JPS6228670Y2 - - Google Patents
Info
- Publication number
- JPS6228670Y2 JPS6228670Y2 JP17127282U JP17127282U JPS6228670Y2 JP S6228670 Y2 JPS6228670 Y2 JP S6228670Y2 JP 17127282 U JP17127282 U JP 17127282U JP 17127282 U JP17127282 U JP 17127282U JP S6228670 Y2 JPS6228670 Y2 JP S6228670Y2
- Authority
- JP
- Japan
- Prior art keywords
- engine
- throttle valve
- pump
- piston
- oil pressure
- 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
- 238000006073 displacement reaction Methods 0.000 claims description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000004580 weight loss Effects 0.000 description 2
- 230000002079 cooperative effect Effects 0.000 description 1
- 230000000875 corresponding effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- High-Pressure Fuel Injection Pump Control (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
Description
【考案の詳細な説明】 本考案は油圧ガバナの安全装置に関する。[Detailed explanation of the idea] The present invention relates to a safety device for a hydraulic governor.
従来、特願昭55−68988に示されるように、エ
ンジンのクランク軸に連動するポンプと、上記ポ
ンプの吐出側と油溜との間に設けられた絞り弁
と、上記ポンプの吐出側と上記絞り弁との間の油
圧の上昇に伴つて変位するピストンと、同ピスト
ンに連動されたラツクとを具備した油圧ガバナが
知られているが、例えば何んらかの原因により上
記ポンプの吐出側と上記絞り弁との間に油圧が発
生しなくなると、上記ピストンと共に上記ラツク
が燃料増方向に変位してしまい、上記エンジンが
過回転により損傷の惧れが生じる。 Conventionally, as shown in Japanese Patent Application No. 55-68988, a pump linked to the crankshaft of an engine, a throttle valve provided between the discharge side of the pump and the oil sump, and a throttle valve provided between the discharge side of the pump and the oil sump have been proposed. Hydraulic governors are known that are equipped with a piston that is displaced as the oil pressure between it and the throttle valve increases, and a rack that is linked to the piston. If oil pressure is no longer generated between the throttle valve and the throttle valve, the rack along with the piston will be displaced in the direction of fuel increase, and the engine may be damaged due to overspeed.
本考案は上記に鑑み創案されたもので、上述の
ようなガバナ装置において、エンジンの回転数が
その最大許容値よりも小さい設定値を越えたとき
に作動する回転数スイツチ、ポンプの吐出側と絞
り弁との間の油圧が、上記エンジンの回転数が上
記設定値にあるときの正常時の油圧よりも小さい
場合に作動する圧力スイツチ、および両スイツチ
の作動により上記エンジンの排気系を絞る排気ブ
レーキ装置を備えたことを特徴とする。 The present invention was devised in view of the above, and in the governor device as described above, there is a rotation speed switch that operates when the engine rotation speed exceeds a set value smaller than the maximum allowable value, and a rotation speed switch on the discharge side of the pump. A pressure switch that operates when the oil pressure between the throttle valve and the throttle valve is lower than the normal oil pressure when the engine speed is at the set value, and an exhaust that throttles the exhaust system of the engine by operating both switches. It is characterized by being equipped with a brake device.
以下、本考案の一実施例を添付図面に従つて詳
細に説明する。 Hereinafter, one embodiment of the present invention will be described in detail with reference to the accompanying drawings.
第１図において、油圧ガバナ０１はエンジンの
回転速度に応じて駆動される容積型ポンプ１の吐
出側と油溜５との間の油路６内に直列に配置され
た固定絞り弁７と可変絞り弁２を有する。可変絞
り弁２はニードル８の先端を収容する開口を具え
たプランジヤ９を有する。プランジヤ９はアクセ
ルペダルに連動するリンク１０に当接し、アクセ
ルペダルの増速または減速作動時にリンク１０が
反時計方向または時計方向に回転することにより
右方または左方へ移動される。最高速制限ピスト
ン１１は右面を油路１２を介してポンプ１と絞り
弁７との間で油路６に連通されている。ピストン
１１の左面にはセツト力が大かつばね定数が小で
ある戻しばね１４が作用している。中低速制御ピ
ストン１５は右面を油路１６を介して絞り弁７と
２との間で油路６に連通され、左面を油路１７を
介して絞り弁２の下流側で油路６に連通されてい
る。ピストン１５の左面にはセツト力が小でかつ
ばね定数が大である戻しばね１３が作用してい
る。ピストン１１は固定部に枢着されたリンク１
９の一端にロツド２０を介して連結され、ピスト
ン１５はリンク１９の他端に一端を枢着されたリ
ンク２１の中央部にロツド２２を介して連結さ
れ、リンク２１の他端は噴射ポンプの噴射量制御
用ラツクに連結される。なお、２３は安全弁、２
４と２５はストツパを示す。 In FIG. 1, a hydraulic governor 01 is connected to a fixed throttle valve 7 arranged in series in an oil passage 6 between an oil sump 5 and the discharge side of a positive displacement pump 1, which is driven according to the rotational speed of the engine. It has a throttle valve 2. The variable throttle valve 2 has a plunger 9 with an opening for receiving the tip of a needle 8. The plunger 9 comes into contact with a link 10 that is linked to the accelerator pedal, and is moved to the right or left when the link 10 rotates counterclockwise or clockwise when the accelerator pedal accelerates or decelerates. The maximum speed limiting piston 11 has its right side communicated with an oil passage 6 between the pump 1 and the throttle valve 7 via an oil passage 12. A return spring 14 having a large setting force and a small spring constant acts on the left side of the piston 11. The medium and low speed control piston 15 has its right side communicated with the oil passage 6 between the throttle valves 7 and 2 via an oil passage 16, and its left side communicates with the oil passage 6 on the downstream side of the throttle valve 2 via an oil passage 17. has been done. A return spring 13 having a small setting force and a large spring constant acts on the left side of the piston 15. The piston 11 is a link 1 pivotally connected to a fixed part.
The piston 15 is connected to one end of the link 19 via a rod 20, and the piston 15 is connected via a rod 22 to the center of a link 21, which has one end pivotally connected to the other end of the link 19. Connected to the injection quantity control rack. In addition, 23 is a safety valve, 2
4 and 25 indicate stoppers.
また、油路６におけるポンプ１の吐出側と絞り
弁７との間の圧力により作動する圧力スイツチ２
６が同油路６に設けられている。圧力スイツチ２
６は、エンジン回転数に応じて作動する回転数ス
イツチ２８と、電源３０と、図示しないが周知の
エンジンの排気系を絞る排気ブレーキ装置を駆動
させるコイル３２とに直列に接続されている。そ
して、回転数スイツチ２８はエンジンの許容最大
回転数よりは小さい設定値N1（例えば1000rpm）
を越えたときに閉成され、また圧力スイツチ２６
はポンプ１と絞り弁７との間の圧力が正常時にお
いて回転数の設定値N1に対応する油圧P1よりも
下つたときに閉成されるように構成されている。 In addition, a pressure switch 2 is operated by the pressure between the discharge side of the pump 1 and the throttle valve 7 in the oil passage 6.
6 is provided in the oil passage 6. pressure switch 2
6 is connected in series to a rotation speed switch 28 that operates according to the engine rotation speed, a power source 30, and a coil 32 that drives a known exhaust brake device (not shown) that throttles the exhaust system of the engine. Then, the rotation speed switch 28 is set to a set value N 1 that is smaller than the maximum allowable rotation speed of the engine (for example, 1000 rpm).
is closed when the pressure exceeds the pressure switch 26.
is configured to close when the pressure between the pump 1 and the throttle valve 7 falls below a hydraulic pressure P 1 corresponding to a set value N 1 of the rotation speed in normal conditions.
次に上述した油圧ガバナの作動について説明す
る。アクセルペダルが増速方向に作動されると、
リンク１０が反時計方向に回転されてプランジヤ
９が右方へ移動され、プランジヤ９の開口とニー
ドル８の先端とによる絞り面積が増大する。その
結果、可変絞り弁２の上流側の油圧は低下し、ピ
ストン１１と１５は図示の位置に保たれ、リンク
２１に連結されたラツクは増量位置にある。した
がつて、エンジンの回転速度が上昇し、エンジン
によつて駆動されるポンプ１からの油圧が増大す
る。 Next, the operation of the above-mentioned hydraulic governor will be explained. When the accelerator pedal is operated in the direction of increasing speed,
The link 10 is rotated counterclockwise, the plunger 9 is moved to the right, and the aperture area created by the opening of the plunger 9 and the tip of the needle 8 is increased. As a result, the oil pressure upstream of the variable throttle valve 2 is reduced, the pistons 11 and 15 remain in the position shown, and the rack connected to the link 21 is in the increasing position. Therefore, the rotational speed of the engine increases and the oil pressure from the pump 1 driven by the engine increases.
エンジンの中低速回転域において、ポンプ１か
らの油圧は最高速制限ピストン１１の右面に作用
するが、ピストン１１の左面には絞り弁７と２に
よつて調節された油圧およびセツト力が大である
戻しばね１４が作用しているので、ピストン１１
は移動せず図示の位置に保たれたままである。絞
り弁７を通つた油圧はまた中低速制御ピストン１
５の右面に作用する。ピストン１５の左面は低圧
の油溜５に連通し、この面にはセツト力が小であ
る戻しばね１８のみが作用しているので、ピスト
ン１５の右面に作用する油圧はばね１８に抗して
ピストン１５を左方へ移動させる。ピストン１５
の移動によりロツド２２も左方へ移動してリンク
２１をリンク１９との枢着点を中心として時計方
向に回転させ、ラツクを減量方向に作動させる。
高速回転域においては、ポンプ１からの油圧が相
当増大し、この油圧は最高速制限ピストン１１の
右面に作用する。絞り弁７における油圧低下が大
きいので、ピストン１１の右面に作用する油圧は
ピストン１１の左面に作用する油圧およびセツト
力の大きいばね１４に抗してピストン１１を左方
へ移動させる。ピストン１１の移動によりロツド
２０も左方へ移動するので、リンク１９が時計方
向に回転され、またリンク２１がロツド２２との
枢着点を中心として時計方向に回転される。その
結果、ラツクは異なつたリンク比を有するリンク
１９と２１の協働作用によりさらに減量方向に作
動される。 In the medium and low speed rotation range of the engine, the oil pressure from the pump 1 acts on the right side of the maximum speed limiting piston 11, but the oil pressure and setting force adjusted by the throttle valves 7 and 2 are large on the left side of the piston 11. Since a certain return spring 14 is acting, the piston 11
does not move and remains in the position shown. The oil pressure passing through the throttle valve 7 is also applied to the medium and low speed control piston 1.
Acts on the right side of 5. The left side of the piston 15 communicates with the low-pressure oil sump 5, and only the return spring 18 with a small setting force acts on this side, so the hydraulic pressure acting on the right side of the piston 15 acts against the spring 18. Move the piston 15 to the left. piston 15
As a result of this movement, the rod 22 also moves to the left, causing the link 21 to rotate clockwise about the pivot point with the link 19, thereby operating the rack in the direction of weight loss.
In the high speed rotation range, the oil pressure from the pump 1 increases considerably, and this oil pressure acts on the right side of the maximum speed limiting piston 11. Since the oil pressure drop in the throttle valve 7 is large, the oil pressure acting on the right side of the piston 11 moves the piston 11 to the left against the oil pressure acting on the left side of the piston 11 and the spring 14 with a large setting force. As the piston 11 moves, the rod 20 also moves to the left, so the link 19 is rotated clockwise, and the link 21 is also rotated clockwise about the pivot point with the rod 22. As a result, the rack is actuated further in the direction of weight loss by the cooperative action of links 19 and 21 having different link ratios.
そして、何んらかの原因により油路６における
ポンプ１の吐出側と絞り弁７との間の油圧が正常
どおり上昇しないときは、エンジンの回転数が
N1を越えた場合に圧力スイツチ２６および回転
数スイツチ２８が閉成されてコイル３２が通電さ
れ、排気ブレーキが作動するので、エンジン回転
数がそれ以上上昇することを防止でき、同エンジ
ンの過回転による損傷を避けることができるとい
う効果を奏する。 If the oil pressure between the discharge side of the pump 1 in the oil passage 6 and the throttle valve 7 does not rise normally due to some reason, the engine speed will decrease.
When N 1 is exceeded, the pressure switch 26 and rotation speed switch 28 are closed, the coil 32 is energized, and the exhaust brake is activated, which prevents the engine speed from increasing further and prevents the engine from overheating. This has the effect of avoiding damage due to rotation.
しかも、圧力スイツチ２６が閉成される設定値
N1はエンジンの許容最大回転数よりも小さく設
定されているので、車両運転中等に突然生じたガ
バナの故障に対して安全上極めて有利である。 Moreover, the set value at which the pressure switch 26 is closed is
Since N 1 is set smaller than the maximum permissible engine speed, this is extremely advantageous in terms of safety against governor failure that suddenly occurs during vehicle operation.
第１図は本考案の一実施例を示す全体図、第２
図は第１図の圧力スイツチ２６を含む電気回路
図、第３図はエンジン回転数と作動油圧との関係
を示す特性図である。
１……ポンプ、５……油溜、７……絞り弁、１
１……ピストン、２６……圧力スイツチ、２８…
…回転数スイツチ、３２……コイル。
Figure 1 is an overall view showing one embodiment of the present invention;
This figure is an electric circuit diagram including the pressure switch 26 shown in FIG. 1, and FIG. 3 is a characteristic diagram showing the relationship between engine speed and working oil pressure. 1... Pump, 5... Oil sump, 7... Throttle valve, 1
1... Piston, 26... Pressure switch, 28...
...Rotational speed switch, 32...Coil.
Claims (1)
記ポンプの吐出側と油溜との間に設けられた絞り
弁と、上記ポンプの吐出側と上記絞り弁との間の
油圧の上昇に伴つて変位するピストンと、同ピス
トンに連動されたラツクとを具備したものにおい
て、上記エンジンの回転数がその許容最大値より
も小さい設定値を越えたときに作動する回転数ス
イツチ、上記ポンプの吐出側と上記絞り弁との間
の油圧が、上記エンジンの回転数が上記設定値に
あるときの正常時の油圧よりも小さい場合に作動
する圧力スイツチ、および両スイツチの作動によ
り上記エンジンの排気系を絞る排気ブレーキ装置
を備えたことを特徴とする油圧ガバナの安全装
置。 A pump linked to the crankshaft of the engine, a throttle valve provided between the discharge side of the pump and the oil sump, and displacement as the oil pressure between the discharge side of the pump and the throttle valve increases. A rotation speed switch that operates when the engine rotation speed exceeds a set value that is smaller than the maximum allowable value of the engine; A pressure switch that operates when the oil pressure between the throttle valve and the throttle valve is lower than the normal oil pressure when the engine speed is at the set value, and an exhaust that throttles the exhaust system of the engine by operating both switches. A safety device for a hydraulic governor characterized by being equipped with a brake device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17127282U JPS5975529U (en) | 1982-11-12 | 1982-11-12 | Hydraulic governor safety device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17127282U JPS5975529U (en) | 1982-11-12 | 1982-11-12 | Hydraulic governor safety device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5975529U JPS5975529U (en) | 1984-05-22 |
| JPS6228670Y2 true JPS6228670Y2 (en) | 1987-07-23 |
Family
ID=30373661
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17127282U Granted JPS5975529U (en) | 1982-11-12 | 1982-11-12 | Hydraulic governor safety device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5975529U (en) |
-
1982
- 1982-11-12 JP JP17127282U patent/JPS5975529U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5975529U (en) | 1984-05-22 |
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