WO2021027734A1 - 液力变矩器和包括该液力变矩器的车辆 - Google Patents

液力变矩器和包括该液力变矩器的车辆 Download PDF

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Publication number
WO2021027734A1
WO2021027734A1 PCT/CN2020/107871 CN2020107871W WO2021027734A1 WO 2021027734 A1 WO2021027734 A1 WO 2021027734A1 CN 2020107871 W CN2020107871 W CN 2020107871W WO 2021027734 A1 WO2021027734 A1 WO 2021027734A1
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WO
WIPO (PCT)
Prior art keywords
torque converter
flange portion
turbine
converter according
masses
Prior art date
Application number
PCT/CN2020/107871
Other languages
English (en)
French (fr)
Inventor
王盛璋
胡勋
毕荣麟
孙艳霞
Original Assignee
法雷奥凯佩科液力变矩器(南京)有限公司
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 法雷奥凯佩科液力变矩器(南京)有限公司 filed Critical 法雷奥凯佩科液力变矩器(南京)有限公司
Priority to DE112020003828.9T priority Critical patent/DE112020003828T5/de
Priority to KR1020227004570A priority patent/KR20220034200A/ko
Priority to JP2022507919A priority patent/JP7341316B2/ja
Priority to US17/633,872 priority patent/US11773953B2/en
Priority to MX2022001692A priority patent/MX2022001692A/es
Publication of WO2021027734A1 publication Critical patent/WO2021027734A1/zh

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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
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • 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
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/243—Connections between pump shell and cover shell of the turbine
    • 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
    • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • 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
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
    • 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
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces

Definitions

  • This application relates to a hydraulic torque converter, in particular to a hydraulic torque converter with a vibration damping device integrated on a turbine disk.
  • This application relates to a vehicle including the torque converter.
  • a hydraulic torque converter is installed between the internal combustion engine and the transmission, and uses fluid as a working medium to transmit torque, convert torque and clutch.
  • the torque converter may include a vibration damping device (for example, a centrifugal force pendulum) to eliminate torsional vibration inherent in the output of the internal combustion engine.
  • damping devices in the prior art are separate devices separate from the turbine discs of the torque converter and other components. Installing a separate damping device on the turbine disc requires additional parts and complex processes such as welding.
  • the vibration damping device in the prior art usually occupies a relatively large axial distance and squeezes the axial space of the torque converter, which is not conducive to forming a compact torque converter.
  • the object of the present invention is to reduce or eliminate the torsional vibration transmitted through the torque converter.
  • a hydraulic torque converter which includes an impeller disc, which has impeller blades, and a turbine disc, which has a supporting portion that supports turbine blades. Driven by fluid to rotate around the axis of rotation.
  • the turbine disk further has a flange portion that extends outward in the radial direction of the support portion and is integrally formed with the support portion.
  • the hydraulic torque converter further includes a vibration damping device. The mass of the vibration damping device is mounted on the flange portion and is configured to be movable relative to the flange portion and apply a torque on the turbine disk .
  • the mass of the vibration damping device will swing relative to the turbine disk and apply torque in the opposite direction to the turbine disk, thereby achieving a vibration reduction effect.
  • the mass block of the vibration damping device is directly installed on the turbine disc, without other parts, which can realize convenient and simple installation.
  • the flange part and the support part are integrally formed by stamping.
  • the flange part and the supporting part are integrally formed by stamping from the same metal plate, the connection strength between the two is high, and it is easy to realize precise positioning of the flange part and the mass block on it.
  • the flange portion extends outward from a radially outer edge of the support portion.
  • a folded part is provided at the radially outer edge of the support part, and the folded part overlaps with the part of the support part in the axial direction; and the proximal end of the folded part is connected to the support part.
  • a radially outer edge, the distal end of the folded portion is connected to the radially inner edge of the flange portion.
  • the flange portion extends in a plane perpendicular to the axial direction.
  • the flange portion is inclined at a certain angle with respect to a plane perpendicular to the axial direction.
  • the flange portion is inclined in a direction away from the pump wheel disc. According to this technical solution, the flange portion is deflected away from the pump wheel disc for a certain distance in the axial direction, allowing the mass block to be arranged further away from the pump wheel disc, thereby reducing the axial size of the hydraulic torque converter.
  • the hydraulic torque converter includes two masses, which are located on both sides of the flange part; wherein the two masses are fixedly connected to each other by a connecting member, and the connection The piece passes through the through hole on the flange portion and can move along the through hole.
  • the connecting member may be a boat-shaped cushion block, which is an interference fit with the openings on the two mass blocks.
  • the spacer block defines a first track
  • the through hole defines a second track diametrically opposite to the first track
  • the roller is disposed between the first track and the second track.
  • the roller is configured to be able to roll along the first track and the second track at the same time, and the two masses can apply torque on the turbine disk via the roller.
  • each mass has an outer waist-shaped hole
  • the flange portion has an inner waist-shaped hole
  • the outer waist-shaped hole and the inner waist-shaped hole are oriented in opposite radial directions, and the rollers penetrate in the axial direction. Pass the outer waist-shaped hole and the inner waist-shaped hole of the two masses.
  • the roller is configured to be able to roll along the outer waist-shaped hole and the inner waist-shaped hole at the same time, and the two masses can apply torque on the turbine disk via the roller.
  • each mass has an outer spring groove
  • the flange portion has an inner spring groove
  • the outer spring groove and the inner spring groove have the same circumferential length
  • the spring member is arranged in the outer spring groove and the inner spring groove.
  • the spring member is configured to be able to contact only the outer spring groove at one end thereof, and only contact the inner spring groove at the opposite end to achieve compression deformation, and the two masses can be on the turbine disk via the spring member Apply torque.
  • a vehicle including any of the torque converters described above.
  • Figure 1 is an overall side view of a torque converter according to the present invention
  • 2A-2D are schematic diagrams of the flange structure of the turbine disc according to different embodiments.
  • 3A-3C are schematic diagrams of the turbine disk of the torque converter according to the first embodiment
  • 4A-4C are schematic diagrams of a turbine disk of a torque converter according to a second embodiment
  • 5A-5C are schematic diagrams of a turbine disk of a torque converter according to a third embodiment.
  • axial direction refers to the direction parallel to the rotation axis X of the torque converter
  • circumferential direction refers to the direction around the rotation axis X
  • radial direction refers to the direction perpendicular to the rotation axis X
  • outward, outside, etc. refer to the direction away from the axis of rotation X radially outward
  • inward and “inside” refer to the direction toward the axis of rotation X radially inward.
  • Fig. 1 is an overall side view of a torque converter according to the present invention.
  • the hydraulic torque converter includes a pump wheel disc 1, a turbine disc 2, a guide wheel 3, a spring damper 4, a lock-up clutch 5 and a rear housing 6.
  • the output shaft of the upstream internal combustion engine drives the pump wheel disk 1 to rotate via the pump wheel disk hub 7. Since the pump wheel disc 1 and the casing 6 are welded together, they can rotate together.
  • the turbine disc 2 and the spring damper 4 are riveted together, and the spring damper 4 is connected to the output shaft of the torque converter via a spline at the hub to output torque to Downstream transmission.
  • the pump wheel disc 1 and the turbine disc 2 face each other and define a fluid cavity.
  • the impeller disc 1 has impeller blades
  • the turbine disc 2 has turbine blades.
  • the impeller blades can drive the turbine blades to rotate via the fluid in the fluid cavity, and then drive the turbine disk 2 to rotate.
  • the present invention proposes to form an extended annular flange portion 9 on the radially outer side of the turbine disk 2, and install a vibration damping device 8 (for example, a centrifugal force pendulum or a dynamic vibration absorber) on the flange portion 9, and
  • a vibration damping device 8 for example, a centrifugal force pendulum or a dynamic vibration absorber
  • the vibration damping device 8 integrated on the turbine disc 2 can be further used to dampen the vibration, which makes it possible to lock at low speed. Possibly, while improving fuel economy and vehicle comfort.
  • vibration damping device 8 and the turbine disc 2 are integrated, which reduces the number of parts and improves the convenience of installation and operation and the reliability of overall performance.
  • the vibration damping device 8 is arranged on the radially outer side of the turbine disk 2, which does not occupy additional axial space, can avoid interference with other components, and contribute to forming a compact overall structure.
  • the turbine disc 2 includes a hub portion 201, a supporting portion 202, and a connecting portion 203 between the two.
  • the supporting portion 202 has an arc profile defining a fluid cavity, and a turbine blade is installed on one side of its concave surface.
  • the supporting portion 202 is connected to the inner edge of the annular flange portion 9 near the outer edge away from the rotation axis X.
  • the turbine disc 2 can be integrally stamped to form flange portions 9 of different structures, as shown in Figs. 2A-D.
  • the flange portion 9 extends outward from the outer edge of the support portion 202. At this time, the inner edge of the flange portion 9 and the outer edge of the supporting portion 202 directly meet. Unlike this, in FIGS. 2C and 2D, the flange portion 9 extends outward from the folded portion 204 located near the outer edge of the support portion 202. The folded portion 204 overlaps with the portion near the outer edge of the support portion 202 in the axial direction.
  • the proximal end of the folding portion 204 (the end closer to the rotation axis X in material) is connected to the radial outer edge of the support portion 202, and the distal end of the folding portion 204 (the end farther away from the rotation axis X in the material) is connected to the flange portion
  • the radial inner edges of 9 meet.
  • the flange part 9 in Figs. 2C and 2D can be arranged to be offset from the pump wheel 1 (see Fig. 1) by a certain distance.
  • the damping device 8 on the flange portion 9 can be offset away from the pump wheel disk 1, which allows the pump wheel disk 1 to be arranged closer to the housing 6, thereby reducing the volume of the torque converter.
  • the flange portion 9 extends along a plane perpendicular to the rotation axis X. Unlike this, in FIGS. 2B and 2D, the flange portion 9 is inclined at a certain angle with respect to the plane perpendicular to the rotation axis X. Preferably, the inclination on the side away from the pump wheel disc 1 is less than/equal to 5°. Compared with the case where there is no inclination angle, the damping device 8 on the flange portion 9 in Figs. 2B and 2D can be arranged to be inclined away from the pump wheel 1, which allows the pump wheel 1 to be arranged closer to the housing 6, So as to further reduce the volume of the torque converter.
  • 3A to 3C show the first embodiment, in which the vibration damping device 8 is a centrifugal force pendulum 10 of interference fit type.
  • the centrifugal force pendulum 10 includes a pair of masses 11 and 12 located on both sides of the flange 9 of the turbine disk 2, and the two are fixedly connected to each other through a boat-shaped spacer 13.
  • An opening 14 is formed on each of the mass blocks 11 and 12, and a through hole 15 is formed on the flange portion 9.
  • the boat-shaped cushion block 13 passes through the through hole 15, and its two ends are respectively fitted in the mass blocks 11 and 11 in an interference fit manner. 12 of the opening 14 in.
  • the radially outer edge of the spacer 13 defines a first track 18, and the radially outer edge of the through hole 15 of the turbine disk 2 defines a second track 17.
  • the rollers 16 are arranged between the first track 18 and the second track 17, and can simultaneously Swing along the two in a circumferential stroke.
  • the roller 16, the second track 17, and the first track 18 cooperate to make the pair of masses 11 and 12 relative to each other under the action of inertia.
  • the turbine disc 2 swings.
  • the masses 11 and 12 apply fluctuating torques in opposite directions to the turbine disc 2 via the rollers 16, so as to at least partially offset the fluctuating torque on the turbine disc 2 and achieve a vibration reduction effect.
  • each pair of masses 11 and 12 are connected by two spacer blocks 13.
  • the structures of the two spacers 13 and the associated through holes 15 and rollers 16 are identical, and they are staggered by a certain angle in the circumferential direction to promote the masses 11 and 12 to swing smoothly relative to the turbine disk 2.
  • 12 through holes 15 are formed in the flange portion 9 on the outer periphery of the turbine disk 2.
  • other numbers of through holes 15 may be provided on the flange portion 9 for mounting masses 11 and 12 of other numbers and arrangements.
  • damping device 8 is a riveted centrifugal force pendulum 20.
  • the centrifugal force pendulum 20 includes a pair of mass blocks 21 and 22 located on both sides of the flange portion 9 of the turbine disk 2, and the two are fixedly connected to each other by a rivet 23.
  • a rivet mounting hole 24 is formed on each of the masses 21 and 22, and a rivet guide groove 25 is formed on the flange portion 9.
  • the rivet 23 passes through the rivet guide groove 25, and its two ends are respectively fitted to the mass block 21 by interference fit. And 22 in the rivet mounting hole 24.
  • An outer waist-shaped hole 26 is also formed on each mass block 21 and 22, and an inner waist-shaped hole 27 is also formed on the flange portion 9.
  • the outer waist-shaped hole 26 and the inner waist-shaped hole 27 have opposite directions.
  • the outer waist-shaped hole 26 is arched toward the radially inner side
  • the inner waist-shaped hole 27 is arched toward the radially outer side.
  • the rollers 28 are arranged through the outer waist-shaped holes 26 on both sides and the inner waist-shaped holes 27 in the middle.
  • the middle portion of the roller 18 engages the inner waist-shaped hole 27, and the two end portions thereof respectively engage the corresponding outer waist-shaped hole 26.
  • each rivet guide groove 25 also has a waist shape to prevent the rivet 23 from interfering with the rolling of the roller 28.
  • the outer waist-shaped hole 26, the inner waist-shaped hole 27 and the roller 28 cooperate to make the pair of masses 21 and 22 face each other under the action of inertia.
  • the masses 21 and 22 apply fluctuating torque in opposite directions to the turbine disk 2 via the roller 28, so as to at least partially offset the fluctuating torque on the turbine disk 2 and achieve a vibration reduction effect.
  • each pair of masses 21 and 22 are connected to each other by three rivets 23, and has two Rollers 28, each roller 28 is arranged between two adjacent rivets 23.
  • the structures of the two rollers 28 and their associated inner waist-shaped holes 26 and outer waist-shaped holes 27 are identical, and they are staggered by a certain angle in the circumferential direction to promote the masses 21 and 22 to stabilize relative to the turbine disk 2 swing.
  • each set of holes includes three rivet guide grooves 25 and two inner waist-shaped holes 26, and each inner waist-shaped hole 26 Located between two adjacent rivet guide grooves 25.
  • other numbers and arrangements of inner waist-shaped holes 26 and rivet guide grooves 25 may be provided on the flange portion 9.
  • FIG. 5A to 5C show a third embodiment in which the vibration damping device 8 is a dynamic shock absorber 30 with a spring.
  • the dynamic damper 30 includes a pair of masses 31 and 32 located on both sides of the flange portion 9 of the turbine disk 2, and the two masses are fixedly connected to each other by rivets 33.
  • a rivet mounting hole is formed on each mass 31 and 32, and a rivet guide groove 34 is formed on the flange portion 9.
  • the rivet 33 passes through the rivet guide groove 34, and its two ends are respectively riveted to the rivet installation on the masses 31 and 32 hole.
  • the middle part of the rivet 33 can slide along the rivet guide groove 34 so that the masses 31 and 32 coupled with the rivet 33 can swing on a circumferential stroke.
  • An outer spring groove 35 is also formed on each of the masses 31 and 32, and an inner spring groove 36 is also formed on the flange portion 9.
  • the inner spring groove 36 and the outer spring groove 35 both extend in the circumferential direction and are aligned with each other, and both have the same circumferential length.
  • a spring member (not shown), such as a spiral straight spring, is arranged in the inner spring groove 36 and the outer spring groove 35. In the static state, one end of the spring member abuts against the first end of the inner spring groove 36 and the outer spring groove 35 at the same time, and the other end of the spring member abuts against the opposite second end of the inner spring groove 36 and the outer spring groove 35 at the same time.
  • the masses 31 and 32 swing relative to the turbine disk 2 under the action of inertia, so that one end of the spring member is separated from the inner spring groove 36 on the turbine disk 2 and only interacts with the mass.
  • the ends of the outer spring groove 35 of the blocks 31 and 32 are in contact; at the same time, the opposite end of the spring member is separated from the outer spring groove 35 of the masses 31 and 32 and only contacts the end of the inner spring groove 36 on the turbine disc 2 .
  • the spring member is compressed and deformed.
  • the masses 31 and 32 apply fluctuating torque in opposite directions to the turbine disk 2 via the spring member, so as to at least partially offset the fluctuating torque on the turbine disk 2 to achieve a vibration damping effect.
  • each pair of masses 31 and 32 are connected by two rivets 33, which are located at The two opposite circumferential sides of the spring member.
  • the structures of the two rivets 33 and the associated rivet guide grooves 34 are identical, and they are staggered by a certain angle in the circumferential direction to promote the masses 31 and 32 to swing smoothly relative to the turbine disk 2.
  • Each set of holes includes two rivet guide grooves 34 and one inner spring groove 36, and each inner spring groove 36 is located at two Between the rivet guide slots 34. In other embodiments, other numbers of inner spring grooves 36 and rivet guide grooves 34 may be provided on the flange portion 9.
  • vehicles such as automobiles, construction vehicles, and agricultural vehicles may include the torque converter as described above. Since the hydraulic torque converter integrates a vibration damping device on the turbine disk, this vibration damping device can provide an additional damping effect to eliminate the torque vibration generated by the internal combustion engine of the vehicle. This is beneficial in saving fuel consumption, reducing noise, and improving vehicle reliability.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Mechanical Operated Clutches (AREA)
  • Control Of Fluid Gearings (AREA)
  • Vibration Dampers (AREA)

Abstract

本发明公开了一种液力变矩器，包括泵轮盘，其具有泵轮叶片；涡轮盘，其具有支撑部，所述支撑部支撑涡轮叶片，涡轮叶片由泵轮叶片经由流体驱动而围绕转动轴线旋转。涡轮盘还具有法兰部，所述法兰部在所述支撑部的径向外侧向外延伸，并与所述支撑部一体成型。所述液力变矩器还包括减振装置，减振装置的质量块安装在所述法兰部上，并且配置为能够相对于所述法兰部移动，并在所述涡轮盘上施加扭矩，从而消减涡轮盘上的扭矩振动。另外，本发明还公开了一种包括该液力变矩器的车辆。

Description

液力变矩器和包括该液力变矩器的车辆 技术领域
本申请涉及液力变矩器，具体涉及一种在涡轮盘上集成减振装置的液力变矩器。本申请涉及包括该液力变矩器的车辆。
背景技术
在车辆传动系中，液力变矩器安装在内燃机和变速器之间，利用流体作为工作介质起到传递扭矩、变矩和离合的作用。液力变矩器可以包括减振装置(例如，离心力摆)，用于消除内燃机的输出所固有的扭转振动。
通过改进液力变矩器的结构而降低扭转振动的需求一直存在。
然而，现有技术中的减振装置大多是与液力变矩器的涡轮盘等部件分开的单独装置。将单独的减振装置安装在涡轮盘上需要额外的零部件，还需要焊接等复杂工艺。另外，现有技术中的减振装置通常占据较大的轴向距离，挤占了液力变矩器的轴向空间，不利于形成紧凑的液力变矩器。
因此，期望提供一种具有改进结构的液力变矩器，以至少克服现有技术中存在的诸多问题。
发明内容
本发明的目的在于降低或消除传递通过液力变矩器的扭转振动。
在本发明的一方面，提供了一种液力变矩器，包括泵轮盘，其具有泵轮叶片；涡轮盘，其具有支撑部，所述支撑部支撑涡轮叶片，涡轮叶片由泵轮叶片经由流体驱动而围绕转动轴线旋转。涡轮盘还具有法兰部，所述法兰部在所述支撑部的径向外侧向外延伸，并与所述支撑部一体成型。所述液力变矩器还包括减振装置，减振装置的质量块安装在所述法兰部上，并且配置为能够相对于所述法兰部移动，并在所述涡轮盘上施加扭矩。根据这一技术方案，如果涡轮盘上存在扭矩波动，在惯性作用下，减振装置的质量块将相对于涡轮盘摆动，并在涡轮盘上施加相反方向的扭矩，从而实现减振效果。另外，减振装置的质量块是直接安装在涡轮盘上，无需其它的零部件，可实现方便简单的安装。
在一些实施例中，所述法兰部和所述支撑部通过冲压一体成型。根据这 一技术方案，法兰部和支撑部利用同一金属板材一体冲压形成，二者之间的连接强度高，且易于实现对于法兰部和其上的质量块的精准定位。
在一些实施例中，所述法兰部从支撑部的径向外边缘处向外延伸。
在一些实施例中，所述支撑部的径向外边缘处设置折叠部，所述折叠部与支撑部的部分在轴向方向上重叠；并且，所述折叠部的近端连接至支撑部的径向外边缘，所述折叠部的远端连接至所述法兰部的径向内边缘。根据这一技术方案，法兰部在轴向方向上远离泵轮盘偏移一段距离，允许质量块布置得更加远离泵轮盘，从而能够缩小液力变矩器的轴向尺寸。
在一些实施例中，所述法兰部在垂直于轴向方向的平面中延伸。
在一些实施例中，所述法兰部相对于垂直于轴向方向的平面倾斜一定角度。有利地，所述法兰部在远离泵轮盘的方向上倾斜。根据这一技术方案，法兰部在轴向方向上远离泵轮盘偏转一段距离，允许质量块布置得更加远离泵轮盘，从而能够缩小液力变矩器的轴向尺寸。
在一些实施例中，所述的液力变矩器包括两个质量块，其位于在所述法兰部的两侧；其中，所述两个质量块由连接件彼此固定联接，所述连接件穿过所述法兰部上的通孔并能够沿着所述通孔移动。
在一些实施例中，所述连接件可以是船形的垫块，其与所述两个质量块上的开口过盈配合。所述垫块限定第一轨道，所述通孔限定与第一轨道径向相对的第二轨道，滚子设置在第一轨道和第二轨道之间。滚子配置为能够同时沿着第一轨道和第二轨道滚动，并且，所述两个质量块能够经由所述滚子在涡轮盘上施加扭矩。
在一些实施例中，每个质量块具有外腰形孔，法兰部具有内腰形孔，外腰形孔和内腰形孔沿相反的径向方向取向，滚子在轴向方向上穿过两个质量块的外腰形孔和内腰形孔。滚子配置为能够同时沿着外腰形孔和内腰形孔滚动，并且，所述两个质量块能够经由所述滚子在涡轮盘上施加扭矩。
在一些实施例中，每个质量块具有外弹簧槽，法兰部具有内弹簧槽，外弹簧槽和内弹簧槽具有相同的周向长度，弹簧件设置在外弹簧槽和内弹簧槽内。弹簧件配置为能够在其一端仅接触外弹簧槽，且在相反的另一端仅接触内弹簧槽，以此实现压缩变形，并且，所述两个质量块能够经由所述弹簧件在涡轮盘上施加扭矩。
在本发明的另一方面，提供了一种车辆，包括根据上文所述的任一种液 力变矩器。
附图说明
图1是根据本发明的液力变矩器的总体侧视图；
图2A-2D是根据不同实施例的涡轮盘的法兰部结构的示意图；
图3A-3C是根据第一实施例的液力变矩器的涡轮盘的示意图；
图4A-4C是根据第二实施例的液力变矩器的涡轮盘的示意图；
图5A-5C是根据第三实施例的液力变矩器的涡轮盘的示意图。
具体实施方式
下面结合附图详细描述本发明的具体实施方式。附图中具有相同和相似附图标记的部件具有相同或相似的功能。
在以下说明中，“轴向方向”指平行于液力变矩器旋转轴线X的方向；“周向方向”指围绕旋转轴线X的方向；“径向方向”指垂直于旋转轴线X的方向，其中，“向外”、“外侧”等指远离转动轴线X径向向外的方向，“向内”、“内侧”指靠近转动轴线X径向向内的方向。
图1是根据本发明的液力变矩器的总体侧视图。如图1所示，液力变矩器包括泵轮盘1、涡轮盘2、导轮3、弹簧减振器4、锁止离合器5和后壳6。在液力变矩器的输入侧，上游的内燃机的输出轴经由泵轮盘毂7驱动泵轮盘1转动。由于泵轮盘1与外壳6焊接在一起，二者可一同转动。在液力变矩器的输出侧，涡轮盘2和弹簧减振器4铆接在一起，弹簧减振器4经由位于毂部的花键连接至液力变矩器的输出轴，以输出扭矩至下游的变速器。泵轮盘1和涡轮盘2彼此面对，并限定流体腔。泵轮盘1具有泵轮叶片，涡轮盘2具有涡轮叶片。泵轮叶片可以经由流体腔中的流体驱动涡轮叶片转动，继而驱动涡轮盘2转动。
当锁止离合器5被致动打开时，外壳6和弹簧减振器4之间的动力传递断开，此时，泵轮盘1仅经由流体驱动涡轮盘2转动，涡轮盘2驱动输出轴转动。这在汽车起步时是有利的，能够起到有效增扭的作用。
当锁止离合器5被致动闭合时，外壳6和弹簧减振器4之间的动力传递接通，此时，泵轮盘1的扭矩依次通过后壳6、锁止离合器5、弹簧减振器4传递至输出轴，弹簧减振器4带动涡轮盘2一起转动。在这一情况下，内燃 机的扭矩波动会传递至下游的变速器，虽然弹簧减振器4可以部分地吸收这一扭矩波动，但依然存在振动、噪音和油耗等方面的问题。
对此，本发明提出，在涡轮盘2的径向外侧形成延伸的具有环形的法兰部9，将减振装置8(例如，离心力摆或动力吸振器)安装在该法兰部9上，从而实现减振装置8和涡轮盘2集成于一体。
在此情况下，当锁止离合器5被闭合时，可以在弹簧减振器4减振的基础上，进一步利用集成在涡轮盘2上的减振装置8减振，这使得在低速下闭锁成为可能，同时提高了燃油经济性和整车的舒适性。
另外，减振装置8和涡轮盘2集成一体，降低了零部件数量，提高了安装操作的便利性和整体性能的可靠性。
再者，减振装置8设置在涡轮盘2的径向外侧，其不占据额外的轴向空间，可避免和其它部件干涉，并有助于形成紧凑的整体结构。
如图2A-D所示，涡轮盘2包括轮毂部201、支撑部202和位于二者之间的连接部203。支撑部202具有限定流体腔的弧形轮廓，在其凹面一侧上安装涡轮叶片。支撑部202在远离转动轴线X的外边缘附近连接至环形的法兰部9的内边缘。涡轮盘2可以一体冲压形成不同结构的法兰部9，如图2A-D所示。
在图2A和图2B中，法兰部9从支撑部202的外边缘处向外延伸。此时，法兰部9的内边缘和支撑部202的外边缘直接相接。与此不同，在图2C和图2D中，法兰部9从位于支撑部202的外边缘附近的折叠部204向外延伸。折叠部204与支撑部202的外边缘附近的部分在轴向上重叠。折叠部204的近端(材料上更靠近转动轴线X的一端)与支撑部202的径向外边缘相接，折叠部204的远端(材料上更远离转动轴线X的一端)与法兰部9的径向内边缘相接。与没有折叠部的情况相比，图2C和图2D中的法兰部9可以设置为远离泵轮盘1(参见图1)偏移一定距离。由此，法兰部9上的减振装置8可以远离泵轮盘1偏移，这允许泵轮盘1设置得更为靠近外壳6，从而缩小液力变矩器的体积。
在图2A和图2C中，法兰部9沿着与转动轴线X垂直的平面延伸。与此不同，在图2B和图2D中，法兰部9相对于与转动轴线X垂直的平面倾斜一定角度。优选地，在远离泵轮盘1的一侧倾斜小于/等于5°。与不存在倾斜角度的情况相比，图2B和图2D中的法兰部9上的减振装置8可以设 置为远离泵轮盘1倾斜，这允许泵轮盘1设置得更靠近外壳6，从而进一步地缩小液力变矩器的体积。
下面结合附图描述本发明的三种具体实施例。需注意，以下实施例仅用于向本领域技术人员呈现实施本发明的一些可行路径。本领域技术人员可对这些实施例进行调整，这些调整均属于本发明的保护范围。
第一实施例
图3A至图3C示出了第一实施例，其中，减振装置8是过盈配合式的离心力摆10。
如图3C所示，离心力摆10包括位于涡轮盘2的法兰部9两侧的一对质量块11和12，二者通过船形的垫块13彼此固定联接。在每个质量块11和12上形成开口14，在法兰部9上形成通孔15，船形的垫块13穿过通孔15，其两端分别以过盈配合方式配合在质量块11和12的开口14中。
垫块13的径向外边限定第一轨道18，涡轮盘2的通孔15的径向外边限定第二轨道17，滚子16设置在第一轨道18和第二轨道17之间，并能够同时沿着二者在一段周向行程上摆动。
在操作中，当涡轮盘2上存在波动的扭矩时，滚子16、第二轨道17、和第一轨道18三者协作，以使所述一对质量块11和12在惯性作用下相对于涡轮盘2摆动，在此期间，质量块11和12经由滚子16向涡轮盘2施加相反方向的波动扭矩，从而至少部分地抵消涡轮盘2上的波动扭矩，实现减振效果。
如图3A所示，六对质量块在轮盘2的法兰部9上沿着周向方向上均匀布置，其中，每一对质量块11和12通过两个垫块13联接。这两个垫块13的结构以及相关联的通孔15和滚子16的结构是等同的，它们沿周向方向错开一定角度，以促进质量块11和12相对于涡轮盘2平稳地摆动。
如图3B所示，在涡轮盘2的外周的法兰部9上形成12个通孔15。在其它实施例中，可以在法兰部9上设置其他数量的通孔15，用于安装其它数量和布置的质量块11、12。
第二实施例
图4A至图4C示出了第二实施例，其中，减振装置8是铆接式的离心力摆20。
如图4C所示，离心力摆20包括位于涡轮盘2的法兰部9两侧的一对质 量块21和22，二者通过铆钉23彼此固定联接。在每个质量块21和22上形成铆钉安装孔24，在法兰部9上形成铆钉引导槽25，铆钉23穿过铆钉引导槽25，其两端分别以过盈配合方式配合在质量块21和22的铆钉安装孔24中。
在每个质量块21和22上还形成外腰形孔26，在法兰部9上还形成内腰形孔27。外腰形孔26和内腰形孔27具有相反的朝向。在所示的实施例中，外腰形孔26朝向径向内侧拱起，而内腰形孔27朝向径向外侧拱起。滚子28穿过两侧的外腰形孔26和中间的内腰形孔27布置。滚子18的中间部分接合内腰形孔27，其两个端部部分分别接合相应的外腰形孔26。如此布置的内腰形孔27和外腰形孔26允许滚子28同时沿着外腰形孔27和内腰形孔26在一段周向行程上滚动。此外，如图4B所示，每个铆钉引导槽25也具有腰形的形状，以避免铆钉23干涉滚子28的滚动。
在操作中，当涡轮盘2上存在波动的扭矩时，外腰形孔26、内腰形孔27和滚子28三者协作，以使得所述一对质量块21和22在惯性作用下相对于涡轮盘2摆动，在此期间，质量块21和22经由滚子28向涡轮盘2施加相反方向的波动扭矩，从而至少部分地抵消涡轮盘2上的波动扭矩，实现减振效果。
如图4A所示，四对质量块沿着轮盘2的法兰部9在周向方向上均匀布置，其中，每一对质量块21和22通过三个铆钉23彼此联接，并具有两个滚子28，每个滚子28设置在两个相邻的铆钉23中间。两个滚子28及其相关联的内腰形孔26和外腰形孔27的结构是等同的，它们沿周向方向错开一定角度，以促进质量块21和22相对于涡轮盘2平稳地摆动。
如图4B所示，在涡轮盘2的外周的法兰部9上形成四组孔，每一组孔包括三个铆钉引导槽25和两个内腰型孔26，每个内腰型孔26位于两个相邻的铆钉引导槽25之间。在其它实施例中，可以在法兰部9上设置其他数量和布置的内腰形孔26和铆钉引导槽25。
第三实施例
图5A至图5C示出了第三实施例，其中，减振装置8是具有弹簧的动力减振器30。
如图5C所示，动力减振器30包括位于涡轮盘2的法兰部9两侧的一对质量块31和32，二者通过铆钉33彼此固定联接。在每个质量块31和32上 形成铆钉安装孔，在法兰部9上形成铆钉引导槽34，铆钉33穿过铆钉引导槽34，其两端分别铆接至质量块31和32上的铆钉安装孔。铆钉33的中间部分可以沿着铆钉引导槽34滑动，使得与铆钉33联接的质量块31和32能够在一段周向行程上摆动。
在每个质量块31和32上还形成外弹簧槽35，在法兰部9上还形成内弹簧槽36。内弹簧槽36和外弹簧槽35均沿周向方向延伸且彼此对准，二者具有相同的周向长度。在内弹簧槽36和外弹簧槽35内设置一弹簧件(未示出)，例如螺旋形直弹簧。在静止状态，弹簧件的一端同时抵靠内弹簧槽36和外弹簧槽35的第一端，弹簧件的另一端同时抵靠内弹簧槽36和外弹簧槽35的相对的第二端。
在操作中，当涡轮盘2上存在波动的扭矩时，质量块31和32在惯性作用下相对于涡轮盘2摆动，使得弹簧件的一端脱离涡轮盘2上的内弹簧槽36而仅与质量块31和32的外弹簧槽35的端部接触；同时，弹簧件的相反的另一端脱离质量块31和32的外弹簧槽35而仅与涡轮盘2上的内弹簧槽36的端部接触。由此，弹簧件压缩变形。在此期间，质量块31和32经由弹簧件向涡轮盘2施加相反方向的波动扭矩，从而至少部分地抵消涡轮盘2上的波动扭矩，实现减振效果。
如图5A所示，四对质量块沿着轮盘2的法兰部9在周向方向上均匀布置，其中，每一对质量块31和32通过两个铆钉33联接，两个铆钉33位于弹簧件的周向相反的两侧。两个铆钉33及其关联的铆钉引导槽34的结构是等同的，它们沿周向方向错开一定角度，以促进质量块31和32相对于涡轮盘2平稳地摆动。
如图5B所示，在涡轮盘2的外周的法兰部9上形成四组孔，每一组孔包括两个铆钉引导槽34和一个内弹簧槽36，每个内弹簧槽36位于两个的铆钉引导槽34之间。在其它实施例中，可以在法兰部9上设置其他数量的内弹簧槽36和铆钉引导槽34。
实际中，诸如汽车、工程车、农用车等车辆可以包括如上所述的液力变矩器。由于该液力变矩器在涡轮盘上集成了减振装置，这一减振装置可以提供额外的减振效果，以消除车辆内燃机所产生的扭矩振动。这对节省油耗、降低噪音、提高车辆可靠性等方面均具有益处。
上文已经详细描述了用于实现本发明的某些最佳实施例和其他实施例， 但应理解，这些实施例的作用仅在于举例，而不在于以任何方式限制本发明的范围、适用或构造。本发明的保护范围由所附权利要求及其等同方式限定。本领域技术人员可以在本发明的教导下对前述各实施例作出诸多改变，这些改变均落入本发明的保护范围。
附图说明
1 泵轮盘
2 涡轮盘
3 导轮
4 弹簧减振器
5 锁止离合器
6 后壳
7 泵轮盘毂
8 减振装置
9 法兰部
201 轮毂部
202 支撑部
203 连接部
204 折叠部
10 离心力摆
11 质量块
12 质量块
13 垫块
14 开口
15 通孔
16 滚子
17 第二轨道
18 第一轨道
20 离心力摆
21 质量块
22 质量块
23 铆钉
24 铆钉安装孔
25 铆钉引导槽
26 外腰形孔
27 内腰形孔
28 滚子
30 动力减振器
31 质量块
32 质量块
33 铆钉
34 铆钉引导槽
35 内弹簧槽
36 外弹簧槽

Claims (12)

  1. 一种液力变矩器，包括：
    泵轮盘(1)，其具有泵轮叶片；
    涡轮盘(2)，其具有支撑部(202)，所述支撑部支撑涡轮叶片，涡轮叶片由泵轮叶片经由流体驱动而围绕转动轴线(X)旋转；
    其中，涡轮盘还具有法兰部(9)，所述法兰部在所述支撑部的径向外侧向外延伸，并与所述支撑部一体成型；
    其中，所述液力变矩器还包括减振装置(8)，减振装置(8)的质量块(11、12、21、22、31、32)安装在所述法兰部上，并且配置为能够相对于所述法兰部移动，并在所述涡轮盘上施加扭矩。
  2. 根据权利要求1所述的液力变矩器，其中，
    所述法兰部和所述支撑部通过冲压一体成型。
  3. 根据权利要求1所述的液力变矩器，其中，
    所述法兰部从支撑部的径向外边缘处向外延伸。
  4. 根据权利要求1所述的液力变矩器，其中，
    所述支撑部的径向外边缘处设置折叠部(204)，所述折叠部与支撑部的部分在轴向方向上重叠；并且
    所述折叠部的近端连接至支撑部的径向外边缘，所述折叠部的远端连接至所述法兰部的径向内边缘。
  5. 根据权利要求3或4所述的液力变矩器，其中，
    所述法兰部在垂直于轴向方向的平面中延伸。
  6. 根据权利要求3或4所述的液力变矩器，其中，
    所述法兰部相对于垂直于轴向方向的平面倾斜一定角度。
  7. 根据权利要求6所述的液力变矩器，其中，
    所述法兰部在远离泵轮盘的方向上倾斜。
  8. 根据权利要求1所述的液力变矩器，其中，
    包括两个质量块，其位于在所述法兰部的两侧；
    其中，所述两个质量块由连接件(13、23、33)彼此固定连接，所述连接件穿过所述法兰部上的通孔(15、25、34)并能够沿着所述通孔移动。
  9. 根据权利要求8所述的液力变矩器，其中，
    所述连接件为船形的垫块(13)，其与所述两个质量块(11、21)上的开 口(14)过盈配合；
    所述垫块限定第一轨道(18)，所述通孔限定与第一轨道径向相对的第二轨道(17)，滚子(16)设置在第一轨道和第二轨道之间；
    其中，滚子配置为能够同时沿着第一轨道和第二轨道滚动，并且，所述两个质量块能够经由所述滚子在涡轮盘上施加扭矩。
  10. 根据权利要求8所述的液力变矩器，其中，
    每个质量块(21、22)具有外腰形孔(26)，法兰部具有内腰形孔(27)，外腰形孔和内腰形孔沿相反的径向方向取向，滚子(28)在轴向方向上穿过两个质量块的外腰形孔和内腰形孔；
    其中，滚子配置为能够同时沿着外腰形孔和内腰形孔滚动，并且，所述两个质量块能够经由所述滚子在涡轮盘上施加扭矩。
  11. 根据权利要求8所述的液力变矩器，其中，
    每个质量块具有外弹簧槽(38)，法兰部具有内弹簧槽(36)，外弹簧槽和内弹簧槽具有相同的周向长度，弹簧件设置在外弹簧槽和内弹簧槽内；
    其中，弹簧件配置为能够在其一端仅接触外弹簧槽，且在相反的另一端仅接触内弹簧槽，以此实现压缩变形，并且，所述两个质量块能够经由所述弹簧件在涡轮盘上施加扭矩。
  12. 一种车辆，其中，包括根据权利要求1至11中的任一项所述的液力变矩器。
PCT/CN2020/107871 2019-08-09 2020-08-07 液力变矩器和包括该液力变矩器的车辆 WO2021027734A1 (zh)

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DE112020003828.9T DE112020003828T5 (de) 2019-08-09 2020-08-07 Drehmomentwandler und fahrzeug, welches den drehmomentwandler enthält
KR1020227004570A KR20220034200A (ko) 2019-08-09 2020-08-07 토크 컨버터 및 토크 컨버터를 포함하는 차량
JP2022507919A JP7341316B2 (ja) 2019-08-09 2020-08-07 トルクコンバータおよびトルクコンバータを含む車両
US17/633,872 US11773953B2 (en) 2019-08-09 2020-08-07 Torque converter and vehicle including the torque converter
MX2022001692A MX2022001692A (es) 2019-08-09 2020-08-07 Convertidor de esfuerzo de torsión y vehículo que incluye el convertidor de esfuerzo de torsión.

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US20220325785A1 (en) 2022-10-13
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