射ポンプの等圧形送出
弁。[Scope of Claim for Utility Model Registration] 1. In an isobaric delivery valve of a fuel injection pump having a delivery side check valve and a return side check valve, the spring constant of the return side check valve is large at a predetermined deflection or more. An equal pressure type delivery valve for a fuel injection pump, characterized by being provided with a return side spring. 2. The equal pressure delivery valve for a fuel injection pump according to claim 1, wherein the return side spring is comprised of an unequal pitch spring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8501286U JPH0313571Y2 (en) | 1986-06-04 | 1986-06-04 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8501286U JPH0313571Y2 (en) | 1986-06-04 | 1986-06-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62197773U JPS62197773U (en) | 1987-12-16 |
| JPH0313571Y2 true JPH0313571Y2 (en) | 1991-03-27 |
Family
ID=30940028
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8501286U Expired JPH0313571Y2 (en) | 1986-06-04 | 1986-06-04 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0313571Y2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101865062A (en) * | 2010-06-03 | 2010-10-20 | 宁波舜田良源油嘴油泵有限公司 | Constant pressure oil outlet valve |
| CN107842452A (en) * | 2017-10-09 | 2018-03-27 | 中国第汽车股份有限公司 | A kind of monoblock type combined valve device, can pressure initialization fuel oil on-off controlling system and control method |
| WO2022091553A1 (en) * | 2020-10-28 | 2022-05-05 | 日立Astemo株式会社 | Fuel pump |
-
1986
- 1986-06-04 JP JP8501286U patent/JPH0313571Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62197773U (en) | 1987-12-16 |
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