WO2024178656A1 - 扭矩传递机构 - Google Patents

扭矩传递机构 Download PDF

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Publication number
WO2024178656A1
WO2024178656A1 PCT/CN2023/078926 CN2023078926W WO2024178656A1 WO 2024178656 A1 WO2024178656 A1 WO 2024178656A1 CN 2023078926 W CN2023078926 W CN 2023078926W WO 2024178656 A1 WO2024178656 A1 WO 2024178656A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
rotating component
torque transmission
transmission mechanism
rotating
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2023/078926
Other languages
English (en)
French (fr)
Inventor
王熙
孙超
甄臻
王杰
宋义
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to PCT/CN2023/078926 priority Critical patent/WO2024178656A1/zh
Priority to CN202380095251.XA priority patent/CN120787291A/zh
Publication of WO2024178656A1 publication Critical patent/WO2024178656A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D31/00—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution
    • F16D31/02—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution using pumps with pistons or plungers working in cylinders
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • 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
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type

Definitions

  • the present invention relates to the field of transmission technology, and in particular to a torque transmission mechanism with vibration reduction and buffering effects.
  • the technical problem to be solved by the present invention is to provide a torque transmission mechanism with vibration reduction and buffering effects.
  • the above technical problem is solved by a torque transmission mechanism according to the present invention.
  • the torque transmission mechanism includes a first rotating component and a second rotating component that can rotate relative to each other, and one of the first rotating component and the second rotating component is arranged radially inside the other.
  • the torque transmission mechanism also includes a hydraulic device, and the torque transmission mechanism is configured to be able to transmit torque between the first rotating component and the second rotating component through the hydraulic device.
  • the torque transmission between the two rotating components is achieved by the hydraulic device, so that torque vibration can be buffered by the hydraulic fluid.
  • the hydraulic device can be one or more pistons
  • the second rotating component includes one or more piston chambers for accommodating hydraulic fluid
  • each piston is movably mounted in a corresponding piston chamber so as to be able to extend the second rotating component to abut the first rotating component.
  • the piston can transmit torque by compressing the hydraulic fluid in the piston chamber, and the hydraulic fluid can buffer the torque vibration transmitted to the piston when transmitting the torque.
  • the first rotating component and the second rotating component can have a non-torque transmission position relative to each other, in which the one or more pistons do not contact or can only contact the first rotating component in a manner that the circumferential component of the thrust resultant force is zero, and when the first rotating component and the second rotating component rotate relative to each other within a predetermined range and deviate from the non-torque transmission position, the first rotating component can abut at least a portion of the one or more pistons in a direction having a circumferential force component, so that the at least a portion of the pistons moves in a direction to retract the second rotating component to compress the hydraulic fluid in the corresponding piston chamber and can transmit torque between the first rotating component and the second rotating component through the at least a portion of the pistons.
  • rigid torque transmission structures such as splines or teeth
  • the hydraulic fluid when each piston is pushed by the first rotating member to compress the hydraulic fluid in the corresponding piston chamber, the hydraulic fluid can leak between the corresponding piston and the piston chamber in a direction opposite to the moving direction of the corresponding piston.
  • the leaked hydraulic fluid can buffer the movement of the piston by moving in the opposite direction of the piston, thereby further reducing vibration.
  • the one or more piston chambers may include a plurality of piston chambers spaced apart along the circumferential direction, and the second rotating component may include an annular liquid storage chamber, which is connected to each piston chamber so as to supply hydraulic fluid to each piston chamber.
  • hydraulic fluid can be supplied to a plurality of piston chambers simultaneously by a supply channel.
  • each piston chamber can be connected to the liquid storage chamber through a corresponding connecting hole, so that the hydraulic fluid in each piston chamber can generate an instantaneous high pressure relative to the hydraulic fluid in the liquid storage chamber when compressed by the corresponding piston.
  • the connecting hole can generate a certain buffering effect between the piston chamber and the liquid storage chamber by shrinking the inner diameter of the flow channel.
  • each piston cavity can be located radially between the liquid storage cavity and the first rotating component. That is, the radial position relationship between the liquid storage cavity and the first rotating component relative to the piston cavity is opposite.
  • the liquid storage cavity is thus arranged away from the first rotating component, thereby facilitating the introduction of hydraulic fluid.
  • the torque transmission mechanism may further include one or more elastic members, each of which is disposed in a corresponding piston cavity and elastically abuts against a corresponding piston in the extension direction.
  • the elastic member may also provide a buffering effect on the retraction movement of the piston, and in particular, may supplement the buffering effect in the case of insufficient hydraulic fluid.
  • the first rotating component may include one or more guide profiles facing the second rotating component, each piston is radially movably mounted in the corresponding piston cavity and abuts the corresponding guide profile, each guide profile is concave in the radial direction facing away from the second rotating component and has a maximum depth position in the circumferential middle, in the non-torque transmission position, each piston abuts at the maximum depth position of the corresponding guide profile, and the concave depth of each guide profile gradually decreases from the corresponding maximum depth position toward both ends in the circumferential direction, so that the corresponding piston is pushed to retract the second rotating component when the first rotating component and the second rotating component deviate from the non-torque transmission position.
  • the thrust of the guide profile on the piston is in the radial direction without a circumferential component, so that no significant torque can be transmitted between the two rotating components.
  • the end of the piston slides along the guide profile to a position with a smaller depth, thereby pushing the piston to retract the second rotating component, and at the same time, when the piston abuts at the non-maximum depth position of the guide profile, the thrust of the guide profile on the piston is no longer parallel to the radial direction and generates a circumferential component, so that torque can be transmitted between the two rotating components. Since the transmitted torque depends on the position of the piston in the piston chamber, the hydraulic fluid can dampen torque vibrations.
  • At least a portion of the one or more guide profiles may have a concave arc profile, and/or, at least a portion of the one or more pistons may have a protruding arc profile at the end thereof for abutting the corresponding guide profile.
  • the arc profile facilitates guiding the piston to slide along the guide profile and can reduce stress concentration.
  • the guide profile may also have a straight line profile such as a triangle or a profile of other shapes.
  • the first rotating component may include one or more A limiting structure
  • the second rotating component may include one or more second limiting structures, when the first rotating component and the second rotating component rotate relative to each other to the limit position of the predetermined rotation range, at least a part of the one or more first limiting structures abuts against the corresponding second limiting structures along the circumferential direction, thereby preventing the first rotating component and the second rotating component from rotating beyond the predetermined rotation range.
  • the two rotating components can transmit torque by abutting against the first limiting structure and the second limiting structure along the circumferential direction.
  • the one or more pistons may include at least one first piston and at least one second piston spaced apart along the circumference, each first piston and each second piston are respectively mounted in the corresponding piston chamber movably along the circumference, each first piston can abut against the first rotating component in the first rotation direction along the circumference, and each second piston can abut against the first rotating component in the second rotation direction opposite to the first rotation direction.
  • the two rotating components can transmit torque in different rotation directions respectively through two groups of circumferentially moving pistons in opposite directions.
  • each piston can have a maximum extension position defined by the corresponding piston chamber, and in the process that the first rotating component rotates relative to the second rotating component in any rotation direction and deviates from the non-torque transmission position, a part of the one or more pistons is pushed by the first rotating component toward the direction of retracting the second rotating component, and the pistons of the one or more pistons that are not pushed by the first rotating component can be constrained in the corresponding maximum extension position and separated from the first rotating component.
  • the first rotating component will not be subjected to the circumferential thrust of the piston in the non-torque transmission position, and when the first rotating component rotates in a certain direction to push a group of pistons, the other group of pistons will be constrained by the piston chamber in the maximum extension position and separated from the first rotating component.
  • the first rotating component may include one or more protrusions protruding toward the second rotating component
  • the second rotating component may include one or more recessed portions recessed away from the first rotating component
  • each protrusion is inserted into a corresponding recessed portion in the radial direction
  • each piston extends out of the side wall of the corresponding recessed portion from the second rotating component and can abut against the side wall of the corresponding protrusion.
  • the at least one first piston and the at least one second piston are alternately distributed in the circumferential direction, and any pair of first pistons and second pistons that are adjacent to each other in the circumferential direction and extend away from each other in the direction of extension of the one or more pistons constitute a piston pair, and each piston pair is installed in the same piston cavity extending in the circumferential direction.
  • the elastic The elastic member can be elastically abutted between the two pistons of the piston pair.
  • FIG. 1 a shows a perspective view of a torque transmission mechanism according to a first embodiment of the present invention
  • FIG. 1 b shows a longitudinal sectional view of a torque transmission mechanism according to a first embodiment of the present invention
  • FIG. 1c shows a partial enlarged view of the torque transmission mechanism according to the first embodiment of the present invention
  • FIG. 2 a shows a perspective view of a torque transmission mechanism according to a second embodiment of the present invention
  • FIG. 2 b shows a perspective cross-sectional view of a torque transmission mechanism according to a second embodiment of the present invention
  • FIG3 a shows a transverse cross-sectional view of a torque transmission mechanism according to a third embodiment of the present invention
  • FIG3 b shows a longitudinal sectional view of a torque transmission mechanism according to a third embodiment of the present invention.
  • FIG4 a shows a perspective view of a torque transmission mechanism according to a fourth embodiment of the present invention.
  • FIG4 b shows a transverse cross-sectional view of a torque transmission mechanism according to a fourth embodiment of the present invention
  • FIG. 5 is a graph showing an operation curve of a torque transmitting mechanism according to an exemplary embodiment of the present invention.
  • FIG. 6 is a simulation graph illustrating a torque transmitting mechanism according to an exemplary embodiment of the present invention.
  • a torque transmission mechanism which can replace a traditional spline transmission mechanism or a gear transmission mechanism with a hydraulic device to transmit torque between two rotating parts.
  • the present invention provides multiple exemplary embodiments of the torque transmission mechanism.
  • the torque transmission mechanism includes an outer rotating member 10 and an inner rotating member 20.
  • the outer rotating member 10 is a substantially annular member
  • the inner rotating member 20 is a substantially disc-shaped or annular member.
  • the inner rotating member 20 is coaxially arranged radially inside the outer rotating member 10.
  • the outer rotating member 10 and the inner rotating member 20 are arranged radially inside the outer rotating member 10.
  • the inner rotating part 20 can rotate relative to each other around a common central axis.
  • the radial support and relative rotation between the outer rotating part 10 and the inner rotating part 20 can be achieved, for example, by bearings or rolling bodies 40 directly mounted therebetween (i.e. the outer and inner rings of the bearings are integrally formed with the rotating part).
  • the torque transmission mechanism further includes one or more pistons 30, and the inner rotating component 20 is formed with one or more piston chambers 21.
  • Each piston 30 is installed in a corresponding piston chamber 21, and can be guided by the side wall of the piston chamber 21 and move along the extension direction of the piston chamber 21.
  • these pistons 30 can be distributed at intervals along the circumference (preferably evenly distributed).
  • these pistons 30 preferably have substantially the same shape and size, and these piston chambers 21 also preferably have substantially the same shape and size.
  • each piston chamber 21 extends approximately radially and penetrates to the outer circumferential surface of the inner rotating component 20, so that the piston 30 installed in the piston chamber 21 can move approximately radially and partially extend out of the piston chamber 21 to abut against the inner circumferential surface of the outer rotating component 10.
  • the outer rotating part 10 includes one or more guide profiles 11 facing the inner rotating part 20 (i.e., facing the radial inside in this embodiment). These guide profiles 11 may be surfaces formed integrally with the outer rotating part 10 or surfaces of additional components fixed to the outer rotating part 10. Each piston 30 corresponds to a corresponding guide profile 11 in the circumferential direction. The end of each piston 30 extending out of the piston cavity 21 may abut against the corresponding guide profile 11. Each guide profile 11 is concave in the radial direction facing away from the inner rotating part 20 (i.e., facing the radial outside in this embodiment).
  • Each guide profile 11 has a maximum depth position in the circumferential middle, and the concave depth (radial depth) of the guide profile 11 gradually decreases from the corresponding maximum depth position toward both ends in the circumferential direction.
  • a guide profile 11 may, for example, have an arcuate profile, a sharp-angled triangular profile, or a triangular profile with rounded vertices.
  • the profile shape of the guide profile 11 may be symmetrical about the maximum depth position.
  • Each piston chamber 21 is filled with hydraulic fluid.
  • the hydraulic pressure generated by the hydraulic fluid causes the piston 30 to extend out of the inner rotating member 20 and abut against the outer rotating member 10.
  • the piston 30 is at its maximum extension position, and the thrust between the piston 30 and the guide profile 11 (excluding the friction force on the contact surface) is substantially along the radial direction. direction without any circumferential (or tangential) component.
  • the outer rotating component 10 and the inner rotating component 20 have a non-torque transmission position relative to each other.
  • the non-torque transmission position is a relative position where no torque can be transmitted or no significant torque (i.e., torque greater than a predetermined amount) can be transmitted between the outer rotating component 10 and the inner rotating component 20, and can also be called a neutral position.
  • the non-torque transmission position can also be regarded as the zero-degree point position of the relative rotation angle between the two rotating components.
  • the guide profile 11 may have a concave arc profile.
  • the end of the piston 30 for abutting the corresponding guide profile 11 may also have a protruding arc profile.
  • the arc profile facilitates guiding the piston to slide along the guide profile and can reduce stress concentration.
  • the end of the piston 30 for abutting the corresponding guide profile 11 may be an integrally formed spherical end, or the end may be a rotatably mounted pulley so that the end of the piston 30 can roll along the guide profile 11.
  • FIG5 shows an operation curve diagram of a torque transmission mechanism according to an exemplary embodiment of the present invention.
  • the horizontal axes of the two curve diagrams in FIG5 represent the rotational position, wherein the middle vertical line corresponds to the non-torque transmission position; the vertical axis of the upper figure represents the recessed depth of the guide profile where the piston 30 abuts, and the vertical axis of the lower figure represents the pressure angle where the piston 30 abuts (a pressure angle of 0 degrees indicates that the pressure acts completely radially).
  • this torque transmission mechanism has two working stages within the rotational range. Near the non-torque transmission position, the torque transmission mechanism is in a decoupling stage.
  • the decoupling stage the angle at which the two rotating components deviate from the non-torque transmission position is small, the pressure angle is small, and the torque transmitted between the two components through the piston 30 is very small and can be ignored.
  • the torque transmission stage the angle of deviation of the two rotating parts from the non-torque transmission position is large, and the pressure angle is large, so that a large torque can be transmitted between the two parts through the piston 30.
  • the vibration of the torque can still be buffered by the hydraulic fluid.
  • an elastic member 50 (such as a coil spring or other elastic member) may be additionally installed in one or more piston chambers 21.
  • the elastic member 50 elastically abuts between the corresponding piston 30 and the end of the piston chamber 21 facing away from the outer rotating component 10 in the radial direction.
  • the elastic force generated by the elastic member 50 can be used as a supplement to the liquid pressure of the hydraulic fluid.
  • each piston 30 may be in non-sealed contact with the side wall of the corresponding piston chamber 21. Therefore, when the piston 30 is pushed by the outer rotating component 10 to compress the hydraulic fluid in the corresponding piston chamber 21, the hydraulic fluid may leak between the corresponding piston 30 and the piston chamber 21 in a direction opposite to the moving direction of the corresponding piston 30. The leaked hydraulic fluid may buffer the movement of the piston 30 by moving in the opposite direction of the piston 30, thereby further reducing vibration.
  • the inner rotating component 20 when the inner rotating component 20 includes a plurality of piston chambers 21 spaced apart along the circumferential direction, the inner rotating component 20 may also preferably include an annular liquid storage chamber 22.
  • the liquid storage chamber 22 is in communication with each piston chamber 21, so that hydraulic fluid can be supplied to each piston chamber 21.
  • hydraulic fluid can be supplied to multiple piston chambers 21 simultaneously by using one supply channel.
  • each piston chamber 21 can be in communication with the liquid storage chamber 22 through a corresponding communication hole 23.
  • the communication hole 23 can produce a certain buffering effect between the corresponding piston chamber 21 and the liquid storage chamber 22 by shrinking the inner diameter of the flow channel, so that the hydraulic fluid in the piston chamber 21 can generate an instantaneous high pressure relative to the hydraulic fluid in the liquid storage chamber 22 when compressed by the corresponding piston 30. Therefore, when the piston 30 vibrates and causes the liquid pressure in the piston chamber 21 to suddenly increase, the conduction of the liquid pressure to the liquid storage chamber 22 will be hindered by the communication hole 23, thereby controlling the distribution range of the transient high pressure in the entire inner rotating component 20, thereby reducing the impact on the structural strength of the inner rotating component 20.
  • the reservoir chamber 22 may be located radially inward of all the piston chambers 21, so that the piston chamber 21 is radially located between the reservoir chamber 22 and the outer rotating component 10.
  • the reservoir chamber 22 is thus arranged away from the outer rotating component 10, thereby facilitating the introduction of hydraulic fluid.
  • the hydraulic fluid may be introduced into the reservoir chamber 22 through the one-way valve 60 located radially inward of the reservoir chamber 22, and further flow to each piston chamber 21 through the reservoir chamber 22.
  • the inner rotating component 20 may not form the liquid storage chamber 22, and this solution is shown in the third embodiment of Figures 3a and 3b.
  • the multiple piston chambers 21 of the inner rotating component 20 are independent of each other, and each piston chamber 21 can be connected to the inner circumference of the inner rotating component 20 through a separate orifice, and each can be equipped with a corresponding one-way valve 60 at the orifice to control the flow of hydraulic fluid into the piston chamber 21.
  • both circumferential ends of the guide profile 11 extend directly to the inner circumferential surface of the inner rotating component 20.
  • the contactable range between the guide profile 11 and the corresponding piston 30 defines the predetermined rotation range between the two rotating components.
  • the magnitude of the torque transmitted between the two rotating components depends on the relative positions of the two rotating components within the predetermined rotation range. When the transmitted torque is too large so that the two rotating components exceed the predetermined rotation range, the piston 30 will break away from the corresponding guide profile 11 and abut against the inner circumferential surface of the inner rotating component 20 between the adjacent guide profiles 11.
  • the pressure angle of the contact surface is zero, the pressure has no circumferential component, and only frictional force along the circumferential direction may exist between the two rotating components. This makes the torque transmission between the two rotating components ineffective, thereby limiting the maximum transmittable torque.
  • a limiting structure is provided to prevent the two rotating parts from rotating beyond a predetermined rotation range.
  • the outer rotating part 10 includes one or more first limiting structures 12, and the inner rotating part 20 includes one or more second limiting structures 24.
  • the outer rotating part 10 and the inner rotating part 20 rotate relative to each other to the limit position of the predetermined rotation range, at least a part of the first limiting structures 12 abuts against the corresponding second limiting structures 24 in the circumferential direction, thereby preventing the two rotating parts from further rotating beyond the predetermined rotation range.
  • the two rotating parts can also transmit a larger torque by abutting against the first limiting structure 12 and the second limiting structure 24 in the circumferential direction.
  • the positions of these limiting structures in the axial direction can overlap or partially overlap with the piston 30 and/or the guide profile 11, or can not overlap with the piston 30 and/or the guide profile 11.
  • the limiting structure same as the second embodiment is also shown.
  • the first limiting structure 12 and the second limiting structure 24 may be step surfaces formed on the corresponding rotating parts and facing each other basically in the circumferential direction (as shown in the figure); or, the first limiting structure 12 may be a step surface formed on the outer rotating part 10, and the second limiting structure may be acted as a piston 30 installed on the inner rotating part 20 (not shown).
  • FIG. 4a and FIG. 4b show a torque transmission mechanism according to a fourth embodiment of the present invention.
  • each piston 30 can only abut the outer rotating component 10 in a unidirectional circumferential direction. Therefore, the torque transmission mechanism of the fourth embodiment includes a plurality of pistons 30 spaced apart in the circumferential direction, and these pistons 30 are composed of at least one first piston 30a and at least one second piston 30b. Among them, each first piston 30a and each second piston 30b are respectively installed in a corresponding piston cavity 21.
  • Each piston cavity 21 extends approximately in the circumferential direction, and can guide the piston 30 (first piston 30a and/or second piston 30b) therein to move in the circumferential direction through its side wall.
  • the end of each piston cavity 21 is circumferentially connected, so that the end of the piston 30 installed therein can partially extend out of the piston cavity 21 and abut the outer rotating component 10.
  • the surface of the outer rotating component 10 abutted by the piston 30 can be a radial surface of a structure formed or fixed on the outer rotating component 10, such as a radially extending step surface or baffle.
  • Each first piston 30a can abut against the outer rotating component 10 in a first rotational direction along the circumferential direction
  • each second piston 30b can abut against the outer rotating component 10 in a second rotational direction opposite to the first rotational direction.
  • the two rotating components rotate in a certain rotational direction
  • one of the first piston 30a and the second piston 30b is pushed to move in a direction of retracting into the corresponding piston chamber 21.
  • the two rotating components can transmit torque and damp vibration in different rotational directions respectively through two groups of circumferentially moving pistons in opposite directions.
  • the circumferential component of the thrust resultant force generated by all the pistons 30 (including the first piston 30a and the second piston 30b) on the outer rotating part 10 is zero.
  • This can include three cases: the first case, in the non-torque transmission position, the piston 30 does not contact the outer rotating part 10; the second case, in the non-torque transmission position, the piston 30 contacts the outer rotating part 10 without thrust; the third case, in the non-torque transmission position, at least a part of the pistons 30 can contact the outer rotating part 10, wherein the thrust generated by a single piston 30 on the outer rotating part 10 is not zero, but the circumferential component of the thrust resultant force generated by all the pistons 30 on the outer rotating part 10 is zero (in this embodiment, the thrust generated by the piston 30 on the outer rotating part 10 acts in the circumferential direction, so the circumferential component of zero means that the thrust resultant force is also zero).
  • the outer rotating part 10 will not be subjected to the circumferential thrust of the piston 30 in the non-torque transmission position.
  • the group of pistons contacts the outer rotating member 10 and moves in the direction of retracting the inner rotating member 20, thereby moving in the corresponding direction.
  • the circumferential thrust in the direction toward the outer rotating member 10 increases while the circumferential thrust in the opposite direction decreases or remains unchanged, so that the resultant force of the circumferential thrusts acting on all the pistons 30 between the outer rotating member 10 increases in the corresponding direction with the rotation position.
  • each piston 30 may have a maximum extension position defined by the corresponding piston cavity 21.
  • the other group of pistons (the second piston 30b or the first piston 30a) of all the pistons 30 that are not pushed by the outer rotating component 10 will be constrained by the corresponding piston cavity 21 at the maximum extension position and separated from the outer rotating component 10.
  • each piston 30 may include a plug body 31 and a plug head 32 divided along the extension direction of the piston cavity 21, wherein the outer diameter of the plug body 31 is larger than the outer diameter of the plug head 32.
  • the inner diameter of the end opening of the piston cavity 21 is smaller than the inner diameter of the piston cavity 21 and the inner diameter of the plug body 31, but larger than the outer diameter of the plug head 32, so that the plug body 31 cannot extend out of the piston cavity 21, but the plug head 32 can extend out of the piston cavity 21.
  • the plug body 31 will abut against the end of the corresponding piston cavity 21 to achieve position limiting.
  • the piston 30 does not contact the outer rotating part 10 in the non-torque transmission position or can only contact the outer rotating part 10 without thrust, the piston 30 is limited to the maximum extension position by the corresponding piston cavity 21 in the non-torque transmission position, and any angle of deviation of the outer rotating part 10 from the non-torque transmission position in the direction away from a certain group of pistons 30 will cause the piston 30 to separate from the group of pistons 30; if the piston 30 contacts the outer rotating part 10 with a non-zero thrust in the non-torque transmission position, the piston 30 does not reach the maximum extension position in the non-torque transmission position.
  • the group of pistons 30 can initially continue to extend from the corresponding piston cavity 21 as the outer rotating part 10 rotates, until the outer rotating part 10 rotates to a predetermined angle, the group of pistons 30 reaches the maximum extension position limited by the corresponding piston cavity 21 and begins to separate from the outer rotating part 10 that continues to rotate.
  • the outer rotating component 10 may include one or more protrusions 13 protruding toward the inner rotating component 20 (towards the radial inside), and the inner rotating component 21 may include one or more recesses 25 recessed away from the outer rotating component 10 (towards the radial inside).
  • Each protrusion 13 is inserted into the corresponding recess 25 in the radial direction, and each piston 30 extends out of the inner rotating component 20 from the side wall of the corresponding recess 25 and can abut against the side wall of the corresponding protrusion 13.
  • the first piston 30a and the second piston 30b are preferably distributed alternately in the circumferential direction.
  • any pair of first pistons 30a and second pistons 30b that are adjacent in the circumferential direction and extend away from each other in the direction of extension constitute a piston pair, and each piston pair
  • the pistons 30 are installed in the same piston cavity 21 extending in the circumferential direction and extend from opposite ends of the piston cavity 21 respectively.
  • the piston pair in the same piston cavity 21 can share an elastic member 50, and the elastic member 50 elastically abuts between the two pistons of the piston pair.
  • each piston 30 can also be installed in an independent piston cavity 21. In this case, the corresponding elastic member 50 can elastically abut between the piston 30 and the end of the piston cavity 21.
  • the surfaces of the two rotating components will directly abut against each other.
  • the protrusion 13 corresponding to the rotation direction will directly abut against the corresponding recessed portion 25, so that the torque can be directly transmitted between the two rotating components and the two rotating components are prevented from further rotating beyond the predetermined rotation range.
  • the inner rotating component 20 may also be formed with a liquid storage chamber 22 and/or a communication hole 23 similar to that of the first embodiment, and its structure and function are similar to those of the first embodiment, and will not be described in detail herein.
  • each piston 30 may also preferably be in non-sealed contact with the side wall of the corresponding piston chamber 21.
  • the piston 30 can be installed in the piston cavity formed in the outer rotating component 10 so as to abut the inner rotating component 20. This allows the positional relationship of various structures in a matching relationship on the two rotating components to be exchanged between the two rotating components.
  • the rotating component used to abut the piston 30 can be collectively referred to as the first rotating component
  • the rotating component used to install the piston 30 can be collectively referred to as the second rotating component.
  • the technical features described in any embodiment can also be applied to other embodiments.
  • the first rotating component and the second rotating component transmit torque through a hydraulic device, so the torque vibration can be buffered by the hydraulic fluid, thereby reducing noise.
  • the piston does not contact the first rotating component or can only contact the first rotating component in a way that the circumferential component of the thrust resultant force is zero.
  • the contact state in which the circumferential component of the thrust resultant force is zero includes three contact states: the first is that there is no thrust between all pistons and the first rotating component (but static friction may exist); the second is that there is thrust between at least a part of the pistons and the first rotating component, but the thrust of each piston does not have a circumferential component (the circumferential component is zero) (first embodiment); the third is There is a thrust with a circumferential component between at least a portion of the pistons and the first rotating part, but the circumferential component of the thrust resultant between all the pistons and the first rotating part is zero, that is, the circumferential thrusts of different pistons acting on the first rotating part cancel each other out (the fourth embodiment).
  • the first rotating part and the second rotating part rotate relative to each other within a predetermined range and deviate from the non-torque transmission position, the first rotating part can abut at least a portion of the piston in the direction with the circumferential force component, thereby pushing at least a portion of the piston to retract the second rotating part to compress the hydraulic fluid in the corresponding piston chamber, and transmit torque between the first rotating part and the second rotating part through at least a portion of the piston.
  • This torque transmission method has the torque transmission effect previously described with reference to Figure 5. Due to the buffering effect of the hydraulic fluid, the vibration and noise of the rotating part can be significantly reduced. This is particularly suitable for (but not limited to) replacing conventional splines or gear transmission mechanisms in the transmission of a vehicle, so as to reduce noise, especially in the state of parking charging or small throttle acceleration.
  • the effect of the torque transmission mechanism according to the present invention can be verified by simulation experiments.
  • the inventors used a multi-body dynamic simulation method to verify the damping effect of such a torque transmission mechanism.
  • the impact force in the charging mode is significantly reduced. This proves that the torque transmission mechanism according to the present invention can advantageously buffer torque shock and vibration, and can also reduce the maximum driving torque in the traction start mode.

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Abstract

一种扭矩传递机构，该扭矩传递机构包括能够相对转动的第一转动部件和第二转动部件，第一转动部件和第二转动部件中的一者布置在另一者的径向内侧。该扭矩传递机构还包括液压装置，该扭矩传递机构配置为能够通过液压装置在第一转动部件与第二转动部件之间传递扭矩。该扭矩传递机构具有改进的减振和缓冲效果。

Description

扭矩传递机构 技术领域
本发明涉及传动技术领域。具体地，本发明涉及一种具有减振和缓冲效果的扭矩传递机构。
背景技术
在现有技术中，通常采用花键或齿轮等机构在两个转动部件之间进行扭矩传递。由于耦合的花键或齿之间存在间隙，转动部件在运行期间可能产生花键或齿的撞击噪声。例如，在变速器的非传扭状态下，这种撞击噪声非常显著。需要在有限的空间中满足高扭矩传递和大阻尼要求才能减少这种撞击噪声。对于当前的刚性传动机构而言，这种问题难以解决。在现有的变速器中，通常通过增加扭矩的方式使配对花键或齿之间始终保持压紧状态来消除花键或齿的噪音。但是这种方式会相应地增加电池能耗和油耗，并且提高电池的工作温度，从而影响电池、电机、热管理系统的相关部件的使用寿命。
发明内容
因此，本发明需要解决的技术问题是，提供一种具有减振和缓冲效果的扭矩传递机构。
上述技术问题通过根据本发明的一种扭矩传递机构而得到解决。该扭矩传递机构包括能够相对转动的第一转动部件和第二转动部件，第一转动部件和第二转动部件中的一者布置在另一者的径向内侧。其中，所述扭矩传递机构还包括液压装置，所述扭矩传递机构配置为能够通过所述液压装置在所述第一转动部件与所述第二转动部件之间传递扭矩。两个转动部件之间的扭矩传递通过液压装置来实现，由此可以通过液压流体来缓冲扭矩振动。
根据本发明的一个优选实施例，该液压装置可以为一个或多个活塞，第二转动部件包括用于容纳液压流体的一个或多个活塞腔，每个活塞可移动地安装在相应的活塞腔中从而能够伸出第二转动部件以抵接第一转动部件。活塞可以通过压缩活塞腔中的液压流体来传递扭矩，而液压流体在传递扭矩时能够缓冲传递到活塞上的扭矩振动。
根据本发明的另一优选实施例，第一转动部件和第二转动部件可以具有相对于彼此的非传扭位置，在非传扭位置，该一个或多个活塞不接触或只能以推力合力的周向分量为零的方式接触第一转动部件，而当第一转动部件和第二转动部件在预定范围内相对转动而偏离非传扭位置时，第一转动部件能够沿具有周向力分量的方向抵接该一个或多个活塞中的至少一部分活塞，从而使该至少一部分活塞向着缩回第二转动部件的方向移动来压缩相应的活塞腔中的液压流体并且能够通过该至少一部分活塞在第一转动部件与第二转动部件之间传递扭矩。在两个转动部件之间没有显著扭矩传递的状态下，可以防止由于振动引起的刚性传扭结构(比如花键或齿)之间的直接撞击，从而减少噪声。
根据本发明的另一优选实施例，当每个活塞由第一转动部件推动而压缩相应的活塞腔中的液压流体时，液压流体能够在相应的活塞与活塞腔之间朝向与相应的活塞的移动方向相反的方向泄漏。泄漏的液压流体能够通过自身与活塞反向的运动来缓冲活塞的运动，从而进一步减少振动。
根据本发明的另一优选实施例，该一个或多个活塞腔可以包括沿周向间隔分布的多个活塞腔，第二转动部件可以包括环形的储液腔，储液腔与每个活塞腔连通，从而能够向每个活塞腔供应液压流体。由此可以利用一个供应通道同时向多个活塞腔供应液压流体。优选地，每个活塞腔可以与储液腔通过相应的连通孔连通，使得每个活塞腔中的液压流体在受到相应的活塞压缩时能够产生相对于储液腔中的液压流体的瞬时高压。连通孔可以通过收缩流道内径的方式在活塞腔与储液腔之间产生一定的缓冲作用，因此当活塞振动导致活塞腔中的液体压力突然升高时，液体压力向储液腔中的传导会受到连通孔的阻碍，由此控制瞬态高压在整个第二转动部件中的分布范围，从而减少对第二转动部件的结构强度的影响。
根据本发明的另一优选实施例，每个活塞腔可以在径向上位于储液腔与第一转动部件之间。也就是说，储液腔和第一转动部件相对于活塞腔的径向位置关系相反。储液腔由此远离第一转动部件布置，从而便于引入液压流体。
根据本发明的另一优选实施例，扭矩传递机构还可以包括一个或多个弹性件，每个弹性件设置在相应的活塞腔中并且沿伸出方向弹性地抵接相应的活塞。弹性件也可以对活塞的缩回运动产生缓冲作用，特别是可以在液压流体不足的情况下补充缓冲效果。
根据本发明的另一优选实施例，第一转动部件可以包括朝向第二转动部件的一个或多个引导型面，每个活塞可径向移动地安装在相应的活塞腔中并且抵接相应的引导型面，每个引导型面沿背向第二转动部件的径向方向凹入并且在周向中部具有最大深度位置，在非传扭位置，每个活塞抵接在相应的引导型面的最大深度位置，每个引导型面的凹入深度在周向上从相应的最大深度位置朝向两端逐渐减小，从而在第一转动部件和第二转动部件偏离非传扭位置时推动相应的活塞缩回第二转动部件。当活塞抵接在引导型面的最大深度位置时，引导型面对活塞的推力沿径向方向而不存在周向分量，因此两个转动部件之间不能传递显著扭矩。当两个转动部件转动偏离非传扭位置时，活塞的端部沿着引导型面滑动到深度更小的位置，从而推动活塞缩回第二转动部件，同时，当活塞抵接在引导型面的非最大深度位置时，引导型面对活塞的推力不再平行于径向而产生周向分量，从而能够在两个转动部件之间传递扭矩。由于所传递的扭矩取决于活塞在活塞腔中的位置，因此液压流体可以缓冲扭矩的振动。
根据本发明的另一优选实施例，在垂直于轴向的剖面中，该一个或多个引导型面中的至少一部分引导型面可以具有凹入的弧形轮廓，和/或，该一个或多个活塞中的至少一部分活塞的用于抵接相应的引导型面的端部可以具有突起的弧形轮廓。弧形轮廓便于引导活塞沿着引导型面滑动，并且可以减少应力集中。替代地，引导型面也可以具有三角形等直线轮廓或其他形状的轮廓。
根据本发明的另一优选实施例，第一转动部件可以包括一个或多个第 一限位结构，第二转动部件可以包括一个或多个第二限位结构，当第一转动部件和第二转动部件相对于彼此转动到预定转动范围的极限位置时，该一个或多个第一限位结构中的至少一部分沿周向抵接相应的第二限位结构，从而防止第一转动部件和第二转动部件转动超过预定转动范围。当达到预定转动范围的极限位置时，两个转动部件能够通过沿周向相互抵接第一限位结构和第二限位结构来传递扭矩。
根据本发明的另一优选实施例，该一个或多个活塞可以包括沿周向间隔分布的至少一个第一活塞和至少一个第二活塞，每个第一活塞和每个第二活塞分别可周向移动地安装在相应的活塞腔中，每个第一活塞能够在沿周向的第一转动方向上抵接第一转动部件，每个第二活塞能够在与第一转动方向相反的第二转动方向上抵接第一转动部件。由此两个转动部件可以通过两组方向相反的周向运动活塞来分别在不同的转动方向上传递扭矩。优选地，每个活塞可以具有由相应的活塞腔限定的最大伸出位置，在第一转动部件沿任一转动方向相对于第二转动部件转动而偏离非传扭位置的过程中，该一个或多个活塞中的一部分活塞被第一转动部件向着缩回第二转动部件的方向推动，并且该一个或多个活塞中未被第一转动部件推动的活塞能够被约束在相应的最大伸出位置而与第一转动部件分离。因此，第一转动部件在非传扭位置不会受到活塞的周向推力，并且当第一转动部件朝向某一方向转动而推动一组活塞时，另一组活塞将由活塞腔约束在最大伸出位置而与第一转动部件分离。
根据本发明的另一优选实施例，第一转动部件可以包括朝向第二转动部件突起的一个或多个突起部，第二转动部件可以包括背向第一转动部件凹入的一个或多个凹陷部，每个突起部沿径向插入相应的凹陷部中，每个活塞从相应的凹陷部的侧壁伸出第二转动部件并且能够抵接相应的突起部的侧壁。这种结构便于实现活塞与第一转动部件的沿周向相互接触。
根据本发明的另一优选实施例，该至少一个第一活塞和该至少一个第二活塞在周向上交替分布，该一个或多个活塞中沿周向相邻并且伸出方向彼此远离的任意一对第一活塞和第二活塞构成活塞对，每个活塞对安装在沿周向延伸的同一活塞腔中。这有利于简化流道结构。在这种情况下，弹 性件可以弹性地抵接在活塞对的两个活塞之间。
附图说明
以下结合附图进一步描述本发明。图中以相同的附图标记来代表功能相同的元件。其中：
图1a示出根据本发明的第一实施例的扭矩传递机构的立体图；
图1b示出根据本发明的第一实施例的扭矩传递机构的纵向剖视图；
图1c示出根据本发明的第一实施例的扭矩传递机构的局部放大图；
图2a示出根据本发明的第二实施例的扭矩传递机构的立体图；
图2b示出根据本发明的第二实施例的扭矩传递机构的立体剖视图；
图3a示出根据本发明的第三实施例的扭矩传递机构的横向剖视图；
图3b示出根据本发明的第三实施例的扭矩传递机构的纵向剖视图；
图4a示出根据本发明的第四实施例的扭矩传递机构的立体图；
图4b示出根据本发明的第四实施例的扭矩传递机构的横向剖视图；
图5示出根据本发明的示例性实施例的扭矩传递机构的运行曲线图；和
图6示出根据本发明的示例性实施例的扭矩传递机构的仿真曲线图。
具体实施方式
以下将结合附图描述根据本发明的扭矩传递机构的具体实施方式。下面的详细描述和附图用于示例性地说明本发明的原理，本发明不限于所描述的优选实施例，本发明的保护范围由权利要求书限定。
根据本发明的实施例，提供了一种扭矩传递机构，这种扭矩传递机构可以以液压装置替代传统的花键传动机构或齿轮传动机构等来在两个转动部件之间传递扭矩。本发明提供了这种扭矩传递机构的多个示例性实施例。
图1a至图1c示出了根据本发明的扭矩传递机构的第一实施例。如图1a所示，扭矩传递机构包括外转动部件10和内转动部件20。外转动部件10是大致圆环状的部件，内转动部件20是大致圆盘状或圆环状的部件，内转动部件20同轴地布置在外转动部件10的径向内侧。外转动部件10和 内转动部件20能够围绕共同的中心轴线相对转动。外转动部件10与内转动部件20之间的径向支撑和相对转动例如可以通过轴承或直接安装在二者之间的滚动体40(即轴承的外圈和内圈与转动部件一体形成)来实现。
如图1b和图1c所示，该扭矩传递机构还包括一个或多个活塞30，内转动部件20形成有一个或多个活塞腔21。每个活塞30安装在相应的活塞腔21中，并且能够由活塞腔21的侧壁引导而沿着活塞腔21的延伸方向移动。当存在多个活塞30(以及相应的多个活塞腔21)时，这些活塞30(并且因此活塞腔21)可以沿周向间隔分布(优选地均匀分布)。此外，这些活塞30优选地具有基本相同的形状和尺寸，并且这些活塞腔21也优选地具有基本相同的形状和尺寸。在第一实施例中，每个活塞腔21大致沿径向延伸并且贯通到内转动部件20的外周面，使得安装在活塞腔21中的活塞30能够大致沿径向移动并且部分地伸出活塞腔21而抵接外转动部件10的内周面。
对应于内转动部件20中的一个或多个活塞30，外转动部件10包括朝向内转动部件20(在本实施例中即朝向径向内侧)的一个或多个引导型面11。这些引导型面11可以是与外转动部件10一体形成的表面或者固定在外转动部件10上的附加部件的表面。每个活塞30在周向上对应于一个相应的引导型面11。每个活塞30的伸出活塞腔21的端部可以抵接在相应的引导型面11上。每个引导型面11沿背向内转动部件20的径向方向(在本实施例中即朝向径向外侧)凹入。每个引导型面11在周向中部具有最大深度位置，并且引导型面11的凹入深度(径向深度)在周向上从相应的最大深度位置朝向两端逐渐减小。在垂直于轴向的剖面中，这种引导型面11例如可以具有弧形轮廓、尖角三角形轮廓或顶点倒圆的三角形轮廓。优选地，在垂直于轴向的剖面中，引导型面11的轮廓形状可以关于最大深度位置对称。
每个活塞腔21中填充有液压流体。液压流体产生的液体压力使活塞30伸出内转动部件20而抵接外转动部件10。当任一活塞30抵接在相应的引导型面11的最大深度位置时，该活塞30位于其最大伸出位置，并且该活塞30与引导型面11之间的推力(不包含接触面上的摩擦力)基本沿着径 向方向而不存在周向(或切向)分量。
外转动部件10和内转动部件20具有相对于彼此的非传扭位置。顾名思义，非传扭位置即外转动部件10与内转动部件20之间不能传递扭矩或不能传递显著扭矩(即大于某一预定量的扭矩)的相对位置，也可以称为中性位置。此外，非传扭位置也可以视为两个转动部件之间的相对转动角度的零度点位置。当外转动部件10和内转动部件20相对于彼此位于非传扭位置时，每个活塞30都抵接在相应的引导型面11的最大深度位置，因此在两个转动部件之间不能传递显著扭矩。当外转动部件10和内转动部件20在预定转动范围内相对于彼此转动而偏离非传扭位置时，由于每个活塞30的端部将沿着引导型面11滑动到深度更小的位置，因此外转动部件10将通过每个引导型面11推动相应的活塞30向着缩回内转动部件20的方向移动(即朝向相应的活塞腔21内部移动)。同时，由于引导型面11在最大深度位置的两侧的延伸方向关于切向倾斜，引导型面11在最大深度位置之外的位置对活塞30的推力不再平行于径向方向而产生周向分量，从而能够在两个转动部件之间传递扭矩。
优选地，在垂直于轴向的剖面中，引导型面11可以具有凹入的弧形轮廓。类似地，活塞30的用于抵接相应的引导型面11的端部也可以具有突起的弧形轮廓。弧形轮廓便于引导活塞沿着引导型面滑动，并且可以减少应力集中。例如，活塞30的用于抵接相应的引导型面11的端部可以为一体形成的球面端部，或者，该端部可以为可转动地安装的滑轮，使得活塞30的端部可以沿着引导型面11滚动。
图5示出了根据本发明的示例性实施例的扭矩传递机构的运行曲线图。图5中两幅曲线图的横坐标表示转动位置，其中中间的竖线对应于非传扭位置；上图的纵坐标表示活塞30抵接处的引导型面的凹入深度，下图的纵坐标表示活塞30抵接处的压力角(0度压力角表示压力完全沿径向作用)。如图所示，这种扭矩传递机构在转动范围内具有两个工作阶段。在非传扭位置附近，扭矩传递机构位于解耦阶段，在解耦阶段，两个转动部件偏离非传扭位置的角度较小，压力角较小，通过活塞30在两个部件之间传递的扭矩非常小，可以忽略不计。这主要对应于转动部件在非工作状态下发生 振动的情况，例如变速箱中的转动部件在停车充电或小油门加速时的发生振动。这种振动的能量可以被活塞腔21中的液压流体吸收，从而减少噪声。在传扭阶段，两个转动部件偏离非传扭位置的角度较大，压力角较大，可以通过活塞30在两个部件之间传递较大扭矩。在传扭阶段，扭矩的振动仍然可以被液压流体缓冲。
优选地，在一个或多个活塞腔21中还可以附加地安装有弹性件50(例如螺旋弹簧或其他弹性件)。弹性件50沿径向弹性地抵接在相应的活塞30与活塞腔21的背向外转动部件10的端部之间。特别是在液压流体不足的状态下，弹性件50产生的弹性力可以作为液压流体的液体压力的补充。
优选地，每个活塞30与相应的活塞腔21的侧壁之间可以为非密封接触。因此，当活塞30由外转动部件10推动而压缩相应的活塞腔21中的液压流体时，液压流体能够在相应的活塞30与活塞腔21之间朝向与相应的活塞30的移动方向相反的方向泄漏。泄漏的液压流体能够通过自身与活塞30反向的运动来缓冲活塞30的运动，从而进一步减少振动。
如图1c所示，在第一实施例中，当内转动部件20包括沿周向间隔分布的多个活塞腔21时，内转动部件20还可以优选地包括环形的储液腔22。储液腔22与每个活塞腔21连通，从而能够向每个活塞腔21供应液压流体。由此可以利用一个供应通道同时向多个活塞腔21供应液压流体。在这种情况下，每个活塞腔21可以与储液腔22通过相应的连通孔23连通。连通孔23可以通过收缩流道内径的方式在相应的活塞腔21与储液腔22之间产生一定的缓冲作用，使得活塞腔21中的液压流体在受到相应的活塞30压缩时能够产生相对于储液腔22中的液压流体的瞬时高压。因此当活塞30振动导致活塞腔21中的液体压力突然升高时，液体压力向储液腔22中的传导会受到连通孔23的阻碍，由此控制瞬态高压在整个内转动部件20中的分布范围，从而减少对内转动部件20的结构强度的影响。优选地，储液腔22可以位于所有活塞腔21的径向内侧，使得活塞腔21在径向上位于储液腔22与外转动部件10之间。储液腔22由此远离外转动部件10布置，从而便于引入液压流体。液压流体可以通过位于储液腔22径向内侧的单向阀60引入储液腔22中，并且通过储液腔22进一步流动到每一个活塞腔21。
替代地，内转动部件20也可以不形成储液腔22，这种方案在图3a和图3b的第三实施例中示出。如图所示，内部转动部件20的多个活塞腔21相互独立，每个活塞腔21可以通过单独的孔口与内转动部件20的内周面连通，并且可以各自在孔口处安装有相应的单向阀60来控制液压流体向活塞腔21内部流动。
在图1a至图1c所示的第一实施例中，引导型面11的周向两端直接延伸到内转动部件20的内周面。引导型面11与相应活塞30的可接触范围限定了两个转动部件之间的预定转动范围。两个转动部件之间传递的扭矩大小取决于两个转动部件在预定转动范围内的相对位置。当传递的扭矩过大使得两个转动部件超出预定转动范围时，活塞30将脱离相应的引导型面11而抵接在相邻引导型面11之间的内转动部件20的内周面上。此时，接触面的压力角为零，压力没有周向分量，在两个转动部件之间仅可能存在沿周向的摩擦力。这使得两个转动部件之间的扭矩传递失效，由此限定了最大可传递扭矩。
不同于第一实施例，在图2a至图2b所示的第二实施例中，设置有限位结构来防止两个转动部件转动超出预定转动范围。如图所示，外转动部件10包括一个或多个第一限位结构12，而内转动部件20包括一个或多个第二限位结构24。当外转动部件10和内转动部件20相对于彼此转动到预定转动范围的极限位置时，至少一部分第一限位结构12分别沿周向抵接相应的第二限位结构24，从而防止两个转动部件进一步转动超出预定转动范围。同时，当达到预定转动范围的极限位置时，两个转动部件还能够通过沿周向相互抵接第一限位结构12和第二限位结构24来传递更大的扭矩。这些限位结构在轴向上的位置既可以与活塞30和/或引导型面11重合或部分重合，也可以与活塞30和/或引导型面11不重合。在图3a和图3b的第三实施例中，也示出了与第二实施例相同的限位结构。在第二实施例和第三实施例中，第一限位结构12和第二限位结构24可以是形成在相应的转动部件上的基本沿周向相互面对的台阶面(如图所示)；或者，第一限位结构12可以是形成在外转动部件10上的台阶面，而第二限位结构可以由安装在内转动部件20上的活塞30来充当(未示出)。
图4a和图4b示出了根据本发明的第四实施例的扭矩传递机构。不同于第一实施例中每个活塞都能够与相应的引导型面11配合来传递双向扭矩的情况，在第四实施例中，每个活塞30只能沿单向的周向方向抵接外转动部件10。因此，第四实施例的扭矩传递机构包括沿周向间隔分布的多个活塞30，并且这些活塞30由至少一个第一活塞30a和至少一个第二活塞30b组成。其中，每个第一活塞30a和每个第二活塞30b分别安装在相应的活塞腔21中。每个活塞腔21大致沿周向延伸，并且能够通过其侧壁引导其中的活塞30(第一活塞30a和/或第二活塞30b)沿周向移动。每个活塞腔21的端部沿周向贯通，使得安装在其中的活塞30的端部能够部分地伸出活塞腔21而抵接外转动部件10。活塞30所抵接的外转动部件10的表面可以是形成或固定在外转动部件10上的结构的径向表面，例如径向延伸的台阶面或挡板。每个第一活塞30a能够在沿周向的第一转动方向上抵接外转动部件10，而每个第二活塞30b能够在与第一转动方向相反的第二转动方向上抵接外转动部件10。当两个转动部件沿某一转动方向转动时，会推动第一活塞30a和第二活塞30b中的一者向着缩回相应的活塞腔21中的方向移动。由此两个转动部件可以通过两组方向相反的周向运动活塞来分别在不同的转动方向上传递扭矩并缓冲振动。
当两个转动部件位于非传扭位置时，所有的活塞30(包括第一活塞30a和第二活塞30b)对外转动部件10产生的推力合力的周向分量为零。这可以包括三种情况：第一种，在非传扭位置，活塞30不接触外转动部件10；第二种，在非传扭位置，活塞30无推力地接触外转动部件10；第三种，在非传扭位置，至少一部分活塞30可以接触外转动部件10，其中单个活塞30对外转动部件10产生的推力不为零，但所有活塞30对外转动部件10产生的推力合力的周向分量为零(在本实施例中，活塞30对外转动部件10产生的推力沿周向方向作用，因此周向分量为零代表推力合力也为零)。在任一种情况下，外转动部件10在非传扭位置不会受到活塞30的周向推力。当外转动部件10相对于内转动部件20朝向某一方向转动而推动对应方向的一组活塞(第一活塞30a或第二活塞30b)时，该组活塞与外转动部件10接触并且向着缩回内转动部件20的方向移动，因此沿相应 方向对外转动部件10的周向推力增大而相反方向的周向推力减小或保持不变，使得作用在所有活塞30在外转动部件10之间的周向推力的合力随着转动位置而朝向相应的方向增加。
优选地，每个活塞30可以具有由相应的活塞腔21限定的最大伸出位置。在外转动部件10沿任一转动方向相对于内转动部件20转动而偏离非传扭位置的过程中，所有的活塞30中未被外转动部件10推动的另一组活塞(第二活塞30b或第一活塞30a)将由相应的活塞腔21约束在最大伸出位置而与外转动部件10分离。具体而言，每个活塞30可以包括沿活塞腔21的延伸方向划分的塞体31和塞头32，其中塞体31的外径大于塞头32的外径。活塞腔21的端部孔口的内径小于活塞腔21内径和塞体31的内径而大于塞头32的外径，使得塞体31无法伸出活塞腔21，但塞头32能够伸出活塞腔21。在最大伸出位置，塞体31将抵接在相应的活塞腔21的端部从而实现限位。如果活塞30在非传扭位置不接触或只能无推力地接触外转动部件10，则活塞30在非传扭位置由相应的活塞腔21限定在最大伸出位置处，外转动部件10向着远离某一组活塞30的方向偏离非传扭位置任意角度都导致活塞30与该组活塞30分离；如果活塞30在非传扭位置以不为零的推力接触外转动部件10，则活塞30在非传扭位置未达到最大伸出位置，在外转动部件10向着远离某一组活塞30的方向偏离非传扭位置的过程中，该组活塞30起初还可以随着外转动部件10的转动而继续伸出相应的活塞腔21，直至外转动部件10转动到某一预定角度时，该组活塞30达到由相应的活塞腔21限定在最大伸出位置并且开始与继续转动的外转动部件10分离。
优选地，外转动部件10可以包括朝向内转动部件20(朝向径向内侧)突起的一个或多个突起部13，内转动部件21可以包括背向外转动部件10(朝向径向内侧)凹入的一个或多个凹陷部25。每个突起部13沿径向插入相应的凹陷部25中，每个活塞30从相应的凹陷部25的侧壁伸出内转动部件20并且能够抵接相应的突起部13的侧壁。此外，第一活塞30a和第二活塞30b优选地在周向上交替分布。其中，沿周向相邻并且伸出方向彼此远离的任意一对第一活塞30a和第二活塞30b构成活塞对，每个活塞对 安装在沿周向延伸的同一活塞腔21中并且分别从该活塞腔21的相反两端伸出。在这种情况下，同一活塞腔21中的活塞对可以共用一个弹性件50，该弹性件50弹性地抵接在活塞对的两个活塞之间。替代地，在第四实施例中，每个活塞30也可以安装在独立的活塞腔21中。在这种情况下，相应的弹性件50可以弹性地抵接在活塞30与活塞腔21的端部之间。
如图4a和图4b所示，在第四实施例中，当两个转动部件转动到预定转动范围的极限位置时，两个转动部件的表面将直接相互抵接。例如，在某一转动方向的极限位置，对应于该转动方向的突起部13将与相应的凹陷部25直接相互抵接，从而能够在两个转动部件之间直接传递扭矩并且防止两个转动部件进一步转动超出预定转动范围。
在第四实施例中，内转动部件20也可以形成有类似于第一实施例的储液腔22和/或连通孔23，其结构与功能与第一实施例中类似，在此不再赘述。同样，在第四实施例中，每个活塞30与相应的活塞腔21的侧壁之间也可以优选地为非密封接触。
需要注意的是，在本发明的各个实施例中，活塞30都可以替代地安装在形成于外转动部件10中的活塞腔中从而能够抵接内转动部件20。这使得两个转动部件上的各种存在配合关系的结构的位置关系在两个转动部件之间交换。为了便于区分，可以将用于抵接活塞30的转动部件统称为第一转动部件，而将用于安装活塞30的转动部件统称为第二转动部件。此外，除了明确说明的差别之外，在任一实施例种描述的技术特征也可以应用于其他实施例中。
在根据本发明的各个实施例的扭矩传递机构中，第一转动部件和第二转动部件通过液压装置来传递扭矩，因此能够通过液压流体来缓冲扭矩振动，从而能够减少噪声。特别是当第一转动部件和第二转动部件位于非传扭位置时，活塞不接触或只能以推力合力的周向分量为零的方式接触第一转动部件。其中，推力合力的周向分量为零的接触状态包含三种接触状态：第一种是所有活塞与第一转动部件之间不存在任何推力(但可能存在静摩擦力)；第二种是至少一部分活塞与第一转动部件之间存在推力，但每个活塞的推力都不具有周向分量(周向分量为零)(第一实施例)；第三种 是至少一部分活塞与第一转动部件之间存在具有周向分量的推力，但所有的活塞与第一转动部件之间的推力合力的周向分量为零，也就是说，不同活塞作用在第一转动部件上的周向推力相互抵消(第四实施例)。当第一转动部件和第二转动部件在预定范围内相对转动而偏离非传扭位置时，第一转动部件能够沿具有周向力分量的方向抵接至少一部分活塞，从而推动该至少一部分活塞缩回第二转动部件来压缩相应的活塞腔中的液压流体，并且通过该至少一部分活塞在第一转动部件与第二转动部件之间传递扭矩。这种扭矩传递方式具有先前参照图5所述的传扭效果。由于液压流体的缓冲作用，可以显著减少转动部件的振动和噪声。这尤其适用于(但不限于)在车辆的变速器中替代常规的花键或齿轮传动机构，以便特别是在停车充电或小油门加速的状态下减少噪声。
通过仿真实验可以验证根据本发明的扭矩传递机构的效果。例如，发明人采用多体动态仿真方法对这种扭矩传递机构的阻尼效果进行了验证。如图6中对车辆变速器的仿真实验的曲线图所示，在充电模式下的冲击力显著减小。这证明，根据本发明的扭矩传递机构可以有利地缓冲扭矩冲击和振动，同时也可以减小牵引启动模式下的最大驱动扭矩。
虽然在上述说明中示例性地描述了可能的实施例，但是应当理解到，仍然通过所有已知的和此外技术人员容易想到的技术特征和实施方式的组合存在大量实施例的变化。此外还应该理解到，示例性的实施方式仅仅作为一个例子，这种实施例绝不以任何形式限制本发明的保护范围、应用和构造。通过前述说明更多地是向技术人员提供一种用于转化至少一个示例性实施方式的技术指导，其中，只要不脱离权利要求书的保护范围，便可以进行各种改变，尤其是关于所述部件的功能和结构方面的改变。
附图标记表
10  外转动部件
11  引导型面
12  第一限位结构
13  突起部
20   内转动部件
21   活塞腔
22   储液腔
23   连通孔
24   第二限位结构
25   凹陷部
30   活塞
30a  第一活塞
30b  第二活塞
31   塞体
32   塞头
40   滚动体
50   弹性件
60   单向阀

Claims (15)

  1. 一种扭矩传递机构，包括能够相对转动的第一转动部件和第二转动部件，所述第一转动部件和所述第二转动部件中的一者布置在另一者的径向内侧，
    其特征在于，
    所述扭矩传递机构还包括液压装置，所述扭矩传递机构配置为能够通过所述液压装置在所述第一转动部件与所述第二转动部件之间传递扭矩。
  2. 根据权利要求1所述的扭矩传递机构，其特征在于，所述液压装置为一个或多个活塞(30)，所述第二转动部件包括用于容纳液压流体的一个或多个活塞腔(21)，每个活塞(30)可移动地安装在相应的活塞腔(21)中从而能够伸出所述第二转动部件以抵接所述第一转动部件。
  3. 根据权利要求2所述的扭矩传递机构，其特征在于，所述第一转动部件和所述第二转动部件具有相对于彼此的非传扭位置，在所述非传扭位置，所述一个或多个活塞(30)不接触或只能以推力合力的周向分量为零的方式接触所述第一转动部件，当所述第一转动部件和所述第二转动部件在预定范围内相对转动而偏离所述非传扭位置时，所述第一转动部件能够沿具有周向力分量的方向抵接所述一个或多个活塞(30)中的至少一部分活塞(30)，从而使所述至少一部分活塞(30)向着缩回所述第二转动部件的方向移动来压缩相应的活塞腔(21)中的液压流体并且能够通过所述至少一部分活塞(30)在所述第一转动部件与所述第二转动部件之间传递扭矩。
  4. 根据权利要求3所述的扭矩传递机构，其特征在于，当每个活塞(30)由所述第一转动部件推动而压缩相应的活塞腔(21)中的液压流体时，所述液压流体能够在相应的活塞(30)与活塞腔(21)之间朝向与相应的活塞(30)的移动方向相反的方向泄漏。
  5. 根据权利要求3所述的扭矩传递机构，其特征在于，所述一个或多个活塞腔(21)包括沿周向间隔分布的多个活塞腔(21)，所述第二转动部件包括环形的储液腔(22)，所述储液腔(22)与每个活塞腔(21)连 通，从而能够向每个活塞腔(21)供应液压流体。
  6. 根据权利要求5所述的扭矩传递机构，其特征在于，每个活塞腔(21)与所述储液腔(22)通过相应的连通孔(23)连通，使得每个活塞腔(21)中的液压流体在受到相应的活塞(30)压缩时能够产生相对于所述储液腔(22)中的液压流体的瞬时高压。
  7. 根据权利要求5所述的扭矩传递机构，其特征在于，每个活塞腔(21)在径向上位于所述储液腔(22)与所述第一转动部件之间。
  8. 根据权利要求3所述的扭矩传递机构，其特征在于，所述扭矩传递机构还包括一个或多个弹性件(50)，每个弹性件(50)设置在相应的活塞腔(21)中并且沿伸出方向弹性地抵接相应的活塞(30)。
  9. 根据权利要求3至8中任一项所述的扭矩传递机构，其特征在于，所述第一转动部件包括朝向所述第二转动部件的一个或多个引导型面(11)，每个活塞(30)可径向移动地安装在相应的活塞腔(21)中并且抵接相应的引导型面(11)，每个引导型面(11)沿背向所述第二转动部件的径向方向凹入并且在周向中部具有最大深度位置，在所述非传扭位置，每个活塞(30)抵接在相应的引导型面(11)的最大深度位置，每个引导型面(11)的凹入深度在周向上从相应的最大深度位置朝向两端逐渐减小，从而在所述第一转动部件和所述第二转动部件偏离所述非传扭位置时推动相应的活塞(30)缩回所述第二转动部件。
  10. 根据权利要求9所述的扭矩传递机构，其特征在于，在垂直于轴向的剖面中，所述一个或多个引导型面(11)中的至少一部分引导型面(11)具有凹入的弧形轮廓，和/或，所述一个或多个活塞(30)中的至少一部分活塞(30)的用于抵接相应的引导型面(11)的端部具有突起的弧形轮廓。
  11. 根据权利要求9所述的扭矩传递机构，其特征在于，所述第一转动部件包括一个或多个第一限位结构(12)，所述第二转动部件包括一个或多个第二限位结构(24)，当所述第一转动部件和所述第二转动部件相对于彼此转动到所述预定转动范围的极限位置时，所述一个或多个第一限位结构(12)中的至少一部分沿周向抵接相应的第二限位结构(24)，从而防止所述第一转动部件和所述第二转动部件转动超过所述预定转动范围。
  12. 根据权利要求3至8中任一项所述的扭矩传递机构，其特征在于，所述一个或多个活塞(30)包括沿周向间隔分布的至少一个第一活塞(30a)和至少一个第二活塞(30b)，每个第一活塞(30a)和每个第二活塞(30b)分别可周向移动地安装在相应的活塞腔(21)中，每个第一活塞(30a)能够在沿周向的第一转动方向上抵接所述第一转动部件，每个第二活塞(30b)能够在与所述第一转动方向相反的第二转动方向上抵接所述第一转动部件。
  13. 根据权利要求12所述的扭矩传递机构，其特征在于，每个活塞(30)具有由相应的活塞腔(21)限定的最大伸出位置，在所述第一转动部件沿任一转动方向相对于所述第二转动部件转动而偏离所述非传扭位置的过程中，所述一个或多个活塞(30)中的一部分活塞(30)被所述第一转动部件向着缩回所述第二转动部件的方向推动，并且所述一个或多个活塞(30)中未被所述第一转动部件推动的活塞(30)能够被约束在相应的最大伸出位置而与所述第一转动部件分离。
  14. 根据权利要求13所述的扭矩传递机构，其特征在于，所述第一转动部件包括朝向所述第二转动部件突起的一个或多个突起部(13)，所述第二转动部件包括背向所述第一转动部件凹入的一个或多个凹陷部(25)，每个突起部(13)沿径向插入相应的凹陷部(25)中，每个活塞(30)从相应的凹陷部(25)的侧壁伸出所述第二转动部件并且能够抵接相应的突起部(13)的侧壁。
  15. 根据权利要求14所述的扭矩传递机构，其特征在于，所述至少一个第一活塞(30a)和所述至少一个第二活塞(30b)在周向上交替分布，所述一个或多个活塞(30)中沿周向相邻并且伸出方向彼此远离的任意一对第一活塞(30a)和第二活塞(30b)构成活塞对，每个活塞对安装在沿周向延伸的同一活塞腔(21)中。
PCT/CN2023/078926 2023-03-01 2023-03-01 扭矩传递机构 Ceased WO2024178656A1 (zh)

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