JPH0618823Y2 - Drive coupling device for four-wheel drive - Google Patents

Description

【考案の詳細な説明】 〔産業上の利用分野〕 本考案は油圧ポンプを用いてなる４輪駆動用駆動連結装
置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a drive connecting device for a four-wheel drive using a hydraulic pump.

〔従来技術〕[Prior art]

４輪駆動車は、雪道等の摩擦係数の低い路面、又は砂利
道等の荒れた路面において高い走行安定性を発揮するこ
とは勿論、通常の路面においても、加減速時及び高速走
行時における安定性に優れており、路面の状況及び天候
の如何に拘わらず快適な走行を実現できるものとして、
近年特に脚光を浴びるようになってきた。A four-wheel drive vehicle not only exhibits high running stability on a road surface with a low friction coefficient such as a snow road or a rough road surface such as a gravel road, but also on a normal road surface during acceleration / deceleration and high speed running. As it is excellent in stability and can realize comfortable running regardless of the road condition and weather,
In recent years, it has come into the spotlight.

このような４輪駆動車としては、前，後輪間に生じる回
転速度差に応じて両者に駆動力を配分する駆動連結装置
を、両者間の伝動軸の中途に備えたものが主流となって
いる。この駆動連結装置の一つとして、油圧ポンプを用
いてなる駆動連結装置がある。これは、前，後輪の一方
に連なる軸体に回転を拘束して取付けたロータを、該軸
体への伝動軸に回転を拘束して取付けられたハウジング
内に同軸回動自在に内挿せしめて油圧ポンプを構成し、
ロータとハウジングとの間に、前，後輪間に生じる回転
速度差に応じた相対回転を生ぜしめ、前記油圧ポンプの
内部に、前，後輪間の回転速度差に応じた油圧を発生さ
せて、この油圧に応じてロータとハウジングとの間に生
じる摩擦力（作用圧）により駆動力の伝達を行うもので
ある。The mainstream of such four-wheel drive vehicles is a vehicle equipped with a drive coupling device that distributes a driving force to both the front and rear wheels according to the difference in rotational speed between the front and rear wheels, midway between the two. ing. As one of the drive connecting devices, there is a drive connecting device using a hydraulic pump. This is because a rotor mounted on a shaft connected to one of the front and rear wheels while restraining its rotation is coaxially rotatably inserted into a housing mounted on the shaft which is constrained to rotate at its transmission shaft. Constituting a hydraulic pump,
Relative rotation is generated between the rotor and the housing according to the rotational speed difference between the front and rear wheels, and hydraulic pressure is generated inside the hydraulic pump according to the rotational speed difference between the front and rear wheels. The driving force is transmitted by the frictional force (working pressure) generated between the rotor and the housing in accordance with the hydraulic pressure.

さて、このような駆動連結装置には、ベーンポンプ，ト
ロコイドポンプ等、種々の形式の回転式油圧ポンプが用
いられるが、これらの油圧ポンプは、いずれも、ハウジ
ング内部に開口する吸込口から導入される油を、ハウジ
ングとロータとの間に封止した状態で、ロータの回転に
伴って回転させて昇圧し、同じくハウジング内部に開口
する吐出口から外部に導出するものである。ところが、
前述した如く、駆動連結装置に用いる油圧ポンプは、ハ
ウジングに対するロータの相対回転に応じて油圧を発生
するようになっており、この相対回転の方向が、前，後
輪間の回転速度差の発生態様に応じて正逆に転換するた
め、正転用及び逆転用に各一組の吸込口と吐出口とを設
ける必要がある。そこで、従来の駆動連結装置において
は、ロータの軸長方向一側にてハウジング内部に開口
し、該ハウジング内部への油の流入のみを許容する吸込
チェック弁を装着してなる吸入口と、軸長方向他側にて
ハウジング内部に開口し、該ハウジング内部からの油の
流出のみを許容する吐出チェック弁を装着してなる吐出
口とを、相対回転方向両側に夫々設け、相対回転の方向
が正，逆いずれの場合においても、相対回転方向上流側
に位置する前記吸込口の一方と、同じく下流側に位置す
る前記吐出口の一方との間において、前記昇圧が行われ
るようにしてある。By the way, various types of rotary hydraulic pumps such as a vane pump and a trochoid pump are used for such a drive coupling device, and all of these hydraulic pumps are introduced from a suction port opened inside the housing. In a state where the oil is sealed between the housing and the rotor, the oil is rotated and the pressure is increased in accordance with the rotation of the rotor, and the oil is discharged to the outside from the discharge port that is also opened inside the housing. However,
As described above, the hydraulic pump used in the drive coupling device is adapted to generate hydraulic pressure in accordance with the relative rotation of the rotor with respect to the housing, and the direction of this relative rotation causes a difference in rotational speed between the front and rear wheels. In order to switch between normal and reverse depending on the mode, it is necessary to provide a pair of inlet and outlet for forward rotation and reverse rotation. Therefore, in a conventional drive coupling device, an intake port that is provided with a suction check valve that opens inside the housing on one side in the axial direction of the rotor and that allows only oil to flow into the housing, and a shaft Discharge ports that are open to the inside of the housing on the other side in the longitudinal direction and are equipped with discharge check valves that allow only the outflow of oil from the inside of the housing are provided on both sides in the relative rotation direction. In either of the forward and reverse cases, the pressurization is performed between one of the suction ports located on the upstream side in the relative rotation direction and one of the discharge ports also located on the downstream side.

〔考案が解決しようとする課題〕[Problems to be solved by the device]

さて、このような４輪駆動用駆動連結装置は、前，後輪
間の伝動系の中途部に配設され、車体下部に位置するた
め、その配設位置に空間的制約が存在し、これの小型化
が切望されている。ところが、油圧ポンプを用いてなる
従来の４輪駆動用駆動連結装置においては、前述した如
く、ロータの軸長方向両側に吸込口及び吐出口が夫々設
けてあり、これらに夫々装着される吸込チェック弁及び
吐出チェック弁の配設スペース、並びに両弁に夫々連な
る油路の形成スペースが必要であり、軸長方向寸法が長
大化し、小型化に限界があるという難点があった。By the way, such a four-wheel drive drive coupling device is disposed in the middle of the transmission system between the front and rear wheels and is located at the lower part of the vehicle body. The miniaturization of is strongly desired. However, as described above, in the conventional four wheel drive drive coupling device using the hydraulic pump, the suction port and the discharge port are provided on both sides in the axial direction of the rotor, and the suction check attached to each of these is checked. There is a problem that a space for arranging the valve and the discharge check valve and a space for forming oil passages connected to both valves are required, and the dimension in the axial length direction becomes large and there is a limit to downsizing.

本願出願人等は、前，後輪間における駆動力の配分が行
える上、左右の動輪間においても回転速度差に応じた駆
動力の配分を行い得る４輪駆動車を先に提案した（特願
昭62-310471号）。これは、左右の動輪に夫々連なる車
軸に回転を拘束して取付けたロータを、両車軸への伝動
軸と連動回転する共通のハウジングに同軸的に内挿し
て、左右夫々の車軸と前記伝動軸との回転速度差に応じ
た油圧を夫々発生する一対の油圧ポンプを構成してなる
駆動連結装置を、前部の差動歯車装置及び／又は後部の
差動歯車装置に置換えたものである。The applicants of the present application previously proposed a four-wheel drive vehicle that can distribute the driving force between the front and rear wheels and can also distribute the driving force between the left and right driving wheels according to the rotational speed difference (see No. 62-310471). This is because the rotors attached to the left and right driving wheels while being restrained from rotation are mounted coaxially in a common housing that rotates in conjunction with the transmission shafts for both axles, and the left and right axles and the transmission shaft The drive coupling device, which constitutes a pair of hydraulic pumps that respectively generate hydraulic pressures according to the difference in rotational speed between the above and the above, is replaced with a front differential gear device and / or a rear differential gear device.

この駆動連結装置においては、これが置換えられる差動
歯車装置と同程度の大きさへの小型化が切望される一
方、同心的に並設される一対の油圧ポンプの夫々に前述
した如きスペースが必要であり、全体としての軸長寸法
が長大化するため、前記小型化に対する要求を満足でき
ないという難点があった。This drive coupling device is desired to be downsized to the same size as the differential gear device to which it is replaced, but the space described above is required for each of the pair of concentrically arranged hydraulic pumps. However, since the overall axial length dimension becomes large, there is a drawback that the requirement for downsizing cannot be satisfied.

本考案は斯かる事情に鑑みてなされたものであり、軸長
方向寸法を短縮し、小型化された駆動連結装置を提供す
ることを目的とする。The present invention has been made in view of such circumstances, and an object thereof is to provide a drive coupling device having a reduced axial length dimension and a reduced size.

〔課題を解決するための手段〕[Means for Solving the Problems]

本考案に係る４輪駆動用駆動連結装置は、動輪と連動回
転するロータと、該ロータを同軸的に内挿し、前記動輪
への伝動軸と連動回転するハウジングとを備え、両者間
の回転速度差に応じた油圧を発生する油圧ポンプによ
り、動輪と伝動軸とを連結する４輪駆動用駆動連結装置
において、前記ロータの軸長方向一側に開口して配設さ
れた吸込吐出口と、長手方向を前記ロータの半径方向と
略一致させて前記ハウジングに形成され、前記吸込吐出
口への流入油を通流させる吸込チェック弁、及び吸込吐
出口からの流出油を通流させる吐出チェック弁が、内部
に同軸的に並設してある油路とを具備することを特徴と
する。A four-wheel drive drive coupling device according to the present invention includes a rotor that rotates in conjunction with a driving wheel and a housing that coaxially inserts the rotor and rotates in conjunction with a transmission shaft to the driving wheel. In a four-wheel drive drive coupling device that couples a driving wheel and a transmission shaft by a hydraulic pump that generates a hydraulic pressure according to the difference, a suction / discharge port that is arranged to open on one side in the axial direction of the rotor, A suction check valve that is formed in the housing with its longitudinal direction substantially aligned with the radial direction of the rotor and that allows the inflow oil to flow into the suction and discharge ports, and a discharge check valve that allows the outflow oil from the suction and discharge ports to flow. However, it is provided with an oil passage coaxially arranged inside.

〔作用〕[Action]

本考案においては、ロータの軸長方向一側に形成され、
吸込チェック弁と吐出チェック弁とを同軸的に並設して
ある油路に連通された吸込吐出口が、ロータ，ハウジン
グ間の相対回転の方向に応じて、吸込口としての機能
と、吐出口としての機能とを夫々果たす。In the present invention, it is formed on one side in the axial direction of the rotor,
The suction and discharge ports, which communicate with the oil passage in which the suction check valve and the discharge check valve are coaxially arranged side by side, have a function as a suction port and a discharge port depending on the direction of relative rotation between the rotor and the housing. And each function as.

〔実施例〕〔Example〕

以下本考案をその実施例を示す図面に基づいて詳述す
る。第１図は、本考案に係る４輪駆動用駆動連結装置
（以下本案装置という）の平面断面図である。Hereinafter, the present invention will be described in detail with reference to the drawings showing an embodiment thereof. FIG. 1 is a plan sectional view of a four wheel drive drive coupling device (hereinafter referred to as the device of the present invention) according to the present invention.

本図に示す駆動連結装置は、前述した特願昭62-310471
号におけるものと同様、後部の差動歯車装置に置換えて
用いられ、前，後輪間における駆動力の配分を行い得る
と共に、左右の後輪間における駆動力の配分をも行い得
るものである。The drive coupling device shown in this figure is based on the above-mentioned Japanese Patent Application No. 62-310471.
Similar to the one in No. 1, it is used by being replaced with a rear differential gear device, and can distribute driving force between the front and rear wheels and also distribute driving force between the left and right rear wheels. .

図において１は、車体下部に固設された本案装置のケー
シングであり、左右２個所に開口部を有し、球形殻状を
なす球状部1bと、該球状部1bの前部に、軸長方向を前後
方向として連設された円筒部1aとからなる。円筒部1aに
は、その一端部を車体の前後方向に延設された図示しな
いプロペラシャフトに連結された伝動軸２が、同軸回動
自在に支承せしめてあり、球状部1b内に適長突出された
伝動軸２の他端部には、小傘歯車2aが外嵌固定されてい
る。In the figure, reference numeral 1 denotes a casing of the device of the present invention which is fixed to the lower part of the vehicle body, and has a spherical shell-shaped spherical portion 1b having openings at two left and right portions, and an axial length at the front of the spherical portion 1b. It is composed of a cylindrical portion 1a that is continuously provided with its direction being the front-rear direction. The cylindrical portion 1a has a transmission shaft 2 whose one end is connected to a propeller shaft (not shown) extending in the front-rear direction of the vehicle body so as to be coaxially rotatable, and protrudes into the spherical portion 1b by an appropriate length. A small bevel gear 2a is externally fitted and fixed to the other end of the transmission shaft 2 thus formed.

本案装置は、前記球状部1b内に、前記伝動軸２と直交す
る態様にて回動自在に支承された外側ハウジング５と、
該ハウジング５内部に構成される左右一対のベーンポン
プ３，４とからなる。The device of the present invention comprises an outer housing 5 rotatably supported in the spherical portion 1b in a manner orthogonal to the transmission shaft 2,
The housing 5 includes a pair of left and right vane pumps 3 and 4.

外側ハウジング５は、大径の中抜き円板の一側に、これ
と等しい内径の円筒を同心的に連設させた形状を有し、
円板部分をケーシング１の球状部1b内に位置せしめ、該
球状部1bの左側開口部に内嵌固定された円錐ころ軸受６
により、円筒部分の外周を回動自在に支承させてある大
径側板50と、小径の中抜き円板の一側に、前記円筒と略
同形の円筒を同心的に連設させた形状を有し、これの円
板部分を前記球状部1b内に位置せしめ、前記大径側板50
の円板部分と対向させた態様にて、球状部1bの右側開口
部に内嵌固定された円錐ころ軸受７により、円筒部分の
外周を回動自在に支承させてある小径側板51と、薄肉円
筒の一側に円板状のフランジを内向きに連設した形状を
有し、前記両側板50,51間に構成されるベーンポンプ
３，４の外側を囲繞する態様にて、両側板50,51間に後
述する如く装着された外筒52とからなる。大径側板50の
中抜き部には、これの左右に両端部を夫々適長突出させ
た態様にて、左軸８ｌが回動自在に支承され、また小径
側板51の中抜き部には、同様に右軸8rが支承されてお
り、左軸８ｌの右端部と右軸8rの左端部とは、両側板5
0,51間においてわずかな間隙を介して対向させてある。
また、前記左軸８ｌの左端部及び右軸8rの右端部は、左
側及び右側の後輪に連なる図示しない車軸に夫々連結さ
れており、左軸８ｌ及び右軸8rは、左側の後輪及び右側
の後輪と夫々連動回転するようになっている。The outer housing 5 has a shape in which a cylinder having an equal inner diameter is concentrically connected to one side of a large-diameter hollow disk.
The disk portion is located in the spherical portion 1b of the casing 1, and the tapered roller bearing 6 is fitted and fixed in the left opening of the spherical portion 1b.
Has a shape in which a large-diameter side plate 50 rotatably supporting the outer periphery of a cylindrical portion and a cylinder of approximately the same shape as the aforementioned cylinder are concentrically connected to one side of a small-diameter hollow disk. Then, the disc portion thereof is positioned in the spherical portion 1b, and the large diameter side plate 50 is
A small-diameter side plate 51 that rotatably supports the outer circumference of the cylindrical portion by a tapered roller bearing 7 that is internally fitted and fixed to the right opening of the spherical portion 1b in a state of facing the circular plate portion of The side plates 50, 4 have a shape in which disc-shaped flanges are continuously arranged inwardly on one side of the cylinder and surround the outside of the vane pumps 3, 4 formed between the side plates 50, 51. It is composed of an outer cylinder 52 mounted between 51 as described later. The left shaft 8l is rotatably supported in the hollowed-out portion of the large-diameter side plate 50 in such a manner that both end portions are projected to the left and right of the large-diametered side plate 50, respectively. Similarly, the right shaft 8r is supported, and the right end portion of the left shaft 8l and the left end portion of the right shaft 8r are both side plates 5.
They are opposed to each other with a slight gap between 0 and 51.
Further, the left end portion of the left shaft 8l and the right end portion of the right shaft 8r are respectively connected to unillustrated axles that are connected to the left and right rear wheels, and the left shaft 8l and the right shaft 8r are connected to the left rear wheel and It is designed to rotate in conjunction with the right rear wheel.

ベーンポンプ３は、短寸円筒状をなすロータ30と、これ
と略等しい軸長寸法を有し、後述する如き偏肉筒状をな
すカムリング31とを備え、ロータ30を、前記左軸８ｌの
右側突出部に外嵌し、これとスプライン結合せしめる一
方、前記大径側板50の右側に、カムリング31を同軸的に
位置させ、更に該カムリング31の右側に、これと略等し
い外径を有する厚肉の中抜き円板状をなす中間プレート
10を同軸的に位置させた状態で、大径側板50及びカムリ
ング31をこの順に貫通し、中間プレート10に形成された
図示しないねじ孔に螺合する複数本の固定ボルト32,32
…により、カムリング31を、大径側板50と中間プレート
10との間に挟持させた態様にてこれらと一体化させてハ
ウジングを形成し、このハウジング内に、前記ロータ30
を同軸回動自在に内挿せしめて構成されている。The vane pump 3 is provided with a rotor 30 having a short cylindrical shape and a cam ring 31 having an axial length dimension substantially equal to the rotor 30 and having an uneven thickness tubular shape as described later. The rotor 30 is mounted on the right side of the left shaft 8l. A cam ring 31 is coaxially positioned on the right side of the large-diameter side plate 50 while being externally fitted to the projecting part and spline-coupled with the projecting part, and further on the right side of the cam ring 31, a thick wall having an outer diameter substantially equal to this. Intermediate plate in the shape of a hollow disk
With the 10 positioned coaxially, a plurality of fixing bolts 32, 32 that penetrate the large-diameter side plate 50 and the cam ring 31 in this order and are screwed into screw holes (not shown) formed in the intermediate plate 10.
The cam ring 31 is attached to the large-diameter side plate 50 and the intermediate plate.
A housing is formed in such a manner as to be integrated with these in a state of being sandwiched between the rotor 30 and the rotor 30.
Is coaxially and rotatably inserted.

また他方のベーンポンプ４は、同様のロータ40及びカム
リング41を備え、ロータ40を、前記右軸8rの左側突出部
に外嵌し、これとスプライン結合せしめる一方、前記中
間プレート10の右側にカムリング41を同軸的に位置さ
せ、更に該カムリング41の右側に前記小径側板51を同軸
的に位置させた状態で、小径側板51及びカムリング41を
この順に貫通し、中間プレート10に螺合する複数本の固
定ボルト42,42…により、カムリング41を、中間プレー
ト10と小径側板51との間に挟持させた態様にてこれらと
一体化させてハウジングを形成し、このハウジング内に
前記ロータ40を同軸回動自在に内挿せしめて構成されて
いる。The other vane pump 4 is also provided with a rotor 40 and a cam ring 41 which are similar to each other. The rotor 40 is externally fitted to the left-side protruding portion of the right shaft 8r and spline-coupled thereto, while the cam ring 41 is provided on the right side of the intermediate plate 10. Is coaxially positioned, and further, the small-diameter side plate 51 is coaxially positioned on the right side of the cam ring 41, the small-diameter side plate 51 and the cam ring 41 are penetrated in this order, and a plurality of screws are screwed into the intermediate plate 10. The cam ring 41 is sandwiched between the intermediate plate 10 and the small-diameter side plate 51 by the fixing bolts 42, 42 to be integrated with them to form a housing, and the rotor 40 is coaxially rotated in the housing. It is constructed so that it can be freely inserted.

外側ハウジング５の外筒52は、そのフランジの内側面を
小径側板51の右側面にメタルパッキン９を介して密着せ
しめた状態で、固定ボルト42,42…により、小径側板51
及びカムリング41と共に中間プレート10に固着され、ま
た、左向きに延びるその円筒部の端面を、大径側板50の
右側面にＯリングを介して係合せしめて、ベーンポンプ
３，４の外側を囲繞する態様にて、両側板50,51間に装
着されており、これの内周面と、カムリング31,41、中
間プレート10及び小径側板51の外周面との間に、ベーン
ポンプ３，４の作動油が導入される環状断面の油タンク
Ｔを形成している。また大径側板50の右側面には、外筒
52の係合位置よりも外側に位置して大傘歯車2bが、大径
側板50を左側から貫通してこれに螺合する複数本の固定
ボルト53,53…により、歯形成面を右向きとして固定さ
れており、伝動軸２の後端部に外嵌固定された小傘歯車
2aに噛合させてある。The outer cylinder 52 of the outer housing 5 is fixed to the right side surface of the small-diameter side plate 51 via the metal packing 9 with the inner surface of the flange thereof fixed by the fixing bolts 42, 42 ...
And a mode in which the end face of the cylindrical portion which is fixed to the intermediate plate 10 together with the cam ring 41 and extends leftward is engaged with the right side face of the large-diameter side plate 50 via an O-ring to surround the outside of the vane pumps 3, 4. Is mounted between both side plates 50 and 51, and the hydraulic oil of the vane pumps 3 and 4 is provided between the inner peripheral surface of the side plates 50 and 51 and the outer peripheral surfaces of the cam rings 31 and 41, the intermediate plate 10 and the small diameter side plate 51. An oil tank T having an annular cross section to be introduced is formed. On the right side of the large diameter side plate 50,
The large bevel gear 2b positioned outside the engagement position of 52 has a plurality of fixing bolts 53, 53 ... Penetrating from the left side of the large diameter side plate 50 and screwed into the large side plate 50 so that the tooth forming surface faces right. A small bevel gear that is fixed and externally fitted and fixed to the rear end of the transmission shaft 2.
It is meshed with 2a.

ベーンポンプ３，４は、このような構成の外側ハウジン
グ５内に前述した如く構成されており、左軸８ｌにスプ
ライン結合されたベーンポンプ３のロータ31は、左側の
後輪に連動してその軸心回りに回転し、また、右軸8rに
スプライン結合されたベーンポンプ４のロータ41は、右
側の後輪に連動してその軸心回りに回転する。一方、ベ
ーンポンプ３のカムリング31は、固定ボルト32,32…に
より大径側板50と一体化されており、またベーンポンプ
４のカムリング41は、前記固定ボルト32,32…と固定ボ
ルト42,42とにより、中間プレート10を介して大径側板5
0と一体化されているから、両カムリング31,41は、小傘
歯車2a及び大傘歯車2bを介して大径側板50に伝達される
伝動軸２の回転に伴って、その軸心回りに共に回転す
る。従って、ベーンポンプ３のロータ30とカムリング31
との間には、左側の後輪の回転速度と、伝動軸２の回転
速度が小傘歯車2aと大傘歯車2bとにより減速された後に
おける回転速度との間の回転速度差に相当する相対回転
が生じ、ベーンポンプ３は、この相対回転に応じた油圧
を発生して、左軸８ｌを介して左側の後輪に駆動力を伝
達し、同様にベーンポンプ４は、右側の後輪の回転速度
と、前記減速後における伝動軸２の回転速度との間の回
転速度差に相当する相対回転に応じた油圧により、右軸
8rを介して右側の後輪に駆動力を伝達する。The vane pumps 3 and 4 are configured as described above in the outer housing 5 having such a configuration, and the rotor 31 of the vane pump 3 spline-coupled to the left shaft 8l is interlocked with the left rear wheel and its axial center is The rotor 41 of the vane pump 4 that rotates around and is spline-coupled to the right shaft 8r rotates around its axis in conjunction with the right rear wheel. On the other hand, the cam ring 31 of the vane pump 3 is integrated with the large-diameter side plate 50 by the fixing bolts 32, 32 ... And the cam ring 41 of the vane pump 4 is fixed by the fixing bolts 32, 32 ... And the fixing bolts 42, 42. , Large diameter side plate 5 through intermediate plate 10
Since the cam rings 31 and 41 are integrated with 0, the cam rings 31 and 41 are rotated around the shaft center of the transmission shaft 2 transmitted to the large diameter side plate 50 through the small bevel gear 2a and the large bevel gear 2b. Rotate together. Therefore, the rotor 30 and the cam ring 31 of the vane pump 3 are
Between the rotation speed of the left rear wheel and the rotation speed of the transmission shaft 2 after the rotation speed of the transmission shaft 2 is reduced by the small bevel gear 2a and the large bevel gear 2b. Relative rotation occurs, the vane pump 3 generates hydraulic pressure according to this relative rotation, and transmits the driving force to the left rear wheel via the left shaft 8l. Similarly, the vane pump 4 rotates the right rear wheel. The right shaft is driven by the hydraulic pressure corresponding to the relative rotation corresponding to the rotational speed difference between the speed and the rotational speed of the transmission shaft 2 after the deceleration.
The driving force is transmitted to the right rear wheel via 8r.

第２図は、第１図のII−II線による拡大断面図であり、
次に本図に基づいてベーンポンプ４の構造について詳述
する。FIG. 2 is an enlarged sectional view taken along line II-II of FIG.
Next, the structure of the vane pump 4 will be described in detail with reference to this drawing.

ベーンポンプ４のロータ40には、半径方向に所定の深さ
寸法を有し、軸長方向の全長に亘る複数本（本実施例に
おいては10本）の細幅の収納溝40b,40b…が、周方向に
等配をなして形成してあり、収納溝40b,40b…には、こ
れらの幅と略等しい肉厚と、ロータ40の軸長寸法と略等
しい長手寸法を有する矩形平板状のベーン40a,40a…
が、ロータ40の半径方向への摺動自在に嵌挿されてい
る。第１図に示す如く、各ベーン40aと収納溝40bの底部
との間には、各一対のコイルばね40c,40cが介装してあ
り、各ベーン40aは、このコイルばね40c,40cと、後述す
る如く収納溝40b,40b…の底部に導入される油圧とによ
り、半径方向外向きに付勢されている。The rotor 40 of the vane pump 4 has a plurality of (10 in this embodiment) narrow-width storage grooves 40b, 40b ... Having a predetermined depth dimension in the radial direction and extending over the entire length in the axial direction. The accommodating grooves 40b, 40b ... Are formed in a circumferentially equidistant manner, and the storage grooves 40b, 40b ... Have a rectangular flat plate-shaped vane having a thickness substantially equal to the width thereof and a longitudinal dimension substantially equal to the axial length dimension of the rotor 40. 40a, 40a ...
Is fitted so as to be slidable in the radial direction of the rotor 40. As shown in FIG. 1, a pair of coil springs 40c, 40c is interposed between each vane 40a and the bottom of the storage groove 40b, and each vane 40a has a coil spring 40c, 40c. As will be described later, it is urged outward in the radial direction by the hydraulic pressure introduced to the bottom of the storage grooves 40b, 40b.

またカムリング41は、ロータ40の外径よりもやや大径の
円の周方向に等配をなす３個所に三日月形の凹部を設
け、図示の如き軸断面形状を有する空洞部41aをその軸
心位置に形成してなる偏肉筒状の部材であり、この空洞
部41aの内周面と、これの内部に同軸的に内挿されるロ
ータ40の外周面との間に、これらと、小径側板51及び中
間プレート10の側面とにより囲繞され、図示の如き三日
月形の断面形状を有する３つのポンプ室43,43,43が形成
されるようになっている。これらのポンプ室43,43,43に
は、三日月形の両端部に開口する各一対の吸込吐出口43
a,43aが、中間プレート10側に形成してあり、これらの
吸込吐出口43a,43a…は、中間プレート10にこれの外周
面から半径方向内向きに延設された各別の油路44,44…
により、前記油タンクＴに連通させてある。この油路44
は、第１図に示す如く、中間プレート10の外周から吸込
吐出口43aの形成位置までの長さよりも十分に大きい深
さを有しており、各吸込吐出口43aは、中間プレート10
の軸長方向に形成された短寸の油路45により、各別の油
路44の中途部に連通させてある。また油路44は、長手方
向を中間プレート10の軸長方向とし、これの右側面に開
口部を有して形成された短寸の油路46により、収納溝40
b,40b…の底部を相互に連通する態様にてロータ40の側
面に形成された環状溝47に、その底部近傍を連通させて
ある。Further, the cam ring 41 is provided with crescent-shaped recesses at three locations which are equally distributed in the circumferential direction of a circle having a diameter slightly larger than the outer diameter of the rotor 40, and a hollow portion 41a having a shaft cross-sectional shape as shown in the drawing is provided at the center of the shaft. And a small-diameter side plate between the inner peripheral surface of the hollow portion 41a and the outer peripheral surface of the rotor 40 that is coaxially inserted therein. Three pump chambers 43, 43, 43, which are surrounded by 51 and the side surface of the intermediate plate 10 and have a crescent-shaped cross-sectional shape as shown in the drawing, are formed. These pump chambers 43, 43, 43 have a pair of suction and discharge ports 43 that open at both ends of the crescent.
a, 43a are formed on the side of the intermediate plate 10, and these suction and discharge ports 43a, 43a ... Are provided on the intermediate plate 10 in the respective oil passages 44 extending radially inward from the outer peripheral surface thereof. , 44 ...
To communicate with the oil tank T. This oil passage 44
1 has a depth sufficiently larger than the length from the outer periphery of the intermediate plate 10 to the formation position of the suction / discharge port 43a, and each suction / discharge port 43a has a depth larger than that of the intermediate plate 10.
The short oil passages 45 formed in the axial direction of the are connected to the midway portions of the respective oil passages 44. Further, the oil passage 44 has a longitudinal direction that is the axial length direction of the intermediate plate 10, and a short oil passage 46 formed with an opening on the right side surface thereof allows the storage groove 40 to be formed.
The bottoms of the b, 40b, ... Are connected to the annular groove 47 formed on the side surface of the rotor 40 so that the bottoms of the b, 40b ...

これらの油路44の夫々には、吸込チェック弁48が、中間
プレート10の外周と油路45への分岐部との間に配設して
あり、また、吐出チェック弁49が、油路45への分岐部と
油路46への分岐部との間に配設してある。吸込チェック
弁48及び吐出チェック弁49は、いずれも、円筒状のケー
シングの軸心位置に形成された縮流部にボールを密着さ
せて流れを遮断するチェック弁であり、油路44内を半径
方向外向きに流れる油を遮断するように向きを設定され
て、油路44に内嵌された状態で固定してあり、油路44の
軸心上において同軸をなしている。In each of these oil passages 44, a suction check valve 48 is arranged between the outer periphery of the intermediate plate 10 and a branch portion to the oil passage 45, and a discharge check valve 49 is provided in the oil passage 45. It is arranged between a branch part to the oil passage and a branch part to the oil passage 46. Each of the suction check valve 48 and the discharge check valve 49 is a check valve that shuts off the flow by closely contacting the ball with the contraction portion formed at the axial center position of the cylindrical casing, and the inside of the oil passage 44 is radiused. The direction is set so as to block the oil flowing outward in the direction, and the oil passage 44 is fixed while being fitted in the oil passage 44, and is coaxial with the axial center of the oil passage 44.

このように構成されたベーンポンプ４においては、ロー
タ40の各ベーン40a,40a…は、各別のコイルばね41c,41c
…による外向きの付勢力により、先端部をカムリング41
の空洞部41aの内周面に押し付けられており、伝動軸２
と右軸8rとの間に回転速度差が生じ、ロータ40がカムリ
ング41に対して相対的に回転した場合、各ポンプ室43内
の油は、相隣するベーン40a,40a間に封止された状態
で、ロータ40の回転に伴って回転せしめられる結果、こ
の回転方向上流側に位置する吸込吐出口43aにおける油
圧は下降し、逆に回転方向下流側に位置する吸込吐出口
43aにおける油圧は上昇する。従って、前者に油路45を
介して連通する油路44内においては、油路45との分岐部
における圧力、即ち、吸込チェック弁48と吐出チェック
弁49との間の圧力が下降し、吸込チェック弁48及び吐出
チェック弁49の動作説明図である第３図に示す如く、吸
込チェック弁48が、これの両側の圧力差により開放状態
となる一方、吐出チェック弁49が同じく閉鎖状態とな
り、逆に、後者に油路45を介して連通する油路44内にお
いては、吸込チェック弁48と吐出チェック弁49との間の
圧力が上昇し、第３図と同様の第４図に示す如く、吐出
チェック弁49が開放状態となる一方、吸込チェック弁48
が閉鎖状態となる。In the vane pump 4 configured as described above, the vanes 40a, 40a, ... Of the rotor 40 have different coil springs 41c, 41c.
The cam ring 41 is attached to the tip by the outward biasing force of
Is pressed against the inner peripheral surface of the hollow portion 41a of the
When a difference in rotational speed occurs between the right shaft 8r and the right shaft 8r and the rotor 40 rotates relative to the cam ring 41, the oil in each pump chamber 43 is sealed between the adjacent vanes 40a, 40a. As a result of being rotated with the rotation of the rotor 40 in this state, the hydraulic pressure at the suction / discharge port 43a located on the upstream side in this rotation direction decreases, and conversely, the suction / discharge port located on the downstream side in the rotation direction.
The hydraulic pressure at 43a rises. Therefore, in the oil passage 44 that communicates with the former via the oil passage 45, the pressure at the branch portion with the oil passage 45, that is, the pressure between the suction check valve 48 and the discharge check valve 49 decreases, and As shown in FIG. 3 which is an explanatory view of the operation of the check valve 48 and the discharge check valve 49, the suction check valve 48 is opened due to the pressure difference between the two sides thereof, while the discharge check valve 49 is also closed. On the contrary, in the oil passage 44 communicating with the latter via the oil passage 45, the pressure between the suction check valve 48 and the discharge check valve 49 rises, and as shown in FIG. 4 similar to FIG. , The discharge check valve 49 is open, while the suction check valve 48
Is closed.

吸込チェック弁48及び吐出チェック弁49が第３図に示す
開閉状態を示している油路44においては、図中に矢符に
て示す如く、油タンクＴ内に封入された油が、吸込チェ
ック弁48を半径方向内向きに通過し、更に油路45及び吸
込吐出口43aを介してポンプ室43内に導入され、また、
前記両チェック弁48,49が第４図に示す開閉状態を示し
ている油路44においては、ポンプ室43内において昇圧さ
れ吸込吐出口43a及び油路45を介して導出される圧油
が、吐出チェック弁49を半径方向内向きに通過し、更に
油路46及び環状溝47を介して、ロータ40の各収納溝40b,
40b…の底部に導入される。即ち、前者の油路44に連通
する吸込吐出口43aが吸込口として機能し、後者の油路4
4に連通する吸込吐出口43aが吐出口として機能する。吐
出チェック弁49を通過して、収納溝40b,40b…の底部に
導入される圧油は、これらに内挿されたベーン40a,40a
…に半径方向外向きの押圧力を加えると共に、ロータ40
の側面と、中間プレート10又は小径側板51の側面との間
のわずかな間隙を介して、中間プレート10及び小径側板
51の中抜き部と、右軸8rとの間に形成される空間内に洩
出し、この洩出の間に減圧されて、中間プレート10の幅
方向略中央部に、これを半径方向に貫通する態様にて形
成された還流油路11を通過して、前記油タンクＴに還流
する。In the oil passage 44 in which the suction check valve 48 and the discharge check valve 49 are in the open / closed state shown in FIG. 3, the oil sealed in the oil tank T is the suction check as shown by the arrow in the figure. It passes through the valve 48 inward in the radial direction, and is further introduced into the pump chamber 43 through the oil passage 45 and the suction / discharge port 43a.
In the oil passage 44 in which both the check valves 48, 49 are in the open / closed state shown in FIG. 4, the pressure oil that is boosted in the pump chamber 43 and discharged through the suction / discharge port 43a and the oil passage 45 is Each storage groove 40b of the rotor 40 passing through the discharge check valve 49 inward in the radial direction and further via the oil passage 46 and the annular groove 47.
Introduced at the bottom of 40b ... That is, the suction discharge port 43a communicating with the former oil passage 44 functions as a suction port, and the latter oil passage 4
The suction discharge port 43a communicating with 4 functions as a discharge port. The pressure oil that has passed through the discharge check valve 49 and is introduced into the bottom of the storage grooves 40b, 40b ... Is the vanes 40a, 40a inserted into these.
A radial outward pressure is applied to the rotor and the rotor 40
Through the slight gap between the side surface of the intermediate plate 10 and the side surface of the intermediate plate 10 or the small diameter side plate 51.
Leakage into the space formed between the hollowed-out portion of the 51 and the right shaft 8r, the pressure is reduced during this leakage, and the intermediate plate 10 is radially penetrated through the approximately central portion in the width direction. Then, the oil is returned to the oil tank T after passing through the oil return passage 11 formed in this manner.

各吸込吐出口43a,43a…が、ロータ40とカムリング41と
の間の相対回転の方向に応じて、前述した如く、吸込口
又は吐出口として機能する結果、ベーンポンプ４の各ポ
ンプ室43,43…の内部には、ロータ40のカムリング41に
対する相対回転速度、即ち右側の後輪に連なる右軸8rの
回転速度と、減速後の伝動軸２の回転速度との間の差に
対応する油圧が発生し、この油圧に応じて、伝動軸２を
介して伝達される駆動力の一部が、右軸8rを介して右側
の後輪に伝達される。As described above, the suction and discharge ports 43a, 43a function as the suction and discharge ports according to the direction of relative rotation between the rotor 40 and the cam ring 41. As a result, the pump chambers 43, 43 of the vane pump 4 are discharged. The hydraulic pressure corresponding to the relative rotation speed of the rotor 40 with respect to the cam ring 41, that is, the difference between the rotation speed of the right shaft 8r connected to the rear wheel on the right side and the rotation speed of the transmission shaft 2 after deceleration, is present inside. A part of the driving force generated and transmitted via the transmission shaft 2 is transmitted to the right rear wheel via the right shaft 8r according to the hydraulic pressure.

左側のベーンポンプ３のロータ30及びカムリング31は、
夫々ロータ40及びカムリング41と同一の構成であり、ま
た、左側のベーンポンプ３は、その吸込吐出口33a,33a
…が、ロータ30の右側（中間プレート10側）にてカムリ
ング31内に開口する態様にて形成されていること以外
は、吸込吐出口33a,33a…の夫々が中間プレート10の外
周面からこれの半径方向に延設された油路34に連通され
ていること、吸込チェック弁38と吐出チェック弁39と
が、油路34内の軸心線上において互いに同軸をなした態
様にて装着されていること等、他の部分の構成もベーン
ポンプ４と全く同様であり、ベーンポンプ４と同様の動
作をなすものである。そして、ベーンポンプ３内に発生
する油圧により、伝動軸２を介して伝達される駆動力の
一部が、左軸８ｌを介して左側の後輪に伝達される。The rotor 30 and the cam ring 31 of the left vane pump 3 are
The vane pump 3 on the left side has the same structure as the rotor 40 and the cam ring 41, respectively.
Are formed so as to open in the cam ring 31 on the right side of the rotor 30 (on the side of the intermediate plate 10), the suction and discharge ports 33 a, 33 a, ... Are respectively formed from the outer peripheral surface of the intermediate plate 10. Is communicated with the oil passage 34 extending in the radial direction, and the suction check valve 38 and the discharge check valve 39 are mounted in a manner coaxial with each other on the axis of the oil passage 34. The configuration of the other parts such as the presence of the vane pump 4 is exactly the same as that of the vane pump 4, and the same operation as that of the vane pump 4 is performed. Then, due to the hydraulic pressure generated in the vane pump 3, a part of the driving force transmitted via the transmission shaft 2 is transmitted to the left rear wheel via the left shaft 8l.

このようにベーンポンプ３及び同４においては、夫々の
ロータ30及びロータ40の軸長方向一側に、夫々の吸込吐
出口33a,33a…及び吸込吐出口43a,43a…を形成すると共
に、これらに各別に連なる油路34,34…及び油路44,44…
を、中間プレート10の半径方向、即ちロータ30及びロー
タ40の半径方向に夫々延設し、各油路34及び油路44内
に、吸込チェック弁38と吐出チェック弁39、及び吸込チ
ェック弁48と吐出チェック弁49とが夫々同軸的に並設さ
れているから、油路34,44、並びに吸込チェック弁38,48
及び吐出チェック弁39,49の配設に必要な軸長方向寸法
が、従来のベーンポンプに比較して大幅に短縮できる。As described above, in the vane pumps 3 and 4, the suction discharge ports 33a, 33a ... And the suction discharge ports 43a, 43a ... Are formed on one side in the axial direction of the rotor 30 and the rotor 40, respectively. Oil passages 34, 34 ... and oil passages 44, 44 ...
Are extended in the radial direction of the intermediate plate 10, that is, in the radial direction of the rotor 30 and the rotor 40, respectively, and the suction check valve 38, the discharge check valve 39, and the suction check valve 48 are provided in the oil passages 34 and 44, respectively. Since the discharge check valve 49 and the discharge check valve 49 are coaxially arranged side by side, respectively, the oil passages 34, 44 and the suction check valves 38, 48
Also, the dimension in the axial direction required for disposing the discharge check valves 39, 49 can be significantly reduced as compared with the conventional vane pump.

なお本実施例においては、油圧ポンプとしてベーンポン
プ３，４を用いているが、トロコイドポンプ等、他の形
式の油圧ポンプを用いて構成された４輪駆動用駆動連結
装置においても本考案は適用可能であることは言うまで
もない。Although the vane pumps 3 and 4 are used as hydraulic pumps in the present embodiment, the present invention is also applicable to a four-wheel drive drive coupling device that is configured using another type of hydraulic pump such as a trochoid pump. Needless to say.

また本実施例においては、２個の油圧ポンプを並設して
なり、差動歯車装置に換えて配設される４輪駆動用駆動
連結装置について説明したが、１個の油圧ポンプを用い
てなり、前．後輪間の伝動系の中途、例えばプロペラシ
ャフトの中途に配設される４輪駆動用駆動連結装置にお
いても本考案は適用可能であり、同様に軸長寸法の短縮
化が実現可能である。Further, in the present embodiment, the description has been given of the four-wheel drive drive coupling device in which two hydraulic pumps are arranged side by side and arranged in place of the differential gear device, but one hydraulic pump is used. And before. The present invention can be applied to a drive coupling device for four-wheel drive, which is disposed in the middle of the transmission system between the rear wheels, for example, in the middle of the propeller shaft, and similarly, the axial length can be shortened.

〔効果〕〔effect〕

以上詳述した如く本案装置においては、吸込チェック弁
と吐出チェック弁とが装着され、吸込口及び吐出口とし
て機能する吸込吐出口を、ロータの軸長方向一側に配
し、しかも前記両チェック弁を、長手方向をロータの半
径方向として形成された油路内に同軸的に配設してある
から、両チェック弁の配設スペース及び前記油路の形成
スペースの削減が可能となり、軸長方向寸法が短縮化さ
れ、大幅な小型化が実現できる等、本考案は優れた効果
を奏する。As described in detail above, in the device of the present invention, the suction check valve and the discharge check valve are mounted, and the suction and discharge ports functioning as the suction port and the discharge port are arranged on one side in the axial direction of the rotor, and both of the above check Since the valves are coaxially arranged in the oil passage formed with the longitudinal direction being the radial direction of the rotor, the space for disposing both check valves and the space for forming the oil passage can be reduced, and the axial length can be reduced. The present invention has excellent effects such as a reduction in the directional dimension and a significant reduction in size.

【図面の簡単な説明】[Brief description of drawings]

図面は本考案の一実施例を示すものであり、第１図は本
案装置の平面断面図、第２図は第１図のII−II線による
拡大横断面図、第３図及び第４図は吸込チェック弁と吐
出チェック弁との開閉状態を示す説明図である。 ２……伝動軸、３，４……ベーンポンプ、30,40……ロ
ータ、31,41……カムリング、34,44……油路、38,48…
…吸込チェック弁、39,49……吐出チェック弁The drawings show one embodiment of the present invention. FIG. 1 is a plan sectional view of the device of the present invention, FIG. 2 is an enlarged transverse sectional view taken along the line II-II of FIG. 1, and FIGS. FIG. 4 is an explanatory diagram showing an open / closed state of a suction check valve and a discharge check valve. 2 ... transmission shaft, 3, 4 ... vane pump, 30, 40 ... rotor, 31, 41 ... cam ring, 34, 44 ... oil passage, 38, 48 ...
… Suction check valve, 39,49 …… Discharge check valve

Claims (1)

【実用新案登録請求の範囲】[Scope of utility model registration request] 【請求項１】動輪と連動回転するロータと、該ロータを
同軸的に内挿し、前記動輪への伝動軸と連動回転するハ
ウジングとを備え、両者間の回転速度差に応じた油圧を
発生する油圧ポンプにより、動輪と伝動軸とを連結する
４輪駆動用駆動連結装置において、 前記ロータの軸長方向一側に開口して配設された吸込吐
出口と、 長手方向を前記ロータの半径方向と略一致させて前記ハ
ウジングに形成され、前記吸込吐出口への流入油を通流
させる吸込チェック弁、及び吸込吐出口からの流出油を
通流させる吐出チェック弁が、内部に同軸的に並設して
ある油路と を具備することを特徴とする４輪駆動用駆動連結装置。1. A rotor that rotates in conjunction with a moving wheel, and a housing that coaxially inserts the rotor and rotates in conjunction with a transmission shaft to the moving wheel, generate a hydraulic pressure according to a difference in rotational speed between the two. In a four-wheel drive drive connecting device for connecting a drive wheel and a transmission shaft by a hydraulic pump, a suction / discharge port opened to one side in the axial direction of the rotor and a longitudinal direction of the rotor in the radial direction of the rotor. A suction check valve, which is formed in the housing so as to substantially match with the above, allows the inflow oil to flow into the suction and discharge ports, and a discharge check valve through which the outflow oil from the suction and discharge ports flow, are coaxially arranged inside. A drive connection device for four-wheel drive, comprising: an oil passage provided.