WO2022017550A2 - 液压换挡拨叉总成和双离合变速器的换挡执行机构 - Google Patents

液压换挡拨叉总成和双离合变速器的换挡执行机构 Download PDF

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Publication number
WO2022017550A2
WO2022017550A2 PCT/CN2021/128175 CN2021128175W WO2022017550A2 WO 2022017550 A2 WO2022017550 A2 WO 2022017550A2 CN 2021128175 W CN2021128175 W CN 2021128175W WO 2022017550 A2 WO2022017550 A2 WO 2022017550A2
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Prior art keywords
hydraulic
partition
oil inlet
shift fork
hydraulic chamber
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Ceased
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PCT/CN2021/128175
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English (en)
French (fr)
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WO2022017550A3 (zh
Inventor
戚超乾
冯晓崇
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Priority to CN202180101613.2A priority Critical patent/CN117980632A/zh
Priority to PCT/CN2021/128175 priority patent/WO2022017550A2/zh
Publication of WO2022017550A2 publication Critical patent/WO2022017550A2/zh
Publication of WO2022017550A3 publication Critical patent/WO2022017550A3/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure

Definitions

  • the present application relates to auto parts, and in particular, to a hydraulic shift fork assembly and a shift actuator of a dual clutch transmission.
  • CN105443745A discloses a shift actuator of a dual-clutch transmission, which includes a connecting plate, a shift fork shaft and at least two shift fork assemblies, the at least two shift fork assemblies are mounted on the same shift fork shaft, each Each fork assembly is driven by a hydraulic cylinder arranged on the connecting plate respectively.
  • CN105443746A (also refer to US20170248231A1) discloses a shift actuator of a dual clutch transmission, which includes a front housing, a rear housing, at least two hydraulic cylinders and at least one connecting sleeve, the at least two hydraulic cylinders are installed The front and rear ends are clamped between the front casing and the rear casing on the same straight line.
  • Each hydraulic cylinder is installed with a fork assembly, a fork positioning seat and two piston rings.
  • the two piston rings are installed in the hydraulic cylinder and are respectively disposed adjacent to both ends of the hydraulic cylinder, and the fork positioning seat is installed in the hydraulic cylinder and located between the two piston rings.
  • the shift fork assembly includes a shift fork and a positioning plate, the positioning plate extends from the outside of the hydraulic cylinder into the hydraulic cylinder, and the positioning plate is located between the two piston rings and forms a stop position with the fork positioning seat Matching; every two adjacent hydraulic cylinders are connected together by one of the connecting sleeves, and a first hydraulic cavity is formed between the piston ring at one end of each hydraulic cylinder close to the connecting sleeve and the connecting sleeve, and the connecting sleeve is There is a first oil passage communicated with the first hydraulic chamber; a second hydraulic chamber is formed between the piston ring at one end of the hydraulic cylinder connected to the front housing close to the front housing and the front housing, and the front housing is provided with a second hydraulic chamber.
  • a second oil passage that communicates with the second hydraulic chamber; a third hydraulic chamber is formed between the piston ring at one end of the hydraulic cylinder connected to the rear casing near the rear casing and the rear casing. There is a third oil passage communicating with the third hydraulic chamber.
  • a hydraulic shift fork assembly which includes:
  • a hydraulic chamber housing which has a partition for isolating the hydraulic chamber, and a first oil inlet and outlet hole and a second oil inlet and outlet holes located on both sides of the partition;
  • the partition is inclined, bent or bent, so that the axial distance between the most distal ends of the first oil inlet and outlet holes and the second oil inlet and outlet holes in the axial direction of the hydraulic chamber housing is less than, The sum of the axial length of the first oil inlet and discharge holes, the axial length of the second oil inlet and discharge holes and the minimum wall thickness of the partition.
  • the first oil inlet and discharge holes and the second oil inlet and discharge holes at least partially overlap in the axial direction of the hydraulic chamber housing.
  • the hydraulic chamber casing is generally cylindrical, and the first oil inlet and discharge holes and the second oil inlet and discharge holes are arranged staggered in the circumferential direction of the hydraulic chamber casing.
  • the partition is in the shape of a step
  • the partition includes a base, a step, and a connecting portion connecting the base and the step, and the base and the step are in the axial direction Stagger settings.
  • the base and the step are flat plates perpendicular to the axial direction.
  • the first oil inlet and outlet holes and the second oil inlet and outlet holes are respectively at least partially accommodated in the two C-shaped parts of the S-shaped partition.
  • the partition is in the shape of a flat plate and is disposed obliquely with respect to the axial direction of the hydraulic chamber housing.
  • the partition is in the shape of a plate with uniform thickness.
  • the piston includes a sealing member disposed at an axial end thereof, the partition forming an axial stop for the piston.
  • the hydraulic chamber housing is an injection-molded or die-cast integral piece.
  • the peripheral wall of the hydraulic chamber housing is provided with two hydraulic chamber finger holes,
  • Each of the shifting forks includes a shifting finger and two fork legs connected to the shifting finger, wherein the two shifting fingers pass through the two hydraulic chamber finger shifting holes respectively and are connected to the two shifting fingers piston.
  • the finger when the piston moves axially, the finger is not in contact with the hole wall of the finger hole of the hydraulic chamber.
  • the hydraulic shift fork assembly further includes a shift fork shaft, and the two shift forks are axially slidably sleeved on the shift fork shaft,
  • the hydraulic chamber housing further includes two spring positioning seats protruding radially from both axial ends of the hydraulic chamber housing, the spring positioning seats being fixed to the fork shaft.
  • a shift actuator of a dual clutch transmission is also provided, which includes the hydraulic shift fork assembly according to the present application.
  • Figure 1 is a schematic cross-sectional view of a possible hydraulic shift fork assembly.
  • FIG. 2 is a schematic cross-sectional view of a hydraulic shift fork assembly according to an embodiment of the present application.
  • FIG. 3A is a partial enlarged view of FIG. 1
  • FIG. 3B is a partial enlarged view of FIG. 2 .
  • FIG. 4 is a perspective view of a hydraulic shift fork assembly according to one embodiment of the present application.
  • FIG. 5 is a schematic structural diagram near the partition of the hydraulic chamber housing of the hydraulic shift fork assembly according to another embodiment of the present application.
  • FIGS 6A and 6B are schematic structural diagrams near the partition of the hydraulic chamber housing of the hydraulic shift fork assembly according to still another embodiment of the present application, wherein the section line of the partition is not shown.
  • FIG. 7 is a schematic structural diagram near the partition of the hydraulic chamber housing of the hydraulic shift fork assembly according to still another embodiment of the present application.
  • a hydraulic chamber housing 10 is used, and each of the two hydraulic chambers 11 and 12 of the hydraulic chamber housing 10 has a piston 20, and two The shifting fingers 41 of each shifting fork 40 pass through the finger shifting holes 13 in the hydraulic chamber and extend into the piston grooves of the pistons 20 in the hydraulic chambers 11 and 12 .
  • the shift fork 40 is driven to perform the shifting operation by hydraulically driving the piston 20 .
  • Each shifting finger 41 and the sealing member 30 at both ends of each piston 20 (usually, also referred to as oil seals) need to be provided with two left and right shift strokes, and the strokes cannot overlap each other. More specifically, the movement range of the finger 41 cannot exceed the axial extension range of the finger hole 13 of the hydraulic chamber, and the sealing member 30 cannot move into the finger hole 13 of the hydraulic chamber.
  • a partition 14 is arranged between the two hydraulic chambers 11 and 12 , and oil inlet and outlet holes 11H and 12H are arranged on both sides of the partition 14 .
  • the partition 14 is provided in the shape of a flat plate. The strokes of the oil inlet and discharge holes 11H, 12H and the piston 20 cannot overlap.
  • the above solution may have the following problems.
  • the hydraulic shift fork assembly may include a hydraulic chamber housing 10 , two pistons 20 and two forks 40 .
  • the hydraulic chamber housing 10 may be substantially cylindrical, in particular, formed in a straight cylindrical shape.
  • the hydraulic chamber housing 10 has a partition 14 for isolating the hydraulic chambers. More specifically, the partition 14 defines two hydraulic chambers 11 and 12 in the hydraulic chamber housing 10 .
  • Two pistons 20 are arranged in the hydraulic chamber housing 10 and located on both sides of the partition 14 , more specifically, the two pistons 20 are arranged in the two hydraulic chambers 11 and 12 respectively.
  • the two forks 40 are respectively connected with the two pistons 20 to be driven by the two pistons 20 respectively.
  • the hydraulic chamber housing 10 may include two hydraulic chamber finger holes 13 formed in the housing peripheral wall of the hydraulic chamber housing 10 in the two hydraulic chambers 11 and 12 respectively.
  • Each shifting fork 40 may include a shifting finger 41 and two fork feet 43 connected with the shifting finger 41 , wherein the two shifting fingers 41 can be respectively connected to, especially fixed, through the two hydraulic chamber finger holes 13 . Connected to the two pistons 20 .
  • the two hydraulic chambers 11, 12 may include a first chamber 11A formed between one of the two pistons 20 (the left piston 20 in FIG. 2) and the partition 14 and formed In the second chamber 12A between the other of the two pistons 20 (piston 20 on the right in FIG. 2 ) and the partition 14 , the hydraulic chamber housing 10 may include a first chamber 11A communicating with the first chamber 11A.
  • the oil intake and discharge holes 11H and the second oil intake and discharge holes 12H communicate with the second chamber 12A.
  • the partition 14 can be bent and arranged so that the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H overlap with the partition 14 in the axial direction A of the hydraulic chamber housing 10 .
  • the axial distance between the most distal ends of the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H in the axial direction A of the hydraulic chamber housing 10 can be smaller than the axial distance of the first oil inlet and discharge holes 11H.
  • first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H may at least partially overlap in the axial direction A of the hydraulic chamber housing 10 .
  • the partition 14 may be stepped, and the partition 14 may include a base 141 , a step 142 , and a connecting portion 143 connecting the base 141 and the step 142 .
  • the base 141 is located on the axial side (left side in FIG. 2 ) of the step 142 , in other words, the base 141 and the step 142 are at least partially offset in the axial direction A.
  • the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H are located on both sides of the partition 14 and are arranged adjacent to the partition 14. 14 overlaps in axis A.
  • the overlapping of the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H with the partition 14 in the axial direction A includes that, in the hydraulic chamber housing 10, the first oil inlet and discharge holes 11H partially overlap with the partition 14 and/or Or the second oil inlet and discharge hole 12H partially overlaps with the partition 14 .
  • the overlapping of the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H with the partition 14 in the axial direction A may mean that in the hydraulic chamber housing 10 , the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 11H and The bore 12H occupies the same axial section of the hydraulic chamber housing 10 as the partition 14 .
  • the first oil inlet and outlet holes 11H and the second oil inlet and outlet holes 12H and the partition 14 exist Overlap or occlude.
  • the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H can be arranged staggered in the circumferential direction of the hydraulic chamber housing 10 , which facilitates the cooperation with the bent partition 14 and reduces the number of partitions 14 and 12 .
  • the partition 14 is a flat plate, the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H are located on both axial sides of the partition 14, and the oil inlet and outlet holes
  • the axial length L1 occupied by the partition 14 is approximately the sum of the diameters of the two oil inlet and discharge holes plus the wall thickness of the partition 14 .
  • the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H overlap with the partition 14 in the axial direction A.
  • the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H completely overlap with the partition 14 in the axial direction A, that is, the first oil inlet and discharge holes 11H do not exceed the base of the partition 14 on one axial side 141, the second oil inlet and discharge hole 12H does not exceed the step 142 of the partition 14 on the other side in the axial direction.
  • the axial length L2 occupied by the oil inlet and outlet holes and the partition 14 is approximately equal to the diameter of one oil inlet and outlet hole plus the wall thickness of the partition 14 .
  • L2 is smaller than L1
  • the solution shown in FIG. 3B can reduce the axial length of the hydraulic shift fork assembly, so that the structure of the hydraulic shift fork assembly is more compact.
  • the base 141 and the step 142 may be flat plates perpendicular to the axial direction A. As shown in FIG.
  • the partition 14 may be in the shape of a plate with a uniform thickness.
  • the connecting portion 143 can connect the base 141 and the step 142 in a smooth transition.
  • the structure of the partition 14 is simple, the manufacture is convenient, and the stress concentration position is not easy to appear.
  • the piston 20 may include a sealing member 30 disposed at its axial end, and the partition 14 may form an axial stop for the piston 20, so that when the piston 20 abuts the partition 14, more specifically , when abutting against the base 141 or the step 142, the sealing member 30 is connected to the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H (more specifically, the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 11H and 12H).
  • the oil hole 12H (opening formed on the inner peripheral surface of the hydraulic chamber case 10 ) does not overlap.
  • the axial stop of the piston 20 can be realized by the partition 14 to prevent the oil inlet and outlet holes from scratching the sealing member 30 .
  • the hydraulic chamber housing 10 may be an injection-molded or die-cast integral piece.
  • the hydraulic chamber housing 10 may be injection-molded from engineering plastics, or the hydraulic chamber housing 10 may be die-casted from a metal such as aluminum.
  • the hydraulic chamber housing 10 is one piece, which reduces the number of components, reduces the assembly work of multiple components, and facilitates the realization of the sealing of the hydraulic chamber.
  • the hydraulic chamber housing 10 can be integrally formed by injection molding or die casting at low cost.
  • hydraulic chamber housing 10 by injection molding or die casting does not preclude possible or necessary subsequent processing, for example, possible or necessary machining of the aluminum hydraulic chamber housing 10 .
  • the finger 41 may not be in contact with the hole wall of the finger hole 13 of the hydraulic chamber. This prevents the finger 41 from hitting the hole wall of the finger hole 13 of the hydraulic chamber, can avoid or reduce the deformation or damage of the housing 10 of the hydraulic chamber, ensure sealing, and reduce leakage of liquid (for example, hydraulic oil).
  • liquid for example, hydraulic oil
  • the hydraulic shift fork assembly may further include a shift fork shaft 60 , and the two shift forks 40 may be axially slidably sleeved on the shift fork shaft 60 .
  • the hydraulic chamber housing 10 may further include two spring positioning seats 15 extending radially from both axial ends of the hydraulic chamber housing 10 , and the spring positioning seats 15 may be fixed to the shift fork shaft 60 . In this way, the positioning of the hydraulic chamber housing 10 relative to the shift fork shaft 60 can be conveniently achieved, for example, the rotation of the hydraulic chamber housing 10 relative to the shift fork shaft 60 can be prevented.
  • the hydraulic shift fork assembly may further include a position sensor for determining the position of the fork 40 , the position sensor may be a magnetic sensor, and a part 51 of the magnetic sensor may be mounted to the two fork feet 43 .
  • the connecting portion 44, the other portion 52 of the magnetic sensor may be mounted to the hydraulic chamber housing 10 or other suitable location for a shift actuator or dual clutch transmission including the hydraulic shift fork assembly, for example, relative to a dual clutch transmission the fixed position of the housing.
  • the shift fork 40 may include: a sleeve 42 formed at the connecting portion 44; two prongs 43 protruding from the connecting portion 44; Refers to 41.
  • the hydraulic shift fork assembly may further include a first oil pipe joint 11J connected to the first oil inlet and discharge holes 11H and a second oil pipe joint 12J connected to the second oil inlet and discharge holes 12H, the first oil pipe joint 12J
  • the oil pipe joint 11J and the second oil pipe joint 12J may be connected to oil pipes for supplying and discharging oil to and from the first and second chambers 11A and 12A.
  • first oil pipe joint 11J and the second oil pipe joint 12J may be integrally formed with the main body (straight pipe portion) of the hydraulic chamber housing 10 .
  • the hydraulic chamber 11 may further include a third chamber 11B formed on an axial side of one of the two pistons 20
  • the hydraulic chamber 12 may further include another piston formed in the two pistons 20 The fourth chamber 12B on the other side in the axial direction of 20 .
  • a piston 20 When supplying oil to the first chamber 11A or the third chamber 11B, a piston 20 can be moved axially, thereby driving a shift fork 40 (the shift fork 40 on the left in FIG. 2 ) to move axially.
  • the fork feet 43 of the fork 40 can push the synchronizer to realize the shifting operation.
  • the other piston 20 when supplying oil to the second chamber 12A or the fourth chamber 12B, the other piston 20 can be moved axially, thereby driving the other fork 40 (the right fork 40 in FIG. 2 ) to move axially , the fork foot 43 of the other fork 40 can push the synchronizer to realize the shifting operation.
  • the present embodiment also provides a shift actuator of a dual-clutch transmission, which includes the hydraulic shift fork assembly of the present application.
  • the shift actuator may also include other components or structures such as oil pipes and oil pumps.
  • FIG. 5 it shows the structure near the partition 14 of the hydraulic chamber housing 10 of the hydraulic shift fork assembly according to another embodiment of the present application.
  • the partitions 14 are arranged in a curved manner.
  • the partition 14 may be S-shaped, and the first oil inlet and discharge holes 11H and the second oil inlet and discharge holes 12H may overlap with the partition 14 in the axial direction A of the hydraulic chamber housing 10 .
  • the S-shape here refers to an S-shape viewed from a radial direction, and the partition 14 can also be called a wave-shape.
  • first oil inlet and outlet holes 11H and the second oil inlet and outlet holes 12H may be respectively at least partially accommodated in the two C-shaped portions 148 and 149 of the S-shaped partition 14 .
  • the portion may include a flat portion so that there is more contact area with the piston 20 when the piston 20 is stopped.
  • the two oil inlet and outlet holes can be partially or completely overlapped in the axial direction A, or completely staggered.
  • FIG. 5 is only used to illustrate the shape of the partition 14 and the positional relationship with the first oil inlet and outlet holes 11H and the second oil inlet and outlet holes 12H.
  • the partition 14 may be closer to the first oil inlet and outlet holes 11H and the second oil inlet and outlet holes 12H.
  • FIGS. 6A and 6B a structure near the partition 14 of the hydraulic chamber housing 10 of the hydraulic shift fork assembly according to still another embodiment of the present application is shown.
  • the partition 14 is in the shape of a flat plate and is inclined with respect to the axial direction A of the hydraulic chamber housing 10 . (the upper and lower ends in FIGS. 6A and 6B ) are arranged adjacently.
  • the two oil inlet and outlet holes 11H and 12H are staggered by 180 degrees in the circumferential direction of the hydraulic chamber housing 10 , so that the space formed by the inclined partition 14 can be fully utilized.
  • FIG. 7 it shows the structure near the partition 14 of the hydraulic chamber housing 10 of the hydraulic shift fork assembly according to still another embodiment of the present application.
  • This embodiment can be regarded as a modification of the embodiment shown in Fig. 3B.
  • the two oil inlet and outlet holes 11H and 12H are staggered by 180 degrees in the circumferential direction of the hydraulic chamber housing 10 .
  • the second oil inlet and outlet holes 12H on the upper side in FIG. 7 may be replaced by oil inlet and outlet holes shown in dotted circles.
  • a plurality of oil inlet and outlet holes such as two, may be provided for the hydraulic chambers 11 and 12 .
  • the cross section of part or all of the oil inlet and discharge holes 11H and 12H may not be circular, for example, may be elliptical.
  • the manufacturing method of the hydraulic chamber housing 10 is not limited to injection molding or die casting, for example, the hydraulic chamber housing 10 may also be formed by metal machining.
  • the present application is not limited to defining two hydraulic chambers 11 and 12 in the hydraulic chamber housing 10 by one partition 14. In other possible solutions, more hydraulic chambers may be defined by multiple partitions 14, thereby More forks 40 are operated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

液压换挡拨叉总成包括：液压腔壳体(10)，其具有隔断(14)和两个液压腔(11、12)；两个活塞(20)；以及两个拨叉(40)，其分别连接到两个活塞(20)。两个液压腔(11、12)包括第一腔室(11A)和第二腔室(12A)，液压腔壳体(10)包括连通到第一腔室(11A)的第一进排油孔(11H)和连通到第二腔室(12A)的第二进排油孔(12H)。隔断(14)倾斜、弯折或弯曲设置。还提供一种双离合变速器的换挡执行机构。

Description

液压换挡拨叉总成和双离合变速器的换挡执行机构 技术领域
本申请涉及汽车配件，且特别地涉及一种液压换挡拨叉总成和双离合变速器的换挡执行机构。
背景技术
CN105443745A公开了一种双离合变速器的换挡执行机构，其包括连接板、拨叉轴以及至少两个拨叉总成，该至少两个拨叉总成安装在该同一根拨叉轴上，每个拨叉总成分别由设置在连接板上的一个液压缸进行驱动。
在CN105443745A中，由并排设置的两个液压缸分别驱动两个拨叉总成，产品部件多，结构不够紧凑。
CN105443746A(还可以参见US20170248231A1)公开了一种双离合变速器的换挡执行机构，其包括前壳体、后壳体、至少两个液压缸筒以及至少一个连接套，该至少两个液压缸筒安装在同一直线上且前后两端夹紧在该前壳体与该后壳体之间。每个液压缸筒安装有拨叉总成、拨叉定位座及两个活塞环。该两个活塞环安装于液压缸筒内且分别临近液压缸筒的两端设置，该拨叉定位座安装于液压缸筒内并位于该两个活塞环之间。该拨叉总成包括拨叉及定位板，该定位板从液压缸筒外伸入液压缸筒内，且该定位板位于该两个活塞环之间并与该拨叉定位座形成止动定位配合；每相邻的两个液压缸筒之间通过一个该连接套连接在一起，每个液压缸筒靠近连接套一端的活塞环与该连接套之间形成第一液压腔，该连接套设有与该第一液压腔连通的第一油道；与该前壳体相连的液压缸筒靠近前壳体一端的活塞环与该前壳体之间形成第二液压腔，该前壳体设有与该第二液压腔连通的第二油道；与该后壳体相连的液压缸筒靠近后壳体一端的活塞环与该后壳体之间形成第三液压腔，该后壳体设有与该第三液压腔连通的第三油道。
在CN105443746A中，由前壳体、后壳体和连接套将两个液压缸筒连接成一条直线，驱动两个拨叉总成，其部件多，结构复杂。
发明内容
本申请的目的在于克服或至少减轻上述现有技术存在的不足，提供一种结构紧凑的液压换挡拨叉总成和双离合变速器的换挡执行机构。
提供一种液压换挡拨叉总成，其包括：
液压腔壳体，其具有用于隔离液压腔的隔断以及位于所述隔断两侧的第一进排油孔和第二进排油孔；
两个活塞，其设置在所述液压腔壳体中并分别位于所述隔断的两侧；以及
两个拨叉，分别受所述两个活塞驱动，
所述隔断倾斜、弯折或弯曲设置，使得所述第一进排油孔和所述第二进排油孔在所述液压腔壳体的轴向上的最远端的轴向距离小于，所述第一进排油孔的轴向长度、所述第二进排油孔的轴向长度和所述隔断的最小壁厚之和。
在至少一个实施方式中，所述第一进排油孔和所述第二进排油孔在所述液压腔壳体的轴向上至少部分重叠。
在至少一个实施方式中，所述液压腔壳体大体呈筒状，所述第一进排油孔和所述第二进排油孔在所述液压腔壳体的周向上错开地布置。
在至少一个实施方式中，所述隔断呈台阶状，所述隔断包括基台、台阶及连接所述基台和所述台阶的连接部，所述基台与所述台阶在所述轴向上错开设置。
在至少一个实施方式中，所述基台和所述台阶为与所述轴向垂直的平板状。
在至少一个实施方式中，所述第一进排油孔和所述第二进排油孔分别至 少部分地收容在S形的所述隔断的两个C形部内。
在至少一个实施方式中，所述隔断呈平板状并且相对于所述液压腔壳体的轴向倾斜设置。
在至少一个实施方式中，其特征在于，所述隔断为厚度均匀的板状。
在至少一个实施方式中，所述活塞包括设置在其轴向端部的密封构件，所述隔断形成所述活塞的轴向止挡部。
在至少一个实施方式中，所述液压腔壳体为注塑成形或压铸成形的一体件。
在至少一个实施方式中，所述液压腔壳体的周壁设置有两个液压腔拨指孔，
每个所述拨叉均包括拨指和与所述拨指相连的两个叉脚，其中，两个所述拨指分别穿过所述两个液压腔拨指孔而连接到所述两个活塞。
在至少一个实施方式中，在所述活塞轴向移动时，所述拨指与所述液压腔拨指孔的孔壁不接触。
在至少一个实施方式中，所述液压换挡拨叉总成还包括拨叉轴，所述两个拨叉可轴向滑动地套设于所述拨叉轴，
所述液压腔壳体还包括从所述液压腔壳体的轴向两端沿径向伸出的两个弹簧定位座，所述弹簧定位座固定到所述拨叉轴。
还提供一种双离合变速器的换挡执行机构，其包括根据本申请的液压换挡拨叉总成。
附图说明
图1是一种可能的液压换挡拨叉总成的剖视示意图。
图2是根据本申请的一个实施方式的液压换挡拨叉总成的剖视示意图。
图3A是图1的局部放大图，图3B是图2的局部放大图。
图4是根据本申请的一个实施方式的液压换挡拨叉总成的立体图。
图5是根据本申请的另一实施方式的液压换挡拨叉总成的液压腔壳体的隔断附近的结构示意图。
图6A和图6B是根据本申请的再一实施方式的液压换挡拨叉总成的液压腔壳体的隔断附近的结构示意图，其中，未示出隔断的剖面线。
图7是根据本申请的还一实施方式的液压换挡拨叉总成的液压腔壳体的隔断附近的结构示意图。
具体实施方式
下面参照附图描述本申请的示例性实施方式。
如图1所示，在一种可能的液压换挡拨叉总成中，使用一个液压腔壳体10，该液压腔壳体10的两个液压腔11、12内各有一个活塞20，两个拨叉40的拨指41穿过液压腔拨指孔13，伸入液压腔11、12内的活塞20的活塞槽中。通过液压驱动活塞20来带动拨叉40执行换挡操作。
每个拨指41、每个活塞20两端的密封构件30(通常，还被称为油封)均需要设置左右两段换挡行程，且各段行程不能相互重叠。更具体地，拨指41的移动范围不能超过液压腔拨指孔13的轴向伸展范围，密封构件30不能移动到液压腔拨指孔13中。
在两个液压腔11、12之间设置有隔断14，在隔断14的两侧设置进排油孔11H和12H。隔断14设置成平板状。进排油孔11H、12H与活塞20的行程不能重叠。
上述方案可能存在如下问题。
(i)拨指41及密封构件30的行程和进排油孔11H、12H及隔断14的设置导致，液压腔壳体10的轴向长度较长，不利于液压换挡拨叉总成及双离合变速箱的换挡执行机构紧凑布置。
(ii)活塞20靠近隔断14地压入液压腔11、12时无止挡，装配及使用过程中进排油孔11H、12H存在刮伤密封构件30的风险。
考虑到上述问题而进一步提出如下实施方式。
应当理解，虽然上面描述了图1所示的液压换挡拨叉总成的一些缺点，但是其至少部分方面或特征相对于一些现有技术仍然是新颖性和具有优势的，图1及上面的描述仍构成本申请的创新的实施方案的一部分。
(第一实施方式)
参照图2和图4，下面描述本申请的一个实施方式的液压换挡拨叉总成。
该液压换挡拨叉总成可以包括液压腔壳体10、两个活塞20和两个拨叉40。液压腔壳体10可以大体上呈筒状，特别地，形成为直筒状。并且，液压腔壳体10具有隔断14，隔断14用于隔离液压腔，更具体地，隔断14在液压腔壳体10中限定出两个液压腔11、12。
两个活塞20设置在液压腔壳体10中并位于隔断14的两侧，更具体地，两个活塞20分别设置在两个液压腔11、12中。
两个拨叉40分别与两个活塞20连接而分别受两个活塞20驱动。
作为示例，液压腔壳体10可以包括分别在两个液压腔11、12形成于液压腔壳体10的壳体周壁的两个液压腔拨指孔13。每个拨叉40均可以包括拨指41和与拨指41相连的两个叉脚43，其中，两个拨指41可以分别穿过两个液压腔拨指孔13而连接到，特别是固定连接到两个活塞20。
参照图2和图3B，两个液压腔11、12可以包括形成于两个活塞20中的一个活塞20(图2中左侧的活塞20)和隔断14之间的第一腔室11A和形成于两个活塞20中的另一个活塞20(图2中右侧的活塞20)和隔断14之间的第二腔室12A，液压腔壳体10可以包括连通到第一腔室11A的第一进排油孔11H和连通到第二腔室12A的第二进排油孔12H。
参照图2和图3B，隔断14可以弯折设置，使得第一进排油孔11H和第二进排油孔12H与隔断14在液压腔壳体10的轴向A上重叠。
这里，可以使第一进排油孔11H和第二进排油孔12H在液压腔壳体10的轴向A上的最远端的轴向距离小于，第一进排油孔11H的轴向长度、第二进 排油孔12H的轴向长度和隔断14的最小壁厚之和。
这里，可以使第一进排油孔11H和第二进排油孔12H在液压腔壳体10的轴向A上至少部分重叠。
具体地，在本实施方式中，隔断14可以呈台阶状，隔断14可以包括基台141、台阶142及连接基台141和台阶142的连接部143。在液压腔壳体10的轴向A上，基台141比台阶142靠轴向一侧(图2中的左侧)，换言之，基台141和台阶142在轴向A上至少部分地错开。第一进排油孔11H和第二进排油孔12H位于隔断14的两侧，与隔断14相邻布置，并且优选地，第一进排油孔11H和第二进排油孔12H与隔断14在轴向A上重叠。
这里，第一进排油孔11H和第二进排油孔12H与隔断14在轴向A上重叠包括，在液压腔壳体10内，第一进排油孔11H与隔断14部分重叠和/或第二进排油孔12H与隔断14部分重叠的情况。
这里，第一进排油孔11H和第二进排油孔12H与隔断14在轴向A上重叠可以指，在液压腔壳体10内，第一进排油孔11H和第二进排油孔12H与隔断14占据液压腔壳体10的相同的轴向区段。或者说，沿液压腔壳体10的至少一个径向观察(例如，沿图2和图3B中的上下方向观察)，第一进排油孔11H和第二进排油孔12H与隔断14存在重叠或遮挡。
参照图3B和图4，第一进排油孔11H和第二进排油孔12H可以在液压腔壳体10的周向上错开地布置，这便于与弯折的隔断14配合，减少隔断14和进排油孔11H、12H占据的轴向空间。
对照图3A和图3B，在图3A所示的方案中，隔断14为平板状，第一进排油孔11H和第二进排油孔12H位于隔断14的轴向两侧，进排油孔和隔断14占据的轴向长度L1大致为两个进排油孔的孔径之和加上隔断14的壁厚。
在图3B中，第一进排油孔11H和第二进排油孔12H与隔断14在轴向A上重叠。特别地，第一进排油孔11H和第二进排油孔12H与隔断14在轴向A上完全重叠，即，第一进排油孔11H在轴向一侧不超出隔断14的基台141，第二进 排油孔12H在轴向另一侧不超出隔断14的台阶142。这样，进排油孔和隔断14占据的轴向长度L2大致为一个进排油孔的孔径加上隔断14的壁厚。
显然，L2小于L1，图3B所示的方案可以减少液压换挡拨叉总成的轴向长度，使液压换挡拨叉总成结构更紧凑。
这里，可选地，基台141和台阶142可以为与轴向A垂直的平板状。
这里，优选地，隔断14可以为厚度均匀的板状。
连接部143可以平滑过渡地连接基台141和台阶142。
这样，隔断14的结构简单，制造方便，不易出现应力集中位置。
参照图2和图3B，活塞20可以包括设置在其轴向端部的密封构件30，隔断14可以形成活塞20的轴向止挡部，从而在活塞20抵接到隔断14时，更具体地，抵接到基台141或台阶142时，密封构件30与第一进排油孔11H和第二进排油孔12H(更具体地，是指第一进排油孔11H和第二进排油孔12H在液压腔壳体10的内周面形成的开口)在所述轴向A上不重叠。
这样，可以由隔断14实现活塞20的轴向止挡，避免进排油孔刮伤密封构件30。
这里，液压腔壳体10可以为注塑成形或压铸成形的一体件。例如，液压腔壳体10可以由工程塑料注塑而成，或者液压腔壳体10可以由例如铝等的金属压铸而成。
液压腔壳体10为一体件，减少了部件的数量，减少了多个部件的组装工作，便于实现液压腔的密封。注塑成形或压铸成形可以低成本地一体成形液压腔壳体10。
可以理解，这里的通过注塑成形或压铸成形形成液压腔壳体10不排除可能或必要的后续加工，例如，对铝制的液压腔壳体10的可能的或必要的机加工。
这里，在活塞20轴向移动时，拨指41与液压腔拨指孔13的孔壁可以不接触。这避免了拨指41撞击液压腔拨指孔13的孔壁，可以避免或减少液压腔壳 体10的变形或损伤，保证密封，减少液体(例如，液压油)泄露。
参照图2和图4，液压换挡拨叉总成可以还包括拨叉轴60，两个拨叉40可以可轴向滑动地套设于拨叉轴60。
液压腔壳体10可以还包括从液压腔壳体10的轴向两端沿径向伸出的两个弹簧定位座15，弹簧定位座15可以固定到拨叉轴60。这样，可以方便地实现液压腔壳体10相对于拨叉轴60的定位，例如，可以防止液压腔壳体10相对于拨叉轴60转动。
参照图4，该液压换挡拨叉总成可以还包括用于确定拨叉40的位置的位置传感器，该位置传感器可以是磁传感器，该磁传感器的一部分51可以安装到两个叉脚43的连接部分44，该磁传感器的另一部分52可以安装到液压腔壳体10或包括该液压换挡拨叉总成的换挡执行机构或双离合变速器的其它适当位置，例如，相对于双离合变速器的壳体固定的位置。
参照图4，拨叉40可以包括：形成于连接部分44处的套筒42；从连接部分44伸出的两个叉脚43；以及从连接部分44远离两个叉脚43地伸出的拨指41。
参照图4，该液压换挡拨叉总成可以还包括连接到第一进排油孔11H的第一油管接头11J和连接到第二进排油孔12H的第二油管接头12J，该第一油管接头11J和第二油管接头12J可以连接用于向第一腔室11A和第二腔室12A供油及从第一腔室11A和第二腔室12A排油的油管。
这里，第一油管接头11J和第二油管接头12J可以和液压腔壳体10的主体(直管部)一体地成形。
参照图2，液压腔11还可以包括形成于两个活塞20中的一个活塞20的轴向一侧的第三腔室11B，液压腔12还可以包括形成于两个活塞20中的另一个活塞20的轴向另一侧的第四腔室12B。
在向第一腔室11A或第三腔室11B供油时，可以使一个活塞20轴向移动，从而带动一个拨叉40(图2中左侧的拨叉40)轴向移动，该一个拨叉40的叉 脚43可以推动同步器实现换挡操作。
同样，在向第二腔室12A或第四腔室12B供油时，可以使另一个活塞20轴向移动，从而带动另一个拨叉40(图2中右侧的拨叉40)轴向移动，该另一个拨叉40的叉脚43可以推动同步器实现换挡操作。
这里，本实施方式还提供一种双离合变速器的换挡执行机构，其包括本申请的液压换挡拨叉总成。
可以理解，除了附图所示及这里描述的液压换挡拨叉总成之外，该换挡执行机构还可以包括油管、油泵等其它部件或结构。
(第二实施方式)
参照图5，其示出了根据本申请的另一实施方式的液压换挡拨叉总成的液压腔壳体10的隔断14附近的结构。
这里，隔断14弯曲设置。作为示例，隔断14可以呈S形，第一进排油孔11H和第二进排油孔12H可以与隔断14在液压腔壳体10的轴向A上重叠。可以理解，这里的S形是指从一个径向观察的S形，该隔断14还可以被称为波浪形。
这里，第一进排油孔11H和第二进排油孔12H可以分别至少部分地收容在S形的隔断14的两个C形部148、149内。
可以理解，这里的S形或C形不必是严格的S形或C形，而是只要是大致S形或C形即可，例如，两个C形部148、149的底部(或称凸出部)可以包括平面部，以便在对活塞20进行止挡时，可以有更多的与活塞20接触的面积。
可以理解，在图3B和图5所示的方案中，两个进排油孔可以在轴向A上部分或完全重叠，或者完全错开。
可以理解，图5仅用于示例性说明隔断14的形状及与第一进排油孔11H和第二进排油孔12H的位置关系。可以对该结构或相应的尺寸进行适当的设计和改变。例如，隔断14与第一进排油孔11H和第二进排油孔12H可以更接近。
(第三实施方式)
参照图6A和图6B，其示出了根据本申请的再一实施方式的液压换挡拨叉总成的液压腔壳体10的隔断14附近的结构。
这里，隔断14呈平板状并且相对于液压腔壳体10的轴向A倾斜设置，第一进排油孔11H和第二进排油孔12H与隔断14的该一个径向R上的两端(图6A和图6B中的上下两端)相邻布置。
在图6A中，沿与该一个径向R垂直的方向观察，该隔断14和进排油孔11H、12H形成“％”形状。
在图6B中，两个进排油孔11H、12H在液压腔壳体10的周向上错开180度，从而可以充分利用倾斜的隔断14所形成的空间。
(第四实施方式)
参照图7，其示出了根据本申请的还一实施方式的液压换挡拨叉总成的液压腔壳体10的隔断14附近的结构。
该实施方式可以被视为图3B所示实施方式的变形。
在一个可选的方案中，两个进排油孔11H、12H在液压腔壳体10的周向上错开180度。
在另一可选的方案中，可以用虚线圆所示的进排油孔代替图7中上侧的第二进排油孔12H。
在仍一可选的方案中，可以为液压腔11、12设置例如两个的多个进排油孔。
当然，本申请不限于上述实施方式，本领域技术人员在本申请的教导下可以对本申请的上述实施方式做出各种变型，而不脱离本申请的范围。这里，进行以下补充说明。
(i)进排油孔11H、12H的部分或全部区域的横截面可以不是圆形，例如可以为椭圆形。
(ii)液压腔壳体10的制造方法不限于注塑或压铸，例如，还可以通过金属机加工形成液压腔壳体10。
(iii)本申请不限于由一个隔断14在液压腔壳体10中限定出两个液压腔11、12，在其它可能的方案中，可以由多个隔断14限定出更多个液压腔，从而操作更多个拨叉40。
附图标记列表
10 液压腔壳体
11、12 液压腔
11A 第一腔室
12A 第二腔室
11B 第三腔室
12B 第四腔室
11H、12H 进排油孔
11J 第一油管接头
12J 第二油管接头
13 液压腔拨指孔
14 隔断
141 基台
142 台阶
143 连接部
148、149 C形部
15 弹簧定位座
20 活塞
30 密封构件
40 拨叉
41 拨指
42 套筒
43 叉脚
44 连接部分
60 拨叉轴
A 轴向

Claims (14)

  1. 一种液压换挡拨叉总成，其特征在于，包括：
    液压腔壳体(10)，其具有用于隔离液压腔的隔断(14)以及位于所述隔断两侧的第一进排油孔(11H)和第二进排油孔(12H)；
    两个活塞(20)，其设置在所述液压腔壳体(10)中并分别位于所述隔断的两侧；以及
    两个拨叉(40)，分别受所述两个活塞(20)驱动，
    所述隔断(14)倾斜、弯折或弯曲设置，使得所述第一进排油孔(11H)和所述第二进排油孔(12H)在所述液压腔壳体(10)的轴向(A)上的最远端的轴向距离小于，所述第一进排油孔(11H)的轴向长度、所述第二进排油孔(12H)的轴向长度和所述隔断(14)的最小壁厚之和。
  2. 根据权利要求1所述的液压换挡拨叉总成，其特征在于，所述第一进排油孔(11H)和所述第二进排油孔(12H)在所述液压腔壳体(10)的轴向(A)上至少部分重叠。
  3. 根据权利要求1所述的液压换挡拨叉总成，其特征在于，所述液压腔壳体大体呈筒状，所述第一进排油孔(11H)和所述第二进排油孔(12H)在所述液压腔壳体(10)的周向上错开地布置。
  4. 根据权利要求1所述的液压换挡拨叉总成，其特征在于，所述隔断(14)呈台阶状，所述隔断(14)包括基台(141)、台阶(142)及连接所述基台(141)和所述台阶(142)的连接部(143)，所述基台(141)与所述台阶(142)在所述轴向上错开设置。
  5. 根据权利要求4所述的液压换挡拨叉总成，其特征在于，所述基台(141)和所述台阶(142)为与所述轴向(A)垂直的平板状。
  6. 根据权利要求1所述的液压换挡拨叉总成，其特征在于，所述第一进排油孔(11H)和所述第二进排油孔(12H)分别至少部分地收容在S形的所 述隔断(14)的两个C形部内。
  7. 根据权利要求1所述的液压换挡拨叉总成，其特征在于，所述隔断(14)呈平板状并且相对于所述液压腔壳体(10)的轴向倾斜设置。
  8. 根据权利要求1至7中任一项所述的液压换挡拨叉总成，其特征在于，所述隔断(14)为厚度均匀的板状。
  9. 根据权利要求1至7中任一项所述的液压换挡拨叉总成，其特征在于，所述活塞(20)包括设置在其轴向端部的密封构件(30)，所述隔断(14)形成所述活塞(20)的轴向止挡部。
  10. 根据权利要求1至7中任一项所述的液压换挡拨叉总成，其特征在于，所述液压腔壳体(10)为注塑成形或压铸成形的一体件。
  11. 根据权利要求1至7中任一项所述的液压换挡拨叉总成，其特征在于，所述液压腔壳体(10)的周壁设置有两个液压腔拨指孔(13)，
    每个所述拨叉(40)均包括拨指(41)和与所述拨指(41)相连的两个叉脚(43)，其中，两个所述拨指(41)分别穿过所述两个液压腔拨指孔(13)而连接到所述两个活塞(20)。
  12. 根据权利要求11所述的液压换挡拨叉总成，其特征在于，在所述活塞(20)轴向移动时，所述拨指(41)与所述液压腔拨指孔(13)的孔壁不接触。
  13. 根据权利要求1至7中任一项所述的液压换挡拨叉总成，其特征在于，所述液压换挡拨叉总成还包括拨叉轴(60)，所述两个拨叉(40)可轴向滑动地套设于所述拨叉轴(60)，
    所述液压腔壳体(10)还包括从所述液压腔壳体(10)的轴向两端沿径向伸出的两个弹簧定位座(15)，所述弹簧定位座(15)固定到所述拨叉轴(60)。
  14. 一种双离合变速器的换挡执行机构，其特征在于，包括权利要求1至13中任一项所述的液压换挡拨叉总成。
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