JP2013170616A

JP2013170616A - Liquid supply device

Info

Publication number: JP2013170616A
Application number: JP2012034258A
Authority: JP
Inventors: Satoru Kasuya; 悟糟谷; Masashi Kito; 昌士鬼頭; Osamu Murai; 修村井; Shigeru Sugisaka; 繁杉坂
Original assignee: Aisin AW Co Ltd
Current assignee: Aisin AW Co Ltd
Priority date: 2012-02-20
Filing date: 2012-02-20
Publication date: 2013-09-02

Abstract

PROBLEM TO BE SOLVED: To materialize a liquid supply device capable of improving energy efficiency by reducing pressure loss, while restraining the enlargement of the device.SOLUTION: An object check valve being at least one of a first check valve 21 and a second check valve, has a rotary valve element 30. The rotary valve element 30 is a rotary member having a rotational axis A in a direction intersecting a flow passage direction of an object supply flow passage being the side of any of a first supply flow passage L1 and a second supply flow passage arranged with the object check valve, and is rotatably constituted between a blocking position in which the rotary valve element 30 assumes a state to overlap with the whole of a flow passage cross section of the object supply flow passage when viewed in the flow passage direction of the object supply flow passage, and an opening position in which the whole of the rotary valve element 30 assumes a state to be positioned outside the flow passage cross section of the object supply flow passage when viewed in the flow passage direction of the object supply flow passage.

Description

本発明は、第一液圧ポンプと、第二液圧ポンプと、第一液圧ポンプにより発生した液圧が供給される第一供給流路と、第二液圧ポンプにより発生した液圧が供給される第二供給流路と、第一供給流路と第二供給流路とが合流して形成される第三供給流路と、第一供給流路に設けられた第一逆止弁と、第二供給流路に設けられた第二逆止弁と、を備えた液体供給装置に関する。 The present invention relates to a first hydraulic pump, a second hydraulic pump, a first supply passage to which a hydraulic pressure generated by the first hydraulic pump is supplied, and a hydraulic pressure generated by the second hydraulic pump. A second supply channel to be supplied, a third supply channel formed by joining the first supply channel and the second supply channel, and a first check valve provided in the first supply channel And a second check valve provided in the second supply flow path.

上記のような液体供給装置の従来技術として、例えば特開２０１１−３８６０１号公報（特許文献１）に記載された技術がある。特許文献１には、供給対象の液体が油とされ、油圧を生成する油圧ポンプとして、駆動力源の互いに異なる２つの油圧ポンプが備えられた油供給装置が記載されている。そして、これら２つの油圧ポンプのそれぞれは、逆流防止弁（逆止弁）を介して共通の油路に接続されており、当該共通の油路を介して、各ポンプにより発生した油圧が、油圧の供給対象箇所（特許文献１の例では、自動変速機の油圧作動機構）に供給される。 As a conventional technique of the liquid supply apparatus as described above, for example, there is a technique described in Japanese Patent Laid-Open No. 2011-38601 (Patent Document 1). Patent Document 1 describes an oil supply apparatus provided with two hydraulic pumps having different driving force sources as a hydraulic pump that generates oil pressure when a liquid to be supplied is oil. Each of these two hydraulic pumps is connected to a common oil passage via a check valve (a check valve), and the hydraulic pressure generated by each pump passes through the common oil passage. To be supplied (in the example of Patent Document 1, the hydraulic operation mechanism of the automatic transmission).

ところで、液体供給装置のエネルギ効率の向上の観点から、通流が許容される方向に液体が逆止弁を通過する際に、当該逆止弁において発生する圧力損失が小さいことが望ましい。しかしながら、逆止弁において発生する圧力損失について、特許文献１では特段の認識がなされていなかった。 By the way, from the viewpoint of improving the energy efficiency of the liquid supply device, it is desirable that the pressure loss generated in the check valve is small when the liquid passes through the check valve in the direction in which the flow is allowed. However, the pressure loss generated in the check valve is not particularly recognized in Patent Document 1.

特開２０１１−３８６０１号公報JP 2011-38601 A

そこで、装置の大型化を抑制しつつ、圧力損失を低減してエネルギ効率の向上を図ることが可能な液体供給装置の実現が望まれる。 Therefore, it is desired to realize a liquid supply apparatus capable of reducing the pressure loss and improving the energy efficiency while suppressing the enlargement of the apparatus.

本発明に係る、第一液圧ポンプと、第二液圧ポンプと、前記第一液圧ポンプにより発生した液圧が供給される第一供給流路と、前記第二液圧ポンプにより発生した液圧が供給される第二供給流路と、前記第一供給流路と前記第二供給流路とが合流して形成される第三供給流路と、前記第一供給流路に設けられた第一逆止弁と、前記第二供給流路に設けられた第二逆止弁と、を備えた液体供給装置の特徴構成は、前記第一逆止弁及び前記第二逆止弁の少なくとも一方である対象逆止弁が回転弁体を備え、前記回転弁体が、前記第一供給流路と前記第二供給流路とのいずれか前記対象逆止弁が設けられた側である対象供給流路の流路方向に対して交差する方向を回転軸とする回転部材であって、前記対象供給流路の流路方向に見て前記回転弁体が前記対象供給流路の流路断面の全体と重複する状態となる閉塞位置と、前記対象供給流路の流路方向に見て前記回転弁体の全体が前記対象供給流路の流路断面の外に位置する状態となる開放位置との間で、回転可能に構成されている点にある。 According to the present invention, the first hydraulic pump, the second hydraulic pump, the first supply passage to which the hydraulic pressure generated by the first hydraulic pump is supplied, and generated by the second hydraulic pump A second supply channel to which hydraulic pressure is supplied, a third supply channel formed by joining the first supply channel and the second supply channel, and the first supply channel. The liquid supply device comprising the first check valve and the second check valve provided in the second supply flow path includes the first check valve and the second check valve. At least one of the target check valves includes a rotary valve body, and the rotary valve body is one of the first supply flow path and the second supply flow path on which the target check valve is provided. A rotating member having a rotation axis in a direction intersecting the flow path direction of the target supply flow path, and the rotary valve body as viewed in the flow path direction of the target supply flow path The closed position where the entire cross section of the target supply flow path overlaps, and the entire rotary valve body as viewed in the flow direction of the target supply flow path is the cross section of the target supply flow path. It is in the point comprised so that rotation is possible between the open position used as the state located outside.

上記の特徴構成によれば、回転弁体が開放位置に位置する状態（開放状態）で、対象供給流路の流路方向に見て回転弁体の全体が当該対象供給流路の流路断面の外に位置するため、開放状態において対象逆止弁の内部に形成される流路（弁内流路）の流路断面積を、対象供給流路の流路断面積と同じ若しくはそれより大きくすることができる。よって、開放状態において形成される弁内流路の流路断面積が、対象供給流路の流路断面積より小さい場合に比べて、対象逆止弁において発生する圧力損失を低減することができる。
また、上記の特徴構成によれば、開放状態において形成される弁内流路を、対象供給流路に対して当該対象供給流路の流路方向に沿って延長した位置に配置することができる。すなわち、開放状態において形成される弁内流路を、対象供給流路の流路方向に対して平行に延びる部分のみにより形成することができる。このことによっても、対象逆止弁において発生する圧力損失を低減することができ、さらに、対象逆止弁が占有する空間の、対象供給流路の流路方向に対して直交する方向の長さを短縮することが容易となる。
以上のように、上記の特徴構成によれば、装置の大型化を抑制しつつ、圧力損失を低減してエネルギ効率の向上を図ることが可能となる。 According to the above characteristic configuration, in a state where the rotary valve body is located at the open position (open state), the entire rotary valve body as viewed in the flow path direction of the target supply flow path is a cross section of the flow path of the target supply flow path. Therefore, the cross-sectional area of the flow path (intra-valve flow path) formed inside the target check valve in the open state is equal to or larger than the cross-sectional area of the target supply flow path. can do. Therefore, the pressure loss generated in the target check valve can be reduced compared to the case where the flow path cross-sectional area of the in-valve flow path formed in the open state is smaller than the flow path cross-sectional area of the target supply flow path. .
Moreover, according to said characteristic structure, the in-valve flow path formed in an open state can be arrange | positioned in the position extended along the flow path direction of the said target supply flow path with respect to the target supply flow path. . That is, the in-valve channel formed in the open state can be formed only by a portion extending in parallel to the channel direction of the target supply channel. This also reduces the pressure loss generated in the target check valve, and further, the length of the space occupied by the target check valve in the direction orthogonal to the flow direction of the target supply flow path. It becomes easy to shorten.
As described above, according to the above characteristic configuration, it is possible to improve the energy efficiency by reducing the pressure loss while suppressing the enlargement of the apparatus.

ここで、前記回転弁体は、当該回転弁体が前記開放位置側から前記閉塞位置側に回転する際の回転方向である閉弁方向を向く受圧面を備え、前記受圧面は、前記回転弁体が前記閉塞位置に位置する状態で、前記対象供給流路の流路方向上流側を向くとともに前記対象供給流路の流路方向に見て当該対象供給流路の流路断面と重複する位置に配置されるように、前記回転弁体に設けられ、前記対象逆止弁は、前記回転弁体を前記閉弁方向に付勢する付勢部材を備える構成とすると好適である。 Here, the rotary valve body includes a pressure receiving surface facing a valve closing direction which is a rotation direction when the rotary valve body rotates from the open position side to the closed position side, and the pressure receiving surface is the rotary valve In a state where the body is located at the closed position, the position faces the upstream side in the flow direction of the target supply flow path and overlaps with the cross section of the target supply flow path when viewed in the flow direction of the target supply flow path Preferably, the target check valve is provided with a biasing member that biases the rotary valve body in the valve closing direction.

この構成によれば、回転弁体に対して流路方向上流側から所定圧以上の液圧が作用している状態でのみ、回転弁体が、閉塞位置に対して開放位置側に回転するように構成することができ、逆止弁としての機能を適切に実現することができる。
また、回転弁体に対して流路方向上流側から作用する液圧が低下した場合には、付勢部材による付勢力により、回転弁体が開放位置から閉塞位置側に向かって回転する。よって、対象逆止弁の応答性（特に、液体の流通を許容する状態から規制する状態への切替時の応答性）を確保することが容易となる。 According to this configuration, the rotary valve body rotates to the open position side with respect to the closed position only in a state where a hydraulic pressure higher than a predetermined pressure is applied to the rotary valve body from the upstream side in the flow path direction. The function as a check valve can be appropriately realized.
Further, when the hydraulic pressure acting on the rotary valve body from the upstream side in the flow path direction decreases, the rotary valve body rotates from the open position toward the closed position side by the biasing force of the biasing member. Therefore, it becomes easy to ensure the responsiveness of the target check valve (particularly, the responsiveness at the time of switching from the state in which liquid circulation is permitted to the state in which liquid is restricted).

上記のように、前記回転弁体が前記受圧面を備えるとともに前記対象逆止弁が前記付勢部材を備える構成において、前記回転弁体が前記開放位置に位置する状態で、前記対象供給流路の流路方向に見て、前記受圧面が前記対象供給流路を形成する壁面と重なるように形成されている構成とすると好適である。 As described above, in the configuration in which the rotary valve body includes the pressure receiving surface and the target check valve includes the biasing member, the target supply flow path is in a state where the rotary valve body is located at the open position. It is preferable that the pressure receiving surface is formed so as to overlap with the wall surface forming the target supply flow channel when viewed in the flow direction.

この構成によれば、開放状態における対象供給流路と弁内流路との境界部での流体の挙動を、対象逆止弁がない場合に近づけることができ、対象逆止弁において発生する圧力損失を低減することが容易となる。 According to this configuration, the behavior of the fluid at the boundary between the target supply flow path and the valve flow path in the open state can be brought closer to the case where there is no target check valve, and the pressure generated in the target check valve It becomes easy to reduce the loss.

また、前記受圧面に対して作用する前記対象供給流路の流路方向上流側からの液圧が零の状態で、前記回転弁体の回転位置が前記閉塞位置となるように、前記付勢部材の付勢力が設定されている構成とすると好適である。 Further, the biasing is performed so that the rotational position of the rotary valve body becomes the closed position in a state where the hydraulic pressure from the upstream side in the flow direction of the target supply flow channel acting on the pressure receiving surface is zero. It is preferable that the urging force of the member is set.

この構成によれば、対象供給流路の流路方向上流側に配置された液圧ポンプが作動していない状態において、当該液圧ポンプに対して液体が逆流するのを実質的に防止することができる。 According to this configuration, in the state where the hydraulic pump arranged upstream in the flow direction of the target supply flow channel is not operating, it is substantially prevented that the liquid flows backward with respect to the hydraulic pump. Can do.

また、前記対象逆止弁は、前記回転弁体を収容する弁室を形成する弁室形成部を備え、前記回転弁体は、前記閉塞位置において前記対象供給流路の流路方向に見て当該対象供給流路の流路断面の全体と重複する部分を有する本体部と、前記本体部に対して前記回転軸の軸方向の両側に設けられた一対の被支持部と、を備え、前記一対の被支持部のそれぞれが、前記弁室形成部に対して回転可能に支持され、前記一対の被支持部の少なくとも一方である対象被支持部が、前記回転軸を基準として前記本体部の最も径方向外側に位置する部分よりも小径とされているとともに、当該対象被支持部の外周面に沿って前記付勢部材としてのコイルばねが配置されているとすると好適である。 The target check valve includes a valve chamber forming portion that forms a valve chamber that houses the rotary valve body, and the rotary valve body is viewed in the flow direction of the target supply flow path at the closed position. A main body having a portion overlapping with the entire flow path cross section of the target supply flow path, and a pair of supported portions provided on both sides in the axial direction of the rotation shaft with respect to the main body, Each of the pair of supported portions is rotatably supported with respect to the valve chamber forming portion, and the target supported portion that is at least one of the pair of supported portions is It is preferable that the coil spring as the urging member is arranged along the outer peripheral surface of the target supported portion while being smaller in diameter than the portion positioned on the outermost radial direction.

この構成によれば、回転弁体を回転軸方向の両側で支持することができるため、回転弁体の支持精度を高めて対象逆止弁を通過する流体量の安定化を図ることができる。また、付勢部材が配置される径方向領域を、対象被支持部が小径とされる分だけ本体部の外周面よりも径方向内側の領域とすることができるため、回転弁体の径方向における小型化を容易に図ることができる。 According to this configuration, since the rotary valve body can be supported on both sides in the rotation axis direction, it is possible to improve the support accuracy of the rotary valve body and stabilize the amount of fluid passing through the target check valve. Further, the radial region in which the urging member is disposed can be a region radially inward of the outer peripheral surface of the main body portion by the amount that the target supported portion has a small diameter. Can be easily reduced in size.

本発明の実施形態に係る油圧供給装置の概略構成を示す油圧回路図である。1 is a hydraulic circuit diagram showing a schematic configuration of a hydraulic pressure supply device according to an embodiment of the present invention. 本発明の実施形態に係る、第一逆止弁の開放状態での油圧供給装置の要部の断面図である。It is sectional drawing of the principal part of the hydraulic pressure supply apparatus in the open state of the 1st non-return valve based on embodiment of this invention. 本発明の実施形態に係る、第一逆止弁の閉塞状態での油圧供給装置の要部の断面図である。It is sectional drawing of the principal part of the hydraulic pressure supply apparatus in the obstruction | occlusion state of the 1st check valve based on embodiment of this invention. 本発明の実施形態に係る油圧供給装置の要部の断面図である。It is sectional drawing of the principal part of the hydraulic supply apparatus which concerns on embodiment of this invention. 図４におけるＶ−Ｖ断面図である。It is VV sectional drawing in FIG. 図２におけるＶＩ−ＶＩ断面図である。It is VI-VI sectional drawing in FIG. 図３におけるＶＩＩ−ＶＩＩ断面図である。It is VII-VII sectional drawing in FIG. 本発明のその他の実施形態に係る油圧供給装置の要部の断面図である。It is sectional drawing of the principal part of the hydraulic supply apparatus which concerns on other embodiment of this invention. 本発明のその他の実施形態に係る油圧供給装置の要部の断面図である。It is sectional drawing of the principal part of the hydraulic supply apparatus which concerns on other embodiment of this invention.

本発明の実施形態について、図面を参照して説明する。ここでは、本発明に係る液体供給装置を、車両に備えられる油供給装置（実質的に油圧供給装置と同義）に適用した場合を例として説明する。すなわち、本実施形態では、図１に示す油圧供給装置１が、本発明における「液体供給装置」に相当する。なお、以下の説明における各部材についての方向や位置等に関する用語は、製造上許容され得る誤差による差異を有する状態も含む概念として用いている。 Embodiments of the present invention will be described with reference to the drawings. Here, a case where the liquid supply device according to the present invention is applied to an oil supply device (substantially synonymous with a hydraulic pressure supply device) provided in a vehicle will be described as an example. That is, in the present embodiment, the hydraulic pressure supply device 1 shown in FIG. 1 corresponds to the “liquid supply device” in the present invention. In addition, the term regarding the direction, position, etc. about each member in the following description is used as a concept including the state which has a difference by the error which can be accept | permitted on manufacture.

１．油圧供給装置の全体構成
図１は、本実施形態に係る油圧供給装置１の概略構成を示す油圧回路図である。図１に示すように、油圧供給装置１は、第一油圧ポンプ１１と、第二油圧ポンプ１２とを備え、第一油圧ポンプ１１が発生した油圧や、第二油圧ポンプ１２が発生した油圧を、油圧制御装置１００に供給する。油圧制御装置１００は、図示は省略するが、油圧制御弁（例えば、リニアソレノイド弁、調圧弁等）と、当該油圧制御弁と連通する油路が設けられたバルブボディと、を備えて構成され、油圧制御装置１００による制御後の油圧が、車両の駆動装置の各部に供給される。本実施形態では、図２に示すように、車両の駆動装置には油圧で動作する摩擦係合装置ＣＬが備えられており、油圧制御装置１００は、当該摩擦係合装置ＣＬの作動油圧室ＣＬａに供給する油圧を制御する油圧制御弁を備えている。また、油圧制御装置１００は、第一油圧ポンプ１１や第二油圧ポンプ１２の吐出圧であるライン圧を制御する、ライン圧制御弁を備えている。本実施形態では、第一油圧ポンプ１１が本発明における「第一液圧ポンプ」に相当し、第二油圧ポンプ１２が本発明における「第二液圧ポンプ」に相当する。 1. FIG. 1 is a hydraulic circuit diagram showing a schematic configuration of a hydraulic pressure supply device 1 according to the present embodiment. As shown in FIG. 1, the hydraulic pressure supply device 1 includes a first hydraulic pump 11 and a second hydraulic pump 12, and the hydraulic pressure generated by the first hydraulic pump 11 and the hydraulic pressure generated by the second hydraulic pump 12. To the hydraulic control device 100. Although not shown, the hydraulic control device 100 includes a hydraulic control valve (for example, a linear solenoid valve, a pressure regulating valve, etc.) and a valve body provided with an oil passage communicating with the hydraulic control valve. The hydraulic pressure controlled by the hydraulic control device 100 is supplied to each part of the drive device of the vehicle. In the present embodiment, as shown in FIG. 2, the drive device of the vehicle is provided with a friction engagement device CL that operates hydraulically, and the hydraulic control device 100 operates the hydraulic pressure chamber CLa of the friction engagement device CL. A hydraulic control valve for controlling the hydraulic pressure supplied to the vehicle is provided. The hydraulic control device 100 also includes a line pressure control valve that controls the line pressure that is the discharge pressure of the first hydraulic pump 11 and the second hydraulic pump 12. In the present embodiment, the first hydraulic pump 11 corresponds to the “first hydraulic pump” in the present invention, and the second hydraulic pump 12 corresponds to the “second hydraulic pump” in the present invention.

図１に示すように、油圧供給装置１は、第一油圧ポンプ１１により発生した油圧が供給される第一供給流路Ｌ１と、第二油圧ポンプ１２により発生した油圧が供給される第二供給流路Ｌ２と、第一供給流路Ｌ１と第二供給流路Ｌ２とが合流して形成される第三供給流路Ｌ３と、を備えている。具体的には、第一供給流路Ｌ１は、第一油圧ポンプ１１の吐出側の油路とされ、第一油圧ポンプ１１とは反対側（すなわち下流側）の端部において合流部９３に接続されている。第二供給流路Ｌ２は、第二油圧ポンプ１２の吐出側の油路とされ、第二油圧ポンプ１２とは反対側（すなわち下流側）の端部において合流部９３に接続されている。そして、第一供給流路Ｌ１と第二供給流路Ｌ２とが合流部９３において合流することで、当該合流部９３の下流側に第三供給流路Ｌ３が形成されている。第三供給流路Ｌ３は、合流部９３とは反対側（すなわち下流側）の端部において、油圧制御装置１００に接続されている。なお、詳細な説明は省略するが、第三供給流路Ｌ３に、油圧制御装置１００に過剰な油圧が供給されることを抑制するためのリリーフ弁が設けられた構成とすることができる。 As shown in FIG. 1, the hydraulic pressure supply device 1 includes a first supply flow path L 1 to which the hydraulic pressure generated by the first hydraulic pump 11 is supplied and a second supply to which the hydraulic pressure generated by the second hydraulic pump 12 is supplied. A flow path L2, and a third supply flow path L3 formed by joining the first supply flow path L1 and the second supply flow path L2. Specifically, the first supply flow path L1 is an oil passage on the discharge side of the first hydraulic pump 11, and is connected to the junction 93 at the end opposite to the first hydraulic pump 11 (that is, the downstream side). Has been. The second supply flow path L 2 is an oil passage on the discharge side of the second hydraulic pump 12, and is connected to the junction 93 at the end opposite to the second hydraulic pump 12 (that is, the downstream side). And the 3rd supply flow path L3 is formed in the downstream of the said junction part 93 because the 1st supply flow path L1 and the 2nd supply flow path L2 merge in the junction part 93. FIG. The third supply flow path L 3 is connected to the hydraulic control device 100 at the end opposite to the merging portion 93 (that is, downstream). Although a detailed description is omitted, a configuration may be adopted in which a relief valve is provided in the third supply flow path L3 to prevent excessive hydraulic pressure from being supplied to the hydraulic control device 100.

上記のように、第一油圧ポンプ１１の吐出側油路である第一供給流路Ｌ１と、第二油圧ポンプ１２の吐出側油路である第二供給流路Ｌ２とは、油圧制御装置１００に接続された第三供給流路Ｌ３に対して互いに並列に接続されている。一方、第一油圧ポンプ１１及び第二油圧ポンプ１２のそれぞれの吸入側油路は、共通のストレーナ９１を介して油貯留部９２に接続されている。そして、第一油圧ポンプ１１及び第二油圧ポンプ１２のそれぞれは、油貯留部９２に貯留された油を吸引して油圧を発生させる。なお、ストレーナ９１は、第一油圧ポンプ１１や第二油圧ポンプ１２が油を吸入する際に、油に含まれる異物を除去するためのろ過器である。また、油を貯留するための油貯留部９２は、本実施形態ではオイルパンにより構成され、車両の駆動装置の各部に供給された油は、油貯留部９２に回収される。 As described above, the first supply flow path L1 that is the discharge-side oil path of the first hydraulic pump 11 and the second supply flow path L2 that is the discharge-side oil path of the second hydraulic pump 12 are the hydraulic control device 100. Are connected in parallel to the third supply flow path L3 connected to the. On the other hand, the respective suction side oil passages of the first hydraulic pump 11 and the second hydraulic pump 12 are connected to an oil reservoir 92 through a common strainer 91. Then, each of the first hydraulic pump 11 and the second hydraulic pump 12 sucks the oil stored in the oil storage unit 92 and generates hydraulic pressure. The strainer 91 is a filter for removing foreign substances contained in the oil when the first hydraulic pump 11 or the second hydraulic pump 12 sucks the oil. Moreover, the oil storage part 92 for storing oil is comprised by the oil pan in this embodiment, and the oil supplied to each part of the drive device of a vehicle is collect | recovered by the oil storage part 92. FIG.

そして、第一供給流路Ｌ１には合流部９３から第一油圧ポンプ１１側へ向かう方向（すなわち上流側に向かう方向）の油の流通を規制する第一逆止弁２１が設けられており、第二供給流路Ｌ２には、合流部９３から第二油圧ポンプ１２側へ向かう方向（すなわち上流側に向かう方向）の油の流通を規制する第二逆止弁２２が設けられている。すなわち、第一逆止弁２１及び第二逆止弁２２のそれぞれは、下流側に向かう方向の油のみの流通を許容する。これにより、第一油圧ポンプ１１の作動中における、第一油圧ポンプ１１が吐出した油の第二油圧ポンプ１２への流入が、第二逆止弁２２により規制（実質的に防止）される。また、第二油圧ポンプ１２の作動中における、第二油圧ポンプ１２が吐出した油の第一油圧ポンプ１１への流入が、第一逆止弁２１により規制（実質的に防止）される。 The first supply flow path L1 is provided with a first check valve 21 that regulates the flow of oil in the direction from the merging portion 93 toward the first hydraulic pump 11 (that is, the direction toward the upstream side), The second supply flow path L2 is provided with a second check valve 22 that restricts the flow of oil in the direction from the merging portion 93 toward the second hydraulic pump 12 (that is, the direction toward the upstream side). In other words, each of the first check valve 21 and the second check valve 22 allows the flow of only oil in the direction toward the downstream side. Accordingly, the second check valve 22 restricts (substantially prevents) the oil discharged from the first hydraulic pump 11 from flowing into the second hydraulic pump 12 during the operation of the first hydraulic pump 11. In addition, the first check valve 21 restricts (substantially prevents) the oil discharged from the second hydraulic pump 12 from flowing into the first hydraulic pump 11 during the operation of the second hydraulic pump 12.

本実施形態では、第一油圧ポンプ１１は、車両の車輪を駆動する駆動力源（例えば、内燃機関や回転電機等）により駆動される油圧ポンプ（機械式ポンプ）とされ、第二油圧ポンプ１２は、車輪の駆動力源とは別に油圧制御専用に設けられた回転電機により駆動される油圧ポンプ（電動ポンプ）とされている。これにより、車輪の駆動力源が回転していない状態でも、第二油圧ポンプ１２を駆動することで、油圧で動作する装置の作動、潤滑、或いは冷却のために必要となる油圧を発生することが可能となっている。なお、本実施形態では、第一油圧ポンプ１１の吐出容量は、第二油圧ポンプ１２の吐出容量より高く設定されている。 In the present embodiment, the first hydraulic pump 11 is a hydraulic pump (mechanical pump) that is driven by a driving force source (for example, an internal combustion engine, a rotating electrical machine, or the like) that drives the wheels of the vehicle. Is a hydraulic pump (electric pump) that is driven by a rotating electrical machine provided exclusively for hydraulic control separately from the driving force source of the wheels. Thereby, even when the driving force source of the wheels is not rotating, the second hydraulic pump 12 is driven to generate the hydraulic pressure necessary for the operation, lubrication, or cooling of the hydraulically operated device. Is possible. In the present embodiment, the discharge capacity of the first hydraulic pump 11 is set higher than the discharge capacity of the second hydraulic pump 12.

そして、本実施形態では、第一逆止弁２１が本発明における「対象逆止弁」とされ、第一逆止弁２１が設けられている第一供給流路Ｌ１が、本発明における「対象供給流路」とされる。次の「２．第一逆止弁の構成」の項で、この第一逆止弁２１の構成について詳細に説明する。 In the present embodiment, the first check valve 21 is the “target check valve” in the present invention, and the first supply flow path L1 provided with the first check valve 21 is the “target check valve” in the present invention. It is referred to as a “supply channel”. The configuration of the first check valve 21 will be described in detail in the next section “2. Configuration of the first check valve”.

２．第一逆止弁の構成
第一逆止弁２１の構成について、図２〜図７を参照して説明する。第一逆止弁２１は、図２、図６等に示すように、回転弁体３０と、当該回転弁体３０を収容する弁室２４を形成する弁室形成部２５と、を備えている。本実施形態では、図２、図５に示すように、弁室形成部２５は、車両の駆動装置のケース２とは独立の部材とされている。そして、回転弁体３０、コイルばね２３、及び固定部材９５が取り付けられた状態の弁室形成部２５（図４参照）を、図５に示すようにケース２に形成された凹部に挿入することで、第一逆止弁２１が第一供給流路Ｌ１に備えられる。本例では、弁室形成部２５は、締結ボルト９４（図４参照）によりケース２に対して固定されている。 2. Configuration of First Check Valve The configuration of the first check valve 21 will be described with reference to FIGS. As shown in FIGS. 2 and 6, the first check valve 21 includes a rotary valve body 30 and a valve chamber forming portion 25 that forms a valve chamber 24 that houses the rotary valve body 30. . In this embodiment, as shown in FIGS. 2 and 5, the valve chamber forming portion 25 is a member independent of the case 2 of the vehicle drive device. And the valve chamber formation part 25 (refer FIG. 4) in the state to which the rotary valve body 30, the coil spring 23, and the fixing member 95 were attached is inserted in the recessed part formed in case 2 as shown in FIG. Thus, the first check valve 21 is provided in the first supply flow path L1. In this example, the valve chamber forming portion 25 is fixed to the case 2 by fastening bolts 94 (see FIG. 4).

弁室形成部２５を挿入するためのケース２に形成された凹部により、第一供給流路Ｌ１は上流側部分と下流側部分とに流路方向Ｙ（図４参照）に分離されており、弁室形成部２５に形成された弁室２４、並びに当該弁室２４の流路方向Ｙの両側に形成された接続室２６を介して、上記の上流側部分と下流側部分とが連通可能に構成されている。なお、本実施形態では、図２に示すように、第一油圧ポンプ１１は、ポンプ室にインナロータとアウタロータとを有する内接型のギヤポンプとされており、インナロータに連結されたポンプ駆動軸（図示せず）が、車輪の駆動力源により駆動可能なように当該駆動力源に駆動連結されている。 The first supply flow path L1 is separated in the flow path direction Y (see FIG. 4) into an upstream portion and a downstream portion by a recess formed in the case 2 for inserting the valve chamber forming portion 25, The upstream portion and the downstream portion can communicate with each other through the valve chamber 24 formed in the valve chamber forming portion 25 and the connection chambers 26 formed on both sides of the valve chamber 24 in the flow direction Y. It is configured. In the present embodiment, as shown in FIG. 2, the first hydraulic pump 11 is an inscribed gear pump having an inner rotor and an outer rotor in the pump chamber, and a pump drive shaft (see FIG. 2) connected to the inner rotor. (Not shown) is drivingly connected to the driving force source so that it can be driven by the driving force source of the wheel.

回転弁体３０は、図４に示すように、第一供給流路Ｌ１の流路方向Ｙに対して交差する方向（本例では直交する方向）を回転軸Ａとする回転部材として構成されている。すなわち、回転軸Ａは、流路方向Ｙに対して交差する方向（本例では直交する方向）に延びる軸とされる。なお、回転軸Ａは、回転弁体３０の形状及び弁室２４の形状により定まる仮想軸である。そして、回転弁体３０は、弁室形成部２５に形成された回転軸Ａ方向に延びる弁室２４に、回転軸Ａ方向に沿って挿入された状態で、挿入方向の後方側に配置された固定部材９５により抜け止め固定されている。このような構成とすることで、回転弁体３０は、回転軸Ａ方向の移動が規制された状態で、弁室２４内に配置される。なお、固定部材９５は、例えば、カシメ固定、別部材による抜け止め固定（例えば締結固定等）等により弁室形成部２５に対して固定される。 As shown in FIG. 4, the rotary valve body 30 is configured as a rotary member having a rotation axis A in a direction intersecting the flow direction Y of the first supply flow path L1 (a direction orthogonal in this example). Yes. That is, the rotation axis A is an axis extending in a direction intersecting the flow path direction Y (a direction orthogonal in this example). The rotation axis A is a virtual axis determined by the shape of the rotary valve body 30 and the shape of the valve chamber 24. And the rotary valve body 30 was arrange | positioned in the valve chamber 24 extended in the rotating shaft A direction formed in the valve chamber formation part 25 along the rotating shaft A direction at the back side of the insertion direction. It is fixed by a fixing member 95 to prevent it from coming off. By setting it as such a structure, the rotary valve body 30 is arrange | positioned in the valve chamber 24 in the state by which the movement of the rotating shaft A direction was controlled. Note that the fixing member 95 is fixed to the valve chamber forming portion 25 by, for example, caulking fixing, retaining fixing by another member (for example, fastening fixing) or the like.

回転弁体３０は、図６に示すように、本体部３３と、当該本体部３３に対して回転軸Ａの軸方向の両側に設けられた一対の被支持部３１，３２とを備えている。そして、一対の被支持部３１，３２のそれぞれは、弁室形成部２５に対して回転可能に支持されている。具体的には、一対の被支持部３１，３２の内の一方である第一被支持部３１は、回転軸Ａ方向の外側（本体部３３とは反対側）の端部が固定部材９５に形成された凹部に対して挿入された状態で、弁室形成部２５に対して回転可能に支持されている。本実施形態では、第一被支持部３１は、固定部材９５に形成された上記凹部に対して摺動可能に当接するように配置されている。また、一対の被支持部３１，３２の内の他方である第二被支持部３２は、回転軸Ａ方向の外側の端部が弁室形成部２５に形成された凹部に挿入された状態で、弁室形成部２５に対して回転可能に支持されている。本実施形態では、第二被支持部３２は、弁室形成部２５に形成された上記凹部に対して摺動可能に当接するように配置されている。このような構成とすることで、本実施形態では、回転弁体３０は、弁室形成部２５又は当該弁室形成部２５に固定された部材（具体的には固定部材９５）により、回転軸Ａの軸方向の両側で径方向外側から回転可能に支持されている。 As shown in FIG. 6, the rotary valve body 30 includes a main body portion 33 and a pair of supported portions 31 and 32 provided on both sides in the axial direction of the rotation axis A with respect to the main body portion 33. . Each of the pair of supported portions 31 and 32 is rotatably supported with respect to the valve chamber forming portion 25. Specifically, the first supported portion 31, which is one of the pair of supported portions 31 and 32, has an end on the outer side (opposite to the main body portion 33) in the direction of the rotation axis A at the fixing member 95. In a state of being inserted into the formed recess, the valve chamber forming portion 25 is rotatably supported. In the present embodiment, the first supported portion 31 is disposed so as to slidably contact the concave portion formed in the fixing member 95. The second supported portion 32, which is the other of the pair of supported portions 31, 32, is inserted in a recess formed in the valve chamber forming portion 25 at the outer end in the rotation axis A direction. The valve chamber forming portion 25 is rotatably supported. In the present embodiment, the second supported portion 32 is disposed so as to slidably contact the concave portion formed in the valve chamber forming portion 25. By adopting such a configuration, in the present embodiment, the rotary valve body 30 is rotated by the valve chamber forming portion 25 or a member (specifically, the fixing member 95) fixed to the valve chamber forming portion 25. It is supported on both sides in the axial direction of A so as to be rotatable from the outside in the radial direction.

そして、回転弁体３０は、第一供給流路Ｌ１の流路方向Ｙに見て回転弁体３０が第一供給流路Ｌ１の流路断面の全体と重複する状態となる閉塞位置（図３、図７参照）と、第一供給流路Ｌ１の流路方向Ｙに見て回転弁体３０の全体が第一供給流路Ｌ１の流路断面の外に位置する状態となる開放位置（図２、図６参照）との間で、回転可能に構成されている。閉塞位置は、第一逆止弁２１を閉状態（具体的には、全閉状態）とするための回転弁体３０の回転位置であり、開放位置は、第一逆止弁２１を開状態（具体的には、全開状態）とするための回転弁体３０の回転位置である。なお、ここで対象とする第一供給流路Ｌ１の流路断面は、第一供給流路Ｌ１における第一逆止弁２１の入力ポート或いは出力ポートを構成する部分の流路断面であり、本実施形態では、第一供給流路Ｌ１における第一逆止弁２１より上流側の部分と、上流側の接続室２６との境界部分の流路断面、或いは、第一供給流路Ｌ１における第一逆止弁２１より下流側の部分と、下流側の接続室２６との境界部分の流路断面とされる。 The rotary valve body 30 is in the closed position where the rotary valve body 30 overlaps the entire flow path cross section of the first supply flow path L1 when viewed in the flow path direction Y of the first supply flow path L1 (FIG. 3). 7), and an open position where the entire rotary valve body 30 is located outside the cross section of the first supply flow path L1 when viewed in the flow direction Y of the first supply flow path L1 (see FIG. 7). 2 and FIG. 6). The closed position is a rotational position of the rotary valve body 30 for closing the first check valve 21 (specifically, a fully closed state), and the open position is a state where the first check valve 21 is opened. This is the rotational position of the rotary valve body 30 (specifically, the fully open state). In addition, the flow path cross section of the first supply flow path L1 as a target here is a flow path cross section of a portion constituting the input port or the output port of the first check valve 21 in the first supply flow path L1. In the embodiment, the cross section of the flow path at the boundary between the upstream portion of the first supply flow path L1 from the first check valve 21 and the upstream connection chamber 26, or the first flow path L1. The cross section of the flow path is a boundary portion between the downstream portion of the check valve 21 and the downstream connection chamber 26.

図７に示すように、回転弁体３０の本体部３３は、閉塞位置において、流路方向Ｙに見て第一供給流路Ｌ１の流路断面の全体と重複する部分を有するように構成されている。そして、開放位置において、流路方向Ｙに見て回転弁体３０の全体が第一供給流路Ｌ１の流路断面の外に位置する状態を実現すべく、本実施形態に係る本体部３３は、流路方向Ｙに見て第一供給流路Ｌ１の流路断面と回転軸Ａの軸方向の位置が重複する部分（以下、「重複部分」という。）が、円柱体から周方向の一部を径方向の全域及び軸方向の全域で切り除いた形状に形成されている。 As shown in FIG. 7, the main body portion 33 of the rotary valve body 30 is configured to have a portion that overlaps the entire flow path section of the first supply flow path L1 when viewed in the flow path direction Y at the closed position. ing. And in the open position, the main body portion 33 according to the present embodiment is configured to realize a state in which the entire rotary valve body 30 is located outside the channel cross section of the first supply channel L1 when viewed in the channel direction Y. A portion where the cross-section of the first supply flow passage L1 and the axial position of the rotation axis A overlap with each other when viewed in the flow passage direction Y (hereinafter referred to as “overlap portion”) The portion is formed in a shape obtained by cutting out the entire region in the radial direction and the entire region in the axial direction.

本実施形態では、第一逆止弁２１は、図４に示すように、第一供給流路Ｌ１における流路方向Ｙが直線状となる部分に配置されている。なお、以下の説明では、特に断らない限り、第一供給流路Ｌ１とはこの直線状の部分を指す。このような第一供給流路Ｌ１の形状に合わせて、本体部３３の上記重複部分は、図２に示すように、円柱体から周方向における半周部分を径方向の全域及び軸方向の全域で切り除いた形状、すなわち、半円柱状に形成されている。また、本実施形態では、第一供給流路Ｌ１の流路断面は、図７において第一供給流路Ｌ１の壁面Ｗを破線で示すように、回転軸Ａ方向の幅が当該回転軸Ａに直交する方向の幅よりも大きい矩形状に形成されている。このような第一供給流路Ｌ１の流路断面の形状に合わせて、上流側及び下流側の双方の接続室２６の流路方向Ｙに直交する断面の形状は、第一供給流路Ｌ１の当該流路断面と同じ矩形状に形成されている。 In the present embodiment, as shown in FIG. 4, the first check valve 21 is disposed in a portion where the flow path direction Y in the first supply flow path L1 is linear. In the following description, the first supply flow path L1 refers to this linear portion unless otherwise specified. In accordance with the shape of the first supply flow path L1, the overlapping portion of the main body portion 33 has a half-circumferential portion in the circumferential direction from the cylindrical body in the entire area in the radial direction and the entire area in the axial direction, as shown in FIG. The cut shape, that is, a semi-cylindrical shape is formed. Further, in the present embodiment, the cross section of the first supply flow path L1 is such that the width in the direction of the rotation axis A corresponds to the rotation axis A as shown by the broken line in the wall surface W of the first supply flow path L1 in FIG. It is formed in a rectangular shape larger than the width in the orthogonal direction. In accordance with the shape of the cross section of the first supply flow path L1, the shape of the cross section perpendicular to the flow direction Y of the upstream and downstream connection chambers 26 is the same as that of the first supply flow path L1. It is formed in the same rectangular shape as the flow path cross section.

本実施形態では、本体部３３の上記重複部分の回転軸Ａ方向の長さＤ１は、図６、図７に示すように、第一供給流路Ｌ１の当該方向の幅に等しく設定されている。なお、本体部３３の上記重複部分を除く部分（本例では、当該重複部分に対して回転軸Ａ方向の両側に配置された部分）は、円柱状に形成されている。これにより、開放位置において形成される弁室２４内の流路の回転軸Ａ方向の幅は、図６、図７に示すように第一供給流路Ｌ１の当該方向の幅と等しくなる。また、回転軸Ａは、流路方向Ｙに見て第一供給流路Ｌ１の壁面Ｗを構成する矩形の直線状部分と重なるように配置されている。これにより、開放位置において形成される弁室２４内の流路の、本体部３３の上記重複部分により区画される側の壁面は、図２に示すように、第一供給流路Ｌ１における第一逆止弁２１の両側に配置された部分のそれぞれの壁面Ｗを、流路方向Ｙに沿って接続するように形成される。すなわち、開放位置において形成される弁室２４内の流路の、本体部３３の上記重複部分により区画される側の壁面は、第一供給流路Ｌ１の壁面Ｗを第一逆止弁２１の内部側に流路方向Ｙに沿って延出した仮想壁面と一致するように形成される。 In the present embodiment, the length D1 of the overlapping portion of the main body 33 in the direction of the rotation axis A is set equal to the width of the first supply flow path L1 in the direction, as shown in FIGS. . In addition, the part (In this example, the part arrange | positioned in the both sides of the rotating shaft A direction with respect to the said overlapping part) except the said overlapping part of the main-body part 33 is formed in the column shape. As a result, the width of the flow path in the valve chamber 24 formed at the open position in the direction of the rotation axis A is equal to the width of the first supply flow path L1 in that direction, as shown in FIGS. Further, the rotation axis A is arranged so as to overlap with the rectangular linear portion constituting the wall surface W of the first supply flow path L1 when viewed in the flow path direction Y. Thereby, the wall surface of the flow path in the valve chamber 24 formed at the open position, which is defined by the overlapping portion of the main body 33, is the first wall in the first supply flow path L1 as shown in FIG. Each wall surface W of the part arrange | positioned at the both sides of the non-return valve 21 is formed so that it may connect along the flow-path direction Y. That is, the wall surface of the flow path in the valve chamber 24 formed at the open position, which is partitioned by the overlapping portion of the main body 33, is connected to the wall surface W of the first supply flow path L 1 by the first check valve 21. It is formed on the inner side so as to coincide with the virtual wall surface extending along the flow path direction Y.

また、本実施形態では、回転弁体３０を収容する弁室２４は、図６に示すように、半径がＤ２の円筒状の内壁面を有するように形成され、当該半径Ｄ２は、第一供給流路Ｌ１の流路断面における回転軸Ａ方向に直交する方向の幅よりも大きく（本例では、１０％〜２０％程度大きく）設定されている。これにより、図２及び図６に示すように、開放位置において形成される弁室２４内の流路の流路断面積は、流路方向Ｙにおける弁の中央部分において、第一供給流路Ｌ１の流路断面積より僅かに大きくなっている。なお、上記の半径Ｄ２を、第一供給流路Ｌ１の流路断面における回転軸Ａ方向に直交する方向の幅と同じ値に設定することも可能である。 Moreover, in this embodiment, as shown in FIG. 6, the valve chamber 24 that accommodates the rotary valve body 30 is formed to have a cylindrical inner wall surface with a radius D2, and the radius D2 is the first supply. It is set to be larger than the width in the direction orthogonal to the direction of the rotation axis A in the channel cross section of the channel L1 (in this example, about 10% to 20% larger). As a result, as shown in FIGS. 2 and 6, the flow passage cross-sectional area of the flow passage in the valve chamber 24 formed at the open position is the first supply flow passage L 1 in the central portion of the valve in the flow passage direction Y. It is slightly larger than the channel cross-sectional area. The radius D2 may be set to the same value as the width in the direction orthogonal to the direction of the rotation axis A in the flow path cross section of the first supply flow path L1.

そして、本実施形態では、第一逆止弁２１は、当該第一逆止弁２１に対して作用する油圧に応じて回転弁体３０の回転位置が定まるように構成されている。具体的には、第一逆止弁２１に対して上流側から作用する油圧が下流側から作用する油圧に対して所定値以上大きくなると、第一逆止弁２１が閉状態から開状態に切り替わるように構成されている。このような構成を実現するための構成について以下説明する。 In the present embodiment, the first check valve 21 is configured such that the rotational position of the rotary valve body 30 is determined according to the hydraulic pressure acting on the first check valve 21. Specifically, when the hydraulic pressure acting on the first check valve 21 from the upstream side becomes greater than a predetermined value relative to the hydraulic pressure acting on the downstream side, the first check valve 21 switches from the closed state to the open state. It is configured as follows. A configuration for realizing such a configuration will be described below.

図３に示すように、回転弁体３０には閉弁方向を向く受圧面Ｐが形成されている。ここで、「閉弁方向」とは、回転弁体３０が開放位置側から閉塞位置側に回転する際の回転方向（図２、図３における反時計回り方向）である。この受圧面Ｐは、図３、図７に示すように、回転弁体３０が閉塞位置に位置する状態で、第一供給流路Ｌ１の流路方向Ｙの上流側を向くとともに、当該流路方向Ｙに見て第一供給流路Ｌ１の流路断面（本例では当該流路断面の全体）と重複する位置に配置されるように、回転弁体３０に設けられている。本実施形態では、上述したように、本体部３３の上記重複部分は半円柱状に形成されており、当該半円柱体の回転軸Ａ方向に延びる平面状の外周部（本例では当該外周部における回転軸Ａに対して一方側の部分）により受圧面Ｐが形成されている。そして、本実施形態では、図６に示すように、受圧面Ｐは、回転弁体３０が開放位置に位置する状態で、流路方向Ｙに見て第一供給流路Ｌ１を形成する壁面Ｗの一部と重なるように配置される。この状態で、上記外周部における回転軸Ａに対して受圧面Ｐとは反対側の部分（受圧面Ｐを構成しない部分）も、第一供給流路Ｌ１を形成する壁面Ｗの当該一部と重なるように配置される。 As shown in FIG. 3, the rotary valve body 30 is formed with a pressure receiving surface P that faces the valve closing direction. Here, the “valve closing direction” is a rotation direction (counterclockwise direction in FIGS. 2 and 3) when the rotary valve body 30 rotates from the open position side to the closed position side. 3 and 7, the pressure receiving surface P faces the upstream side in the flow direction Y of the first supply flow path L1 in a state where the rotary valve body 30 is located at the closed position, and the flow path It is provided in the rotary valve body 30 so as to be disposed at a position overlapping with the channel cross section of the first supply channel L1 as viewed in the direction Y (in this example, the entire channel cross section). In the present embodiment, as described above, the overlapping portion of the main body portion 33 is formed in a semi-cylindrical shape, and is a planar outer peripheral portion (in this example, the outer peripheral portion extending in the rotation axis A direction). The pressure receiving surface P is formed by a portion on one side with respect to the rotation axis A in FIG. And in this embodiment, as shown in FIG. 6, the pressure receiving surface P is the wall surface W which forms the 1st supply flow path L1 seeing in the flow path direction Y in the state in which the rotary valve body 30 is located in an open position. It arrange | positions so that it may overlap with a part of. In this state, the portion of the outer peripheral portion opposite to the pressure receiving surface P with respect to the rotation axis A (the portion that does not constitute the pressure receiving surface P) is also the portion of the wall surface W that forms the first supply flow path L1. Arranged to overlap.

さらに、本実施形態では、図５に示すように、第一被支持部３１は、回転軸Ａを基準として本体部３３の最も径方向外側に位置する部分よりも小径とされているとともに、第一被支持部３１の外周面に沿ってコイルばね２３が配置されている。本実施形態では、第一被支持部３１は円柱状に形成され、第二被支持部３２も、第一被支持部３１と同径の円柱状に形成されている。コイルばね２３は、回転軸Ａの軸方向における本体部３３と固定部材９５との間に形成された空間に、回転弁体３０を閉弁方向に付勢するように配置されている。これにより、回転弁体３０の回転位置は、受圧面Ｐに作用する上流側からの油圧と、コイルばね２３による閉弁方向への付勢力（本例では復元力）と、に応じて定まる。本実施形態では、第一被支持部３１が本発明における「対象被支持部」とされ、コイルばね２３が本発明における「付勢部材」に相当する。 Furthermore, in the present embodiment, as shown in FIG. 5, the first supported portion 31 has a smaller diameter than the portion positioned on the outermost radial direction of the main body portion 33 with respect to the rotation axis A, and A coil spring 23 is disposed along the outer peripheral surface of the one supported portion 31. In the present embodiment, the first supported portion 31 is formed in a cylindrical shape, and the second supported portion 32 is also formed in a cylindrical shape having the same diameter as the first supported portion 31. The coil spring 23 is disposed in a space formed between the main body 33 and the fixing member 95 in the axial direction of the rotation axis A so as to urge the rotary valve body 30 in the valve closing direction. Thereby, the rotational position of the rotary valve body 30 is determined according to the hydraulic pressure from the upstream side acting on the pressure receiving surface P and the biasing force (restoring force in this example) in the valve closing direction by the coil spring 23. In the present embodiment, the first supported portion 31 is the “target supported portion” in the present invention, and the coil spring 23 corresponds to the “biasing member” in the present invention.

コイルばね２３の復元力は、回転弁体３０と弁室２４の内面との間の摩擦係数等に基づき設定される。そして、図３に示すように、受圧面Ｐに対して作用する第一供給流路Ｌ１の流路方向Ｙの上流側からの液圧が零の状態では、回転弁体３０の回転位置が閉塞位置となるように、コイルばね２３の配置構成（例えば復元力等）が設定されている。更に、第一油圧ポンプ１１の吐出圧が零から予め設定された第一油圧に到達すると、回転弁体３０が閉塞位置から開放位置に向かって回転し始め、第一油圧ポンプ１１の吐出圧が上記第一油圧よりも高い値に設定された第二油圧に到達すると、回転弁体３０が開放位置に位置するように、コイルばね２３の配置構成は、これらの第一油圧や第二油圧にも基づき設定されている。 The restoring force of the coil spring 23 is set based on the coefficient of friction between the rotary valve body 30 and the inner surface of the valve chamber 24. As shown in FIG. 3, when the hydraulic pressure from the upstream side in the flow direction Y of the first supply flow path L1 acting on the pressure receiving surface P is zero, the rotational position of the rotary valve body 30 is blocked. The arrangement configuration (for example, restoring force) of the coil spring 23 is set so as to be in the position. Further, when the discharge pressure of the first hydraulic pump 11 reaches a preset first hydraulic pressure from zero, the rotary valve body 30 starts to rotate from the closed position to the open position, and the discharge pressure of the first hydraulic pump 11 is reduced. When the second hydraulic pressure set to a value higher than the first hydraulic pressure is reached, the arrangement configuration of the coil spring 23 is set to the first hydraulic pressure and the second hydraulic pressure so that the rotary valve body 30 is located at the open position. Is also set based on.

なお、本実施形態では、閉塞位置に位置する回転弁体３０に対して下流側から油圧が作用した場合に、回転弁体３０が図３に示す閉塞位置から更に半時計回り方向側に回転することが許容される構成となっている。しかし、この場合、回転弁体３０の半時計回り方向側への回転変位量に応じてコイルばね２３による閉弁方向とは反対側（図３における時計回り方向側）への付勢力が回転弁体３０に作用する。これにより、回転弁体３０に対して下流側から油圧が作用した場合であっても、第二逆止弁２２の閉状態が維持されるように構成されている。なお、回転弁体３０が図３に示す閉塞位置から半時計回り方向側に回転するのを規制する機械的なストッパを設けることも可能である。 In the present embodiment, when hydraulic pressure is applied to the rotary valve body 30 located at the closed position from the downstream side, the rotary valve body 30 further rotates counterclockwise from the closed position shown in FIG. This is an acceptable configuration. However, in this case, the urging force of the coil spring 23 on the side opposite to the valve closing direction (clockwise direction in FIG. 3) according to the amount of rotational displacement of the rotary valve body 30 in the counterclockwise direction is the rotary valve. Acts on the body 30. Thereby, even if it is a case where oil_pressure | hydraulic acts from the downstream with respect to the rotary valve body 30, it is comprised so that the closed state of the 2nd non-return valve 22 may be maintained. It is also possible to provide a mechanical stopper that restricts the rotary valve body 30 from rotating in the counterclockwise direction from the closed position shown in FIG.

詳細な説明は省略するが、本実施形態では、第二逆止弁２２は、球状の弁体が流路方向Ｙに沿って移動可能に構成された弁とされ、全開状態においても、第二供給流路Ｌ２の流路方向に見て球状弁体の全体が第二供給流路Ｌ２の流路断面内に位置する状態となるように構成されている。 Although a detailed description is omitted, in the present embodiment, the second check valve 22 is a valve in which a spherical valve body is configured to be movable along the flow path direction Y. The entire spherical valve element is configured to be positioned within the cross section of the second supply flow path L2 when viewed in the flow path direction of the supply flow path L2.

３．その他の実施形態
最後に、本発明に係る液体供給装置の、その他の実施形態について説明する。なお、以下のそれぞれの実施形態で開示される構成は、矛盾が生じない限り、他の実施形態で開示される構成と組み合わせて適用することが可能である。 3. Other Embodiments Finally, other embodiments of the liquid supply apparatus according to the present invention will be described. Note that the configurations disclosed in the following embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises.

（１）上記の実施形態では、弁室形成部２５が、車両の駆動装置のケース２とは独立の部材とされ、弁室形成部２５が、ケース２に形成された凹部に挿入された状態で当該ケース２に対して固定されている構成を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、図８、図９に示すように、弁室形成部２５がケース２と一体的に当該ケース２の一部として形成された構成とすることも、本発明の好適な実施形態の一つである。このような構成では、ケース２の弁室形成部２５には、図９に示すように、流路方向Ｙに直交する方向に延びるとともに円筒状の内壁面を有する弁室２４が形成され、当該弁室２４に対して、回転弁体３０、コイルばね２３、及び固定部材９５を順に挿入することで、第一逆止弁２１が形成される。 (1) In the above-described embodiment, the valve chamber forming portion 25 is a member independent of the case 2 of the vehicle drive device, and the valve chamber forming portion 25 is inserted into the recess formed in the case 2. The configuration fixed to the case 2 has been described as an example. However, the embodiment of the present invention is not limited to this, and a configuration in which the valve chamber forming portion 25 is formed integrally with the case 2 as a part of the case 2 as shown in FIGS. This is also a preferred embodiment of the present invention. In such a configuration, the valve chamber forming portion 25 of the case 2 is formed with a valve chamber 24 extending in a direction perpendicular to the flow direction Y and having a cylindrical inner wall surface, as shown in FIG. The first check valve 21 is formed by sequentially inserting the rotary valve body 30, the coil spring 23, and the fixing member 95 into the valve chamber 24.

（２）上記の実施形態では、付勢部材としてのコイルばね２３が第一被支持部３１に配置された構成を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、第一被支持部３１に配置される付勢部材が、例えば板ばね等のコイルばね２３以外の付勢部材とされる構成とすることも可能である。また、上記の実施形態では、第一被支持部３１及び第二被支持部３２の内、第一被支持部３１のみが本発明における「対象被支持部」とされる構成を例として説明したが、第一被支持部３１に加えて第二被支持部３２も本発明における「対象被支持部」とされ、第二被支持部３２の外周面にも付勢部材（例えば、コイルばね等）が配置される構成とすることも可能である。なお、第一被支持部３１及び第二被支持部３２の内、第二被支持部３２のみが本発明における「対象被支持部」とされる構成とすることも可能である。 (2) In the above embodiment, the configuration in which the coil spring 23 as the urging member is disposed on the first supported portion 31 has been described as an example. However, the embodiment of the present invention is not limited to this, and the biasing member disposed in the first supported portion 31 is a biasing member other than the coil spring 23 such as a leaf spring, for example. It is also possible to do. Moreover, in said embodiment, the structure by which only the 1st supported part 31 is made into the "target supported part" in this invention among the 1st supported part 31 and the 2nd supported part 32 was demonstrated as an example. However, in addition to the first supported portion 31, the second supported portion 32 is also referred to as a “target supported portion” in the present invention, and a biasing member (for example, a coil spring or the like) is also provided on the outer peripheral surface of the second supported portion 32. ) May be arranged. Of the first supported portion 31 and the second supported portion 32, only the second supported portion 32 can be configured as the “target supported portion” in the present invention.

（３）上記の実施形態では、回転弁体３０の回転軸Ａが、第一供給流路Ｌ１の流路方向Ｙに対して直交する軸とされた構成を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、回転弁体３０の回転軸Ａが、第一供給流路Ｌ１の流路方向Ｙに対して鋭角で交差する方向（例えば、８５度や８０度で交差する方向）に延びる軸とされる構成とすることもできる。また、上記の実施形態では、回転軸Ａが、流路方向Ｙに見て第一供給流路Ｌ１の壁面Ｗを構成する矩形の直線状部分と重なるように配置されている構成を例として説明したが、回転軸Ａが当該直線状部分に対して流路内部側の位置又は流路内部とは反対側に離間した位置に配置された構成とすることもできる。この場合においても、回転弁体３０が開放位置に位置する状態で、流路方向Ｙに見て受圧面Ｐが第一供給流路Ｌ１を形成する壁面Ｗの一部と重なるように、回転弁体３０の上記重複部分を形成すると好適である。 (3) In the above embodiment, the configuration in which the rotation axis A of the rotary valve body 30 is an axis orthogonal to the flow path direction Y of the first supply flow path L1 has been described as an example. However, the embodiment of the present invention is not limited to this, and the rotation axis A of the rotary valve body 30 intersects the flow direction Y of the first supply flow path L1 at an acute angle (for example, 85 It is also possible to adopt a configuration in which the axis extends in the direction intersecting at a degree or 80 degrees. In the above embodiment, the rotation axis A is described as an example of a configuration in which the rotation axis A is arranged so as to overlap the rectangular linear portion that forms the wall surface W of the first supply flow path L1 when viewed in the flow path direction Y. However, it can also be set as the structure by which the rotating shaft A is arrange | positioned in the position spaced apart to the position inside a flow path, or the opposite side to the flow path inside with respect to the said linear part. Also in this case, the rotary valve 30 is located in the open position so that the pressure receiving surface P overlaps a part of the wall surface W forming the first supply flow path L1 when viewed in the flow path direction Y. Preferably, the overlapping part of the body 30 is formed.

（４）上記の実施形態では、受圧面Ｐが、回転弁体３０が開放位置に位置する状態で、流路方向Ｙに見て第一供給流路Ｌ１を形成する壁面Ｗの一部と重なるように配置される構成を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、回転弁体３０が開放位置に位置する状態で、受圧面Ｐが、流路方向Ｙに見て第一供給流路Ｌ１を形成する壁面Ｗに対して流路内部とは反対側に離間した位置に配置される構成とすることも可能である。 (4) In the above embodiment, the pressure receiving surface P overlaps with a part of the wall surface W forming the first supply flow path L1 when viewed in the flow path direction Y in a state where the rotary valve body 30 is located at the open position. The configuration arranged as described above has been described as an example. However, the embodiment of the present invention is not limited to this, and the pressure receiving surface P forms the first supply flow path L1 when viewed in the flow path direction Y with the rotary valve body 30 positioned at the open position. It is also possible to adopt a configuration in which the wall surface W is arranged at a position spaced away from the inside of the flow path.

（５）上記の実施形態では、第一逆止弁２１及び第二逆止弁２２の内、第一逆止弁２１のみが本発明における「対象逆止弁」とされる構成を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、第二逆止弁２２を第一逆止弁２１と同様に構成し、第一逆止弁２１及び第二逆止弁２２の双方が本発明における「対象逆止弁」とされる構成とすることも可能である。また、第一逆止弁２１及び第二逆止弁２２の内、第二逆止弁２２のみが本発明における「対象逆止弁」とされ、第一逆止弁２１が上記実施形態とは異なる構成の逆止弁とされる構成とすることも可能である。 (5) In the above embodiment, the configuration in which only the first check valve 21 among the first check valve 21 and the second check valve 22 is the “target check valve” in the present invention will be described as an example. did. However, the embodiment of the present invention is not limited to this, and the second check valve 22 is configured in the same manner as the first check valve 21, and the first check valve 21 and the second check valve 22 are configured. Both may be configured as “target check valves” in the present invention. Of the first check valve 21 and the second check valve 22, only the second check valve 22 is the “target check valve” in the present invention, and the first check valve 21 is the above embodiment. It is also possible to adopt a configuration in which the check valve has a different configuration.

（６）上記の実施形態では、本発明に係る液体供給装置を、車両に備えられる油供給装置に適用した場合を例として説明した。しかし、本発明の実施形態はこれに限定されるものではなく、本発明に係る液体供給装置を、車両以外の装置に備えられる油供給装置に適用することや、油以外の液体を供給する液体供給装置に適用することも可能である。 (6) In the above embodiment, the case where the liquid supply device according to the present invention is applied to an oil supply device provided in a vehicle has been described as an example. However, the embodiment of the present invention is not limited to this, and the liquid supply apparatus according to the present invention is applied to an oil supply apparatus provided in an apparatus other than a vehicle, or a liquid that supplies a liquid other than oil. It is also possible to apply to a supply device.

（７）その他の構成に関しても、本明細書において開示された実施形態は全ての点で例示であって、本発明の実施形態はこれに限定されない。すなわち、本願の特許請求の範囲に記載されていない構成に関しては、本発明の目的を逸脱しない範囲内で適宜改変することが可能である。 (7) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and the embodiments of the present invention are not limited thereto. In other words, configurations that are not described in the claims of the present application can be modified as appropriate without departing from the object of the present invention.

本発明は、第一液圧ポンプと、第二液圧ポンプと、第一液圧ポンプにより発生した液圧が供給される第一供給流路と、第二液圧ポンプにより発生した液圧が供給される第二供給流路と、第一供給流路と第二供給流路とが合流して形成される第三供給流路と、第一供給流路に設けられた第一逆止弁と、第二供給流路に設けられた第二逆止弁と、を備えた液体供給装置に好適に利用することができる。 The present invention relates to a first hydraulic pump, a second hydraulic pump, a first supply passage to which a hydraulic pressure generated by the first hydraulic pump is supplied, and a hydraulic pressure generated by the second hydraulic pump. A second supply channel to be supplied, a third supply channel formed by joining the first supply channel and the second supply channel, and a first check valve provided in the first supply channel And a second check valve provided in the second supply flow path can be suitably used for a liquid supply apparatus.

１：油圧供給装置（液体供給装置）
１１：第一油圧ポンプ（第一液圧ポンプ）
１２：第二油圧ポンプ（第二液圧ポンプ）
２１：第一逆止弁（対象逆止弁）
２２：第二逆止弁
２３：コイルばね（付勢部材）
２４：弁室
２５：弁室形成部
３０：回転弁体
３１：第一被支持部（対象被支持部）
３２：第二被支持部
３３：本体部
Ａ：回転軸
Ｌ１：第一供給流路（対象供給流路）
Ｌ２：第二供給流路
Ｌ３：第三供給流路
Ｐ：受圧面
Ｗ：壁面
Ｙ：流路方向 1: Hydraulic supply device (liquid supply device)
11: First hydraulic pump (first hydraulic pump)
12: Second hydraulic pump (second hydraulic pump)
21: First check valve (target check valve)
22: Second check valve 23: Coil spring (biasing member)
24: Valve chamber 25: Valve chamber forming portion 30: Rotary valve element 31: First supported portion (target supported portion)
32: Second supported part 33: Main part A: Rotating shaft L1: First supply channel (target supply channel)
L2: Second supply channel L3: Third supply channel P: Pressure receiving surface W: Wall surface Y: Channel direction

Claims

A first hydraulic pump, a second hydraulic pump, a first supply passage to which the hydraulic pressure generated by the first hydraulic pump is supplied, and a hydraulic pressure generated by the second hydraulic pump are supplied. A second supply flow path, a third supply flow path formed by joining the first supply flow path and the second supply flow path, and a first check provided in the first supply flow path A liquid supply apparatus comprising: a valve; and a second check valve provided in the second supply flow path,
The target check valve which is at least one of the first check valve and the second check valve includes a rotary valve body,
A direction in which the rotary valve body intersects the flow direction of the target supply flow path that is one of the first supply flow path and the second supply flow path on which the target check valve is provided. A rotating member serving as a rotating shaft, wherein the rotary valve body is in a state overlapping with the entire flow path section of the target supply flow path when viewed in the flow path direction of the target supply flow path, and the target A liquid supply configured to be rotatable between an open position where the entire rotary valve body is located outside the cross section of the target supply flow path when viewed in the flow path direction of the supply flow path apparatus.

The rotary valve body includes a pressure receiving surface facing a valve closing direction that is a rotation direction when the rotary valve body rotates from the open position side to the closed position side,
The pressure receiving surface faces the upstream side in the flow direction of the target supply flow channel and the target supply flow channel when viewed from the flow direction of the target supply flow channel with the rotary valve body positioned at the closed position. Provided in the rotary valve body so as to be disposed at a position overlapping with the flow path cross section of
The liquid supply apparatus according to claim 1, wherein the target check valve includes a biasing member that biases the rotary valve body in the valve closing direction.

The pressure receiving surface is formed so as to overlap with a wall surface forming the target supply flow path when viewed in the flow direction of the target supply flow path in a state where the rotary valve body is located at the open position. 3. The liquid supply apparatus according to 2.

The biasing member is arranged so that the rotational position of the rotary valve body becomes the closed position in a state where the hydraulic pressure from the upstream side in the flow direction of the target supply flow channel acting on the pressure receiving surface is zero. The liquid supply apparatus according to claim 2, wherein an urging force is set.

The target check valve includes a valve chamber forming portion that forms a valve chamber that houses the rotary valve body,
The rotary valve body has a main body portion having a portion overlapping with the entire flow path section of the target supply flow path when viewed in the flow path direction of the target supply flow path at the closed position, A pair of supported portions provided on both sides in the axial direction of the rotating shaft,
Each of the pair of supported parts is rotatably supported with respect to the valve chamber forming part,
The target supported portion, which is at least one of the pair of supported portions, has a smaller diameter than a portion located on the outermost radial direction of the main body with respect to the rotation axis, and the target supported portion The liquid supply apparatus according to any one of claims 2 to 4, wherein a coil spring as the urging member is disposed along an outer peripheral surface.