JPH034780Y2 - - Google Patents
Info
- Publication number
- JPH034780Y2 JPH034780Y2 JP1985024378U JP2437885U JPH034780Y2 JP H034780 Y2 JPH034780 Y2 JP H034780Y2 JP 1985024378 U JP1985024378 U JP 1985024378U JP 2437885 U JP2437885 U JP 2437885U JP H034780 Y2 JPH034780 Y2 JP H034780Y2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- vane
- feed pump
- pressure
- drive shaft
- 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
- 239000000446 fuel Substances 0.000 claims description 45
- 239000003921 oil Substances 0.000 claims description 27
- 239000010687 lubricating oil Substances 0.000 claims description 26
- 238000002347 injection Methods 0.000 claims description 15
- 239000007924 injection Substances 0.000 claims description 15
- 230000001050 lubricating effect Effects 0.000 claims description 3
- 238000003780 insertion Methods 0.000 description 12
- 230000037431 insertion Effects 0.000 description 12
- 238000005461 lubrication Methods 0.000 description 11
- 230000005284 excitation Effects 0.000 description 6
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000007865 diluting Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
- F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
- F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
- F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
- F02M41/125—Variably-timed valves controlling fuel passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
この考案は、デイーゼル機関に使用される分配
型の燃料噴射ポンプに関するものである。[Detailed Description of the Invention] (Industrial Application Field) This invention relates to a distribution type fuel injection pump used in diesel engines.
（従来の技術）
いわゆるボツシユ式の分配型燃料噴射ポンプ
は、噴射ポンプ本体内のリア側にフイードポンプ
を設け、このフイードポンプと噴射ポンプ本体の
ヘツド部との間にカム室を構成し、このカム室に
おいて駆動軸とプランジヤとをカムによつて連結
して、このプランジヤに往復回転動を与えるよう
にしている。(Prior Art) A so-called bottle-type distribution fuel injection pump includes a feed pump provided on the rear side of the injection pump body, a cam chamber formed between the feed pump and the head portion of the injection pump body, and a cam chamber formed between the feed pump and the head portion of the injection pump body. The drive shaft and the plunger are connected by a cam so as to impart reciprocating rotational motion to the plunger.
そして、通常、上記カム室が燃料室として利用
され、フイードポンプから吐出された燃料がカム
室に入り、その入つた燃料がカム等への潤滑にも
供せられるようになつているが、燃料は粘度が低
く、潤滑油としての性能が不十分であるため、特
に高負荷、高速で使用されるものにあつては、カ
ム等への潤滑のために専用の潤滑油を用いたいと
いう要求があつた。 Normally, the cam chamber is used as a fuel chamber, and the fuel discharged from the feed pump enters the cam chamber, and the entered fuel is also used to lubricate the cam etc. Due to its low viscosity and insufficient performance as a lubricating oil, there is a demand for the use of a special lubricating oil to lubricate cams, etc., especially when used at high loads and high speeds. Ta.
この要求を満足する手段として、特開昭56−
154134号公報においては、噴射ポンプ本体のヘツ
ド部に電磁弁を設けて、シリンダとプランジヤと
に囲まれた圧力室から溢流する燃料量を制御し、
この電磁弁によりカム室のガバナや制御スリーブ
を代わりを成さしめ、フイードポンプの出口と電
磁弁の入口とを、カム室を迂回する連通路を介し
て連通し、カム室には燃料の流通を遮断して専用
の潤滑を供給するようにしたことが開示されてい
る。 As a means to satisfy this requirement,
In Publication No. 154134, a solenoid valve is provided in the head of the injection pump body to control the amount of fuel overflowing from a pressure chamber surrounded by a cylinder and a plunger.
This solenoid valve replaces the governor and control sleeve of the cam chamber, and the outlet of the feed pump and the inlet of the solenoid valve are communicated via a communication path that bypasses the cam chamber, so that fuel does not flow into the cam chamber. It is disclosed that a dedicated lubrication is supplied by shutting off the lubrication.
（考案が解決しようする問題点）
しかしながら、上記公報においては、カム室を
含む潤滑空間とフイードポンプとの間のシールに
ついては何等開示しておらず、このシールを通常
のオイルシールによつて行わせると、フイードポ
ンプで加圧された燃料の圧力がオイルシールにか
かり、その燃料がオイルシールの部分から潤滑空
間へ漏れて潤滑空間内の潤滑油を希釈し、潤滑油
の性能を低下させるという問題点があつた。(Problem to be solved by the invention) However, the above-mentioned publication does not disclose anything about the seal between the lubrication space including the cam chamber and the feed pump, and this seal is performed by an ordinary oil seal. The problem is that the pressure of the fuel pressurized by the feed pump is applied to the oil seal, and the fuel leaks from the oil seal into the lubrication space, diluting the lubricating oil in the lubrication space and reducing the performance of the lubricating oil. It was hot.
そこで、この考案は、フイードポンプの燃料が
潤滑空間に漏れるのを防止し、より耐久性に優れ
た分配型の燃料噴射ポンプを提供することを課題
としている。 Therefore, the object of this invention is to provide a distribution type fuel injection pump that prevents the fuel from the feed pump from leaking into the lubrication space and is more durable.
（問題点を解決するための手段）
しかして、この考案の要旨とするところは、潤
滑油が供給される潤滑空間に隣接してフイードポ
ンプを設けた分配型燃料噴射ポンプにおいて、前
記潤滑空間とフイードポンプとの間を駆動軸の周
囲に設けられたオイルシールをもつてシールし、
このオイルシールが配置されたシール室と前記フ
イードポンプの低圧側とを圧力逃がし通路を介し
て連通したことにある。(Means for Solving the Problems) The gist of this invention is that in a distributed fuel injection pump in which a feed pump is provided adjacent to a lubrication space to which lubricating oil is supplied, the lubrication space and the feed pump An oil seal installed around the drive shaft is used to seal the gap between the
The seal chamber in which the oil seal is disposed communicates with the low pressure side of the feed pump through a pressure relief passage.
（作用）
したがつて、シール室とフイードポンプの低圧
側とが圧力逃がし通路を介して連通しているの
で、オイルシールにかかる燃料の圧力をフイード
ポンプの低圧側に逃がし、このシール室の圧力を
オイルシールを介して燃料が漏れる圧力値以下に
制限することができ、そのため上記課題を達成す
ることができるものである。(Function) Therefore, since the seal chamber and the low pressure side of the feed pump communicate through the pressure relief passage, the pressure of the fuel applied to the oil seal is released to the low pressure side of the feed pump, and the pressure in this seal chamber is released to the oil It is possible to limit the pressure to a value below which fuel leaks through the seal, and therefore the above object can be achieved.
（実施例）
以下、この考案の実施例を図面により説明す
る。(Example) Hereinafter, an example of this invention will be described with reference to the drawings.
第１図、第２図において、噴射ポンプ本体１
は、リア部１ｂの一端にヘツド部１ａが固装され
て構成されてる。該本体１のリア部１ｂの中心に
は、駆動軸挿入孔２が形成され、この駆動軸挿入
孔２に駆動軸３が挿入されている。この駆動軸３
は、駆動軸挿入孔２の両側でプレーンベアリング
４ａ，４ｂにより回転自在に支持され、該駆動軸
２の一端がリア部１ｂから突出してエンジンから
の駆動力を受けるようになつていると共に、該駆
動軸３の他端が前記本体１内に形成されたカム室
５に延びている。 In Figs. 1 and 2, the injection pump main body 1
The head part 1a is fixed to one end of the rear part 1b. A drive shaft insertion hole 2 is formed in the center of the rear portion 1b of the main body 1, and a drive shaft 3 is inserted into the drive shaft insertion hole 2. This drive shaft 3
is rotatably supported by plain bearings 4a and 4b on both sides of the drive shaft insertion hole 2, and one end of the drive shaft 2 protrudes from the rear portion 1b to receive the driving force from the engine. The other end of the drive shaft 3 extends into a cam chamber 5 formed within the main body 1.
一方、前記本体１のヘツド部１ａには、バレル
６が挿入固定され、このバレル６の中心にシリン
ダ７が形成され、このシリンダ７にプランジヤ８
が摺動自在に嵌挿されており、このシリンダ７と
プランジヤ８とにより圧力室９が構成されてい
る。このプランジヤ８の一端は、カム室５にあつ
て、ピン１０を介してカムデイスク１１の一面に
連結されている。このカムデイスク１１は、十字
状のカツプリング１２を介して前記駆動軸３の端
部に軸方向の移動を許すように連結されている。
また、このカツプリング１２の周囲には、前記本
体１のリア部１ｂに固定されたローラホルダ１３
が配置されている。このローラホルダ１３には図
示しない複数のローラが回転自在に支持されてい
ると共に、カムデイスク１１の他面には周方向に
山と谷が交互にあるカム面が形成され、このカム
面に前記ローラが当接してカムを構成している。
そして、カムデイスク１１の一面にはスプリング
受け１４を介して押圧スプリング１５の押圧力が
作用しており、駆動軸３が回転すると、プランジ
ヤ８が回転すると共に、前記カムと押圧スプリン
グ１５ととの協働により往復動するようになつて
いる。 On the other hand, a barrel 6 is inserted and fixed into the head portion 1a of the main body 1, a cylinder 7 is formed at the center of the barrel 6, and a plunger 8 is formed in the cylinder 7.
is slidably inserted therein, and the cylinder 7 and plunger 8 constitute a pressure chamber 9. One end of the plunger 8 is located in the cam chamber 5 and connected to one surface of a cam disk 11 via a pin 10. The cam disk 11 is connected to the end of the drive shaft 3 via a cross-shaped coupling 12 so as to allow axial movement.
Further, around this coupling ring 12, a roller holder 13 fixed to the rear portion 1b of the main body 1 is provided.
is located. A plurality of rollers (not shown) are rotatably supported by the roller holder 13, and a cam surface having alternating peaks and troughs in the circumferential direction is formed on the other surface of the cam disk 11, and the cam surface has the above-mentioned cam surfaces. The rollers make contact to form a cam.
The pressing force of a pressing spring 15 acts on one surface of the cam disk 11 via a spring receiver 14, and when the drive shaft 3 rotates, the plunger 8 rotates and the cam and pressing spring 15 are Collaboration has led to reciprocating movements.
電磁弁１５は、電磁弁本体１６が前記本体１の
ヘツド部１ａの上部にねじ止めされ、この電磁弁
本体１６と該本体１６の上部に固定された蓋体１
７との間にアーマチユア１８が配置されている。
また、このアーマチユア１８に対向して電磁弁本
体１６には、励磁コイル１９を有するステータ２
０が固定されている。また、アーマチユア１８の
下面中心からは弁棒２１が下方へ延び、この弁棒
２１の先端が電磁弁本体１６に形成された弁座２
２に着座している。さらに、電磁弁本体１６と弁
棒２１との間には戻しばね２３が介在されてお
り、励磁コイル１９を励磁すると、戻しばね２３
に抗して弁棒２１の先端が弁座２２に着座して、
電磁弁本体１６に形成された入口２４と出口２５
との連通を遮断し、励磁コイル１９を消磁する
と、戻しばね２３により弁棒２１の先端が弁座２
２から離れて、前記入口２４と出口２５とを連通
する。 The solenoid valve 15 has a solenoid valve main body 16 screwed to the upper part of the head portion 1a of the main body 1, and a lid body 1 fixed to the upper part of the solenoid valve main body 16 and the main body 16.
An armature 18 is disposed between the armature 7 and the armature 7.
Further, a stator 2 having an excitation coil 19 is disposed in the solenoid valve body 16 opposite to the armature 18.
0 is fixed. Further, a valve stem 21 extends downward from the center of the lower surface of the armature 18, and the tip of the valve stem 21 is connected to a valve seat 2 formed in the electromagnetic valve body 16.
I am seated at number 2. Further, a return spring 23 is interposed between the electromagnetic valve body 16 and the valve stem 21, and when the excitation coil 19 is excited, the return spring 23
The tip of the valve stem 21 seats on the valve seat 22 against the
An inlet 24 and an outlet 25 formed in the solenoid valve body 16
When the excitation coil 19 is demagnetized, the return spring 23 causes the tip of the valve stem 21 to return to the valve seat 2.
2, and communicates the inlet 24 with the outlet 25.
この電磁弁１６の出口２５は、前記本体１のヘ
ツド部１ａとバレル６に形成された燃料吸入通路
２６を介して圧力室９と連通している。また、プ
ランジヤ８の軸中心には、一端が圧力室９に開口
する縦孔２８が形成され、この縦孔２８の他端が
同じくプランジヤ８に形成された吐出グループ２
９に接続されている。この吐出グループ２９の周
囲で前記本体１のヘツド部１ａには気筒数に対応
した数の分配孔（図示せず）が形成され、この分
配孔が送出弁を有する送出部３０に接続されてい
る。 An outlet 25 of the electromagnetic valve 16 communicates with the pressure chamber 9 via a fuel intake passage 26 formed in the head portion 1a of the main body 1 and the barrel 6. Further, a vertical hole 28 whose one end opens into the pressure chamber 9 is formed at the axial center of the plunger 8, and the other end of this vertical hole 28 opens into the discharge group 2, which is also formed in the plunger 8.
Connected to 9. Around this discharge group 29, a number of distribution holes (not shown) corresponding to the number of cylinders are formed in the head portion 1a of the main body 1, and these distribution holes are connected to a delivery section 30 having a delivery valve. .
前記本体１のヘツド部１ａとリア部１ｂとには
それぞれコネクタ３１ａ，３１ｂがねじ止めされ
ている。ヘツド側のコネクタ３１ａは、前記本体
１のヘツド部１ａに形成された連通路３２を介し
て電磁弁１６の入口２４が接続されていると共
に、前記本体１の外側に設けられた接続パイプ３
３を介してリア側のコネクタ３１ｂに接続され、
該リア側のコネクタ３１ｂは、下記するフイード
ポンプ３４の燃料出口４３に接続されている。 Connectors 31a and 31b are screwed to the head portion 1a and rear portion 1b of the main body 1, respectively. The head-side connector 31a is connected to the inlet 24 of the solenoid valve 16 via a communication path 32 formed in the head portion 1a of the main body 1, and a connecting pipe 3 provided on the outside of the main body 1.
3 to the rear side connector 31b,
The rear connector 31b is connected to a fuel outlet 43 of a feed pump 34, which will be described below.
フイードポンプ３４は、前記本体１内でカム室
５に隣接して設けられ、第３図にも示すように、
それ自体は周知のベーン型で、円形のロータ３５
を有し、このロータ３５は、該ロータ３５と前記
駆動軸３とのそれぞれに形成されたキー溝３６
ａ，３６ｂに嵌合するキー３７を介して、駆動軸
３に固装されている。このロータ３５の半径方向
にはベーン溝３８が例えば90度毎に形成され、該
ベーン溝３８のそれぞれにベーン３９が摺動自在
に挿入されている。また、ロータ３５の周囲に
は、円形の案内リング４０がロータ３５から偏心
して設けられており、この案内リング４０の内面
にベーン３９の先端が案内されながらベーン３９
が回転し、ロータ３５、ベーン３９及び案内リン
グ４０に囲まれた作動室４１がロータ３５の回転
に伴つて容積変化し、リア部１ｂに形成された燃
料入口４２から燃料を吸入し、加圧して同じくリ
ア部１ｂに形成された燃料出口４３から吐出する
ようになつている。 The feed pump 34 is provided adjacent to the cam chamber 5 in the main body 1, and as shown in FIG.
The rotor itself is of a well-known vane type and has a circular rotor 35.
The rotor 35 has a keyway 36 formed in each of the rotor 35 and the drive shaft 3.
It is fixed to the drive shaft 3 via a key 37 that fits into the keys 36a and 36b. Vane grooves 38 are formed, for example, every 90 degrees in the radial direction of the rotor 35, and vanes 39 are slidably inserted into each of the vane grooves 38. Further, a circular guide ring 40 is provided around the rotor 35 eccentrically from the rotor 35, and the tips of the vanes 39 are guided by the inner surface of the guide ring 40, and the vanes 39
rotates, and the volume of the working chamber 41 surrounded by the rotor 35, vane 39, and guide ring 40 changes as the rotor 35 rotates, sucks fuel from the fuel inlet 42 formed in the rear part 1b, and pressurizes it. Similarly, the fuel is discharged from a fuel outlet 43 formed in the rear portion 1b.
前記案内リング４０は、リア部１ｂとカバー４
４との間で挟持されている。このカバー４４は、
そ中心に挿通孔４５が形成され、この挿通孔４５
に駆動軸３が挿通していると共に、該カバー４４
の反ロータ側の面に筒部４６が突出して形成さ
れ、この筒部４６と駆動軸３に形成されたフラン
ジ４７との間にワツシヤ４８が介在され、駆動軸
３、カバー４４及びワツシヤ４８に囲まれた第１
のシール室４９ａが構成されている。また、ロー
タ３５と接するリア部１ｂの面には環状溝５１が
駆動軸挿入孔２の一端に続いて形成され、駆動軸
３、プレーンベアリング４ａ、ロータ３５及び環
状溝５１に囲まれた第２のシール室４９ｂが構成
されている。上記シール室４９ａ，４９ｂにはそ
れぞれゴム等から成るオイルシール５０ａ，５０
ｂが収納され、それぞれフイードポンプ３４の作
動室４１を潤滑油が供給される潤滑空間からシー
ルするようになつている。 The guide ring 40 connects the rear portion 1b and the cover 4.
It is sandwiched between 4 and 4. This cover 44 is
An insertion hole 45 is formed in the center of the insertion hole 45.
The drive shaft 3 is inserted through the cover 44.
A cylindrical portion 46 is formed to protrude from the surface opposite to the rotor, and a washer 48 is interposed between the cylindrical portion 46 and a flange 47 formed on the drive shaft 3. surrounded first
A seal chamber 49a is configured. Further, an annular groove 51 is formed on the surface of the rear part 1b that contacts the rotor 35 following one end of the drive shaft insertion hole 2, and a second annular groove 51 surrounded by the drive shaft 3, the plain bearing 4a, the rotor 35, and the annular groove 51 is formed. A seal chamber 49b is configured. Oil seals 50a and 50 made of rubber or the like are provided in the seal chambers 49a and 49b, respectively.
b are accommodated, and each seals the working chamber 41 of the feed pump 34 from the lubricating space to which lubricating oil is supplied.
即ち、潤滑空間は、この実施例においては、フ
イードポンプ３４の両側の駆動軸挿入孔２とカム
室５とであり、前記本体１のリア部１ｂには、そ
の上部に潤滑油入口部５２が形成されていると共
に、この潤滑油入口部５２と、駆動軸挿入孔２、
駆動軸３及びプレーンベアリング４ａ，４ｂで囲
まれた潤滑油溜り室５３とを連通する第１のオイ
ル孔５４が形成され、潤滑油入口部５２からエン
ジンオイル等の潤滑油が潤滑油溜り室５３に供給
される。また、駆動軸３には、プレーンベアリン
グ４ａ，４ｂの内面に一端が開口する第２のオイ
ル孔５５ａ，５５ｂが半径方向に形成されている
と共に、この第２のオイル孔５５ａ，５５ｂとカ
ム室５とを連通する第３のオイル孔５６が軸方向
に形成され、駆動軸３とプレーンベアリング４
ａ，４ｂとの間のクリアランスで絞られた潤滑油
が第２及び第３のオイル孔５５ａ，５５ｂ，５６
を介してカム室５に供給されるようになつてい
る。尚、カム室５の所定位置にはオーバフロー孔
５７が形成され、カム室５に所定レベル以上の潤
滑油が溜まつた場合に、余分の潤滑油をタンク側
へ戻すようになつている。 That is, in this embodiment, the lubrication space is the drive shaft insertion hole 2 and the cam chamber 5 on both sides of the feed pump 34, and the rear portion 1b of the main body 1 has a lubricating oil inlet portion 52 formed in its upper part. At the same time, this lubricating oil inlet portion 52 and the drive shaft insertion hole 2,
A first oil hole 54 is formed that communicates with a lubricating oil reservoir 53 surrounded by the drive shaft 3 and plain bearings 4a and 4b, and lubricating oil such as engine oil flows from the lubricating oil inlet 52 into the lubricating oil reservoir chamber 53. is supplied to Further, second oil holes 55a, 55b are formed in the drive shaft 3 in the radial direction, one end of which opens on the inner surface of the plain bearings 4a, 4b, and the second oil holes 55a, 55b and the cam chamber A third oil hole 56 is formed in the axial direction to communicate with the drive shaft 3 and the plain bearing 4.
The lubricating oil squeezed by the clearance between the oil holes 55a and 4b flows through the second and third oil holes 55a, 55b, 56.
The water is supplied to the cam chamber 5 via the cam chamber 5. An overflow hole 57 is formed at a predetermined position in the cam chamber 5, so that when lubricating oil of a predetermined level or more accumulates in the cam chamber 5, excess lubricating oil is returned to the tank side.
ここで、この明細書において、特に新規なもの
として開示するのは次の２点である。 Here, the following two points are particularly disclosed as new in this specification.
まず第１に、カバー４４には圧力逃がし通路５
８が形成されている点で、この圧力逃がし通路５
８は、その一端が前記第１のシール室４９ａのに
開口し、他端が燃料入口４２付近で作動室４１に
開口している。しかして、出口４３側で作動室４
１の燃料が高圧になると、その圧力がロータ３５
とリア部１ｂ及びカバー４４とのクリアランスを
介してシール室４９ａ，４９ｂに伝達され、該シ
ール室４９ａ，４９ｂに溜まつている燃料も高圧
となり、その燃料がオイルシール５０ａ，５０ｂ
を通過して駆動軸挿入孔２又はカム室５へ逃げよ
うとするのを、該圧力逃がし通路５８を介してシ
ール室４９ａ，４９ｂを低圧とすることによつて
防止するものである。尚、第１のシール室４９ａ
と第２のシール室４９ｂとは、ロータ３５のキー
溝３６ａを介して連通し、常に略等しい圧力に保
たれている。 First of all, the cover 44 has a pressure relief passage 5.
8 is formed, this pressure relief passage 5
8 has one end opening into the first seal chamber 49a and the other end opening into the working chamber 41 near the fuel inlet 42. Therefore, the working chamber 4 on the outlet 43 side
When the fuel in No. 1 becomes high pressure, the pressure is applied to the rotor 35.
The fuel is transmitted to the seal chambers 49a, 49b through the clearance between the rear part 1b and the cover 44, and the fuel accumulated in the seal chambers 49a, 49b also becomes high pressure, and the fuel is transferred to the oil seals 50a, 50b.
The seal chambers 49a and 49b are kept under low pressure via the pressure relief passage 58, thereby preventing the pressure from escaping through the drive shaft insertion hole 2 or the cam chamber 5. Note that the first seal chamber 49a
and the second seal chamber 49b communicate with each other via the keyway 36a of the rotor 35, and are always maintained at approximately the same pressure.
次に、第３図、第４図に示すように、ベーン３
９の前面に等圧溝５９が縦方向に形成され、ベー
ン３９の背部でロータ３５との間に形成された背
圧室６０と当該ベーン３９より先行する作動室４
１とが該等圧溝５９を介して連通している点であ
り、これにより、ベーン３９が引き込んで作動室
４１，４１間が連通するのを防止することができ
る。即ち、背圧室６０は、ロータ３５とリア部１
ｂ又はカバー４４とのクリアランスを介して高圧
燃料が漏れて高圧に保たれ、ベーン３９が引き込
むのを防止するようになつているが、この実施例
のように、シール室４９ａ，４９ｂを低圧にする
と、背圧室６０も低圧となり、作動室４１からの
圧力が背圧室６０からの圧力を上回り、ベーン３
９が引き込む虞がある。そこで、ベーン３９に上
述した等圧溝５９を形成し、作動室４１の圧力が
上昇するのに従つて背圧室６０の圧力も上昇させ
るようにし、作動室４１からベーン３９へ作用す
る圧力に対抗することができるようにしたもので
ある。 Next, as shown in FIGS. 3 and 4, the vane 3
An equal pressure groove 59 is vertically formed in the front surface of the vane 9, and a back pressure chamber 60 is formed at the back of the vane 39 between the rotor 35 and the working chamber 4 preceding the vane 39.
1 are in communication with each other via the equal pressure groove 59, and this can prevent the vane 39 from retracting and causing the working chambers 41, 41 to communicate with each other. That is, the back pressure chamber 60 is located between the rotor 35 and the rear section 1.
High-pressure fuel leaks through the clearance between the seal chamber 49a and the cover 44 and is kept at a high pressure to prevent the vane 39 from being drawn in. However, as in this embodiment, the seal chambers 49a and 49b are kept at a low pressure. Then, the back pressure chamber 60 also becomes low pressure, the pressure from the working chamber 41 exceeds the pressure from the back pressure chamber 60, and the vane 3
There is a risk that 9 will be drawn in. Therefore, the above-described equal pressure groove 59 is formed in the vane 39 so that as the pressure in the working chamber 41 increases, the pressure in the back pressure chamber 60 also increases, and the pressure acting from the working chamber 41 on the vane 39 is reduced. It was made so that it could be fought against.
上記構成において、駆動軸３が回転すると、ベ
ーンポンプ３４が駆動し、作動室４１の容積が増
大することで燃料入口４２から作動室４１に吸入
し、作動室４１の容積が減少することで燃料を加
圧して燃料出口４３から吐出し、リア側のコネク
タ３１ｂ、接続パイプ３３、ヘツド側のコネクタ
３１ａ、及び連通路３２を介して電磁弁１５の入
口２４に至る。また、これと同時に駆動軸３の回
転がカツプリング１２及びカムデイスク１１を介
してプランジヤ８に伝達され、このプランジヤ８
が往復回転運動を行い、該プランジヤ８が後退す
る吸入行程時には圧力室９内の圧力が低下し、該
プランジヤ８が前進する吐出行程時には圧力室９
内の圧力が上昇する。 In the above configuration, when the drive shaft 3 rotates, the vane pump 34 is driven, the volume of the working chamber 41 increases and fuel is sucked into the working chamber 41 from the inlet 42, and the volume of the working chamber 41 decreases and fuel is sucked into the working chamber 41. The pressurized fuel is discharged from the fuel outlet 43 and reaches the inlet 24 of the solenoid valve 15 via the rear connector 31b, the connection pipe 33, the head connector 31a, and the communication path 32. At the same time, the rotation of the drive shaft 3 is transmitted to the plunger 8 via the coupling ring 12 and the cam disc 11.
performs reciprocating rotational motion, and during the suction stroke in which the plunger 8 retreats, the pressure within the pressure chamber 9 decreases, and during the discharge stroke in which the plunger 8 moves forward, the pressure in the pressure chamber 9 decreases.
The pressure inside increases.
しかして、このプランジヤ８の吸入行程時に電
磁弁１５の励磁コイル１９が消磁されていると、
電磁弁１５が開かれるので、フイードポンプ３４
により電磁弁１５の入口２４に送られた燃料が電
磁弁１５の弁棒２１と弁座２２との間、該電磁弁
１５の出口２５及び燃料吸入通路２６を介して圧
力室９内に吸入される。続いて圧縮行程時に電磁
弁１５の励磁コイル１９を励磁すると、電磁弁１
５が閉じられるので、圧力室９内の燃料が加圧さ
れ、プランジヤ８の縦孔２８、吐出グループ２９
及び図示しない分配通路を通り、送出部３０から
送出され、圧縮行程時に電磁弁１５の励磁コイル
１９を消磁すると電磁弁１５が開かれて燃料の噴
射が完了するものである。 However, if the excitation coil 19 of the solenoid valve 15 is demagnetized during the suction stroke of the plunger 8,
Since the solenoid valve 15 is opened, the feed pump 34
The fuel sent to the inlet 24 of the solenoid valve 15 is sucked into the pressure chamber 9 between the valve stem 21 and the valve seat 22 of the solenoid valve 15, through the outlet 25 of the solenoid valve 15, and the fuel suction passage 26. Ru. Subsequently, when the excitation coil 19 of the solenoid valve 15 is energized during the compression stroke, the solenoid valve 1
5 is closed, the fuel in the pressure chamber 9 is pressurized, and the vertical hole 28 of the plunger 8 and the discharge group 29
The fuel is sent out from the delivery section 30 through a distribution passage (not shown), and when the excitation coil 19 of the solenoid valve 15 is demagnetized during the compression stroke, the solenoid valve 15 is opened and the fuel injection is completed.
一方、潤滑油は、潤滑油入口部５２から第１の
オイル孔５４及び潤滑油溜り室５３を介して駆動
軸３とプレーンベアリング４ａ，４ｂとの間に送
られて該部分の潤滑に供され、さらに駆動軸３の
第２のオイル孔５５ａ，５５ｂ及び第３のオイル
孔５６を通つてカム室５に供給される。このカム
室５に供給された潤滑油は、駆動軸３、カツプリ
ング１２、カムデイスク１１等の摺動部分の潤滑
に供され、このカム室５内の潤滑油のレベルがオ
ーバフロー孔５７以上に上昇すると、このオーバ
フロー孔５７を通つてタンク側に戻される。 On the other hand, the lubricating oil is sent between the drive shaft 3 and the plain bearings 4a, 4b from the lubricating oil inlet 52 through the first oil hole 54 and the lubricating oil reservoir chamber 53 to lubricate these parts. Further, the oil is supplied to the cam chamber 5 through the second oil holes 55a, 55b and the third oil hole 56 of the drive shaft 3. The lubricating oil supplied to this cam chamber 5 is used to lubricate sliding parts such as the drive shaft 3, coupling 12, cam disk 11, etc., and the level of lubricating oil in this cam chamber 5 rises above the overflow hole 57. Then, it is returned to the tank side through this overflow hole 57.
ここで、フイードポンプ３４の燃料が駆動軸挿
入孔２又はカム室５に漏れると、その潤滑油が希
釈されるが、この実施例のように、シール室４９
ａ，４９ｂの圧力がカバー４４に形成された圧力
逃がし通路５８を介してフイードポンプ３４の低
圧側に逃げるようになつているので、オイルシー
ル５０ａ，５０ｂにかかる燃料の圧力が低くな
り、上記燃料漏れを防止することができる。ま
た、背圧室６０は、ベーン３９の等圧溝５９を介
して作動室４１と連通しているので、背圧室６０
からベーン３９に作用する力が作動室４１からベ
ーンに作用する力を常に上回り、これによりベー
ン３９がベーン溝３８の奥側へ引き込むのを防止
することができるものである。 Here, when the fuel from the feed pump 34 leaks into the drive shaft insertion hole 2 or the cam chamber 5, the lubricating oil is diluted.
Since the pressure in the oil seals 50a and 49b is designed to escape to the low pressure side of the feed pump 34 through the pressure relief passage 58 formed in the cover 44, the pressure of the fuel applied to the oil seals 50a and 50b is lowered, and the fuel leakage is prevented. can be prevented. Further, since the back pressure chamber 60 communicates with the working chamber 41 via the equal pressure groove 59 of the vane 39, the back pressure chamber 60
The force acting on the vane 39 from the working chamber 41 always exceeds the force acting on the vane from the working chamber 41, thereby preventing the vane 39 from being pulled into the back side of the vane groove 38.
尚、上記実施例においては、駆動軸挿入孔２と
カム室５との双方に潤滑油を供給するようにして
いるが、いずれか一方に潤滑油を供給する形式の
ものに対してもこの考案を適用することができ
る。また、上記実施例においては、フイードポン
プ３４にベーン型のものを採用したが、歯車ポン
プ等の他の形式のものを使用してもよく、さら
に、圧力逃がし通路５８は、カバー４４ばかりで
はなく、例えば噴射ポンプ本体１のリア部１ｂに
形成してもよい。 In the above embodiment, lubricating oil is supplied to both the drive shaft insertion hole 2 and the cam chamber 5, but this invention can also be applied to a type in which lubricating oil is supplied to either one of them. can be applied. Further, in the above embodiment, a vane type feed pump is used as the feed pump 34, but other types such as a gear pump may also be used.Furthermore, the pressure relief passage 58 is not limited to the cover 44. For example, it may be formed in the rear portion 1b of the injection pump main body 1.
（考案の効果）
以上述べたように、この考案によれば、潤滑油
が供給される潤滑空間と燃料を加圧するフイード
ポンプとの間をオイルシールをもつてシールし、
このオイルシールが配置されたシール室とフイー
ドポンプの低圧側とを圧力逃がし通路を介して連
通したので、シール室を常に低圧に保つことがで
き、フイードポンプから潤滑空間への燃料漏れを
防止することができ、潤滑油の性能を長時間に渡
つて確保し、もつて装置の寿命の延長に貢献する
ことができるものである。(Effects of the invention) As described above, according to this invention, an oil seal is used to seal between the lubrication space where lubricating oil is supplied and the feed pump which pressurizes the fuel.
Since the seal chamber in which this oil seal is placed and the low pressure side of the feed pump are communicated via a pressure relief passage, the seal chamber can always be kept at a low pressure, and fuel leakage from the feed pump to the lubrication space can be prevented. It is possible to ensure the performance of the lubricating oil over a long period of time, thereby contributing to extending the life of the equipment.
第１図はこの考案の分配型燃料噴射ポンプを示
す横断面図、第２図は第１図のＡ−Ａ線断面図、
第３図は同上の実施例に用いたフイードポンプの
側面図、第４図は同上のフイードポンプのベーン
を示す斜視図である。
２……駆動軸挿入孔、３……駆動軸、５……カ
ム室、３４……フイードポンプ、３５……ロー
タ、３９……ベーン、４０……案内リング、４１
……作動室、４９ａ，４９ｂ……シール室、５０
ａ，５０ｂ……オイルシール、５９……等圧溝、
６０……背圧室。
FIG. 1 is a cross-sectional view showing the distribution type fuel injection pump of this invention, FIG. 2 is a cross-sectional view taken along the line A-A in FIG. 1,
FIG. 3 is a side view of the feed pump used in the above embodiment, and FIG. 4 is a perspective view showing the vane of the feed pump. 2... Drive shaft insertion hole, 3... Drive shaft, 5... Cam chamber, 34... Feed pump, 35... Rotor, 39... Vane, 40... Guide ring, 41
... Working chamber, 49a, 49b ... Seal chamber, 50
a, 50b...oil seal, 59...equal pressure groove,
60...Back pressure chamber.
Claims (1)
ードポンプを設けた分配型燃料噴射ポンプにお
いて、前記潤滑空間とフイードポンプとの間を
駆動軸の周囲に設けられたオイルシールをもつ
てシールし、このオイルシールが配置されたシ
ール室と前記フイードポンプの低圧側とを圧力
逃がし通路を介して連通したことを特徴とする
分配型燃料噴射ポンプ。 ２ フイードポンプは、駆動軸に固装されたロー
タと、このロータに嵌挿されたベーンと、この
ベーンの先端を案内する案内リングとを具備
し、ロータ、ベーン及び案内リングに囲まれた
作動室の容積変化にて燃料を加圧するようにな
つており、前記ベーンの背部に形成された背圧
室と該ベーンより先行する作動室とを連通する
等圧溝を前記ベーンに形成したことを特徴とす
る実用新案登録請求の範囲第１項記載の分配型
燃料噴射ポンプ。[Claims for Utility Model Registration] 1. In a distribution type fuel injection pump in which a feed pump is provided adjacent to a lubricating space where lubricating oil is supplied, an oil feed pump provided around a drive shaft between the lubricating space and the feed pump 1. A distribution type fuel injection pump, characterized in that the oil seal is sealed, and the seal chamber in which the oil seal is disposed communicates with the low pressure side of the feed pump via a pressure relief passage. 2. A feed pump includes a rotor fixed to a drive shaft, a vane fitted into the rotor, and a guide ring that guides the tip of the vane, and has an operating chamber surrounded by the rotor, vanes, and guide ring. The fuel is pressurized by a change in volume of the vane, and an equal pressure groove is formed in the vane to communicate a back pressure chamber formed at the back of the vane with an operating chamber preceding the vane. A distribution type fuel injection pump according to claim 1 of the utility model registration claim.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985024378U JPH034780Y2 (en) | 1985-02-22 | 1985-02-22 | |
| GB08602943A GB2172339B (en) | 1985-02-22 | 1986-02-06 | Distributor-type fuel injection pump |
| KR2019860001783U KR900009524Y1 (en) | 1985-02-22 | 1986-02-17 | Distributor-type fuel injektion pump |
| DE19863605452 DE3605452A1 (en) | 1985-02-22 | 1986-02-20 | DISTRIBUTOR INJECTION PUMP |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1985024378U JPH034780Y2 (en) | 1985-02-22 | 1985-02-22 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61140171U JPS61140171U (en) | 1986-08-30 |
| JPH034780Y2 true JPH034780Y2 (en) | 1991-02-07 |
Family
ID=12136524
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1985024378U Expired JPH034780Y2 (en) | 1985-02-22 | 1985-02-22 |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPH034780Y2 (en) |
| KR (1) | KR900009524Y1 (en) |
| DE (1) | DE3605452A1 (en) |
| GB (1) | GB2172339B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3943299A1 (en) * | 1989-12-29 | 1991-07-04 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| FR2721352B1 (en) * | 1994-06-17 | 1996-09-06 | Leduc Rene Hydro Sa | High pressure pump to supply fuel injectors for internal combustion engines. |
| US7137789B2 (en) | 1997-07-18 | 2006-11-21 | Rpm Industries, Inc. | Vent for reducing seal pressure in pump assembly |
| US6544008B1 (en) * | 1997-07-18 | 2003-04-08 | John K. Apostolides | Internal vent for reducing seal pressure in prelubrication pump assembly |
| JP5126097B2 (en) * | 2009-02-06 | 2013-01-23 | 株式会社デンソー | Fuel supply device |
| CN104696128A (en) * | 2015-01-15 | 2015-06-10 | 东风朝阳朝柴动力有限公司 | Fuel injection pump with ventilation function |
| DE102015111025A1 (en) | 2015-07-08 | 2017-01-12 | Volkswagen Ag | Self lubricated high pressure pump |
| DE102018120777A1 (en) * | 2018-08-24 | 2020-02-27 | Volkswagen Aktiengesellschaft | High-pressure pump comprising pressure lubrication |
| CN110360041A (en) * | 2019-08-08 | 2019-10-22 | 思达耐精密机电（常熟）有限公司 | A kind of novel fuel pump for preventing oil sealing from leaking and detecting oil seal failure |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE967934C (en) * | 1953-01-30 | 1957-12-27 | Kloeckner Humboldt Deutz Ag | Device for fastening and sealing the relief valve guide body in fuel injection pumps |
| DE1734877U (en) * | 1955-05-04 | 1956-11-29 | Bosch Gmbh Robert | FUEL INJECTION PUMP WITH DISTRIBUTOR. |
| US3154020A (en) * | 1962-04-05 | 1964-10-27 | Roth Co Roy E | Sealing means for rotary pump shafts and the like |
| US3381615A (en) * | 1966-12-09 | 1968-05-07 | Caterpillar Tractor Co | Driving and timing mechanism for fuel injection pump |
-
1985
- 1985-02-22 JP JP1985024378U patent/JPH034780Y2/ja not_active Expired
-
1986
- 1986-02-06 GB GB08602943A patent/GB2172339B/en not_active Expired
- 1986-02-17 KR KR2019860001783U patent/KR900009524Y1/en not_active IP Right Cessation
- 1986-02-20 DE DE19863605452 patent/DE3605452A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB2172339A (en) | 1986-09-17 |
| GB2172339B (en) | 1988-06-29 |
| KR860010826U (en) | 1986-09-08 |
| DE3605452C2 (en) | 1990-09-13 |
| GB8602943D0 (en) | 1986-03-12 |
| DE3605452A1 (en) | 1986-08-28 |
| JPS61140171U (en) | 1986-08-30 |
| KR900009524Y1 (en) | 1990-10-13 |
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