201204957 六、發明說明： 【發明所屬之技術領域】 本發明大體上係關於液壓耦合器，且更具體言之係關 於-種具有包括&旋轉能力t自行調整液體傳遞路徑之液 壓耦合器。 【先前技術】 液壓耦合器為載具傳動列中使用之熟知裝置。典型 地，液壓耦合器操作性地支撐於外殼内且與液壓液之供應 源液體連通。此等裝置操作以耦合諸如傳動軸或繞旋轉軸 線之輪軸半軸之一對旋轉構件。因此，液壓耦合器已用作 操作性地麵合載具之前輪軸及後輪轴之變速箱之一部八 用於用以耦合輪軸半軸之限滑及鎖定差速器中以 〜項技 術中通常已知之其他應用中。 先前技術中已知之類型之液壓耦合器可包括藉由外彀 支撐且包括經設計以實現藉由液壓耦合器耦合於一 ' %之旋 轉構件之間的相對旋轉的齒輪組之齒輪箱。另外 " ’I ，此等裝 置亦包括操作以鎖定旋轉構件以用於一起旋轉 乂 j祸合機 構’諸如離合器套件。液壓液用以致動活塞或類似求置以 嚙合離合器且因此將旋轉構件耦合於一起。典型 箱經外殼支撐以在其内旋轉，但耦合機構並 个如此。實情 為，耦合機構可經由輥軸承或其類似物支撐於旋轉構件中 之一者上。然而，因為其支撐於旋轉構件上且通常鄰近旋 轉之齒輪箱’且因為其用於將旋轉構件耦合於— 起，所以 201204957 在正常操作條件期 加壓液壓液供應源 殼傳遞至耦合機構 壓液之兩種方式。 間’耦合機構經受扭力。舉例而言，當 位於耦合機構外時，其必須經由固定外 在此等情況下，通常存在用於傳遞加 種做法為使用可彎曲咬播 Λ ^ ^ 次撓曲以在外殼與耦合機構之 間建立液體連接之可撓性管。 &然而，此做法具有管無「抗 旋轉」特徵之缺點。因此，在 在利用可撓性管路之情況下， 液壓搞合态必須亦白紅田，、，4 ^, 、 括用以相對於齒輪箱以及外殼穩定耦 合機構之抗旋轉突出部或專 女裝，、去構。此情形需要耦合 機構以及齒輪箱以搞$古4· 特疋方式、'且裴從而以特定方式對準液壓 耗合器之此等零部件0 士卜，声形Λ & & 匕if化^加先刖技術中已知之液壓 耦合器之複雜性以及其製造成本。 將加壓液壓液傳遞至搞合機構之另一種做法為利用自 外殼延伸絲合機構之硬質管質管W統提供抗旋轉 態樣且幫助輕合機構抵抗經由此系統施加之扭力。然而， 因為此做法亦為「硬質的」，所以必須將液體路徑之所有相 關聯孔隙及安裝點極準確定位。孔隙位置之相對於設計之 輕微偏差可在製造程序期間產生難題。此情形增加與製造 外殼以及耦合機構兩者相關聯之成本。另外，其亦使裝置 之組裝複雜。 因此’在此項技術中需要一種具有液體路徑之液壓耦 合器’该液體路徑具有可撓性及自行調整性以致形成於外 设以及麵合機構中之相應孔不必須極其精確地定位。另 外，在此項技術中需要一種具有液體路徑之液壓耦合器， 201204957 該液體路徑具有抗旋轉態樣以便消 、^人& 除對抗旋轉突出部或用 以將麵&機構安裝至外殼之其他特 将疋機構之需要。另外， 在此項技術中需要一種具有液體路 一 k又液壓耦合器，該液 體路徑考慮到液體路徑之内部安 顯著未對準。 文装點之間的 【發明内容】 本發明克服液壓耦合器中之先前 r无刖技術中之缺點，該液 壓耦合器用於包括一對旋轉構件 秋丹得勤列中。該液壓 輕合器包括與加壓液供應源液體連通之外殼。齒輪箱經由 :卜殼支禮以旋轉且操作性地輕合至旋轉構件。輕合機構非 可旋轉地支撐於外殼内且鄰近齒 . mu 州迎菌輪相。耦合機構可操作以 選擇性地將一對旋轉構件耦合 起。液體路徑在外殼盥 糕合誠之間延伸。液體路徑包括形成於外殼中且第 —直徑及縱向軸線之第一孔+ 几丨承以及形成於耦合機構中之 —孔隙。具有第一部分之硬質 嶸買β道絰由外设中之第一孔隙 申，該第一部分之直徑小一 … 昂孔隙之第一直徑以便界 =整㈣’以致硬質管道可回應於第一及第二孔隙之間 料而移動出與縱向輪線對準。另外，硬質管道包括 弟一部分，其與耦合機構 之第一孔隙摩擦喃合而被密封 土也收納，以致硬質營；首Μ 質^道棱供對施加於耦合機構上之扭力的 抗性。 广 本么明之液壓耦合器提供一液體路徑，該液體 U可撓性及自行調整性以致形成於外殼以及耦合機 201204957 構中之相應孔不必須極其精確地定位。另外，本發明之液 壓耦合器具有一液體路徑，該液體路徑具有抗旋轉態樣以 便消除對抗旋轉突出部或用以將耦合機構安裝至外殼之其 他特定機構之需要。因此，本發明之液壓耦合器具有一液 ，路徑’該液體路徑考慮到液體路徑之内部安裝點與外部 安裝點之間的顯著未對準，同時為其提供抗旋轉特徵。 【實施方式】 將易於瞭解本發明之其他目的、特徵及優勢，此係因 為在結合隨附圖式閱讀後續描述之後會較佳理解本發明之 其他目的、特徵及優勢。 用於載具傳動列中之液壓耦合器之代表性實施例大體 在圖1中以10指示，其中遍及諸圖式，類似數字用以表示 類似結構。一般熟習此項技術者將認識到液壓耦合器可用 作操作性地耦合載具前輪軸及後輪軸之變速箱之一部分； 用作用以耦合輪轴半軸之限滑差速器或鎖定差速器之一部 分；以及如此項技術中通常已知之在載具傳動列中之其他 應用。因此，一般熟習此項技術者將自以下描述瞭解，該 等圖式之目的為說明本發明之一個實施例且不意欲對其力·] 以限制。 如上所述’液壓搞合器10用於包括一對旋轉構件之載 具傳動列中。為此’液壓耦合器包括外殼，其一半大體以 12指示，該外殼與在圖1至圖2中以14示意性說明之加壓 液供應源液體連通。加壓液供應源14可包括用以潤滑及冷 201204957 部载具傳動列之各種組件之初級泵或如此項技術中通常已 知之任何其他適合加壓液壓液供應源。大體以1 6指示之齒 輪相厶外设12支撐以在其内旋轉。為此，齒輪箱可視具體 情況藉由傳動輪軸或載具後驅傳動軸經由小齒輪傳動。一 丨齒輪1 8、20亦經安裝以隨齒輪箱丨6中之旋轉構件中 之各別者旋轉。因此，該對側齒輪1 8、20中之每一者包括 、^ °周適以與旋轉構件上之相應栓槽（圖中未示）配合之栓 槽内徑22、24。 在此等圖式中所說明之代表性實施例中，液壓耦合器 亦充田差速$。然而且如上所述，本發明之液壓耦合器 1〇不限於此特定應用。無論如何，十字銷26均固定地安裝 ,ω輪箱16以隨其旋轉。一對小齒輪2 8經安裝以在十字 肖走轉且與-對側齒輪1 8、20中之每-者上所形成之齒 輪齒呈.嚙合關係。側齒輪18、20與小齒輪28配合以在： 此項技術中通常已知之旋轉構件之間提供差動旋轉。° 卜本發明之液壓耦合器10包括大體以3〇指示之 搞合機構’其非可旋轉地支樓於外殼12内且鄰近於齒輪松 輕合機構30可操作以選擇性地將該對旋轉構件輕：： 「起。在此情形下’本發明之液壓麵合器1〇可包 罢 速二或鎖疋差速器。因此，本發明之輕合機構⑺可操作以 允許在某些情況下該對旋轉構件之間相對旋轉，且 以在其他操作條件下將旋轉構件鎖定於一起。 為此’本發明之液壓耦合器 之離合器總成，其具有側齒輪1 8 10亦包括大體以3 2指示 、20可以不同速度旋轉之 201204957 開啟位置及液壓耦合器1 〇經鎖定以致側齒輪1 8、2〇以實 質上相同之速度旋轉之閉合位置。耦合機構30包括外殼34 及可移動地支撐於外殼34内之活塞36。活塞36及外殼34 用以界定其之間的可膨脹腔室3 8。如下文更詳細描述，可 膨脹腔室38與加壓液供應源14液體連通。耦合機構3〇之 外殼3 4亦可包括如此項技術中通常已知之淨化配件4 〇，其 用於當最初填充系統時將空氣淨化一次。 更具體言之’離合器總成32包括複數個環形板42，其 在其外徑栓槽接合至齒輪箱16 ^另外，離合器總成32包括 複數個環形摩擦盤44，其在其内徑栓槽接合至該對側齒輪 18或20中之一者。在本文所說明之代表性實施例中，環形 摩擦盤44在其内徑栓槽接合至側齒輪2〇。然而，一般熟習 此項技術者將瞭解，環形摩擦盤44可經由側齒輪丨8或2〇 中之任一者或兩者支撐以旋轉。當離合器總成32處於其開 啟位置時，複數個環形板42及環形摩擦盤44彼此之間交 錯且用以越過彼此以實質上非接觸關係旋轉。另—方=， 當離合器總成32處於其閉合位置時，環形板42及摩擦盤 44可在其栓槽互連後轴向移動成_於彼此摩擦喷合^ 此降低環形板42與盤44之間的相對旋轉。因此，;離^ 器總成32處於其閉合位置時，側齒輪18、2〇—起旋0 離合器總成32包括在活塞36與複數個交錯環 及摩擦盤44之間延伸之傳遞銷46。如下文更詳細描201204957 VI. Description of the Invention: TECHNICAL FIELD OF THE INVENTION The present invention relates generally to hydraulic couplers and, more particularly, to a hydraulic coupler having a self-adjusting liquid transfer path including & [Prior Art] A hydraulic coupler is a well-known device used in a carrier drive train. Typically, the hydraulic coupler is operatively supported within the housing and in fluid communication with a supply of hydraulic fluid. These devices operate to couple a pair of rotating members, such as a drive shaft or an axle half shaft about a rotational axis. Therefore, the hydraulic coupler has been used as one of the gearboxes of the front axle and the rear axle of the operative ground-engagement carrier, which is used to couple the limited-slip and lock differential of the axle half-shaft. Often used in other applications. A hydraulic coupler of the type known in the prior art may include a gearbox supported by an outer casing and including a gear set designed to couple relative rotation between a '% of rotating members by a hydraulic coupler. In addition, "'I, these devices also include an operation to lock the rotating member for rotating together, such as a clutch kit. Hydraulic fluid is used to actuate the piston or the like to engage the clutch and thereby couple the rotating members together. A typical box is supported by the outer casing for rotation therein, but the coupling mechanism is the same. In other words, the coupling mechanism can be supported on one of the rotating members via a roller bearing or the like. However, because it is supported on the rotating member and is generally adjacent to the rotating gearbox 'and because it is used to couple the rotating member, 201204957 is pressurized to the coupling fluid pressure source housing during normal operating conditions. Two ways. The inter-coupled mechanism is subjected to a torsion. For example, when located outside of the coupling mechanism, it must be externally fixed, and there is usually a method for transferring the seeding to use a flexible biting to flex between the outer casing and the coupling mechanism. Establish a flexible tube that is connected to the liquid. & However, this approach has the disadvantage of not having the "anti-rotation" feature. Therefore, in the case of using flexible pipelines, the hydraulic pressure must also be white, and 4^, including anti-rotation protrusions or women's wear for the gearbox and the stable coupling mechanism of the casing. Deconstruction. In this case, the coupling mechanism and the gearbox are required to make the parts of the hydraulic accumulator in a specific way, and the parts are 0, and the sound shape is &&& The complexity of the hydraulic coupler known in the art and its manufacturing costs. Another way to transfer pressurized hydraulic fluid to the engagement mechanism is to provide a non-rotational aspect using the rigid tubing from the outer casing extension of the wire-bonding mechanism and to assist the light-fitting mechanism against the torque applied through the system. However, because this practice is also “hard”, all associated pores and mounting points of the liquid path must be accurately positioned. A slight deviation of the pore position relative to the design can create difficulties during the manufacturing process. This situation adds to the cost associated with both the manufacturing enclosure and the coupling mechanism. In addition, it also complicates the assembly of the device. Thus, there is a need in the art for a hydraulic coupler having a liquid path that is flexible and self-adjusting such that the corresponding apertures formed in the outer and face mechanisms do not have to be positioned extremely accurately. In addition, there is a need in the art for a hydraulic coupler having a liquid path, 201204957. The liquid path has an anti-rotational state to eliminate the need to rotate the protrusion or to mount the face & mechanism to the outer casing. Other special needs of the organization. Additionally, there is a need in the art for a fluid path and a hydraulic coupler that takes into account the apparent misalignment of the interior of the liquid path. SUMMARY OF THE INVENTION The present invention overcomes the shortcomings of prior art flawless techniques in hydraulic couplers for use in including a pair of rotating members. The hydraulic clutch includes an outer casing in fluid communication with a supply of pressurized fluid. The gearbox is rotated and operatively coupled to the rotating member via a shell. The light-spinning mechanism is non-rotatably supported in the outer casing and adjacent to the teeth. Mu State welcomes the phase of the wheel. The coupling mechanism is operable to selectively couple a pair of rotating members. The liquid path extends between the shell and the cake. The liquid path includes a first aperture + a plurality of bearings formed in the outer casing and having a first diameter and a longitudinal axis and an aperture formed in the coupling mechanism. The first part of the hard 嵘 buy beta 绖 is made up of the first aperture in the peripheral, the diameter of the first part is smaller... The first diameter of the angstrom aperture is bounded = the whole (four)' so that the hard pipe can respond to the first and the first The two pores are moved to align with the longitudinal wheel line. In addition, the hard pipe includes a portion of the body that is frictionally woven with the first aperture of the coupling mechanism and is also received by the sealing soil so that the hard dam is provided; the first ridge is provided for resistance to the torsion applied to the coupling mechanism. A wide range of hydraulic couplers provide a liquid path that is flexible and self-adjusting so that the corresponding holes formed in the housing and the coupling machine 201204957 do not have to be positioned extremely accurately. Additionally, the hydraulic coupler of the present invention has a liquid path that is resistant to rotation to eliminate the need to counter the rotating projections or other specific mechanisms for mounting the coupling mechanism to the housing. Accordingly, the hydraulic coupler of the present invention has a fluid path that takes into account significant misalignment between the internal mounting point of the liquid path and the external mounting point while providing it with anti-rotation features. Other objects, features and advantages of the present invention will become apparent from the <RTIgt; A representative embodiment of a hydraulic coupler for use in a carrier drive train is generally indicated at 10 in Figure 1, wherein like numerals are used throughout the drawings to indicate similar structures. Those skilled in the art will recognize that a hydraulic coupler can be used as part of a gearbox that operatively couples the front and rear axles of the vehicle; as a limited slip differential or lock differential for coupling the axle axles One part of the device; and other applications commonly found in such a technology in the vehicle drive train. Therefore, those skilled in the art will understand from the following description, which is intended to illustrate one embodiment of the invention and is not intended to be limited. As described above, the hydraulic clutch 10 is used in a carrier drive train including a pair of rotating members. To this end, the hydraulic coupler includes a housing, one half of which is generally indicated at 12, which is in fluid communication with a pressurized fluid supply source as schematically illustrated at 14 in Figures 1-2. The pressurized fluid supply 14 may include a primary pump to lubricate and cool various components of the 201204957 carrier drive train or any other suitable pressurized hydraulic fluid supply as generally known in the art. The gear wheel, generally indicated at 16 , is supported by the peripheral 12 to rotate therein. For this purpose, the gearbox can be driven via a pinion via the drive axle or the carrier rear drive shaft, as the case may be. A pinion gear 18, 20 is also mounted for rotation with each of the rotating members in the gearbox bore 6. Accordingly, each of the pair of side gears 18, 20 includes a groove inner diameter 22, 24 that is adapted to engage a corresponding pin groove (not shown) on the rotating member. In the representative embodiment illustrated in these figures, the hydraulic coupler also charges the differential $. However, as described above, the hydraulic coupler 1 of the present invention is not limited to this particular application. In any event, the cross pin 26 is fixedly mounted with the ω wheel box 16 rotated therewith. A pair of pinion gears 28 are mounted to travel in a cruciform relationship and in meshing relationship with the gear teeth formed on each of the -to-side gears 18, 20. The side gears 18, 20 cooperate with the pinion gear 28 to provide differential rotation between the rotating members generally known in the art. The hydraulic coupler 10 of the present invention includes a fitting mechanism that is generally indicated by 3'. its non-rotatable branch within the outer casing 12 and adjacent to the gear loosening mechanism 30 is operable to selectively rotate the pair of rotating members Light:: "From this situation, the hydraulic clutch 1 of the present invention can be used to stop the second or lock differential. Therefore, the light fitting mechanism (7) of the present invention is operable to allow in some cases The pair of rotating members rotate relative to each other and lock the rotating members together under other operating conditions. For this reason, the clutch assembly of the hydraulic coupler of the present invention having the side gears 1 8 10 also includes substantially 3 2 The indication, 20 can be rotated at different speeds 201204957 open position and the hydraulic coupler 1 is locked so that the side gears 18, 2〇 are rotated at substantially the same speed. The coupling mechanism 30 includes a housing 34 and is movably supported A piston 36 within the outer casing 34. The piston 36 and outer casing 34 are used to define an expandable chamber 38 therebetween. As described in more detail below, the expandable chamber 38 is in fluid communication with the pressurized fluid supply 14. The coupling mechanism 3 〇之The outer casing 34 may also include a purge fitting 4 通常 generally known in the art for purifying air once when initially filling the system. More specifically, the clutch assembly 32 includes a plurality of annular plates 42 in which The outer diameter pin slot is coupled to the gearbox 16 . Additionally, the clutch assembly 32 includes a plurality of annular friction disks 44 that are coupled to one of the pair of side gears 18 or 20 at their inner diameter slots. In a representative embodiment, the annular friction disk 44 is coupled to the side gear 2〇 at its inner diameter slot. However, it will be understood by those skilled in the art that the annular friction disk 44 can be via either a side gear 丨 8 or 2 One or both are supported for rotation. When the clutch assembly 32 is in its open position, the plurality of annular plates 42 and annular friction disks 44 are staggered with each other and are used to rotate in substantially non-contact relationship over each other. =, when the clutch assembly 32 is in its closed position, the annular plate 42 and the friction disk 44 can be axially displaced after their bolted grooves are interconnected to frictionally spray against each other, thereby reducing the relationship between the annular plate 42 and the disk 44. Relative rotation. Therefore, away from When the assembly 32 is in its closed position, the side gears 18, 2, 0, 0, clutch assembly 32 include a transmission pin 46 extending between the piston 36 and the plurality of interleaved rings and friction discs 44. As described in more detail below
遞銷46回應於活塞36之移動以將離合器總成32 J 位置移動至其閉合位置。 〃 4啟 201204957 本發明之液壓紅人 路徑，其與加壓液徂：、：〇亦包括大體以48指示之液體 3〇之門延伸士八心源14連通且在外殼12與耦合機構 30之間延伸。如圖3及圖 大體以50指示之第一Μ最佳展不，液體路徑48包括 士 ,一 第一孔隙，其形成於外殼12中且具有宽 一直徑及縱向車由線a。另认 、 卜，液體路徑48包括第二孔隙52, 其形成於耦合機構3〇中。 ， 11下文更詳細描述，硬質管道5 4 在第一孔隙5〇與第二孔隙52之間延伸。 *更具體言之，硬質管道54具有I部分％，其經由外 忒12中之第一孔隙5 〇 1甲且直徑小於第一孔隙5 0之第一 直徑。因此’硬質管道之第一部分56及第一孔隙5〇之第 Γ直徑界定調整間隙G。如圖4所示，此間隙G幫助硬質 …回應於第-及第二孔隙5G、52之間的未對準而移 動出與縱向軸線A對準。硬質管道54亦包括第二部分58， 其與输'.合機構3 〇 Φ夕笛-3丨姐、c 1 Λ f之第一孔隙52摩擦嚙合而被密封地收 、.内如下文中將更詳細描述，因為其相對硬度，故硬質管 道54提供對施加於耦合機構3〇上之扭力之抗性。 繼續參考圖3及圖4，外殼12中之第一孔隙5〇包括入 口 60及出口 62，其中縱向軸線A在其之間延伸。外殼12 亦包括則腔室64，其具有鄰近於第—孔隙5〇之入口 60而 界定之基座66。前腔室64之直徑大於第一孔隙5〇之第一 直徑。硬質管道54包括頭部68，其收納於前腔室64中與 基座66呈鄰接關係且鄰近於第一孔隙之入口 60。更具體言 之’硬質管道54之第一部分56包括環形凸肩7〇及安置於 環形凸肩7〇與外殼12之間的密封構件72。凸肩70圍繞硬 201204957 質管道54之頭部68環形地延 命脓74 —糾姓从 凸肩7〇界定環形、U形 二腔74。密封構件72可包括 ^ Λ, ττ ^ 形衣、墊圈或其類似物，其 收納於環形U形空腔74中 | 關俜而容番A , ”則腔室64之基座66呈密封 關係而文置。為此，液體路徑 W『包括扣件7 6，其相射 於松封構件72圍繞凸肩7〇而 m ^ ^ ΒΛ ^ ^ 女置以便將頭部68及凸肩70 = 之基座66鄰接且密封接觸。扣… ，自包括扣％、併緊螺帽、壓入配合環或其類似物之群。 ,^ 时％减到’為此目的，可利用 先則技術中通常已知之任何適合扣件。 液體路徑48亦包括至少一宓 … /在封構件78,其安置在硬質 4之第二部分58與形成於耦合機構30中之第二孔隙 門更-體σ之且在本文所說明之代表性具體實例 中’密封構件可包括一系列密封構件78，其圍繞硬質管道 54之第一部分58之外圓周相對於彼此呈縱向間隔關係而安 置。為此，第二孔隙52可包括一系列環形槽8〇,其中密封 構件78中之每一者安置於環形槽8〇中與硬質管道之第 二部分，58鄰接密封接觸。第二孔隙_立可膨脹腔室38 與加壓液供應源14之間的液體連通。因此，活塞％可回 應於由可膨脹腔室38中之加壓液產生之偏壓自離合器總成 32處於其開啟位置之第一位置移動至活塞％移動傳遞銷 46且因此移動離合器總《32至,】達其閉合位置以致側齒輪 18、20 —起旋轉之第二位置。 因為硬質管道54之第一部分56與第一孔隙5〇之間所 界定的調整間隙，本發明之液體路徑48具有可撓性及自行 12 201204957 調整性。因此，形成於外殼12及耦合機構3〇中之第一及 第二孔隙50 ' 52不必須極其精確地定位。圖4中最佳說明 此調整能力，其中展示硬質管道54相對於縱向軸線A歪 斜。以此方式，具有考慮到液體路徑48之内部安裝點與外 部安裝點之間顯著未對準之液體路徑48的本發明之液壓耦 合器1〇顯著降低此裝置之製造成本。另外，因為管道54 為硬質的，所以第一與第二孔隙5〇、52之間建立之液體路 徑抵抗耦合機構30之外殼34相對於齒輪箱16之相對旋 轉。因此，此特徵用以消除對抗旋轉突出部或用以將搞合 機構30安裝至外殼12之其他特定機構之需要。因此，本 發明之液壓耦合器10之製造成本進一步降低。 本發明已極詳細描述於上述說明書中，且咸信-般孰 習此項技術者H於對本說明f之閱讀及理解將易於想到^ 發明之各種變化及修改。意欲所有該等變化及修改包括於 本發明中，如同其亦. 、 T在匕附申請專利範圍之範疇内一般。 【圖式簡單說明】 圖1為本發明之液壓耦合器之橫截面側視圖； 圖為本电明之液麼轉合器之部分橫截面側視圖，其 說明搞合機構及液體路經· 圖3為本發明之液體路徑之放大橫截面側視圖；及 圖 4為本發明之游μ 夜體路徑之放大橫截面，其說明處於 歪斜位置之硬質管道。 ' 13 201204957 【主要元件符號說明】 10 液壓耦合器 12 外殼 14 加壓液供應源 16 齒輪箱 18 側齒輪 20 側齒輪 22 栓槽内徑 24 栓槽内徑 26 十字銷 28 小齒輪 30 耦合機構 32 離合器總成 34 外殼 36 活塞 38 可膨脹腔室 40 淨化配件 42 環形板 44 環形摩擦盤 46 傳遞銷 48 液體路徑 50 第一孔隙 52 第二孔隙 54 硬質管道 14 201204957 56 硬質管道之第一 部分 58 硬質管道之第二 部分 60 入口 62 出口 64 前腔室 66 基座 68 頭部 70 環形凸肩 72 密封構件 74 環形U形空腔 76 扣件 78 密封構件 80 環形槽 A · 縱向軸線 G 間隙 15The delivery 46 is responsive to movement of the piston 36 to move the clutch assembly 32J position to its closed position. 〃 4 启 201204957 The hydraulic red man path of the present invention, which is connected to the pressurized liquid 徂:, 〇, and the liquid, which is generally indicated by 48, is connected to the outer core 14 and is coupled to the outer casing 12 and the coupling mechanism 30. Extended between. 3 and the first preferred embodiment generally indicated at 50, the liquid path 48 includes a first aperture formed in the outer casing 12 and having a wide diameter and a longitudinal vehicle line a. It is also known that the liquid path 48 includes a second aperture 52 formed in the coupling mechanism 3A. As described in more detail below, the rigid conduit 5 4 extends between the first aperture 5 〇 and the second aperture 52. * More specifically, the hard conduit 54 has a portion I percent that passes through the first aperture 5 in the outer bore 12 and has a diameter that is less than the first diameter of the first aperture 50. Thus, the first portion 56 of the rigid conduit and the first diameter of the first aperture 5'' define the adjustment gap G. As shown in Figure 4, this gap G helps the hard ... to move out of alignment with the longitudinal axis A in response to misalignment between the first and second apertures 5G, 52. The rigid duct 54 also includes a second portion 58 which is frictionally engaged with the first aperture 52 of the ' 合 3 、 夕 夕 、 、 、 、 、 、 、 、 、 、 、 、 、 、 . . . . . . . . . . Detailed description, because of its relative stiffness, the rigid conduit 54 provides resistance to the torsional forces applied to the coupling mechanism 3〇. With continued reference to Figures 3 and 4, the first aperture 5 in the outer casing 12 includes an inlet 60 and an outlet 62 with a longitudinal axis A extending therebetween. The outer casing 12 also includes a chamber 64 having a base 66 defined adjacent the inlet 60 of the first aperture 5. The diameter of the front chamber 64 is greater than the first diameter of the first aperture 5〇. The rigid conduit 54 includes a head 68 that is received in the front chamber 64 in abutting relationship with the base 66 and adjacent to the inlet 60 of the first aperture. More specifically, the first portion 56 of the rigid conduit 54 includes an annular shoulder 7〇 and a sealing member 72 disposed between the annular shoulder 7〇 and the outer casing 12. The shoulder 70 extends circumferentially around the head 68 of the hard 201204957 conduit 54 to define a ring-shaped, U-shaped two-chamber 74 from the shoulder 7〇. The sealing member 72 may include a Λ, ττ^ garment, a gasket or the like, which is received in the annular U-shaped cavity 74, and the base 66 of the chamber 64 is in a sealed relationship. For this purpose, the liquid path W includes a fastener 7 6 that is incident on the loosening member 72 around the shoulder 7 and m ^ ^ ΒΛ ^ ^ to place the head 68 and the shoulder 70 = The seat 66 is adjacent and in sealing contact. The buckle... is included in the group of the buckle, the tightening nut, the press-fit ring or the like. The amount of % is reduced to 'for this purpose, and the prior art is usually used. Any suitable fastener is also known. The liquid path 48 also includes at least one 宓 ... / in the sealing member 78 disposed between the second portion 58 of the hard 4 and the second louver gate formed in the coupling mechanism 30. In a representative embodiment illustrated herein, the 'seal member' can include a series of sealing members 78 disposed about the outer circumference of the first portion 58 of the rigid conduit 54 in a longitudinally spaced relationship relative to each other. To this end, the second aperture 52 can A series of annular grooves 8〇 are included, wherein each of the sealing members 78 is disposed in the annular groove 8 The second portion of the hard conduit is in abutting sealing contact. The second orifice _ the vertical fluid chamber 38 is in fluid communication with the pressurized fluid supply source 14. Thus, the piston % is responsive to the expandable chamber 38. The bias generated by the pressurized fluid moves from the first position in which the clutch assembly 32 is in its open position to the piston % shift transfer pin 46 and thus moves the clutch total "32" to its closed position so that the side gears 18, 20 - a second position of rotation. Because of the adjustment gap defined between the first portion 56 of the rigid conduit 54 and the first aperture 5, the liquid path 48 of the present invention has flexibility and self-regulation 12 201204957. The first and second apertures 50' 52 in the outer casing 12 and the coupling mechanism 3A do not have to be positioned extremely accurately. This adjustment capability is best illustrated in Figure 4, wherein the rigid conduit 54 is shown skewed relative to the longitudinal axis A. In this manner, the hydraulic coupler 1 of the present invention having a liquid path 48 that allows for a significant misalignment between the internal mounting point of the liquid path 48 and the external mounting point significantly reduces the manufacturing cost of the device. Additionally, because the conduit 54 is rigid, the liquid path established between the first and second apertures 5, 52 resists relative rotation of the outer casing 34 of the coupling mechanism 30 relative to the gearbox 16. Thus, this feature is used to eliminate confrontation The need to rotate the projection or to mount the engagement mechanism 30 to other specific mechanisms of the outer casing 12. Accordingly, the manufacturing cost of the hydraulic coupler 10 of the present invention is further reduced. The present invention has been described in great detail in the above description, and is salty. </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; It is generally within the scope of the patent application. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional side view of a hydraulic coupler of the present invention; FIG. 1 is a partial cross-sectional side view of the liquid coupling of the present invention, illustrating the engagement mechanism and the liquid path. An enlarged cross-sectional side view of the liquid path of the present invention; and Figure 4 is an enlarged cross section of the travel path of the present invention illustrating a rigid conduit in a skewed position. ' 13 201204957 【Main component symbol description】 10 Hydraulic coupler 12 Housing 14 Pressurized fluid supply source 16 Gearbox 18 Side gear 20 Side gear 22 Bolted groove inner diameter 24 Bobbin inner diameter 26 Cross pin 28 Pinion 30 Coupling mechanism 32 Clutch assembly 34 Housing 36 Piston 38 Expandable chamber 40 Purification fitting 42 Annular plate 44 Annular friction disk 46 Transfer pin 48 Liquid path 50 First aperture 52 Second aperture 54 Hard pipe 14 201204957 56 The first part of the hard pipe 58 Hard pipe Second part 60 inlet 62 outlet 64 front chamber 66 base 68 head 70 annular shoulder 72 sealing member 74 annular U-shaped cavity 76 fastener 78 sealing member 80 annular groove A · longitudinal axis G gap 15