JPH03156131A - Centrifugal governor for fuel injection engine - Google Patents
Centrifugal governor for fuel injection engineInfo
- Publication number
- JPH03156131A JPH03156131A JP2292214A JP29221490A JPH03156131A JP H03156131 A JPH03156131 A JP H03156131A JP 2292214 A JP2292214 A JP 2292214A JP 29221490 A JP29221490 A JP 29221490A JP H03156131 A JPH03156131 A JP H03156131A
- Authority
- JP
- Japan
- Prior art keywords
- centrifugal
- centrifugal governor
- locking mechanism
- locking
- governor
- 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
- 238000002347 injection Methods 0.000 title claims description 7
- 239000007924 injection Substances 0.000 title claims description 7
- 239000000446 fuel Substances 0.000 title claims description 4
- 230000007246 mechanism Effects 0.000 claims abstract description 20
- 230000009471 action Effects 0.000 claims abstract description 4
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 230000036316 preload Effects 0.000 abstract description 3
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 101100135641 Caenorhabditis elegans par-3 gene Proteins 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000001447 compensatory effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000001404 mediated effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
- F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
- F02D1/10—Transmission of control impulse to pump control, e.g. with power drive or power assistance mechanical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
- F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
- F02D1/04—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors
- F02D1/045—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors characterised by arrangement of springs or weights
-
- 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
- F02M59/447—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 means specially adapted to limit fuel delivery or to supply excess of fuel temporarily, e.g. for starting of the engine
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は、特許請求の範囲第１頂上位概念に記載の遠心
調速器に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a centrifugal governor according to the first aspect of the claims.
［従来の技術］
遠心調速器であって、遠心錘から供給量調節部材への調
整運動の伝達が、調速器スリーブを介して行なわれ、こ
のスリーブの作用長さが、ねじ山への締込みにより変更
できる形式のものは公知である（ＣＨ−ＰＳ３１９３５
７）。[Prior Art] Centrifugal governors, in which the transmission of the adjustment movement from the centrifugal weight to the feed rate adjusting member takes place via a governor sleeve, the working length of which A type that can be changed by tightening is known (CH-PS31935
7).
［発明が解決しようとする課題〕
この形式の遠心調速器は、更に、シフトレバ−を、始動
燃料供給量レリーズレバ−の形式で操作する付加機能を
有している。通常、レバー位置の調節は、予め供給量調
節部材と遠心錘とを互いに精密に位置配属させるｒＲＭ
ｉを行なうさいに、−緒に行なわれる。それによってレ
バーの所望位置が変更されるので、始動供給量レリーズ
レバ−に予定された機能が損われたり、十分に果たされ
なかったりする。[Problems to be Solved by the Invention] This type of centrifugal governor further has an additional function of operating the shift lever in the form of a starting fuel supply amount release lever. Normally, the adjustment of the lever position is performed by adjusting the rRM by precisely aligning the supply amount adjusting member and the centrifugal weight with respect to each other in advance.
When doing i, - is done together. As a result, the desired position of the lever is changed, so that the intended function of the starting supply release lever is impaired or not performed satisfactorily.
更に、シフトレバ−の位置は、遠心調速器の構成部品に
影響される。これら構成部品の組合せで一連の公差が形
成され、この結果、合計公差によりシフトレバ−の後調
整域が広いものとなる。Furthermore, the position of the shift lever is influenced by the components of the centrifugal governor. The combination of these components creates a series of tolerances that result in a wide range of rear adjustment of the shift lever due to the total tolerance.
シフトレバ−の調節は、通例は、シフトレバ−の曲げの
後調節により行なわれるが、そのさい、後調節域が広い
ため、シフトレバ−が折しることがある。折れるに至ら
ない場合でも、少なくともひび割れは生じる。このため
、シフトレバ−の機能が、遠心調速器の作動中に予告な
しに失われることがある。The shift lever is normally adjusted by bending the shift lever and then adjusting the shift lever, but at that time, the shift lever may bend because the post-adjustment range is wide. Even if it doesn't break, it will at least crack. Therefore, the function of the shift lever may be lost without prior notice during operation of the centrifugal governor.
［課題を解決するための手段］
これに対し、請求項１記載の特徴を有する本発明の遠心
調速器は、前記欠点を除去した点が長所となっている。[Means for Solving the Problems] On the other hand, the centrifugal governor of the present invention having the features set forth in claim 1 has an advantage in that the above drawbacks are eliminated.
このため、本発明による遠心調速器は、係止機構を有し
ており、この係止機構を介して、始動供給量レリーズレ
バ−として作業するシフトレバ−のリンク位置の調節を
、敏感かつ公差に精密に合わせて行・うことができる。For this purpose, the centrifugal governor according to the invention has a locking mechanism, via which the adjustment of the link position of the shift lever, which acts as a starting supply release lever, can be made sensitively and tolerably. It can be done with precision.
こうして達成された調節は、スリップばねの予荷重と、
係止機構の歯のセルフロック式形状接続との協働により
固定化される。The adjustment thus achieved is based on the preload of the slip spring and
Fixation is achieved through cooperation with a self-locking form-locking connection of the teeth of the locking mechanism.
この調節は、シフトレバ−の位置に影響を与えるだけで
、所定回転数時の始動供給量を正確にレリーズすること
ができる。This adjustment can accurately release the starting supply amount at a predetermined rotation speed simply by affecting the position of the shift lever.
請求項２以下の各項に記載の措置により、請求項１に記
載の遠心調速器の、その他のを利な構成及び改良が可能
である。By the measures described in each of the following claims, other advantageous configurations and improvements of the centrifugal governor according to claim 1 are possible.
請求項２記載の調節器は、軸方向に可動のストップピン
を有しており、シフトレバ−の起動を生じさせる端縁と
呼ばれる端面が、このストップピンの場合には、１１１
４節器のボディに制限された輪郭寸法にもとづくもので
はなく、別個の構成部材、すなわちストップピンにより
間接的に形成され、したがって独自に調節が可能である
。この場合、ストップピンに直接に案内面を設けておき
、この案内面により、ストップピンを介したシフトレバ
−の調節のさい、支承部内でのストップピンの回動位置
が確定される。The adjuster according to claim 2 has an axially movable stop pin, the end surface of which causes activation of the shift lever being 111 in the case of this stop pin.
It is not based on contour dimensions that are limited to the body of the four-bar, but is indirectly formed by a separate component, namely the stop pin, and is therefore independently adjustable. In this case, a guide surface is provided directly on the stop pin, which guide surface determines the rotational position of the stop pin in the bearing during adjustment of the shift lever via the stop pin.
特に有利な点は、シフトレバ−の位置を調節し、ストッ
プピン位置を調節可能に変更するために、請求項７記載
の特徴による係止機構が用いられている点である。この
係止機構の場合、形状接続と摩擦接続との組合せによる
有利な機能が得られ、ひいては良好な位置固定と弛み防
止が達成される。A particular advantage is that a locking mechanism according to the features of claim 7 is used to adjust the position of the shift lever and to adjustably change the stop pin position. With this locking mechanism, an advantageous function is obtained due to the combination of form-locking and frictional connection, thus achieving good positional fixation and prevention of loosening.
請求項】ＯＩ：記載のように、加圧片と支承部とないし
ストップピンとの間には、付加スリップばねが挟込まれ
ており、これにより、調節器の軸方向行程を僅かにし、
ばね定数の有利に変更することができる。Claim: OI: As stated, an additional slip spring is inserted between the pressure piece and the bearing or the stop pin, which reduces the axial travel of the regulator and
The spring constant can be changed to advantage.
■実施例］ 次に本発明の２つの実施例を添付図面につき詳説する。■Example] Two embodiments of the invention will now be described in detail with reference to the accompanying drawings.
第１図に略示した遠心調速器は、ケーシング１１内に遠
心錘調整器１３を有している。この調整器１３は、一部
だけ図示された自体公知の内燃機関用噴射ポンプ１５の
駆動軸１２に取付けられている。この調整器１３の遠心
錘Ｉ４は、公知の形式で、遠心力の作用により調整ばね
１６の力に抗して、その調整運動をアングルレバ−１７
と連結ピン１８とを介して、調速器スリーブとして構成
された調節器１９へ伝達するとりわけ肩２２と端面２３
を形成する、壁部２１の外側輪郭を介して調節器１９は
、調速器リンケージ２４と接続されている。リンケージ
２４は、公知の形式で調節レバー２５を有し、このレバ
ー２５は、制限された角度範囲内で旋回可能であり、か
つまた回転数のプリセットに役立つ。このレバー２５の
運動は、公知の形式で調整ロッド３１へ伝えられる。調
整バー３１は、調節部材３２の位置決めに用いられる。The centrifugal governor shown schematically in FIG. 1 has a centrifugal weight regulator 13 in a housing 11. This regulator 13 is mounted on a drive shaft 12 of a known injection pump 15 for an internal combustion engine, only a part of which is shown. The centrifugal weight I4 of this adjuster 13 is of a known type, and by the action of centrifugal force resists the force of the adjusting spring 16 and moves its adjusting movement to the angle lever 17.
and a connecting pin 18 to a regulator 19 configured as a governor sleeve, in particular a shoulder 22 and an end face 23.
The regulator 19 is connected to the governor linkage 24 via the outer contour of the wall 21 , which forms an outer contour of the wall 21 . The linkage 24 has in a known manner an adjusting lever 25 which can be pivoted within a limited angular range and which also serves to preset the rotational speed. This movement of the lever 25 is transmitted to the adjusting rod 31 in a known manner. The adjustment bar 31 is used for positioning the adjustment member 32.
調整バー３Ｉの路程は、供給量増加方向にはストッパ３
３により制限されている。ストッパ３３は、対応ストッ
パ３５と協働する。調速器リンケージ２４が、調整バー
３１をストッパ３３により制限された位置を超えて押し
ずらすと、直ちにリンケージ２４の過剰の運動は、間接
的に調節器１９へ伝達される。それにより、同じく調節
器１９内に配置されたスリップばね３６が、過重圧力全
受け、リンケージ２４は、過負荷を防止される。The travel distance of the adjustment bar 3I is determined by the stopper 3 in the direction of increasing the supply amount.
3. Stop 33 cooperates with a corresponding stop 35 . As soon as the governor linkage 24 pushes the adjusting bar 31 beyond the position limited by the stop 33, the excess movement of the linkage 24 is transmitted indirectly to the regulator 19. As a result, the slip spring 36, which is also arranged in the regulator 19, is fully exposed to the overload pressure and the linkage 24 is prevented from being overloaded.
この第１実施例は、第２図に、また第２ａ図の部分拡大
図に示されているように、壁２１内に穴３７を有してお
り、連結ピン１８が、この穴内を運動用の遊びをもって
貫通案内され、僅かに、横への回避運動を行なうことが
できる。This first embodiment has a hole 37 in the wall 21, as shown in FIG. 2 and in the partially enlarged view of FIG. It is guided through with a certain amount of play, and a slight sideways avoidance movement can be performed.
加圧片３４は、壁２１により制限された調節器縦孔３８
内に配置され、縦孔の外の端側３９を介して連結ピン１
８に当付けられ、これにより間接的に遠心錘にりンク結
合されている。加圧片３４の縦孔内に位置する端側４１
は、スリップばね３６の一端を支えている。このばねは
圧縮コイルばねとして構成されている。The pressure piece 34 has a regulator vertical hole 38 limited by the wall 21.
The connecting pin 1 is arranged inside the vertical hole through the outer end side 39 of the vertical hole.
8 and is thereby indirectly linked to the centrifugal weight. End side 41 located within the vertical hole of the pressure piece 34
supports one end of the slip spring 36. This spring is designed as a compression coil spring.
スリップばね３６は、他端が支承部４４のつば４３の内
側４２に支えられている。支承部４４は、スリップばね
３６内へ突入している基体４６と、基体４６を半径方向
に拡張しているつば４３とから成っている。The other end of the slip spring 36 is supported by the inner side 42 of the collar 43 of the support portion 44 . The bearing 44 consists of a base body 46 that projects into the slip spring 36 and a collar 43 that extends the base body 46 in the radial direction.
５４は外ねじ山５６を有し、この外ねじ山５６つば４３
は、これも半径方向に突出した突起４７を有し、この突
起４７が壁２１の穴４８に突入し、回動が防止され、か
つ、スリップばね３６の予荷重に相応して、調節器１９
内での支承部４４の位置に関し、支承部４４が軸方向に
固定される。穴４８の軸方向の延びは、突起４７の軸方
向寸法より犬であるため、支承部４４が、スリップばね
３６の調節力に抗して、僅かの補償運動を行なうことが
できる。54 has an external thread 56, and this external thread 56 collar 43
also has a radially projecting projection 47 which projects into a hole 48 in the wall 21 and prevents rotation and, corresponding to the preload of the slip spring 36, adjuster 19
Regarding the position of the bearing 44 within, the bearing 44 is axially fixed. The axial extent of the hole 48 is greater than the axial dimension of the projection 47, so that the bearing 44 can carry out a small compensatory movement against the adjusting force of the slip spring 36.
支承部４４は、その基体４６内では横断面が円形ではな
く、平らな互いに平行に向い合った２つの部分を備えて
おり、これらの部分が案内面として役立っている。これ
らの部分は、運動用の遊びをもってストップピン５３の
頭部５２を案内している。ストップピン５３は、相応の
形態と案内面５１を有し、支承部４４の基体４６内には
め込まれている。In its basic body 46, the bearing 44 is not circular in cross section, but instead has two flat, parallel parts facing each other, which serve as guide surfaces. These parts guide the head 52 of the stop pin 53 with a kinematic play. The stop pin 53 has a corresponding design and a guide surface 51 and is inserted into the basic body 46 of the bearing 44 .
ストップピン５３は、頭部５２のほかに、横断面が円形
の軸部５４を有している。この軸部は、軸部５４を軸方
向に部分的に取囲むｗ！４節部材５８の内ねじ山５７と
噛合っている。In addition to the head 52, the stop pin 53 has a shaft portion 54 having a circular cross section. This shaft portion partially surrounds the shaft portion 54 in the axial direction w! It meshes with the internal thread 57 of the four-section member 58.
頭部と反対の側には、調節器１９の端面２３から突出す
る端縁６１が形成され、この端縁は凸レンズ形を有して
いる。この端縁には、たとえばＣＨ−ＰＳ３１９３５７
に記載のように、公知の形式で、ばね負荷されたシフト
レバ−６２がリンク接続されている。シフトレバ−６２
は、始動供給量レリーズレバ−として働き、全負荷供給
量と始動供給量の２つの位置の間で調整バー３１の位置
決めを、シフトレバ−により位置決めされるストッパ３
３と、供給量調節部材３２に接続された対応ストッパ３
５とを介して制御する。On the side opposite the head, an edge 61 is formed that projects from the end face 23 of the adjuster 19, this edge having the shape of a convex lens. For example, CH-PS319357
A spring-loaded shift lever 62 is linked in a known manner as described in . shift lever 62
The stopper 3, which is positioned by the shift lever, acts as a starting supply amount release lever and controls the positioning of the adjustment bar 31 between the two positions of the full load supply amount and the starting supply amount.
3 and a corresponding stopper 3 connected to the supply amount adjusting member 32
5.
調節部材５８は、調節器１９の縦孔３８内に支承されて
いる細い中空円筒の基本形を有し、外側端面６３と内側
端面６４とを備えている。The adjustment member 58 has the basic shape of a narrow hollow cylinder, which is seated in the longitudinal bore 38 of the adjustment device 19 and has an outer end face 63 and an inner end face 64 .
内側端面は、支承部４４のつば４３の外側６６と平行に
延びている。The inner end surface extends parallel to the outer side 66 of the collar 43 of the support portion 44 .
調節部材５８は、調節ナツトの機能を有し、係止機構６
７の一部である。係止機構は、つば４３に向い合った内
側端面６４に形成された係止歯６８で形成されている。The adjustment member 58 has the function of an adjustment nut, and the locking mechanism 6
It is part of 7. The locking mechanism is formed by locking teeth 68 formed on the inner end surface 64 facing the collar 43.
これらの係止歯６８は、つば４３の外側６６に形成され
た対応歯と噛合っている。These locking teeth 68 mesh with corresponding teeth formed on the outside 66 of the collar 43.
係止歯６８と対応歯６９との間の摩擦接続が維持され、
この接続がスリ・ノブばね３６を介して仲介されるよう
に、調節部材は、軸方向固定部材７１により軸方向に不
動にされている。この部材７１は、スナップリングの形
式で、壁２１内に係合している。A frictional connection between the locking tooth 68 and the corresponding tooth 69 is maintained;
The adjustment member is made axially immobile by an axial fixing member 71 such that this connection is mediated via the slide knob spring 36. This member 71 engages within the wall 21 in the form of a snap ring.
調節部材５８の外部端面６３のところには、回動工具受
容部７２が設けられ、これを介して調節部材５８は、図
示されていない工具と連結され、回動されることが可能
である。回動工具受容部７２は、第１実施例の場合、凹
所の形状に構成されているが、突起の形状に構成するこ
とも可能である。A pivoting tool receptacle 72 is provided at the outer end face 63 of the adjusting element 58, via which the regulating element 58 can be connected to a tool (not shown) and pivoted. In the case of the first embodiment, the rotary tool receiving portion 72 is configured in the shape of a recess, but it can also be configured in the shape of a protrusion.
前述の諸部材が、調節部材５８、支承部５８スリツプば
ね３６を主構成要素とする係止機構６７と組合されて、
１つの機能単位となる。７このことを前提とし、調節工
具により調節部材５８に生ぜしめられる回転運動により
、ストップピン５３と端縁６１の軸方向運動が生じるこ
の軸方向運動は、係上段によりセルフ０ツクされる。The above-mentioned members are combined with a locking mechanism 67 whose main components are an adjustment member 58, a support portion 58, and a slip spring 36,
It becomes one functional unit. 7. Given this, the rotary movement produced in the adjusting member 58 by the adjusting tool causes an axial movement of the stop pin 53 and the end edge 61, which axial movement is self-zeroed by the locking stage.
端縁６１が、調節器１９に対してこのように軸方向に変
位することにより、始動供給量レリーズレバ−として作
用するシフトレバ−６２の位置変更ができ、シフトレバ
−６２が調節され一方では、調節器１９の肩２２を介し
て調速器リンケージのリンク結合が生じ、他方では、調
節器１９内に支承された連結ピン１８を介して遠心錘１
４のリンク結合が生じる。This axial displacement of the edge 61 relative to the regulator 19 allows a change in the position of the shift lever 62, which acts as a starting supply release lever, so that the shift lever 62 is adjusted while the regulator A linkage of the governor linkage takes place via a shoulder 22 of the regulator 19, and on the other hand a linkage of the centrifugal weight 1 via a connecting pin 18 mounted in the regulator 19.
4 link combinations occur.
ラジアル歯継手の形式で作業する係止機構６７の代りに
、別の歯形式、たとえば外側セレイションとして構成す
ることもできる。Instead of the locking mechanism 67 operating in the form of a radial tooth joint, it can also be designed in another tooth type, for example as an external serration.
第２の実施例では、調節器１９内に、付加スリップ部材
７３（第２図に破線で示す）が配置されている。加えて
、加圧片３４のところには、第１のばね対応受け７４が
、また支承部４４ないし、それに代りストップピン５３
のところには第２のばね対応受け７６が設けられている
。双方の対応受けの間には、付加スリップばね７６が、
スリップばね３６同様、圧縮コイルばねとして構成され
、配置されている。In a second embodiment, an additional slip member 73 (shown in phantom in FIG. 2) is arranged within the regulator 19. In addition, at the pressure piece 34 there is also a first spring-receiving support 74 which can also be connected to the bearing 44 or, alternatively, to the stop pin 53.
A second spring-compatible receiver 76 is provided there. An additional slip spring 76 is provided between the two corresponding receivers.
Like the slip spring 36, it is constructed and arranged as a compression coil spring.
こうすることにより、スリップばね３６との協働の結果
、ばね定数の変化と、ひいては、調節器１９のふれの減
少を介して遠心調速器の調速挙動とに、有利な影響が与
えられる。In this way, as a result of the cooperation with the slip spring 36, the variation of the spring constant and thus the governing behavior of the centrifugal governor is advantageously influenced via a reduction in the deflection of the regulator 19. .
第３図の実施例では、双方のばね対応受け７４．７６を
介して行なわれる付加スリップばね７３の支持が、第２
図の突出構成の代りに、円筒形の凹所７７により行なわ
れる。この構成は、支承部４４の第２のばね対応受け７
６にも転用できる。In the embodiment of FIG. 3, the support of the additional slip spring 73 via the two spring counters 74, 76 is
Instead of the protruding arrangement shown, this is done by a cylindrical recess 77. This configuration allows the second spring-compatible receiver 7 of the support portion 44 to
It can also be used for 6.
第１図は本発明による遠心調速器の略示縦断面図、第２
図は、係止機構の一部として構成された遠心調速基調節
部材を有する第１実施例の部分断面図、第２ａ図は第２
図の部分拡大図、第３図は、第２実施例の付加スリップ
ばね対応受けの部分を示した図である。
１１・・・ケーシング、１２・・・駆動軸、１３・・、
遠心錘調整器、１４・・・遠心錘、１５・・・噴射ポン
プ１６・・・調整ばね、１７・・・アングルレバ−１８
・・・連結ピン、１９・・・調節器、２１・・・壁、２
２、・・肩、２３・・・端面、２４・・・調速器リンケ
ージ、２５・・・調節レバー ３１・・・調整パー ３
２・・・調節部材、３３・・・ストッパ、３４・・・加
圧片、３５・・・対応ストッパ、３６・・・スリップば
ね、３７−＝穴、３８・・・縦孔、３９・・・端側、４
１・・・端側、４２・・・つば内側、４３・・・つば、
４４・・・支承部、４６・・・基体、４７・・・突起、
４８・・・穴、５１・・・案内面、５２・・・ヘット部
分、５３・・・ストップピン、５４・・・軸部、５６・
・・外ねじ山、５７・・・内ねじ山６２・・・シフトレ
バ−６３・・・外側端面、６４・・・内側端面、６７・
・・係止機構、６８・・・係止歯、６９・・・対応歯、
７１・・・軸方向固定部材、７２・・・回動工具受容部
、７３・・・付加スリップばね、７４・・・ばね対応受
け、
７６・・・ばね対応受け、７７
・・凹所。FIG. 1 is a schematic longitudinal sectional view of a centrifugal governor according to the present invention, and FIG.
The figure is a partial sectional view of the first embodiment having a centrifugal speed governor adjustment member configured as a part of the locking mechanism, and FIG.
FIG. 3, which is a partially enlarged view of the figure, shows a portion of the additional slip spring corresponding receiver of the second embodiment. 11...Casing, 12...Drive shaft, 13...
Centrifugal weight regulator, 14... Centrifugal weight, 15... Injection pump 16... Adjustment spring, 17... Angle lever 18
...Connecting pin, 19...Adjuster, 21...Wall, 2
2...Shoulder, 23...End face, 24...Governor linkage, 25...Adjustment lever 31...Adjustment par 3
2... Adjustment member, 33... Stopper, 34... Pressure piece, 35... Corresponding stopper, 36... Slip spring, 37-=hole, 38... Vertical hole, 39...・End side, 4
1... end side, 42... brim inside, 43... brim,
44...Supporting part, 46...Base body, 47...Protrusion,
48... Hole, 51... Guide surface, 52... Head portion, 53... Stop pin, 54... Shaft portion, 56...
...Outer thread, 57...Inner thread 62...Shift lever 63...Outer end surface, 64...Inner end surface, 67.
...locking mechanism, 68...locking teeth, 69...corresponding teeth,
71... Axial fixing member, 72... Rotating tool receiver, 73... Additional slip spring, 74... Spring compatible receiver, 76... Spring compatible receiver, 77... Recess.
Claims (1)
（１４）が、少なくとも１つのスリップばね（３６）を
有する、調整スリーブとして役立つ調節器（１９）を、
少なくとも１つの調整ばね（１６）の力に抗して回転数
に応じて調整し、この調節器（１９）が、調速器リンケ
ージ（２４）を介して噴射ポンプ（１５）の供給量調節
部材（３２）を操作し、かつまたこの調節器（１９）内
にはシフトレバー（６２）と連結可能なストップピン（
５３）が受容されており、しかも、少なくとも１つのス
トッパ（３３）を介して供給量調節部材（３２）の路程
が制限され、全負荷量を制限するストッパ（３３）が、
供給量調節部材（３２）と結合された対応ストッパ（３
５）の路程を超えて、シフトレバー（６２）を介して運
動可能であり、供給量調節部材（３２）が、全負荷量を
超える始動供給量を計算する位置へ移動可能である形式
のものにおいて、ストップピン（５３）の軸方向の位置
決めが、係止機構（６７）により変更可能であり、この
係止機構が、係止歯（６８）を介して、調節器（１９）
内に回動不能に配置された支承部（４４）と、スリップ
ばね（３６）の作用を受けて噛合うことを特徴とする燃
料噴射機関用の遠心調速器。 ２、調節器（１９）が、一方では、その外輪部をなす肩
（２２）を介して調速器リンケージ（２４）と、また、
端縁（６１）を介して間接的にシフトレバー（６２）と
、それぞれ連結され、他方では、遠心錘（１４）への連
結部をなしている連結ピン（１８）を支承しており、更
に、ストップピン（５３）が、調節器（１９）の縦孔（
３８）内を軸方向に可動であり、かつ、周側の案内面（
５１）を介して支承部（４４）内を形状接続式に案内さ
れていることを特徴とする請求項１記載の遠心調速器。 ３、支承部（４４）が、半径方向に突出する突起（４７
）を有するつば（４３）を備えており、この突起（４７
）が、調節器（１９）の壁部（２１）の穴内に係合し、
回動が防止されることを特徴とする請求項２記載の遠心
調速器。 ４、ストップピン（５３）の軸方向運動が調節部材（５
８）を介して行なわれ、この調節部材が、調節器（１９
）の縦孔（３８）内に支承され、軸方向固定部材（７１
）に密接していることを特徴とする請求項２又は３のい
ずれか１項記載の遠心調速器。 ５、調節部材（５８）が、支承部（４４）と向い合った
端側に係止歯（６８）を有していることを特徴とする請
求項４記載の遠心調速器６、支承部（４４）が、つば（
４３）のところに、係止歯（６８）と噛合う対応歯（６
９）を有していることを特徴とする請求項５記載の遠心
調速器。 ７、係止機構（６７）を形成する係止歯（６８）と対応
歯（６９）とが、ラジアル歯継手の形式に構成されてい
ることを特徴とする請求項６記載の遠心調速器。 ８、係止機構（６７）が、外部に位置するセレーション
の形式に構成されていることを特徴とする請求項６記載
の遠心調速器。 ９、スリップばね（３６）が、支承部（４４）と、連結
ピン（１８）に支えられた加圧片（３４）との間に挟込
まれていることを特徴とする請求項１から８までのいず
れか１項記載の遠心調速器。 １０、加圧片（３４）と支承部（４４）ないしストップ
ピン（５３）との間に、付加スリップばね（７３）が挟
込まれていることを特徴とする請求項１から９までのい
ずれか１項記載の遠心調速器。Claims: 1. Centrifugal governor for fuel injection engines, the centrifugal weight (14) of which has a regulator (19) serving as a regulating sleeve, with at least one slip spring (36). ,
The feed rate regulating member of the injection pump (15) is adjusted in dependence on the rotational speed against the force of at least one regulating spring (16), and this regulator (19) is connected via a governor linkage (24) to the supply quantity regulating member of the injection pump (15). (32) and also has a stop pin (inside this adjuster (19) that can be connected to the shift lever (62)).
53) is received, and the travel of the feed rate adjusting member (32) is limited via at least one stop (33), the stop (33) limiting the total load amount.
A corresponding stopper (3) coupled to a supply amount adjusting member (32)
5), which is movable via the shift lever (62) and in which the feed rate adjusting member (32) is movable to a position for calculating a starting feed rate that exceeds the full load amount. , the axial positioning of the stop pin (53) can be varied by a locking mechanism (67), which locking mechanism, via locking teeth (68), can
A centrifugal speed governor for a fuel injection engine, characterized in that a bearing part (44) is non-rotatably disposed therein and meshes with it under the action of a slip spring (36). 2. The regulator (19) is connected on the one hand to the governor linkage (24) via the shoulder (22) forming its outer ring;
It is indirectly connected to the shift lever (62) via the edge (61), and on the other hand supports a connecting pin (18) forming a connecting part to the centrifugal weight (14), and furthermore , the stop pin (53) is inserted into the vertical hole (
38) is movable in the axial direction within the circumferential guide surface (
2. Centrifugal governor according to claim 1, characterized in that it is guided in a form-locking manner in the bearing (44) via the centrifugal governor (51). 3. The support portion (44) has a protrusion (47) projecting in the radial direction.
) with a collar (43), and this protrusion (47
) engages in a hole in the wall (21) of the regulator (19);
The centrifugal governor according to claim 2, characterized in that rotation is prevented. 4. The axial movement of the stop pin (53) is controlled by the adjustment member (5).
8), and this adjusting member is connected to the adjuster (19).
) is supported in the vertical hole (38) of the axial fixing member (71
4. The centrifugal governor according to claim 2, wherein the centrifugal governor is in close contact with the centrifugal speed governor. 5. The centrifugal governor 6 according to claim 4, wherein the adjustment member (58) has locking teeth (68) on the end side facing the support (44). (44) is Tsuba (
43), there is a corresponding tooth (6) that meshes with the locking tooth (68).
9) The centrifugal governor according to claim 5, characterized in that it has: 7. The centrifugal governor according to claim 6, characterized in that the locking teeth (68) and the corresponding teeth (69) forming the locking mechanism (67) are constructed in the form of a radial tooth joint. . 8. Centrifugal governor according to claim 6, characterized in that the locking mechanism (67) is constructed in the form of externally located serrations. 9. Claims 1 to 8, characterized in that the slip spring (36) is sandwiched between the support portion (44) and the pressure piece (34) supported by the connecting pin (18). The centrifugal governor according to any one of the preceding items. 10. Any one of claims 1 to 9, characterized in that an additional slip spring (73) is sandwiched between the pressure piece (34) and the support portion (44) or the stop pin (53). The centrifugal governor according to item 1.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3936184.5 | 1989-10-31 | ||
| DE3936184A DE3936184A1 (en) | 1989-10-31 | 1989-10-31 | CENTRIFUGAL SPEED REGULATOR FOR INJECTION ENGINE |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03156131A true JPH03156131A (en) | 1991-07-04 |
Family
ID=6392562
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2292214A Pending JPH03156131A (en) | 1989-10-31 | 1990-10-31 | Centrifugal governor for fuel injection engine |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0425801B1 (en) |
| JP (1) | JPH03156131A (en) |
| DE (2) | DE3936184A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2626524C1 (en) * | 2016-02-09 | 2017-07-28 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Вятский государственный университет" | Diesel control system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH319357A (en) * | 1953-02-14 | 1957-02-15 | Bosch Gmbh Robert | Fuel injection system for internal combustion engines |
| AT288088B (en) * | 1967-11-14 | 1971-02-25 | Bosch Gmbh Robert | Centrifugal governor for speed control of diesel engines |
| DE2308260C2 (en) * | 1973-02-20 | 1983-11-24 | Robert Bosch Gmbh, 7000 Stuttgart | Centrifugal governor for internal combustion engines |
| DE2334729B2 (en) * | 1973-07-07 | 1978-04-06 | Robert Bosch Gmbh, 7000 Stuttgart | Centrifugal governor for internal combustion engines |
| DE3301416A1 (en) * | 1983-01-18 | 1984-07-19 | Robert Bosch Gmbh, 7000 Stuttgart | SPEED CONTROLLER OF A FUEL INJECTION PUMP |
-
1989
- 1989-10-31 DE DE3936184A patent/DE3936184A1/en not_active Withdrawn
-
1990
- 1990-09-13 DE DE90117627T patent/DE59003688D1/en not_active Expired - Fee Related
- 1990-09-13 EP EP90117627A patent/EP0425801B1/en not_active Expired - Lifetime
- 1990-10-31 JP JP2292214A patent/JPH03156131A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE3936184A1 (en) | 1991-05-02 |
| EP0425801A1 (en) | 1991-05-08 |
| EP0425801B1 (en) | 1993-12-01 |
| DE59003688D1 (en) | 1994-01-13 |
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