JP2012149715A - Constant mesh transmission - Google Patents

Constant mesh transmission Download PDF

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JP2012149715A
JP2012149715A JP2011009351A JP2011009351A JP2012149715A JP 2012149715 A JP2012149715 A JP 2012149715A JP 2011009351 A JP2011009351 A JP 2011009351A JP 2011009351 A JP2011009351 A JP 2011009351A JP 2012149715 A JP2012149715 A JP 2012149715A
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shaft
driven gear
gear
clutch
output shaft
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JP5773480B2 (en
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Koji Nishimura
浩二 西村
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TCM Corp
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Abstract

PROBLEM TO BE SOLVED: To provide a constant mesh transmission in which a structure is made simpler by eliminating a shaft, which is not provided with a clutch, and a gear fixed to the shaft and miniaturization and weight saving are achieved by shortening the whole width, in the constant mesh transmission of advance two stages and reverse one stage used for a loading vehicle such as a fork lift.SOLUTION: The constant mesh transmission comprises an input shaft 2, an input shaft driving gear 3, an input shaft driven gear 4, an advance first speed clutch 5, an intermediate shaft 6, an intermediate shaft driving gear 7, an intermediate shaft driven gear 8, a reverse clutch 9, an output shaft 10, an output shaft driving gear 11, an output shaft driven gear 12 and an advance second speed clutch 13 where the input shaft driving gear 3 is meshed with the intermediate shaft driving gear 7 or the intermediate shaft driven gear 8 and the output shaft driven gear 12, and the output shaft driving gear 11 is meshed with the input shaft driven gear 4, the intermediate shaft driven gear 8 or the intermediate shaft driving gear 7.

Description

本発明は、例えばフォークリフト等の荷役車両に適用される前進二段後進一段（前進二速後進一速）の常時噛合式変速機（トランスミッション）の改良に関する。   The present invention relates to an improvement in a continuously-meshing transmission (transmission) of forward two-stage reverse one-stage (forward two-speed reverse one-speed) applied to a cargo handling vehicle such as a forklift.

従来、この種の前進二段後進一段の常時噛合式変速機としては、例えば特許文献１や特許文献２に記載されたものが知られている。   2. Description of the Related Art Conventionally, as this type of continuously meshing type transmission with two forward stages and one reverse stage, for example, those described in Patent Document 1 and Patent Document 2 are known.

前者のものは、基本的には、入力軸と、入力軸に固着された入力歯車と、入力軸に枢着された主従動歯車と、入力軸と主従動歯車との間に設けられた前進二速クラッチと、第一中間軸と、第一中間軸に固着された第一駆動歯車と、第一中間軸に枢着された第一従動歯車と、第一中間軸と第一従動歯車との間に設けられた前進一速クラッチと、第二中間軸と、第二中間軸に固着された第二駆動歯車と、第二中間軸に枢着された第二従動歯車と、第二中間軸と第二従動歯車との間に設けられた後進クラッチと、第三中間軸と、第三中間軸に固着された反転歯車と、出力軸と、出力軸に固着された出力歯車とを備え、入力歯車には、第一駆動歯車が噛合されていると共に、反転歯車を介して第二駆動歯車が噛合され、主従動歯車には、第一従動歯車と第二従動歯車と出力歯車とが噛合されている。   The former is basically an input shaft, an input gear fixed to the input shaft, a main driven gear pivotally attached to the input shaft, and an advance provided between the input shaft and the main driven gear. A second speed clutch, a first intermediate shaft, a first drive gear fixed to the first intermediate shaft, a first driven gear pivotally attached to the first intermediate shaft, a first intermediate shaft and a first driven gear; A forward first speed clutch provided between the second intermediate shaft, a second drive gear fixed to the second intermediate shaft, a second driven gear pivotally attached to the second intermediate shaft, and a second intermediate A reverse clutch provided between the shaft and the second driven gear, a third intermediate shaft, a reverse gear fixed to the third intermediate shaft, an output shaft, and an output gear fixed to the output shaft. The input gear is meshed with the first drive gear, and the second drive gear is meshed with the reverse gear, and the main driven gear is the first driven gear. A second driven gear and the output gear are meshed.

後者のものは、基本的には、入力軸と、入力軸に固着された入力歯車と、入力軸に枢着された主従動歯車と、入力軸と主従動歯車との間に設けられた後進クラッチと、第一中間軸と、第一中間軸に固着された第一駆動歯車と、第一中間軸に枢着された第一従動歯車と、第一中間軸と第一従動歯車との間に設けられた前進一速クラッチと、第二中間軸と、第二中間軸に固着された第二駆動歯車と、第二中間軸に枢着された第二従動歯車と、第二中間軸と第二従動歯車との間に設けられた前進二速クラッチと、出力軸と、出力軸に固着された出力歯車とを備え、入力歯車には、第一駆動歯車と第二駆動歯車とが噛合されていると共に、出力歯車には、主従動歯車と第一従動歯車と第二従動歯車とが噛合されている。   The latter basically consists of an input shaft, an input gear fixed to the input shaft, a main driven gear pivotally attached to the input shaft, and a reverse gear provided between the input shaft and the main driven gear. Between the clutch, the first intermediate shaft, the first drive gear fixed to the first intermediate shaft, the first driven gear pivotally attached to the first intermediate shaft, and the first intermediate shaft and the first driven gear A forward first speed clutch, a second intermediate shaft, a second drive gear fixed to the second intermediate shaft, a second driven gear pivotally attached to the second intermediate shaft, and a second intermediate shaft A forward second-speed clutch provided between the second driven gear, an output shaft, and an output gear fixed to the output shaft; the input gear meshes with the first drive gear and the second drive gear; In addition, the main driven gear, the first driven gear, and the second driven gear are meshed with the output gear.

特許第３５７９８５１号公報Japanese Patent No. 3579851 特開２０１０−２１００３４号公報JP 2010-210034 A

ところが、これらのものは、入力軸と第一中間軸と第二中間軸に夫々単一のクラッチが設けられているので、全長（前後方向の長さ）を短くできるものの、クラッチが設けられていない第三中間軸や出力軸だけでなく、これらに固着された反転歯車や出力歯車が必要であったので、部品点数が多くて構造が複雑化すると共に、全幅が長くなってコンパクト化や軽量化が図れなかった。   However, since these are provided with a single clutch on the input shaft, the first intermediate shaft, and the second intermediate shaft, respectively, the overall length (length in the front-rear direction) can be shortened, but the clutch is provided. Not only the third intermediate shaft and output shaft, but also the reversing gear and output gear fixed to them were required, so the number of parts was complicated and the structure was complicated, and the overall width became longer, making it compact and lightweight. It was not possible to make it.

本発明は、叙上の問題点に鑑み、これを解消する為に創案されたもので、その課題とする処は、クラッチが設けられていない軸やこれに固着された歯車を割愛して構造をより簡単化すると共に、全幅を小さくしてコンパクト化と軽量化を図る様にした常時噛合式変速機を提供する事にある。   The present invention was devised in view of the above-mentioned problems, and was devised to solve this problem. The subject of the present invention is a structure that omits a shaft not provided with a clutch and a gear fixed to the shaft. It is to provide an always-meshing type transmission that is simpler and more compact and lighter by reducing the overall width.

本発明の常時噛合式変速機は、基本的には、入力軸と、入力軸に固着された入力軸駆動歯車と、入力軸に枢着された入力軸従動歯車と、入力軸と入力軸従動歯車との間に設けられた前進一速クラッチ又は前進二速クラッチと、中間軸と、中間軸に固着された中間軸駆動歯車と、中間軸に枢着された中間軸従動歯車と、中間軸と中間軸従動歯車との間に設けられた後進クラッチと、出力軸と、出力軸に固着された出力軸駆動歯車と、出力軸に枢着された出力軸従動歯車と、出力軸と出力軸従動歯車との間に設けられた前進二速クラッチ又は前進一速クラッチとを備え、入力軸駆動歯車は、中間軸駆動歯車又は中間軸従動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸従動歯車又は中間軸駆動歯車とに噛合される事に特徴が存する。   The constant mesh transmission of the present invention basically includes an input shaft, an input shaft drive gear fixed to the input shaft, an input shaft driven gear pivotally attached to the input shaft, an input shaft and an input shaft driven A forward first speed clutch or a forward second speed clutch provided between the intermediate gear, an intermediate shaft, an intermediate shaft drive gear fixed to the intermediate shaft, an intermediate shaft driven gear pivotally attached to the intermediate shaft, and an intermediate shaft; A reverse clutch, an output shaft, an output shaft drive gear fixed to the output shaft, an output shaft driven gear pivotally attached to the output shaft, an output shaft and an output shaft A forward two-speed clutch or a forward first-speed clutch provided between the driven gear and the input shaft driving gear is meshed with the intermediate shaft driving gear or the intermediate shaft driven gear and the output shaft driven gear and outputs The shaft drive gear includes an input shaft driven gear and an intermediate shaft driven gear or an intermediate shaft driven gear. Together it is that to lie is a feature.

入力軸と中間軸と出力軸は、単一のクラッチと駆動歯車と従動歯車とが設けられて歯車の歯数のみが異なる所謂略同構造の三つのクラッチ軸、つまり入力用クラッチ軸と中間用クラッチ軸と出力用クラッチ軸にされている。
而して、出力用クラッチ軸と中間用クラッチ軸とのうちの少なくとも出力用クラッチ軸は、他のクラッチ軸に対して前後方向の向きが逆になる様に配置されている。つまり、駆動歯車が従動歯車に噛合されると共に、従動歯車が駆動歯車に噛合される様に配置されている。この事に依り、従来の様に出力歯車を備えた出力軸がなくても、中立状態を成立させる事ができる。
要するに、必要最小限の速度段分のクラッチを備えたクラッチ軸のみで構成し、クラッチを設けていない中間軸や出力軸を割愛したので、それだけ部品点数が少なくて済み、構造が非常に簡単になると共に、全幅も小さくできてコンパクト化と軽量化を図る事ができる。 The input shaft, the intermediate shaft, and the output shaft are provided with a single clutch, a driving gear, and a driven gear, and differ only in the number of teeth of the gear, so-called three clutch shafts having substantially the same structure, that is, the input clutch shaft and the intermediate shaft The clutch shaft and the output clutch shaft are used.
Thus, at least the output clutch shaft of the output clutch shaft and the intermediate clutch shaft is arranged so that the direction in the front-rear direction is opposite to the other clutch shaft. That is, the drive gear is arranged so as to mesh with the driven gear, and the driven gear is meshed with the drive gear. As a result, the neutral state can be established without an output shaft having an output gear as in the prior art.
In short, it is composed of only the clutch shaft with the minimum required speed stage clutch, omitting the intermediate shaft and output shaft without the clutch, so the number of parts is reduced and the structure is very simple. At the same time, the overall width can be reduced, and the size and weight can be reduced.

前進一速クラッチは、入力軸と入力軸従動歯車との間に設けられていると共に、前進二速クラッチは、出力軸と出力軸従動歯車との間に設けられているのが好ましい。この様にすれば、前進一速クラッチを入力軸に設ける事ができるので、設計に幅を持たせる事ができる。   The forward first speed clutch is preferably provided between the input shaft and the input shaft driven gear, and the forward second speed clutch is preferably provided between the output shaft and the output shaft driven gear. In this way, since the forward first speed clutch can be provided on the input shaft, the design can be widened.

前進一速クラッチは、出力軸と出力軸従動歯車との間に設けられていると共に、前進二速クラッチは、入力軸と入力軸従動歯車との間に設けられているのが好ましい。この様にすれば、前進一速クラッチを出力軸に設ける事ができるので、設計に幅を持たせる事ができる。   The forward first speed clutch is preferably provided between the output shaft and the output shaft driven gear, and the forward second speed clutch is preferably provided between the input shaft and the input shaft driven gear. In this way, since the forward first speed clutch can be provided on the output shaft, the design can be widened.

入力軸駆動歯車は、中間軸駆動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸従動歯車とに噛合されるのが好ましい。この様にすれば、入力用クラッチ軸と中間用クラッチ軸との前後方向の向きを揃える事ができると共に、これらに対して出力用クラッチ軸の前後方向の向きを逆にする事ができるので、設計に幅を持たせる事ができる。   The input shaft driving gear is preferably meshed with the intermediate shaft driving gear and the output shaft driven gear, and the output shaft driving gear is preferably meshed with the input shaft driven gear and the intermediate shaft driven gear. In this way, the front-rear direction of the input clutch shaft and the intermediate clutch shaft can be aligned, and the front-rear direction of the output clutch shaft can be reversed with respect to these. The design can be widened.

入力軸駆動歯車は、中間軸従動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸駆動歯車とに噛合されるのが好ましい。この様にすれば、中間用クラッチ軸と出力用クラッチ軸との前後方向の向きを揃える事ができると共に、これらに対して入力用クラッチ軸の前後方向の向きを逆にする事ができるので、設計に幅を持たせる事ができる。   The input shaft drive gear is preferably meshed with the intermediate shaft driven gear and the output shaft driven gear, and the output shaft drive gear is meshed with the input shaft driven gear and the intermediate shaft drive gear. In this way, the front and rear direction of the intermediate clutch shaft and the output clutch shaft can be aligned, and the front and rear direction of the input clutch shaft can be reversed. The design can be widened.

本発明に依れば、次の様な優れた効果を奏する事ができる。
（１） 入力軸、入力軸駆動歯車、入力軸従動歯車、前進一速クラッチ、中間軸、中間軸駆動歯車、中間軸従動歯車、後進クラッチ、出力軸、出力軸駆動歯車、出力軸従動歯車、前進二速クラッチとを備え、入力軸駆動歯車は、中間軸駆動歯車又は中間軸従動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸従動歯車又は中間軸駆動歯車とに噛合されるので、クラッチが設けられていない軸やこれに固着された歯車を割愛する事ができ、構造をより簡単化する事ができると共に、全幅が小さくなってコンパクト化と軽量化を図る事ができる。
（２） 必要最低限の速度段分のクラッチを備えたクラッチ軸のみで構成したので、ポンプ等の補機類をトランスミッションに取付ける際には、これのスペースを確保する事ができる。
（３） 必要最低限の速度段分のクラッチを備えたクラッチ軸のみで構成したので、排ガス規制に依りマフラの大型化やＤＰＦ（微粒子除去装置）等の追加が必要になっても、これらの搭載スペースを確保する事ができる。 According to the present invention, the following excellent effects can be achieved.
(1) Input shaft, input shaft drive gear, input shaft driven gear, forward first speed clutch, intermediate shaft, intermediate shaft drive gear, intermediate shaft driven gear, reverse clutch, output shaft, output shaft drive gear, output shaft driven gear, A forward two-speed clutch, and the input shaft drive gear meshes with the intermediate shaft drive gear or the intermediate shaft driven gear and the output shaft driven gear, and the output shaft drive gear includes the input shaft driven gear and the intermediate shaft driven gear. Or because it is meshed with the intermediate shaft drive gear, the shaft without the clutch and the gear fixed to this can be omitted, the structure can be simplified, and the overall width is reduced and compact. And weight reduction.
(2) Since it is composed only of the clutch shaft provided with the clutch for the minimum required speed stage, it is possible to secure a space for attaching auxiliary equipment such as a pump to the transmission.
(3) Since it is composed only of a clutch shaft having a clutch for the minimum required speed stage, even if it is necessary to increase the size of the muffler or add a DPF (particulate removal device) due to exhaust gas regulations, these Mounting space can be secured.

本発明の第一例に係る常時噛合式変速機の概要を示す縦断側面図。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal side view showing an overview of a constant mesh transmission according to a first example of the present invention. 図１の正面図。The front view of FIG. 本発明の第二例に係る常時噛合式変速機の概要を示す縦断側面図。The vertical side view which shows the outline | summary of the constant meshing type transmission which concerns on the 2nd example of this invention. 図３の正面図。FIG. 4 is a front view of FIG. 3. 本発明の第三例に係る常時噛合式変速機の概要を示す縦断側面図。The longitudinal side view which shows the outline | summary of the constant meshing type transmission which concerns on the 3rd example of this invention. 本発明の第四例に係る常時噛合式変速機の概要を示す縦断側面図。The vertical side view which shows the outline | summary of the constant meshing type transmission which concerns on the 4th example of this invention.

以下、本発明の実施の形態を、図面に基づいて説明する。
図１及び図２は、本発明の常時噛合式変速機の第一例を示している。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 and 2 show a first example of a constant mesh transmission according to the present invention.

図１及び図２に於て、常時噛合式変速機１は、入力軸２、入力軸駆動歯車３、入力軸従動歯車４、前進一速クラッチ５、中間軸６、中間軸駆動歯車７、中間軸従動歯車８、後進クラッチ９、出力軸１０、出力軸駆動歯車１１、出力軸従動歯車１２、前進二速クラッチ１３から構成されて居り、フォークリフト等の荷役車両に適用される。   1 and 2, the constant mesh transmission 1 includes an input shaft 2, an input shaft drive gear 3, an input shaft driven gear 4, a forward first speed clutch 5, an intermediate shaft 6, an intermediate shaft drive gear 7, and an intermediate shaft. The shaft driven gear 8, the reverse clutch 9, the output shaft 10, the output shaft drive gear 11, the output shaft driven gear 12, and the forward two-speed clutch 13, are applied to a cargo handling vehicle such as a forklift.

図１に示す如く、入力軸２と中間軸６と出力軸１０は、図略したケースに水平軸廻りに回転可能に設けられていると共に、夫々平行状態を為している。   As shown in FIG. 1, the input shaft 2, the intermediate shaft 6, and the output shaft 10 are provided in a case (not shown) so as to be rotatable around a horizontal axis, and are in a parallel state.

図２に示す如く、入力軸２は、左上側に配置されていると共に、中間軸６は、入力軸２の右側に配置され、出力軸１０は、入力軸２の下側に配置されている。   As shown in FIG. 2, the input shaft 2 is disposed on the upper left side, the intermediate shaft 6 is disposed on the right side of the input shaft 2, and the output shaft 10 is disposed on the lower side of the input shaft 2. .

入力軸駆動歯車３は、入力軸２に回転不能に固着されたもので、この例では、前側（図１に於て左側、以下同様）に配置されている。
入力軸駆動歯車３には、中間軸駆動歯車７が噛合されていると共に、出力軸従動歯車１２が噛合されている。 The input shaft drive gear 3 is fixed to the input shaft 2 so as not to rotate. In this example, the input shaft drive gear 3 is disposed on the front side (the left side in FIG. 1, and so on).
The input shaft drive gear 3 is meshed with the intermediate shaft drive gear 7 and the output shaft driven gear 12 is meshed.

入力軸従動歯車４は、入力軸２に回転可能に枢着されたもので、この例では、後側（図１に於て右側、以下同様）に配置されている。   The input shaft driven gear 4 is pivotally attached to the input shaft 2 and is arranged on the rear side (right side in FIG. 1, the same applies hereinafter) in this example.

前進一速クラッチ５は、入力軸２と入力軸従動歯車４との間に設けられたもので、この例では、入力軸２から入力軸従動歯車４への動力を接断する様にしてある。   The forward first speed clutch 5 is provided between the input shaft 2 and the input shaft driven gear 4. In this example, the power from the input shaft 2 to the input shaft driven gear 4 is connected and disconnected. .

中間軸駆動歯車７は、中間軸６に回転不能に固着されたもので、この例では、前側に配置されている。   The intermediate shaft drive gear 7 is fixed to the intermediate shaft 6 so as not to rotate, and in this example, is disposed on the front side.

中間軸従動歯車８は、中間軸６に回転可能に枢着されたもので、この例では、後側に配置されている。   The intermediate shaft driven gear 8 is pivotally attached to the intermediate shaft 6 and is arranged on the rear side in this example.

後進クラッチ９は、中間軸６と中間軸従動歯車８との間に設けられたもので、この例では、中間軸６から中間軸従動歯車８への動力を接断する様にしてある。   The reverse clutch 9 is provided between the intermediate shaft 6 and the intermediate shaft driven gear 8, and in this example, the power from the intermediate shaft 6 to the intermediate shaft driven gear 8 is connected and disconnected.

出力軸駆動歯車１１は、出力軸１０に回転不能に固着されたもので、この例では、後側に配置されている。
出力軸駆動歯車１１には、入力軸従動歯車４が噛合されていると共に、中間軸従動歯車８が噛合されている。 The output shaft drive gear 11 is fixed to the output shaft 10 so as not to rotate, and in this example, is disposed on the rear side.
The output shaft drive gear 11 meshes with the input shaft driven gear 4 and the intermediate shaft driven gear 8.

出力軸従動歯車１２は、出力軸１０に回転可能に枢着されたもので、この例では、前側に配置されている。   The output shaft driven gear 12 is pivotally attached to the output shaft 10 and is arranged on the front side in this example.

前進二速クラッチ１３は、出力軸１０と出力軸従動歯車１２との間に設けられたもので、この例では、出力軸従動歯車１２から出力軸１０への動力を接断する様にしてある。   The forward two-speed clutch 13 is provided between the output shaft 10 and the output shaft driven gear 12. In this example, the power from the output shaft driven gear 12 to the output shaft 10 is connected and disconnected. .

次に、この様な構成に基づいてその作用を述解する。
前進一速クラッチ５が接合されると、入力軸２からの動力は、前進一速クラッチ５→入力軸従動歯車４→出力軸駆動歯車１１→出力軸１０へと伝達され、前進一速状態が得られる。
前進二速クラッチ１３が接合されると、入力軸２からの動力は、入力軸駆動歯車３→出力軸従動歯車１２→前進二速クラッチ１３→出力軸１０へと伝達され、前進二速状態が得られる。
後進クラッチ９が接合されると、入力軸２からの動力は、入力軸駆動歯車３→中間軸駆動歯車７→中間軸６→後進クラッチ９→中間軸従動歯車８→出力軸駆動歯車１１→出力軸１０へと伝達され、後進（後進一速）状態が得られる。 Next, the operation will be described based on such a configuration.
When the forward first speed clutch 5 is engaged, the power from the input shaft 2 is transmitted from the forward first speed clutch 5 → the input shaft driven gear 4 → the output shaft drive gear 11 → the output shaft 10, and the forward first speed state is established. can get.
When the forward second speed clutch 13 is engaged, the power from the input shaft 2 is transmitted from the input shaft drive gear 3 to the output shaft driven gear 12 → the forward second speed clutch 13 → the output shaft 10, and the forward second speed state is established. can get.
When the reverse clutch 9 is engaged, the power from the input shaft 2 is supplied to the input shaft drive gear 3 → the intermediate shaft drive gear 7 → the intermediate shaft 6 → the reverse clutch 9 → the intermediate shaft driven gear 8 → the output shaft drive gear 11 → output. It is transmitted to the shaft 10 and a reverse (first reverse speed) state is obtained.

入力軸２と中間軸６と出力軸１０は、単一のクラッチと駆動歯車と従動歯車とが設けられて歯車の歯数のみが異なる所謂略同構造の三つのクラッチ軸、つまり入力用クラッチ軸Ａと中間用クラッチ軸Ｂと出力用クラッチ軸Ｃにされている。
而して、出力用クラッチ軸Ｃは、他のクラッチ軸Ａ，Ｂに対して前後方向の向きが逆になる様に配置されている。つまり、駆動歯車（出力軸駆動歯車１１）が後側にされて従動歯車（入力軸従動歯車４、中間軸従動歯車８）に噛合されると共に、従動歯車（出力軸従動歯車１２）が前側にされて駆動歯車（入力軸駆動歯車３）に噛合される様に配置されている。この事に依り、従来の様に出力歯車を備えた出力軸がなくても、中立状態を成立させる事ができる。 The input shaft 2, the intermediate shaft 6, and the output shaft 10 are provided with a single clutch, a drive gear, and a driven gear so that only the number of gear teeth is different, that is, three clutch shafts having substantially the same structure, that is, an input clutch shaft A, an intermediate clutch shaft B, and an output clutch shaft C.
Thus, the output clutch shaft C is arranged so that the direction of the front-rear direction is reversed with respect to the other clutch shafts A and B. In other words, the drive gear (output shaft drive gear 11) is rearwardly engaged with the driven gear (input shaft driven gear 4, intermediate shaft driven gear 8), and the driven gear (output shaft driven gear 12) is moved forward. And arranged so as to mesh with the drive gear (input shaft drive gear 3). As a result, the neutral state can be established without an output shaft having an output gear as in the prior art.

つまり、必要最小限の速度段分のクラッチを備えたクラッチ軸Ａ，Ｂ，Ｃのみで構成し、クラッチを設けていない中間軸や出力軸を割愛したので、それだけ部品点数が少なくて済み、構造が非常に簡単になると共に、全幅も小さくできてコンパクト化と軽量化を図る事ができる。   In other words, it is composed of only the clutch shafts A, B, C with the minimum required speed stage clutch, and the intermediate shaft and output shaft without the clutch are omitted, so the number of parts can be reduced. Can be made very simple, and the overall width can be reduced to achieve compactness and weight reduction.

次に、本発明の第二例を図３及び図４に基づいて説明する。
第二例は、前進一速クラッチ５と前進二速クラッチ１３とを、第一例とは逆になる様に配置したものである。つまり、前進一速クラッチ５は、出力軸１０と出力軸従動歯車１２との間に設けられていると共に、前進二速クラッチ１３は、入力軸２と入力軸従動歯車４との間に設けられている。
この場合、各歯車は、各速度段に見合った歯数にされている。そして、入力軸駆動歯車３は、中間軸駆動歯車７と出力軸従動歯車１２とに噛合されると共に、出力軸駆動歯車１１は、入力軸従動歯車４と中間軸従動歯車８とに噛合される様に夫々幅が厚く形成されている。 Next, a second example of the present invention will be described with reference to FIGS.
In the second example, the forward first speed clutch 5 and the forward second speed clutch 13 are arranged so as to be opposite to the first example. That is, the forward first speed clutch 5 is provided between the output shaft 10 and the output shaft driven gear 12, and the forward second speed clutch 13 is provided between the input shaft 2 and the input shaft driven gear 4. ing.
In this case, each gear has a number of teeth corresponding to each speed stage. The input shaft driving gear 3 is meshed with the intermediate shaft driving gear 7 and the output shaft driven gear 12, and the output shaft driving gear 11 is meshed with the input shaft driven gear 4 and the intermediate shaft driven gear 8. In this way, the width is formed thick.

前進一速クラッチ５が接合されると、入力軸２からの動力は、入力軸駆動歯車３→出力軸従動歯車１２→前進一速クラッチ５→出力軸１０へと伝達され、前進一速状態が得られる。
前進二速クラッチ１３が接合されると、入力軸２からの動力は、前進二速クラッチ１３→入力軸従動歯車４→出力軸駆動歯車１１→出力軸１０へと伝達され、前進二速状態が得られる。
後進クラッチ９が接合されると、入力軸２からの動力は、入力軸駆動歯車３→中間軸駆動歯車７→中間軸６→後進クラッチ９→中間軸従動歯車８→出力軸駆動歯車１１→出力軸１０へと伝達され、後進（後進一速）状態が得られる。
而して、この様なものは、第一例と同様の効果を奏する事ができる。加えて、前進一速クラッチ５と前進二速クラッチ１３とを、第一例とは逆になる様に配置できるので、設計に幅を持たせる事ができる。 When the forward first speed clutch 5 is engaged, the power from the input shaft 2 is transmitted from the input shaft driving gear 3 → the output shaft driven gear 12 → the forward first speed clutch 5 → the output shaft 10. can get.
When the forward second speed clutch 13 is engaged, the power from the input shaft 2 is transmitted from the forward second speed clutch 13 → the input shaft driven gear 4 → the output shaft drive gear 11 → the output shaft 10, and the forward second speed state is established. can get.
When the reverse clutch 9 is engaged, the power from the input shaft 2 is supplied to the input shaft drive gear 3 → the intermediate shaft drive gear 7 → the intermediate shaft 6 → the reverse clutch 9 → the intermediate shaft driven gear 8 → the output shaft drive gear 11 → output. It is transmitted to the shaft 10 and a reverse (first reverse speed) state is obtained.
Therefore, such a thing can have the same effect as the first example. In addition, the forward first speed clutch 5 and the forward second speed clutch 13 can be arranged so as to be opposite to those in the first example, so that the design can be widened.

次に、本発明の第三例を図５に基づいて説明する。
第三例は、中間用クラッチ軸Ｂを、第一例とは逆向きになる様に配置したものである。つまり、駆動歯車（中間軸駆動歯車７）が後側になると共に、従動歯車（中間軸従動歯車８）が前側になる様に配置されている。
この為、入力軸駆動歯車３は、中間軸従動歯車８と出力軸従動歯車１２とに噛合されると共に、出力軸駆動歯車１１は、入力軸従動歯車４と中間軸駆動歯車７とに噛合される。
而して、この様なものは、第一例と同様の効果を奏する事ができる。加えて、中間用クラッチ軸Ｂと出力用クラッチ軸Ｃとの前後方向の向きを揃える事ができると共に、これらに対して入力用クラッチ軸Ａの前後方向の向きを逆にする事ができるので、設計に幅を持たせる事ができる。 Next, a third example of the present invention will be described with reference to FIG.
In the third example, the intermediate clutch shaft B is arranged in the opposite direction to the first example. That is, the drive gear (intermediate shaft drive gear 7) is arranged on the rear side, and the driven gear (intermediate shaft driven gear 8) is arranged on the front side.
For this reason, the input shaft drive gear 3 is meshed with the intermediate shaft driven gear 8 and the output shaft driven gear 12, and the output shaft drive gear 11 is meshed with the input shaft driven gear 4 and the intermediate shaft drive gear 7. The
Therefore, such a thing can have the same effect as the first example. In addition, the front and rear direction of the intermediate clutch shaft B and the output clutch shaft C can be aligned, and the front and rear direction of the input clutch shaft A can be reversed. The design can be widened.

次に、本発明の第四例を図６に基づいて説明する。
第四例は、中間用クラッチ軸Ｂを、第二例とは逆向きになる様に配置したものである。つまり、駆動歯車（中間軸駆動歯車７）が後側になると共に、従動歯車（中間軸従動歯車８）が前側になる様に配置されている。
この為、入力軸駆動歯車３は、中間軸従動歯車８と出力軸従動歯車１２とに噛合されると共に、出力軸駆動歯車１１は、入力軸従動歯車４と中間軸駆動歯車７とに噛合される。
而して、この様なものは、第二例と同様の効果を奏する事ができる。加えて、中間用クラッチ軸Ｂと出力用クラッチ軸Ｃとの前後方向の向きを揃える事ができると共に、これらに対して入力用クラッチ軸Ａの前後方向の向きを逆にする事ができるので、設計に幅を持たせる事ができる。 Next, a fourth example of the present invention will be described with reference to FIG.
In the fourth example, the intermediate clutch shaft B is arranged in the opposite direction to the second example. That is, the drive gear (intermediate shaft drive gear 7) is arranged on the rear side, and the driven gear (intermediate shaft driven gear 8) is arranged on the front side.
For this reason, the input shaft drive gear 3 is meshed with the intermediate shaft driven gear 8 and the output shaft driven gear 12, and the output shaft drive gear 11 is meshed with the input shaft driven gear 4 and the intermediate shaft drive gear 7. The
Thus, such a thing can have the same effect as the second example. In addition, the front and rear direction of the intermediate clutch shaft B and the output clutch shaft C can be aligned, and the front and rear direction of the input clutch shaft A can be reversed. The design can be widened.

１…常時噛合式変速機、２…入力軸、３…入力軸駆動歯車、４…入力軸従動歯車、５…前進一速クラッチ、６…中間軸、７…中間軸駆動歯車、８…中間軸従動歯車、９…後進クラッチ、１０…出力軸、１１…出力軸駆動歯車、１２…出力軸従動歯車、１３…前進二速クラッチ、Ａ…入力用クラッチ軸、Ｂ…中間用クラッチ軸、Ｃ…出力用クラッチ軸。   DESCRIPTION OF SYMBOLS 1 ... Continuously meshing type transmission, 2 ... Input shaft, 3 ... Input shaft drive gear, 4 ... Input shaft driven gear, 5 ... Forward first speed clutch, 6 ... Intermediate shaft, 7 ... Intermediate shaft drive gear, 8 ... Intermediate shaft Drive gear, 9 ... reverse clutch, 10 ... output shaft, 11 ... output shaft drive gear, 12 ... output shaft driven gear, 13 ... forward second speed clutch, A ... input clutch shaft, B ... intermediate clutch shaft, C ... Output clutch shaft.

Claims (5)

入力軸と、入力軸に固着された入力軸駆動歯車と、入力軸に枢着された入力軸従動歯車と、入力軸と入力軸従動歯車との間に設けられた前進一速クラッチ又は前進二速クラッチと、中間軸と、中間軸に固着された中間軸駆動歯車と、中間軸に枢着された中間軸従動歯車と、中間軸と中間軸従動歯車との間に設けられた後進クラッチと、出力軸と、出力軸に固着された出力軸駆動歯車と、出力軸に枢着された出力軸従動歯車と、出力軸と出力軸従動歯車との間に設けられた前進二速クラッチ又は前進一速クラッチとを備え、入力軸駆動歯車は、中間軸駆動歯車又は中間軸従動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸従動歯車又は中間軸駆動歯車とに噛合される事を特徴とする常時噛合式変速機。   An input shaft, an input shaft drive gear fixed to the input shaft, an input shaft driven gear pivotally attached to the input shaft, and a forward one-speed clutch or forward second gear provided between the input shaft and the input shaft driven gear A speed clutch, an intermediate shaft, an intermediate shaft drive gear fixed to the intermediate shaft, an intermediate shaft driven gear pivotally attached to the intermediate shaft, and a reverse clutch provided between the intermediate shaft and the intermediate shaft driven gear , An output shaft, an output shaft drive gear fixed to the output shaft, an output shaft driven gear pivotally attached to the output shaft, and a forward two-speed clutch or forward gear provided between the output shaft and the output shaft driven gear A first-speed clutch, and the input shaft drive gear meshes with the intermediate shaft drive gear or the intermediate shaft driven gear and the output shaft driven gear, and the output shaft drive gear includes the input shaft driven gear and the intermediate shaft driven gear or Always meshed transmission characterized by being meshed with intermediate shaft drive gear 前進一速クラッチは、入力軸と入力軸従動歯車との間に設けられていると共に、前進二速クラッチは、出力軸と出力軸駆動歯車との間に設けられている請求項１に記載の常時噛合式変速機。   The forward first speed clutch is provided between the input shaft and the input shaft driven gear, and the forward second speed clutch is provided between the output shaft and the output shaft drive gear. Constant mesh transmission. 前進一速クラッチは、出力軸と出力軸駆動歯車との間に設けられていると共に、前進二速クラッチは、入力軸と入力軸従動歯車との間に設けられている請求項１に記載の常時噛合式変速機。   The forward first speed clutch is provided between the output shaft and the output shaft drive gear, and the forward second speed clutch is provided between the input shaft and the input shaft driven gear. Constant mesh transmission. 入力軸駆動歯車は、中間軸駆動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸従動歯車とに噛合される請求項１に記載の常時噛合式変速機。   2. The constant meshing according to claim 1, wherein the input shaft driving gear is meshed with the intermediate shaft driving gear and the output shaft driven gear, and the output shaft driving gear is meshed with the input shaft driven gear and the intermediate shaft driven gear. Type transmission. 入力軸駆動歯車は、中間軸従動歯車と出力軸従動歯車とに噛合されると共に、出力軸駆動歯車は、入力軸従動歯車と中間軸駆動歯車とに噛合される請求項１に記載の常時噛合式変速機。   2. The constant meshing according to claim 1, wherein the input shaft driving gear is meshed with the intermediate shaft driven gear and the output shaft driven gear, and the output shaft driving gear is meshed with the input shaft driven gear and the intermediate shaft driving gear. Type transmission.
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109296725A (en) * 2018-11-22 2019-02-01 浙江金道科技股份有限公司 Small tonnage fork car double-velocity transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62113944A (en) * 1985-11-09 1987-05-25 Yanmar Diesel Engine Co Ltd Forward-rearward two speed type reduction reversing device for ship
JPS63501811A (en) * 1985-09-26 1988-07-21 キャタピラ−・インク countershaft transmission
JPH05272603A (en) * 1992-03-23 1993-10-19 Daihatsu Motor Co Ltd Reverse mechanism for gear transmission
JPH10194196A (en) * 1997-01-13 1998-07-28 Kanzaki Kokyukoki Mfg Co Ltd Ship reversing device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63501811A (en) * 1985-09-26 1988-07-21 キャタピラ−・インク countershaft transmission
JPS62113944A (en) * 1985-11-09 1987-05-25 Yanmar Diesel Engine Co Ltd Forward-rearward two speed type reduction reversing device for ship
JPH05272603A (en) * 1992-03-23 1993-10-19 Daihatsu Motor Co Ltd Reverse mechanism for gear transmission
JPH10194196A (en) * 1997-01-13 1998-07-28 Kanzaki Kokyukoki Mfg Co Ltd Ship reversing device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109296725A (en) * 2018-11-22 2019-02-01 浙江金道科技股份有限公司 Small tonnage fork car double-velocity transmission
CN109296725B (en) * 2018-11-22 2024-02-20 浙江金道科技股份有限公司 Double-speed gearbox for small-tonnage forklift

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