JP2006097480A - Centrifugal governor of diesel engine - Google Patents

Centrifugal governor of diesel engine Download PDF

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JP2006097480A
JP2006097480A JP2004281322A JP2004281322A JP2006097480A JP 2006097480 A JP2006097480 A JP 2006097480A JP 2004281322 A JP2004281322 A JP 2004281322A JP 2004281322 A JP2004281322 A JP 2004281322A JP 2006097480 A JP2006097480 A JP 2006097480A
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governor
lever
spring
force input
force
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Tomoyoshi Sakano
倫祥 坂野
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Kubota Corp
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Kubota Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To prevent hunching from occurring in the rotational speed of an engine by using a spring with a large spring constant as a governor spring without increasing a governor weight. <P>SOLUTION: A distance B from the axis X of the pivot shaft 61 of a governor lever 20 to a spring locking part 31 is set longer than a distance A from the axis X to a governor input part 41, and as viewed in a line of sight parallel with the axis Y of the governor shaft 10, the spring locking part 31 and the governor input part 41 are disposed on the same side with respect to the axis X of the pivot shaft 61. A spring force input lever 21 and a governor force input lever 22 are swingably supported on a lever holder 60 through one pivot shaft 61, and the pivot shaft 61 is disposed on the opposite side of the spring locking part 31 based on a virtual line Z connecting to each other the positions of two mounting bolts 62 and 63 mounting the lever holder 60 on the frame wall of the engine. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、ディーゼルエンジンの遠心式ガバナに関し、詳しくは、遠心式ガバナのハンチングを防止する技術に関する。   The present invention relates to a centrifugal governor of a diesel engine, and more particularly to a technique for preventing hunting of the centrifugal governor.

ディーゼルエンジンの遠心式ガバナの従来技術として、例えば、図３及び図４に示すものが知られている。この遠心式ガバナ１０３は、支点軸１６１に揺動自在に支持されたガバナレバー１２０を備えており、ガバナレバー１２０はスプリング力入力レバー１２１とガバナ力入力レバー１２２とからなっている。スプリング力入力レバー１２１にはスプリング係止部３１が設けられ、ガバナスプリング３２の一端をこのスプリング係止部３１に係止するとともに、他端を調速レバー３３に係止し、スプリング力入力レバー１２１をガバナスプリング力で燃料増量側に付勢している。他方、ガバナ力入力レバー１２２にはガバナ力入力部４１が設けられ、このガバナ力入力部４１にガバナスリーブ１２を介してガバナウェイト（図外）のガバナ力を作用させてガバナ力入力レバー１２２を燃料減量側に押圧させるとともに、このガバナ力入力レバー１２２に出力部４２を設けて、この出力部４２に図外の燃料噴射ポンプの燃料調量部を連動連結させている。そして、ガバナ力とガバナスプリング力との不釣合い力で、ガバナレバー１２０を揺動させることにより、燃料調量部が調量移動されるようになっている。   As a conventional technology of a centrifugal governor of a diesel engine, for example, those shown in FIGS. 3 and 4 are known. The centrifugal governor 103 includes a governor lever 120 that is swingably supported on a fulcrum shaft 161. The governor lever 120 includes a spring force input lever 121 and a governor force input lever 122. The spring force input lever 121 is provided with a spring locking portion 31. One end of the governor spring 32 is locked to the spring locking portion 31 and the other end is locked to the speed control lever 33. 121 is biased toward the fuel increase side by the governor spring force. On the other hand, the governor force input lever 122 is provided with a governor force input portion 41, and a governor force of a governor weight (not shown) is applied to the governor force input portion 41 via the governor sleeve 12 to cause the governor force input lever 122 to move. While pressing to the fuel reduction side, an output portion 42 is provided in the governor force input lever 122, and a fuel metering portion of a fuel injection pump (not shown) is linked to the output portion 42. The fuel metering section is metered and moved by swinging the governor lever 120 with an unbalanced force between the governor force and the governor spring force.

この従来の遠心式ガバナ１０３では、ガバナレバー１２０の支点軸１６１の軸心線ｘからスプリング係止部３１までの距離ｂが同軸心線ｘからガバナ力入力部４１までの距離ａよりも長くなるように構成されている。また、図３に示すように、ガバナ軸１０の軸心線Ｙと平行な視線で見た場合に、スプリング係止部３１とガバナ力入力部４１とがガバナレバー１２０の支点軸１６１の軸心線ｘを基準に同じ側に配置されている。なお、図３・図４において、符号１６０は支点軸１６１を支持するレバーホルダ、符号６２・６３はレバーホルダ１６０をエンジン機壁４に着脱自在に取り付ける取付ボルト、符号６６は支点軸位置決め用ボルトである。   In this conventional centrifugal governor 103, the distance b from the axial center line x of the fulcrum shaft 161 of the governor lever 120 to the spring locking part 31 is longer than the distance a from the coaxial core line x to the governor force input part 41. It is configured. Further, as shown in FIG. 3, when viewed in a line of sight parallel to the axis Y of the governor shaft 10, the spring locking portion 31 and the governor force input portion 41 are connected to the axis of the fulcrum shaft 161 of the governor lever 120. They are arranged on the same side with respect to x. 3 and 4, reference numeral 160 is a lever holder for supporting the fulcrum shaft 161, reference numerals 62 and 63 are mounting bolts for detachably attaching the lever holder 160 to the engine machine wall 4, and reference numeral 66 is a fulcrum shaft positioning bolt. It is.

特開平７−３３２１２５号公報JP 7-332125 A 特開２００２−１５５７６４号公報JP 2002-155664 A

一般に、エンジン回転数のハンチング防止にはバネ定数の大きいガバナスプリングを用いればよい。しかし、ガバナスプリングとしてバネ定数の大きいバネを用いた場合には、ガバナスプリング力と拮抗させるガバナ力も大きくする必要があるため、ガバナウェイトを大きく（重く）する等の対策が必要となる。   In general, a governor spring having a large spring constant may be used to prevent hunting of the engine speed. However, when a spring having a large spring constant is used as the governor spring, it is necessary to increase the governor force to be antagonized with the governor spring force. Therefore, measures such as increasing (heavy) the governor weight are required.

しかし、収容スペースの制約等の理由によりガバナウェイトを大きくすることは困難な場合が多く、特に、特許文献２に示すように、ガバナウェイトとしてウェイトボールを用い、このウェイトボールを伝動ギヤ内に収容させた場合には、伝動ギヤ自体の大きさの制約により、ウェイトボールの大きさを大きくすることは極めて困難であった。   However, it is often difficult to increase the governor weight due to the limitation of the accommodation space. In particular, as shown in Patent Document 2, a weight ball is used as the governor weight, and this weight ball is accommodated in the transmission gear. In such a case, it is extremely difficult to increase the size of the weight ball due to the limitation of the size of the transmission gear itself.

本発明は、かかる課題の解決を目的としており、ガバナウェイトを大きくしなくても、ガバナスプリングとしてバネ定数の大きいバネを使用することができ、これによりエンジン回転数のハンチングを防止することができるディーゼルエンジンの遠心式ガバナを提供することを目的とする。   The present invention aims to solve such a problem, and a spring having a large spring constant can be used as a governor spring without increasing the governor weight, thereby preventing hunting of the engine speed. An object is to provide a centrifugal governor for a diesel engine.

上記課題を解決するために、本発明は以下のように構成したことを特徴とする。
すなわち、支点軸（６１）に揺動自在に支持されたガバナレバー（２０）を備え、このガバナレバー（２０）はスプリング力入力レバー（２１）とガバナ力入力レバー（２２）とを具備し、前記スプリング力入力レバー（２１）にスプリング係止部（３１）を設けて、このスプリング係止部（３１）にガバナスプリング（３２）の一端を係止するとともに、ガバナスプリング（３２）の他端を調速レバー（３３）に係止して、前記スプリング力入力レバー（２１）をガバナスプリング力（ＧＳ）で燃料増量側（Ｒ）に付勢し、前記ガバナ力入力レバー（２２）にガバナ力入力部（４１）を設けて、このガバナ力入力部（４１）に、ガバナ軸（１０）にスライド自在に設けられたガバナスリーブ（１２）を介してガバナウェイトのガバナ力（ＧＦ）を作用させてガバナ力入力レバー（２２）を燃料減量側（Ｌ）に押圧させるとともに、前記ガバナ力入力レバー（２２）に出力部（４２）を設けて、この出力部（４２）に燃料噴射ポンプの燃料調量部を連動連結し、ガバナ力（ＧＦ）とガバナスプリング力（ＧＳ）との不釣合い力で、前記ガバナレバー（２０）を揺動させることにより、前記燃料調量部を調量移動させるようにした、ディーゼルエンジンの遠心式ガバナであって、ガバナレバー（２０）の支点軸（６１）の軸心線（Ｘ）からスプリング係止部（３１）までの距離（Ｂ）が同軸心線（Ｘ）からガバナ力入力部（４１）までの距離（Ａ）よりも長くなるようにし、ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、前記スプリング係止部（３１）と前記ガバナ力入力部（４１）とが前記支点軸（６１）の軸心線（Ｘ）を基準に同じ側に配置されている、ディーゼルエンジンの遠心式ガバナにおいて、前記スプリング力入力レバー（２１）と前記ガバナ力入力レバー（２２）とを１本の支点軸（６１）でレバーホルダ（６０）に揺動自在に支持し、このレバーホルダ（６０）はエンジン機壁（４）に少なくとも２つの取付ボルト（６２）・（６３）で着脱自在に取り付けられ、ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、前記支点軸（６１）を、前記２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）を基準にスプリング係止部（３１）とは反対側に配置した、ことを特徴とする。 In order to solve the above problems, the present invention is configured as follows.
In other words, a governor lever (20) supported swingably on a fulcrum shaft (61) is provided. The governor lever (20) comprises a spring force input lever (21) and a governor force input lever (22), and the spring The force input lever (21) is provided with a spring locking portion (31), and one end of the governor spring (32) is locked to the spring locking portion (31) and the other end of the governor spring (32) is adjusted. The spring force input lever (21) is urged to the fuel increase side (R) by the governor spring force (GS) by engaging with the speed lever (33), and the governor force input to the governor force input lever (22) is input. A governor force (G) of a governor weight is provided via a governor sleeve (12) slidably provided on the governor shaft (10) to the governor force input portion (41). ) To press the governor force input lever (22) toward the fuel reduction side (L), and the governor force input lever (22) is provided with an output portion (42). The output portion (42) is provided with fuel. The fuel metering unit of the injection pump is linked and connected, and the fuel metering unit is adjusted by swinging the governor lever (20) by the unbalanced force between the governor force (GF) and the governor spring force (GS). This is a centrifugal governor of a diesel engine that is moved by an amount, and the distance (B) from the axis (X) of the fulcrum shaft (61) of the governor lever (20) to the spring locking portion (31) is coaxial. The spring is longer than the distance (A) from the core wire (X) to the governor force input portion (41) and viewed in a line of sight parallel to the shaft center line (Y) of the governor shaft (10). Locking portion (31) and governor force The centrifugal force governor of a diesel engine, wherein the force portion (41) is arranged on the same side with respect to the axis (X) of the fulcrum shaft (61), the spring force input lever (21) and the governor The force input lever (22) is swingably supported by the lever holder (60) by a single fulcrum shaft (61), and the lever holder (60) is attached to the engine machine wall (4) with at least two mounting bolts ( 62) and (63) are detachably attached, and when viewed in a line of sight parallel to the axis (Y) of the governor shaft (10), the fulcrum shaft (61) is connected to the two mounting bolts (62). ) And (63) are arranged on the side opposite to the spring locking portion (31) with reference to an imaginary line (Z) connecting the positions of (63).

ここで、前記支点軸（６１）の軸心線（Ｘ）が前記２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）に平行であることが望ましい。   Here, it is desirable that the axial center line (X) of the fulcrum shaft (61) is parallel to a virtual line (Z) connecting the positions of the two mounting bolts (62) and (63).

また、前記支点軸（６１）は、一体形成されたレバーホルダ（６０）に支持されていることが望ましい。   The fulcrum shaft (61) is preferably supported by an integrally formed lever holder (60).

本発明の作用効果を従来技術と対比して説明すると以下のとおりである（図２参照）。
図３に示す従来の遠心式ガバナ（１０３）において、支点・力点・作用点の関係をそれぞれ揺動支点（ｘ）・ガバナ力入力部（４１）・スプリング係止部（３１）において検証する。ガバナ力入力部（４１）に作用するガバナ力をＦ１、スプリング係止部（３１）（ガバナスプリング係止位置）でのガバナ力の作用をＦ２、ガバナレバー（１２０）の揺動支点（ｘ）からガバナ力入力部（４１）までの距離をａ、同揺動支点（ｘ）からスプリング係止部（３１）までの距離をｂとした場合、以下の関係が成り立つ。
Ｆ２＝（ａ／ｂ）Ｆ１
このＦ２がガバナスプリング力（ＧＳ）と直接拮抗することになる。 The effects of the present invention will be described in comparison with the prior art (see FIG. 2).
In the conventional centrifugal governor (103) shown in FIG. 3, the relationship between the fulcrum, the force point, and the action point is verified at the swing fulcrum (x), the governor force input part (41), and the spring locking part (31). The governor force acting on the governor force input portion (41) is F 1 , the governor force action at the spring locking portion (31) (the governor spring locking position) is F 2 , and the swing fulcrum (x ) To the governor force input portion (41) is a, and the distance from the swing fulcrum (x) to the spring locking portion (31) is b, the following relationship holds.
F 2 = (a / b) F 1
The F 2 is to antagonize directly governor spring force (GS).

これに対し、本発明では、例えば図１に示すように、ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、ガバナレバー（２０）の支点軸（６１）を、レバーホルダ（６０）に設けられた２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）を基準にスプリング係止部（３１）とは反対側に配置したので、ガバナレバー（２０）の揺動支点（Ｘ）（支点軸（６１）の軸心線）からガバナ力入力部（４１）までの距離及び同揺動支点（Ｘ）からスプリング係止部（３１）までの距離がそれぞれ長くなる。本発明におけるガバナレバー（２０）の揺動支点（Ｘ）からガバナ力入力部（４１）までの距離をＡ、同揺動支点（Ｘ）からスプリング係止部（３１）までの距離をＢとし、従来技術の場合と同じ大きさのガバナ力Ｆ１がガバナ力入力部（４１）に作用したとすると、スプリング係止部（３１）（ガバナスプリング係止位置）でのガバナ力の作用Ｆ２’は次のようになる。
Ｆ２’＝（Ａ／Ｂ）Ｆ１
なお、本発明と図３・４の従来の遠心式ガバナ（１０３）の場合とでエンジン機壁（４）における取付ボルト（６２）・（６３）の取り付け位置は変わらないものとする。 On the other hand, in the present invention, for example, as shown in FIG. 1, the fulcrum shaft (61) of the governor lever (20) when viewed in a line of sight parallel to the axis (Y) of the governor shaft (10), Since it is arranged on the side opposite to the spring locking portion (31) with respect to the virtual line (Z) connecting the positions of the two mounting bolts (62) and (63) provided on the lever holder (60), the governor lever ( 20) The distance from the swing fulcrum (X) (axis of the fulcrum shaft (61)) to the governor force input part (41) and the distance from the swing fulcrum (X) to the spring locking part (31) Each becomes longer. In the present invention, the distance from the swing fulcrum (X) of the governor lever (20) to the governor force input part (41) is A, and the distance from the swing fulcrum (X) to the spring locking part (31) is B, Assuming that the governor force F 1 having the same magnitude as that in the prior art is applied to the governor force input portion (41), the action F 2 ′ of the governor force at the spring engaging portion (31) (the governor spring engaging position). Is as follows.
F 2 '= (A / B) F 1
It should be noted that the mounting positions of the mounting bolts (62) and (63) on the engine machine wall (4) are not changed between the present invention and the conventional centrifugal governor (103) shown in FIGS.

ここで、比較のために、図２に示すように、従来技術の支点軸（１６１）の軸心線（ｘ）と本発明の支点軸（６１）の軸心線（Ｘ）との離間距離をｍとし、Ａ＝ａ＋ｍ，Ｂ＝ｂ＋ｍとすると、本発明では、ガバナレバー（２０）の揺動支点（Ｘ）からスプリング係止部（３１）までの距離Ｂは同揺動支点（Ｘ）からガバナ力入力部（４１）までの距離Ａよりも長いので（Ａ＜Ｂないしａ＜ｂ）、
（ａ／ｂ）＜（Ａ／Ｂ）
したがって、Ｆ２＜Ｆ２’となる。 Here, for comparison, as shown in FIG. 2, the distance between the axial center line (x) of the fulcrum shaft (161) of the prior art and the axial center line (X) of the fulcrum shaft (61) of the present invention. In the present invention, the distance B from the swinging fulcrum (X) of the governor lever (20) to the spring locking portion (31) is from the swinging fulcrum (X), where m is A = a + m and B = b + m. Since it is longer than the distance A to the governor force input part (41) (A <B or a <b),
(A / b) <(A / B)
Therefore, F 2 <F 2 ′.

このように、本発明では、ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、前記支点軸（６１）を、２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）を基準にスプリング係止部（３１）と同じ側に配置した場合と比べて、同じ大きさのガバナ力がガバナ力入力部（４１）に作用する場合でも、大きな力をスプリング係止部（３１）に作用させることができるので、ガバナスプリング（３２）のバネ定数を大きくすることができる。この結果、エンジン回転数のハンチングを防止することができ、また、ガバナウェイトの重量を大きくしてガバナ力入力部（４１）に作用するガバナ力自体の大きさを大きくする必要もない。   Thus, in the present invention, the fulcrum shaft (61) is connected to the two mounting bolts (62) and (63) when viewed in a line of sight parallel to the axis (Y) of the governor shaft (10). Compared to the case where the governor force of the same magnitude acts on the governor force input portion (41) as compared with the case where the governor force is applied to the governor force input portion (41) compared with the case where the governor force is applied to the governor force input portion (41). Since force can be applied to the spring locking portion (31), the spring constant of the governor spring (32) can be increased. As a result, it is possible to prevent hunting of the engine speed, and it is not necessary to increase the weight of the governor weight to increase the magnitude of the governor force itself acting on the governor force input portion (41).

以下、本発明の実施形態を図面に基づいて説明する。図１は本発明の実施形態に係る遠心式ガバナの正面図、図２は上記実施形態と従来技術との作用の違いを模式的に説明する側面図である。なお、説明の便宜のため、従来技術と同じ部材には同じ符号を付して説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a front view of a centrifugal governor according to an embodiment of the present invention, and FIG. 2 is a side view schematically illustrating a difference in operation between the embodiment and the prior art. For convenience of explanation, the same members as those in the prior art will be described with the same reference numerals.

本実施形態の遠心式ガバナ３は、前記従来例（図３及び図４）とほぼ同様の基本構成を備える。図１に示すように、本実施形態の遠心式ガバナ３が適用されるディーゼルエンジン１には、図示しない燃料噴射ポンプが収容されるポンプ室（図外）に隣接してガバナ室２が設けられている。本実施形態の遠心式ガバナ３はこのガバナ室２に収容される。ガバナ室２とポンプ室とはエンジン機壁４によって区画される（図４参照）。   The centrifugal governor 3 of the present embodiment has a basic configuration substantially the same as that of the conventional example (FIGS. 3 and 4). As shown in FIG. 1, the diesel engine 1 to which the centrifugal governor 3 of the present embodiment is applied is provided with a governor chamber 2 adjacent to a pump chamber (not shown) in which a fuel injection pump (not shown) is accommodated. ing. The centrifugal governor 3 of this embodiment is accommodated in the governor chamber 2. The governor chamber 2 and the pump chamber are partitioned by the engine machine wall 4 (see FIG. 4).

このガバナ室２には、燃料噴射カム軸１０の一端が導入される。この燃料噴射カム軸１０の一端にガバナウェイト（不図示）及びガバナスリーブ１２が取り付けられる。ガバナウェイトはウェイトボールからなり、燃料噴射カム軸１０の一端に設けられた伝動ギヤ（燃料噴射カムギヤ。不図示）内に公知の態様で収納され、燃料噴射カム軸１０の回転による遠心力（ガバナ力）の作用により移動し、ガバナスリーブ１２を押圧するようになっている（例えば特許文献２参照）。ガバナスリーブ１２は燃料噴射カム軸１０の一端にスライド自在に外嵌され、ガバナウェイトのガバナ力ＧＦを受けてスライドするようになっている。なお、本実施例では、燃料噴射カム軸１０がガバナ軸に相当するが、ガバナウェイト及びガバナスリーブ１２が取り付けられるガバナ軸は燃料噴射カム軸１０でなくてもよい。   One end of the fuel injection cam shaft 10 is introduced into the governor chamber 2. A governor weight (not shown) and a governor sleeve 12 are attached to one end of the fuel injection cam shaft 10. The governor weight is formed of a weight ball, and is housed in a known manner in a transmission gear (fuel injection cam gear, not shown) provided at one end of the fuel injection cam shaft 10, and centrifugal force (governor is controlled) by the rotation of the fuel injection cam shaft 10. It moves by the action of the force) and presses the governor sleeve 12 (see, for example, Patent Document 2). The governor sleeve 12 is slidably fitted to one end of the fuel injection camshaft 10 and is slid by receiving the governor force GF of the governor weight. In the present embodiment, the fuel injection cam shaft 10 corresponds to a governor shaft, but the governor shaft to which the governor weight and the governor sleeve 12 are attached may not be the fuel injection cam shaft 10.

本実施形態の遠心式ガバナ３は、支点軸６１に揺動自在に支持されたガバナレバー２０を備える。ガバナレバー２０は、スプリング力入力レバー２１とガバナ力入力レバー２２とからなる。   The centrifugal governor 3 of the present embodiment includes a governor lever 20 that is swingably supported by the fulcrum shaft 61. The governor lever 20 includes a spring force input lever 21 and a governor force input lever 22.

スプリング力入力レバー２１にはスプリング係止部３１が設けられ、このスプリング係止部３１にガバナスプリング３２の一端が係止されるとともに、ガバナスプリング３２の他端は調速レバー３３に係止される。ガバナスプリング３２はスプリング力入力レバー２１を燃料増量側Ｒへ付勢する。   The spring force input lever 21 is provided with a spring locking portion 31. One end of a governor spring 32 is locked to the spring locking portion 31, and the other end of the governor spring 32 is locked to a speed control lever 33. The The governor spring 32 biases the spring force input lever 21 toward the fuel increase side R.

ガバナ力入力レバー２２にはガバナ力入力部４１が設けられ、このガバナ力入力部４１にガバナスリーブ１２を介してガバナウェイトのガバナ力ＧＦを作用させてガバナ力入力レバー２２を燃料減量側Ｌに押圧させるようになっている。また、ガバナ力入力レバー２２には出力部４２が設けられ、この出力部４２に、図示しない燃料噴射ポンプの燃料調量部を連動連結している。   The governor force input lever 22 is provided with a governor force input portion 41, and a governor force GF of a governor weight is applied to the governor force input portion 41 via the governor sleeve 12 to move the governor force input lever 22 to the fuel reduction side L. It is designed to be pressed. Further, the governor force input lever 22 is provided with an output portion 42, and a fuel metering portion of a fuel injection pump (not shown) is linked to the output portion 42 in conjunction with the output portion 42.

具体的には、ガバナ力入力レバー２２は二股状に形成され、その一方の分岐の先端に出力部４２を設けて、燃料噴射ポンプの燃料調量部（コントロールラック）に設けられたラックピン４５と係合させている（図１及び図２参照）。ガバナ力入力部４１はピン状に形成され、二股状レバーの各分岐に設けられている。本実施形態におけるガバナ力入力部４１は、図１に示すように、ガバナ軸１０の軸心Ｙを基準として点対称の位置にあり、かつ、ガバナ力入力部４１とガバナ軸１０の軸心Ｙとを結ぶ直線がガバナレバー２０の支点軸６１の軸心線Ｘと平行になるように配置されている。   Specifically, the governor force input lever 22 is formed in a bifurcated shape, and an output part 42 is provided at the tip of one branch thereof, and a rack pin 45 provided in a fuel metering part (control rack) of the fuel injection pump; They are engaged (see FIGS. 1 and 2). The governor force input portion 41 is formed in a pin shape and is provided at each branch of the bifurcated lever. As shown in FIG. 1, the governor force input unit 41 in the present embodiment is in a point-symmetrical position with respect to the axis Y of the governor shaft 10, and the axis Y of the governor force input unit 41 and the governor shaft 10. Are arranged so as to be parallel to the axis X of the fulcrum shaft 61 of the governor lever 20.

スプリング力入力レバー２１とガバナ力入力レバー２２との間にはトルクアップ装置５０が介装され、無負荷（０／４）と全負荷（４／４）の間では、トルクピン５１が退入した状態で、スプリング力入力レバー２１とガバナ力入力レバー２２とが一体に揺動して、図外の燃料噴射ポンプの燃料調量部を調量移動させる。エンジン１が過負荷運転に移行するとエンジン回転数が低下し、ガバナスプリング３２で引かれたスプリング力入力レバー２１は燃料制限具５２で全負荷相当位置に受け止められ、トルクスプリング５３がトルクピン５１を押し出して、ガバナ力入力レバー２２を燃料増量側Ｒへ揺動させる。これにより、エンジン１は粘り強さを発揮する。なお、図１中の符号５６はスタートスプリングである。   A torque-up device 50 is interposed between the spring force input lever 21 and the governor force input lever 22, and the torque pin 51 is retracted between no load (0/4) and full load (4/4). In this state, the spring force input lever 21 and the governor force input lever 22 swing together to move the fuel metering portion of the fuel injection pump (not shown) by metering. When the engine 1 shifts to overload operation, the engine speed decreases, the spring force input lever 21 pulled by the governor spring 32 is received at the full load equivalent position by the fuel limiter 52, and the torque spring 53 pushes out the torque pin 51. Then, the governor force input lever 22 is swung to the fuel increase side R. Thereby, the engine 1 exhibits tenacity. In addition, the code | symbol 56 in FIG. 1 is a start spring.

以上のように構成されたガバナレバー２０（スプリング力入力レバー２１及びガバナ力入力レバー２２）は、１本の支点軸６１でレバーホルダ６０に揺動自在に支持される。このレバーホルダ６０は一体に形成され、エンジン機壁４に２つの取付ボルト６２・６３で着脱自在に取り付けられる。これら２つの取付ボルト６２・６３は、両者の軸心を結ぶ直線Ｚが支点軸６１の軸心線Ｘと平行となるように配置されている。なお、符号６６は、支点軸位置決め用ボルトである。また、本実施形態と図３・４の従来の遠心式ガバナ１０３の場合とでエンジン機壁４における取付ボルト６２・６３の取り付け位置は変わらないものとする。   The governor lever 20 (the spring force input lever 21 and the governor force input lever 22) configured as described above is swingably supported by the lever holder 60 with one fulcrum shaft 61. The lever holder 60 is integrally formed and is detachably attached to the engine machine wall 4 with two attachment bolts 62 and 63. These two mounting bolts 62 and 63 are arranged so that a straight line Z connecting the two axes is parallel to the axis X of the fulcrum shaft 61. Reference numeral 66 denotes a fulcrum shaft positioning bolt. Further, the mounting positions of the mounting bolts 62 and 63 on the engine machine wall 4 are not changed between the present embodiment and the conventional centrifugal governor 103 of FIGS.

本実施形態の遠心式ガバナ３は、ガバナレバー２０の支点軸６１の軸心線Ｘからスプリング係止部３１までの距離Ｂが同軸心線Ｘからガバナ力入力部４１までの距離Ａよりも長くなるように構成されている。また、ガバナ軸１０の軸心線Ｙと平行な視線で見た場合に、スプリング係止部３１とガバナ力入力部４１とが支点軸６１の軸心線Ｘを基準に同じ側に配置されている。   In the centrifugal governor 3 of the present embodiment, the distance B from the axial center line X of the fulcrum shaft 61 of the governor lever 20 to the spring locking portion 31 is longer than the distance A from the coaxial core line X to the governor force input portion 41. It is configured as follows. Further, when viewed in a line of sight parallel to the axis Y of the governor shaft 10, the spring locking portion 31 and the governor force input portion 41 are arranged on the same side with respect to the axis X of the fulcrum shaft 61. Yes.

さらに、本実施形態の遠心式ガバナ３では、ガバナ軸１０の軸心線Ｙと平行な視線で見た場合に、前記支点軸６１が、前記２つの取付ボルト６２・６３の位置を結ぶ仮想線Ｚを基準にスプリング係止部３１とは反対側に配置されている。   Further, in the centrifugal governor 3 of the present embodiment, the fulcrum shaft 61 connects the positions of the two mounting bolts 62 and 63 when viewed in a line of sight parallel to the axis Y of the governor shaft 10. It is arranged on the side opposite to the spring locking portion 31 with respect to Z.

次に、本実施形態の作用について説明する（図２参照）。
本実施形態において、ガバナレバー２０の揺動支点Ｘからガバナ力入力部４１までの距離をＡ、同揺動支点からスプリング係止部３１までの距離をＢ、ガバナ力入力部４１に作用するガバナ力をＦ１とすると、スプリング係止部３１（ガバナスプリング係止位置）でのガバナ力の作用Ｆ２’は、支点（揺動支点Ｘ）・力点（ガバナ力入力部４１）・作用点（スプリング係止部３１）の関係から次のようになる。
Ｆ２’＝（Ａ／Ｂ）Ｆ１ Next, the effect | action of this embodiment is demonstrated (refer FIG. 2).
In the present embodiment, the distance from the swing fulcrum X of the governor lever 20 to the governor force input portion 41 is A, the distance from the swing fulcrum to the spring locking portion 31 is B, and the governor force acting on the governor force input portion 41. the When F 1, the action of the governor force F 2 'is at the spring locking portion 31 (governor spring locking position), the fulcrum (fulcrum X) - power point (governor force input portion 41) acting point (spring From the relationship of the locking portion 31), it is as follows.
F 2 '= (A / B) F 1

他方、図３に示す従来の遠心式ガバナ１０３において、ガバナレバー１２０の揺動支点ｘ（支点軸１６１の軸心線）からガバナ力入力部４１までの距離をａ、同揺動支点ｘからスプリング係止部３１までの距離をｂとし、本実施形態と従来技術とで同じ大きさのガバナ力Ｆ１がガバナ力入力部４１に作用したとすると、スプリング係止部３１におけるガバナ力の作用Ｆ２は、以下のようになる。
Ｆ２＝（ａ／ｂ）Ｆ１ On the other hand, in the conventional centrifugal governor 103 shown in FIG. 3, the distance from the swinging fulcrum x of the governor lever 120 (axial center line of the fulcrum shaft 161) to the governor force input portion 41 is a, and from the swinging fulcrum x to the spring engagement. Assuming that the distance to the stopper 31 is b, and the governor force F 1 having the same magnitude is applied to the governor force input portion 41 in the present embodiment and the prior art, the action F 2 of the governor force in the spring engaging portion 31. Is as follows.
F 2 = (a / b) F 1

ここで、比較のために、従来技術の支点軸１６１の軸心線ｘと本発明の支点軸６１の軸心線Ｘとの離間距離をｍとし、Ａ＝ａ＋ｍ，Ｂ＝ｂ＋ｍとすると、本発明では、ガバナレバー２０の揺動支点Ｘからスプリング係止部３１までの距離Ｂは同揺動支点Ｘからガバナ力入力部４１までの距離Ａよりも長いので（Ａ＜Ｂないしａ＜ｂ）、
（ａ／ｂ）＜（Ａ／Ｂ）
したがって、Ｆ２＜Ｆ２’となる。 Here, for comparison, when the distance between the axis x of the fulcrum shaft 161 of the prior art and the axis X of the fulcrum shaft 61 of the present invention is m, and A = a + m and B = b + m, In the present invention, the distance B from the swing fulcrum X of the governor lever 20 to the spring locking portion 31 is longer than the distance A from the swing fulcrum X to the governor force input portion 41 (A <B or a <b).
(A / b) <(A / B)
Therefore, F 2 <F 2 ′.

このように、本実施形態では、ガバナ軸１０の軸心線Ｙと平行な視線で見た場合に、前記支点軸６１を、２つの取付ボルト６２・６３の位置を結ぶ仮想線Ｚを基準にスプリング係止部３１と同じ側に配置した場合と比べて、同じ大きさのガバナ力がガバナ力入力部４１に作用する場合でも、大きな力をスプリング係止部３１に作用させることができるので、ガバナスプリング３２のバネ定数を大きくすることができる。この結果、エンジン回転数のハンチングを防止することができ、また、ガバナウェイトの重量を大きくしてガバナ力入力部４１に作用するガバナ力自体の大きさを大きくする必要もない。   Thus, in the present embodiment, when viewed in a line of sight parallel to the axis Y of the governor shaft 10, the fulcrum shaft 61 is based on the imaginary line Z connecting the positions of the two mounting bolts 62 and 63. Compared with the case where it is arranged on the same side as the spring locking part 31, even when a governor force of the same magnitude acts on the governor force input part 41, a large force can be applied to the spring locking part 31, The spring constant of the governor spring 32 can be increased. As a result, it is possible to prevent hunting of the engine speed, and it is not necessary to increase the weight of the governor weight to increase the magnitude of the governor force itself acting on the governor force input portion 41.

本発明の実施形態に係る遠心式ガバナの正面図（ガバナ軸１０の軸心線Ｙと平行な視線で見た図）The front view of the centrifugal governor which concerns on embodiment of this invention (The figure seen by the gaze parallel to the axial line Y of the governor axis | shaft 10) 上記実施形態と従来技術との作用の違いを模式的に説明する側面図Side view schematically explaining the difference in operation between the embodiment and the prior art 従来の遠心式ガバナの正面図（ガバナ軸１０の軸心線Ｙと平行な視線で見た図）Front view of a conventional centrifugal governor (viewed in a line of sight parallel to the axis Y of the governor shaft 10) 従来の遠心式ガバナの分解斜視図Exploded perspective view of a conventional centrifugal governor

符号の説明Explanation of symbols

４…エンジン機壁、１０…燃料噴射カム軸（ガバナ軸）、１２…ガバナスリーブ、２０…ガバナレバー、２１…スプリング力入力レバー、２２…ガバナ力入力レバー、３１…スプリング係止部、３２…ガバナスプリング、３３…調速レバー、４１…ガバナ力入力部、４２…出力部、６０…レバーホルダ、６１…支点軸、６２…取付ボルト、６３…取付ボルト、ＧＳ…ガバナスプリング力、ＧＦ…ガバナ力、Ｒ…燃料増量方向、Ｌ…燃料減量方向、Ｘ…支点軸の軸心線（揺動支点）、Ｙ…ガバナ軸の軸心線、Ｚ…２つの取付ボルトの位置を結ぶ仮想線、Ａ…支点軸の軸心線Ｘからガバナ力入力部までの距離、Ｂ…支点軸の軸心線Ｘからスプリング係止部までの距離。 4 ... engine machine wall, 10 ... fuel injection cam shaft (governor shaft), 12 ... governor sleeve, 20 ... governor lever, 21 ... spring force input lever, 22 ... governor force input lever, 31 ... spring locking portion, 32 ... governor Spring, 33 ... governing lever, 41 ... governor force input section, 42 ... output section, 60 ... lever holder, 61 ... fulcrum shaft, 62 ... mounting bolt, 63 ... mounting bolt, GS ... governor spring force, GF ... governor force , R: fuel increasing direction, L: fuel decreasing direction, X: axial center line (oscillating fulcrum) of fulcrum shaft, Y: axial center line of governor shaft, Z: virtual line connecting positions of two mounting bolts, A ... distance from the axis X of the fulcrum shaft to the governor force input part, B ... distance from the axis X of the fulcrum axis to the spring locking part.

Claims (3)

支点軸（６１）に揺動自在に支持されたガバナレバー（２０）を備え、このガバナレバー（２０）はスプリング力入力レバー（２１）とガバナ力入力レバー（２２）とを具備し、
前記スプリング力入力レバー（２１）にスプリング係止部（３１）を設けて、このスプリング係止部（３１）にガバナスプリング（３２）の一端を係止するとともに、ガバナスプリング（３２）の他端を調速レバー（３３）に係止して、前記スプリング力入力レバー（２１）をガバナスプリング力（ＧＳ）で燃料増量側（Ｒ）に付勢し、
前記ガバナ力入力レバー（２２）にガバナ力入力部（４１）を設けて、このガバナ力入力部（４１）に、ガバナ軸（１０）にスライド自在に設けられたガバナスリーブ（１２）を介してガバナウェイトのガバナ力（ＧＦ）を作用させてガバナ力入力レバー（２２）を燃料減量側（Ｌ）に押圧させるとともに、前記ガバナ力入力レバー（２２）に出力部（４２）を設けて、この出力部（４２）に燃料噴射ポンプの燃料調量部を連動連結し、
ガバナ力（ＧＦ）とガバナスプリング力（ＧＳ）との不釣合い力で、前記ガバナレバー（２０）を揺動させることにより、前記燃料調量部を調量移動させるようにした、ディーゼルエンジンの遠心式ガバナであって、
ガバナレバー（２０）の支点軸（６１）の軸心線（Ｘ）からスプリング係止部（３１）までの距離（Ｂ）が同軸心線（Ｘ）からガバナ力入力部（４１）までの距離（Ａ）よりも長くなるようにし、
ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、前記スプリング係止部（３１）と前記ガバナ力入力部（４１）とが前記支点軸（６１）の軸心線（Ｘ）を基準に同じ側に配置されている、ディーゼルエンジンの遠心式ガバナにおいて、
前記スプリング力入力レバー（２１）と前記ガバナ力入力レバー（２２）とを１本の支点軸（６１）でレバーホルダ（６０）に揺動自在に支持し、このレバーホルダ（６０）はエンジン機壁（４）に少なくとも２つの取付ボルト（６２）・（６３）で着脱自在に取り付けられ、
ガバナ軸（１０）の軸心線（Ｙ）と平行な視線で見た場合に、前記支点軸（６１）を、前記２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）を基準にスプリング係止部（３１）とは反対側に配置した、ことを特徴とするディーゼルエンジンの遠心式ガバナ。 The fulcrum shaft (61) is provided with a governor lever (20) swingably supported. The governor lever (20) comprises a spring force input lever (21) and a governor force input lever (22).
The spring force input lever (21) is provided with a spring locking portion (31), and one end of the governor spring (32) is locked to the spring locking portion (31) and the other end of the governor spring (32). Is engaged with the governing lever (33), and the spring force input lever (21) is urged to the fuel increase side (R) by the governor spring force (GS),
The governor force input lever (22) is provided with a governor force input portion (41), and the governor force input portion (41) is provided via a governor sleeve (12) slidably provided on the governor shaft (10). The governor force (GF) of the governor weight is applied to press the governor force input lever (22) toward the fuel reduction side (L), and the output portion (42) is provided on the governor force input lever (22). The fuel metering part of the fuel injection pump is linked to the output part (42),
A centrifugal engine of a diesel engine in which the fuel metering unit is metered and moved by swinging the governor lever (20) by an unbalanced force between a governor force (GF) and a governor spring force (GS). Governor,
The distance (B) from the axis (X) of the fulcrum shaft (61) of the governor lever (20) to the spring locking portion (31) is the distance from the coaxial core (X) to the governor force input portion (41) ( A) longer than,
When viewed in a line of sight parallel to the axis (Y) of the governor shaft (10), the spring locking portion (31) and the governor force input portion (41) are axial centers of the fulcrum shaft (61). In the centrifugal governor of the diesel engine, which is arranged on the same side with respect to the line (X),
The spring force input lever (21) and the governor force input lever (22) are swingably supported by a lever holder (60) by a single fulcrum shaft (61), and the lever holder (60) is an engine machine. It is detachably attached to the wall (4) with at least two mounting bolts (62), (63),
When viewed in a line of sight parallel to the axis (Y) of the governor shaft (10), the fulcrum shaft (61) is connected to an imaginary line (Z) connecting the positions of the two mounting bolts (62) and (63). ) On the side opposite to the spring locking portion (31). 請求項１に記載のディーゼルエンジンの遠心式ガバナにおいて、
前記支点軸（６１）の軸心線（Ｘ）が前記２つの取付ボルト（６２）・（６３）の位置を結ぶ仮想線（Ｚ）に平行である、ことを特徴とするディーゼルエンジンの遠心式ガバナ。 The centrifugal governor of the diesel engine according to claim 1,
The centrifugal type of a diesel engine, characterized in that an axis (X) of the fulcrum shaft (61) is parallel to an imaginary line (Z) connecting the positions of the two mounting bolts (62) and (63). Governor. 請求項１又は２に記載のディーゼルエンジンの遠心式ガバナにおいて、
前記支点軸（６１）は、一体形成されたレバーホルダ（６０）に支持されている、ことを特徴とするディーゼルエンジンの遠心式ガバナ。

In the centrifugal governor of the diesel engine according to claim 1 or 2,
The fulcrum shaft (61) is supported by an integrally formed lever holder (60), and is a centrifugal governor for a diesel engine.

JP2004281322A 2004-09-28 2004-09-28 Centrifugal governor of diesel engine Pending JP2006097480A (en)

Priority Applications (1)

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JP2004281322A JP2006097480A (en) 2004-09-28 2004-09-28 Centrifugal governor of diesel engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004281322A JP2006097480A (en) 2004-09-28 2004-09-28 Centrifugal governor of diesel engine

Publications (1)

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JP2006097480A true JP2006097480A (en) 2006-04-13

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JP2004281322A Pending JP2006097480A (en) 2004-09-28 2004-09-28 Centrifugal governor of diesel engine

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