JPH03514Y2 - - Google Patents
Info
- Publication number
- JPH03514Y2 JPH03514Y2 JP15234584U JP15234584U JPH03514Y2 JP H03514 Y2 JPH03514 Y2 JP H03514Y2 JP 15234584 U JP15234584 U JP 15234584U JP 15234584 U JP15234584 U JP 15234584U JP H03514 Y2 JPH03514 Y2 JP H03514Y2
- Authority
- JP
- Japan
- Prior art keywords
- plunger
- spring
- yoke
- cam
- fuel injection
- 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 12
- 238000002347 injection Methods 0.000 claims description 10
- 239000007924 injection Substances 0.000 claims description 10
- 238000002485 combustion reaction Methods 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000002788 crimping Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 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
- 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
- F02M41/121—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 with piston arranged axially to driving shaft
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
【考案の詳細な説明】
産業上の利用分野
本考案は、多気筒内燃機関用の燃料噴射ポンプ
であつて、回転並びに往復行程運動を行なうプラ
ンジヤと、プランジヤを駆動する回転式のカム円
板とを備え、カム円板は回転運動に伴つて正面カ
ムを介して定位置のローラ上を運動してローラに
プランジヤに対して軸線方向に延びている複数の
押しばねによつて圧着され、これらの押しばねは
プランジヤ軸線から等間隔をおいて一方ではポン
プハウジングに支えられ、他方では、カム円板に
対して同心的に配置されてカム円板に支えられた
不動のヨークに支えられており、プランジヤを包
囲してプランジヤの一区分上を滑動する制御スラ
イダが設けられていて、この制御スライダは燃料
噴射量を変えるために調節部材によつて操作可能
である形式のものに関する。[Detailed Description of the Invention] Industrial Application Field The present invention is a fuel injection pump for a multi-cylinder internal combustion engine, which includes a plunger that performs rotational and reciprocating stroke motion, and a rotary cam disc that drives the plunger. The cam disc moves over the roller in a fixed position via the front cam as the cam disk rotates, and is pressed against the roller by a plurality of pressure springs extending in the axial direction with respect to the plunger. The pressure spring is supported on the one hand by the pump housing at equal distances from the plunger axis and on the other hand by a stationary yoke arranged concentrically with respect to the cam disk and supported by the cam disk; A control slide is provided which surrounds the plunger and slides over a section of the plunger, said control slide being of the type which can be actuated by an adjusting member to vary the amount of fuel injected.
従来の技術
この種の公知の燃料噴射ポンプの一例によれ
ば、不動のローラリングのローラに接触している
カム円板の正面カムの回転運動面の圧着が押しば
ねとしての２つのコイルばねによつてなされ、こ
れらのコイルばねはヨークに180゜互いにずらして
作用している。これら両方のコイルばねによつて
ヨークが球面状のスラスト軸受を介して一様にカ
ム円板に圧着され、カム円板はその中心へ作用す
るばね力を受けてローラに接触する。BACKGROUND OF THE INVENTION According to an example of a known fuel injection pump of this type, the rotationally moving surface of the front cam of the cam disk, which is in contact with the roller of a stationary roller ring, is pressed against two coil springs as pressure springs. These coil springs act on the yoke with a 180° offset from each other. These two coil springs uniformly press the yoke against the cam disk via the spherical thrust bearing, and the cam disk contacts the roller under the spring force acting on its center.
考案が解決しようとする問題点
このような公知例の場合、所定のばね力の時、
カム円板のバウンス回転数、即ち正面カムがロー
ラ面からはずれるバウンス現象を呈する回転数は
カムの勾配が大になるに従つて低下する。個個の
コイルばねのばね力を任意に強くすることはでき
ないので、カム円板の最大往復行程および最大回
転数、ひいてはプランジヤの往復行程および回転
数は狭い限界内にとどまる。Problems to be solved by the invention In the case of such a known example, when a predetermined spring force is applied,
The bounce rotational speed of the cam disk, that is, the rotational speed at which the front cam exhibits a bounce phenomenon in which it comes off the roller surface, decreases as the slope of the cam becomes larger. Since the spring force of the individual coil springs cannot be increased arbitrarily, the maximum reciprocating stroke and the maximum rotational speed of the cam disk, and thus the reciprocating stroke and the rotational speed of the plunger, remain within narrow limits.
本考案は、冒頭に述べた形式の燃料噴射ポンプ
において、正面カムがローラ面からはずれるよう
なことなしに極めて高い回転数が保証されるよう
にすることを課題とする。 The object of the present invention is to provide a fuel injection pump of the type mentioned at the outset with an extremely high rotational speed without the front cam coming off the roller surface.
考案の利点
このような課題を解決した実用新案登録請求の
範囲第１項に示す構成の本考案の燃料噴射ポンプ
は、押しばねの数を増したことによつてローラへ
のカム円板の圧着力を著しく強めることができ
て、臨界バウンス回転数を著しく高めることがで
きるという利点を有する。このことはまたプラン
ジヤの一層大きな回転数又は一層勾配の大きなカ
ム面、ひいてはプランジヤの最大往復行程の拡大
を可能にする。押しばねが配置されたポンプ室内
には制御スライダも位置しているので、この制御
スライダに係合している調節部材が３つの押しば
ねを回転対称でない配置に偏位させる作用を及ぼ
す。本考案のこれら３つの押しばねの配置および
ばね力の設定によれば、ほぼリング状のヨークが
一様に負荷を受けることになつて、３つの押しば
ねの作用点がプランジヤ軸線上の一点に位置する
ことになる。このようなばね力設定の場合第３の
押しばねのばね力はいわば有効てこ腕の比が小さ
くなり、90゜よりは大きくて120゜よりは小さい角
度範囲内で両方の押しばねの１つのばね力よりも
小さい。Advantages of the Invention The fuel injection pump of the present invention having the configuration shown in claim 1 of the utility model registration that solves the above problems has a structure in which the cam disc is pressed against the roller by increasing the number of compression springs. It has the advantage that the force can be significantly increased and the critical bounce rotational speed can be significantly increased. This also allows a higher rotational speed of the plunger or a steeper cam surface, and thus an increase in the maximum reciprocating stroke of the plunger. A control slide is also located in the pump chamber in which the pressure springs are arranged, so that the adjusting member engaged with this control slide has the effect of deflecting the three pressure springs into a rotationally asymmetrical arrangement. According to the arrangement of these three push springs and the setting of the spring force of the present invention, the approximately ring-shaped yoke receives the load uniformly, and the point of action of the three push springs is at one point on the plunger axis. will be located. With such a spring force setting, the spring force of the third compression spring is, as it were, the ratio of the effective lever arm is small, and within an angular range greater than 90° and less than 120°, the spring force of the third compression spring is reduced by one spring of both compression springs. less than force.
実施例
燃料噴射ポンプのハウジング10内に駆動軸１１
が支承されている。この駆動軸１１は軸線に対し
て直角に配置されたカム円板１２に連結されてい
る。カム円板１２は機関シリンダと同じ数の正面
カム１３を有している。カム円板１２の回転運動
面は、不動のローラリング１５内に保持されたロ
ーラ１４上に位置する。円筒ブツシユ１６内で滑
動するプランジヤ１７はその駆動側端部につば１
８を有しており、このつば１８はピン１９によつ
てカム円板１２に相対回転不能に結合されている
（第２図）。燃料噴射ポンプを制御するために、プ
ランジヤ１７を包囲している制御スライダ２０が
駆動側のプランジヤ区分１７１上を滑動する。こ
の制御スライダ２０上には、周知の形式で調速機
につて制御される調節部材２１が係合している。Example Drive shaft 11 in housing 10 of fuel injection pump
is supported. This drive shaft 11 is connected to a cam disk 12 arranged at right angles to the axis. The cam disk 12 has the same number of front cams 13 as engine cylinders. The rotationally moving surface of the cam disk 12 rests on rollers 14 held in a stationary roller ring 15. A plunger 17 sliding within a cylindrical bushing 16 has a collar 1 at its drive end.
8, and this collar 18 is connected to the cam disk 12 by a pin 19 in a manner that prevents relative rotation (FIG. 2). To control the fuel injection pump, a control slide 20 surrounding the plunger 17 slides on the drive-side plunger section 171. On this control slide 20, an adjusting member 21 is engaged which is controlled by the governor in a known manner.
つば１８上には下側のすべり円板２２および上
側のすべり円板２３が装着されている。上側の円
板２３にはリング状のヨーク２４が３つの軸平行
のコイルばね２５，２６，２７によつて押し付け
られている。コイルばね２５，２６，２７はガイ
ドピン２８，２９，３０上に保持されている。ガ
イドピン２８，２９，３０は一端がハウジング１
０内にねじ付けられ、他端がヨーク２４内の嵌合
孔に嵌まつている。このようにしてヨーク２４は
回動を防止されている。コイルばね２５，２６，
２７はケーシング１０とヨーク２４とに支えられ
ており、これによりカム円板１２の正面カム１３
がローラ１４に圧着される。 A lower sliding disc 22 and an upper sliding disc 23 are mounted on the collar 18. A ring-shaped yoke 24 is pressed against the upper disk 23 by three axis-parallel coil springs 25, 26, and 27. Coil springs 25, 26, 27 are held on guide pins 28, 29, 30. The guide pins 28, 29, 30 have one end connected to the housing 1.
0, and the other end fits into a fitting hole in the yoke 24. In this way, the yoke 24 is prevented from rotating. Coil springs 25, 26,
27 is supported by the casing 10 and the yoke 24, so that the front cam 13 of the cam disk 12
is pressed onto the roller 14.
コイルばね２５，２６，２７はリング状のヨー
ク２４の周方向に分配されていて、２つのコイル
ばね２５，２６が残る１つのコイルばね２７に対
して同じ角度αだけずらされている。第３図に示
されている実施例の場合この角度は104゜である。
両方のコイルばね２５，２６のばね力K1，K2は
同じ大きさである。第３のコイルばね２７のばね
力K3は両方のコイルばね２５，２６のそれぞれ
角度αのコサインを乗じたばね力K1，K2の合計
に等しく設定されており、次の式にわされる：
K3＝K1cosα＋K2cosα
K1＝K2＝Ｋ
コイルばね２５，２６のばね力がそれぞれＫで
あれば、第３のコイルばね２７のばね力K3は角
度α＝104゜の場合0.5Kである。このコイルばね２
７のばね力K3は角度αが増大すると共に大きく
なり、α＝120゜の角度の場合コイルばね２５，２
６のそれぞれのばね力に等しい。しかしこの角度
α＝120゜は制御スライダ２０に係合する調節部材
２１のため実際には実施できない。 The coil springs 25, 26, 27 are distributed in the circumferential direction of the ring-shaped yoke 24, and the two coil springs 25, 26 are offset from the remaining one coil spring 27 by the same angle α. In the embodiment shown in FIG. 3, this angle is 104°.
The spring forces K 1 and K 2 of both coil springs 25 and 26 are of the same magnitude. The spring force K 3 of the third coil spring 27 is set equal to the sum of the spring forces K 1 and K 2 of both coil springs 25 and 26, respectively, multiplied by the cosine of the angle α, and is given by the following formula: : K 3 = K 1 cos α + K 2 cos α K 1 = K 2 = K If the spring forces of the coil springs 25 and 26 are each K, the spring force K 3 of the third coil spring 27 is when the angle α = 104° It is 0.5K. This coil spring 2
The spring force K 3 of 7 increases as the angle α increases, and for an angle α = 120°, the coil spring 25, 2
equal to each spring force of 6. However, this angle α=120° cannot be implemented in practice due to the adjustment member 21 engaging the control slide 20.
以上のコイルばね２５，２６，２７の配置およ
びそのばね力の設計によつて、すべてのコイルば
ねはヨーク２４の中心に作用し、ローラ１４の１
つにカム円板１２の回転運動面が片寄つて強く圧
着されることになるような回転モーメントが発生
することもない。さらに、カム円板１２に働く全
圧着力を従来可能であつた最大圧着力に比して例
えば25％増大させることができる。最大可能な角
度αはたんに制御スライダ２０に係合する調節部
材２１の構造によつて制限を受けるだけである。 Due to the arrangement of the coil springs 25, 26, 27 and the design of their spring force, all the coil springs act on the center of the yoke 24, and one of the rollers 14
There is also no occurrence of a rotational moment that would cause the rotationally moving surface of the cam disk 12 to become biased and strongly pressed. Furthermore, the total crimping force acting on the cam disk 12 can be increased, for example, by 25% compared to the maximum crimping force that was conventionally possible. The maximum possible angle α is only limited by the structure of the adjustment member 21 that engages the control slide 20.
第１図は燃料噴射ポンプの側面図、第２図は第
１図中の範囲Ａの拡大縦断面図、第３図は第２図
中の−線による横断面図である。
１０……ポンプハウジング、１１……駆動軸、
１２……カム円板、１３……正面カム、１４……
ローラ、１５……ローラリング、１６……円筒ブ
ツシユ、１７……プランジヤ、１８……つば、１
９……ピン、２０……制御スライダ、２１……調
節部材、２２……すべり円板、２３……すべり円
板、２４……ヨーク、２５，２６，２７……コイ
ルばね、２８，２９，３０……ガイドピン。
FIG. 1 is a side view of the fuel injection pump, FIG. 2 is an enlarged vertical cross-sectional view of range A in FIG. 1, and FIG. 3 is a cross-sectional view taken along the - line in FIG. 2. 10...Pump housing, 11...Drive shaft,
12...Cam disk, 13...Front cam, 14...
Roller, 15...Roller ring, 16...Cylindrical bushing, 17...Plunger, 18...Brim, 1
9... Pin, 20... Control slider, 21... Adjustment member, 22... Sliding disk, 23... Sliding disk, 24... Yoke, 25, 26, 27... Coil spring, 28, 29, 30...Guide pin.
Claims (1)
て、回転並びに往復行程運動を行なうプランジ
ヤと、プランジヤを駆動する回転式のカム円板
とを備え、カム円板は回転運動に伴つて正面カ
ムを介して定位置のローラ上を運動してローラ
にプランジヤに対して軸線方向に延びている複
数の押しばねによつて圧着され、これらの押し
ばねはプランジヤ軸線から等間隔をおいて一方
ではポンプハウジングに支えられ、他方では、
カム円板に対して同心的に配置されてカム円板
に支えられた不動のヨークに支えられており、
プランジヤを包囲してプランジヤの一区分上を
滑動する制御スライダが設けられていて、この
制御スライダは燃料噴射量を変えるために調節
部材によつて操作可能である形式のものにおい
て、カム円板１２を圧着するために、３つの押
しばね２５，２６，２７がリング状に構成され
たヨーク２４の周方向に分配されて配置されて
おり、２つの押しばね２５，２６は互いに等し
いばね力で第３の押しばね２７に対して対称的
にそれぞれ90゜よりも大きな等しい角度αだけ
ずらされており、第３の押しばね２７のばね力
は両方の押しばね２５，２６のそれぞれの角度
αのコサインを乗じたばね力の合計に等しく設
定されていることを特徴とする、燃料噴射ポン
プ。 ２ 角度αが120℃よりも小さな値である実用新
案登録請求の範囲第１項記載の燃料噴射ポン
プ。[Claims for Utility Model Registration] 1. A fuel injection pump for a multi-cylinder internal combustion engine, comprising a plunger that performs rotation and reciprocating stroke motion, and a rotary cam disc that drives the plunger, the cam disc being With the rotational movement, the front cam moves over the roller at a fixed position, and the roller is pressed against the plunger by a plurality of pressure springs extending in the axial direction. supported at intervals by the pump housing on the one hand, and on the other hand.
It is supported by an immovable yoke that is placed concentrically to and supported by the cam disk.
A control slide is provided which surrounds the plunger and slides over a section of the plunger, which control slide is operable by means of an adjusting member to vary the amount of fuel injected into the cam disk 12. In order to press the yoke 24, three pressure springs 25, 26, 27 are distributed and arranged in the circumferential direction of the yoke 24, which is configured in a ring shape. The third pressure spring 27 is symmetrically offset by an equal angle α greater than 90° with respect to the third pressure spring 27, and the spring force of the third pressure spring 27 is the cosine of the respective angle α of both pressure springs 25, 26. Fuel injection pump, characterized in that it is set equal to the sum of the spring forces multiplied by . 2. The fuel injection pump according to claim 1, wherein the angle α is smaller than 120°C.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19833336869 DE3336869A1 (en) | 1983-10-11 | 1983-10-11 | Fuel injection pump for multi-cylinder internal combustion engines |
| DE3336869.4 | 1983-10-11 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6077770U JPS6077770U (en) | 1985-05-30 |
| JPH03514Y2 true JPH03514Y2 (en) | 1991-01-10 |
Family
ID=6211489
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15234584U Granted JPS6077770U (en) | 1983-10-11 | 1984-10-11 | Fuel injection pump for multi-cylinder internal combustion engines |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPS6077770U (en) |
| DE (1) | DE3336869A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61112771A (en) * | 1984-11-06 | 1986-05-30 | Nissan Motor Co Ltd | Distributive fuel injection pump |
| DE3516455A1 (en) * | 1985-05-08 | 1986-11-13 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP |
| DE3843162A1 (en) * | 1988-12-22 | 1990-06-28 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2923423A1 (en) * | 1979-06-09 | 1980-12-11 | Bosch Gmbh Robert | Fuel injection pump for IC engine - has two return springs in series, with spring plate between, to prevent resonant vibration of springs |
-
1983
- 1983-10-11 DE DE19833336869 patent/DE3336869A1/en not_active Ceased
-
1984
- 1984-10-11 JP JP15234584U patent/JPS6077770U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6077770U (en) | 1985-05-30 |
| DE3336869A1 (en) | 1985-04-25 |
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