Torque converter and vehicle including the same

Abstract

The present invention discloses a hydraulic torque converter, comprising an impeller disc having impeller blades; a turbine disc having a support portion, wherein the support portion supports the turbine blades, and the turbine blades are driven by the impeller blades via a fluid to rotate around a rotation axis. The turbine disc also has a flange portion, which is located radially outside the support portion and extends outward, and is integrally formed with the support portion. The hydraulic torque converter also includes a vibration damping device, wherein a mass block of the vibration damping device is mounted on the flange portion and is configured to be movable relative to the flange portion and to absorb torque fluctuations on the turbine disc, thereby reducing torque vibrations on the turbine disc. In addition, the present invention also discloses a vehicle including the hydraulic torque converter.

Description

Technical Field

[0001] The present application relates to a hydraulic torque converter, and more particularly to a hydraulic torque converter with a vibration damping device integrated on a turbine disk. The present application also relates to a vehicle including the hydraulic torque converter. Background Art

[0002] In a vehicle's powertrain, a torque converter is installed between the internal combustion engine and the transmission, utilizing fluid as a working medium to transmit torque, convert torque, and engage / disengage the clutch. The torque converter may include a vibration damping device (e.g., a centrifugal pendulum) to eliminate torsional vibrations inherent in the engine's output.

[0003] There has always been a demand to reduce torsional vibration by improving the structure of the torque converter.

[0004] However, conventional vibration dampers are often separate from components such as the torque converter's turbine disk. Mounting a separate vibration damper on the turbine disk requires additional parts and complex processes such as welding. Furthermore, conventional vibration dampers typically occupy a significant axial distance, encroaching on the torque converter's axial space and hindering the creation of a compact torque converter.

[0005] Therefore, it is desired to provide a torque converter with an improved structure to at least overcome the problems existing in the prior art. Summary of the Invention

[0006] An object of the present invention is to reduce or eliminate torsional vibrations from an engine.

[0007] In one aspect of the present invention, a hydraulic torque converter is provided, comprising an impeller disc having impeller blades; a turbine disc having a support portion, wherein the support portion supports the turbine blades, and the turbine blades are driven by the impeller blades via the fluid to rotate around the axis of rotation. The turbine disc also has a flange portion, which is located radially outside the support portion and extends outward, and is integrally formed with the support portion. The hydraulic torque converter also includes a vibration damping device, wherein a mass block of the vibration damping device is mounted on the flange portion and is configured to be movable relative to the flange portion and to absorb torque fluctuations on the turbine disc. According to this technical solution, if there is torque fluctuation on the turbine disc, under the action of inertia, the mass block of the vibration damping device will swing relative to the turbine disc, thereby achieving a vibration damping effect. In addition, the mass block of the vibration damping device is directly mounted on the turbine disc, without the need for other components, and can be conveniently and simply installed.

[0008] In some embodiments, the flange portion and the support portion are integrally formed by stamping. According to this technical solution, the flange portion and the support portion are integrally stamped from the same metal sheet, which provides a high connection strength and facilitates accurate positioning of the flange portion and the mass thereon.

[0009] In some embodiments, the flange portion extends outward from a radially outer edge of the support portion.

[0010] In some embodiments, a folded portion is provided at the radially outer edge of the support portion, the folded portion axially overlapping a portion of the support portion. Furthermore, the proximal end of the folded portion is connected to the radially outer edge of the support portion, while the distal end of the folded portion is connected to the radially inner edge of the flange portion. According to this technical solution, the flange portion is axially offset from the pump impeller disc, allowing the mass to be positioned further away from the pump impeller disc, thereby reducing the axial size of the torque converter.

[0011] In some embodiments, the flange portion extends in a plane perpendicular to the axial direction.

[0012] In some embodiments, the flange portion is inclined at a predetermined angle relative to a plane perpendicular to the axial direction. Advantageously, the flange portion is inclined away from the pump impeller disc. According to this technical solution, the flange portion is deflected a certain distance away from the pump impeller disc in the axial direction, allowing the mass to be positioned further away from the pump impeller disc, thereby reducing the axial dimension of the torque converter.

[0013] In some embodiments, the torque converter includes two mass blocks, which are located on both sides of the flange portion; wherein the two mass blocks are fixedly connected to each other by a connecting member, and the connecting member passes through a through hole on the flange portion and is capable of moving along the through hole.

[0014] In some embodiments, the connector can be a boat-shaped spacer that forms an interference fit with openings in the two masses. The spacer defines a first track, the through-hole defines a second track radially opposite the first track, and the roller is disposed between the first and second tracks. The roller is configured to roll simultaneously along the first and second tracks, and the two masses can apply torque to the turbine disk via the roller.

[0015] In some embodiments, each mass has an outer waist-shaped hole, and the flange has an inner waist-shaped hole. The outer and inner waist-shaped holes are oriented in opposite radial directions, and rollers axially pass through the outer and inner waist-shaped holes of the two masses. The rollers are configured to roll simultaneously along the outer and inner waist-shaped holes, and the two masses can apply torque to the turbine disk via the rollers.

[0016] In some embodiments, each mass has an outer spring slot, and the flange has an inner spring slot. The outer and inner spring slots have the same circumferential length, and a spring member is disposed within the outer and inner spring slots. The spring member is configured to contact only the outer spring slot at one end and only the inner spring slot at the opposite end during compression deformation. Furthermore, the two masses are capable of applying torque to the turbine disk via the spring member.

[0017] In another aspect of the present invention, a vehicle is provided, comprising any one of the torque converters described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is an overall side view of a torque converter according to the present invention;

[0019] Figure 2A -D is a schematic diagram of the flange structure of a turbine disk according to different embodiments;

[0020] Figure 3A -C is a schematic diagram of a turbine disk of a torque converter according to the first embodiment;

[0021] Figure 4A -C is a schematic diagram of a turbine disk of a torque converter according to a second embodiment;

[0022] Figure 5A -C is a schematic diagram of a turbine disk of a torque converter according to a third embodiment. DETAILED DESCRIPTION

[0023] The following describes the specific embodiments of the present invention in detail with reference to the accompanying drawings. Components with the same or similar reference numerals in the accompanying drawings have the same or similar functions.

[0024] In the following description, "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, among which "outward", "outside", etc. refer to the direction radially outward away from the rotation axis X, and "inward" and "inside" refer to the direction radially inward close to the rotation axis X.

[0025] Figure 1 FIG. 1 is an overall side view of a torque converter according to the present invention. Figure 1As shown, the torque converter includes an impeller disc 1, a turbine disc 2, a guide wheel 3, a spring damper 4, a lock-up clutch 5 and a rear housing 6. On the input side of the torque converter, the output shaft of the upstream internal combustion engine drives the welded impeller disc 1 and the rear housing 6 to rotate together. On the output side of the torque converter, the turbine disc 2 and the spring damper 4 are riveted together, and the spring damper 4 is connected to the input shaft of the transmission via a spline located on the hub to output torque to the downstream transmission. The impeller disc 1 and the turbine disc 2 face each other and define a fluid cavity. The impeller disc 1 has impeller blades, and the turbine disc 2 has turbine blades. The impeller blades can drive the turbine disc 2 to rotate via the fluid in the fluid cavity.

[0026] When the lockup clutch 5 is disengaged, the power transmission between the rear housing 6 and the spring damper 4 is disconnected. At this point, the pump impeller 1 drives the turbine disc 2 solely through the fluid, which in turn drives the output shaft. This is beneficial when the vehicle is starting, effectively increasing torque.

[0027] When the lockup clutch 5 is closed, power transmission between the rear housing 6 and the spring damper 4 is established. Torque is then transmitted to the output shaft through the rear housing 6, the lockup clutch 5, and the spring damper 4. The spring damper 4 then rotates the turbine disk 2. In this situation, torque fluctuations from the internal combustion engine are transmitted to the downstream transmission. While the spring damper 4 can partially absorb these torque fluctuations, issues with vibration, noise, and fuel consumption still exist.

[0028] To this end, the present invention proposes to form an extended annular flange portion 9 on the radial outer side of the turbine disk 2, and install a vibration damping device 8 (for example, a centrifugal pendulum or a dynamic vibration absorber) on the flange portion 9, thereby integrating the vibration damping device 8 and the turbine disk 2 into one.

[0029] In this case, when the lockup clutch 5 is closed, the vibration reduction device 8 integrated on the turbine disc 2 can be further utilized to reduce vibration on the basis of the vibration reduction of the spring vibration reducer 4, which makes locking possible at low speeds while improving fuel economy and vehicle comfort.

[0030] In addition, the vibration damping device 8 and the turbine disk 2 are integrated into one body, which reduces the number of parts and improves the convenience of installation operation and the reliability of overall performance.

[0031] Furthermore, 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 helps to form a compact overall structure.

[0032] like Figure 2AAs shown in FIG. 2-D, the turbine disk 2 includes a hub portion 201, a support portion 202, and a connecting portion 203 located therebetween. The support portion 202 has an arcuate profile defining a fluid chamber, and turbine blades are mounted on its concave side. The support portion 202 is connected to the inner edge of the annular flange portion 9 near its outer edge away from the rotation axis X. The turbine disk 2 can be integrally stamped to form a flange portion 9 of different structures, such as Figure 2A -D as shown.

[0033] exist Figure 2A and Figure 2B In the embodiment, the flange portion 9 extends outward from the outer edge of the support portion 202. In this case, the inner edge of the flange portion 9 and the outer edge of the support portion 202 are directly connected. Figure 2C and Figure 2D In the embodiment, 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 the portion near the outer edge of the support portion 202 in the axial direction. The proximal end of the folded portion 204 (the end closer to the rotation axis X in terms of material) is connected to the radial outer edge of the support portion 202, and the distal end of the folded portion 204 (the end farther away from the rotation axis X in terms of material) is connected to the radial inner edge of the flange portion 9. Compared with the case without the folded portion, Figure 2C and Figure 2D The flange portion 9 can be arranged to be away from the pump impeller 1 (see Figure 1 ) is offset by a certain distance. As a result, the vibration damping device 8 on the flange portion 9 can be offset away from the pump impeller 1, which allows the pump impeller 1 to be arranged closer to the rear housing 6, thereby reducing the volume of the torque converter.

[0034] exist Figure 2A and Figure 2C In FIG, the flange portion 9 extends along a plane perpendicular to the rotation axis X. In contrast, in Figure 2B and Figure 2D In the embodiment, the flange portion 9 is tilted at a certain angle relative to a plane perpendicular to the rotation axis X. Preferably, the tilt on the side away from the pump impeller 1 is less than or equal to 5°. Compared with the case where there is no tilt angle, Figure 2B and Figure 2D The vibration damping device 8 on the flange portion 9 can be arranged to be inclined away from the pump impeller 1, which allows the pump impeller 1 to be arranged closer to the rear shell 6, thereby further reducing the volume of the torque converter.

[0035] Three specific embodiments of the present invention are described below with reference to the accompanying drawings. It should be noted that the following embodiments are intended only to provide those skilled in the art with some feasible paths for implementing the present invention. Those skilled in the art may make adjustments to these embodiments, and such adjustments fall within the scope of protection of the present invention.

[0036] First embodiment

[0037] Figures 3A to 3C A first embodiment is shown, in which the vibration damping device 8 is a centrifugal pendulum 10 with an interference fit.

[0038] like Figure 3C As shown, centrifugal pendulum 10 includes a pair of masses 11 and 12 located on either side of flange 9 of turbine disk 2, and fixedly coupled to each other via a boat-shaped spacer 13. An opening 14 is formed in each mass 11 and 12, and a through-hole 15 is formed in flange 9. Boat-shaped spacer 13 passes through through-hole 15, with its ends respectively engaging in openings 14 of masses 11 and 12 with an interference fit.

[0039] The radial outer edge of the pad 13 defines a first track 18, and the radial outer edge of the through hole 15 of the turbine disk 2 defines a second track 17. The roller 16 is arranged between the first track 18 and the second track 17 and can swing along the first track 18 and the second track 17 simultaneously over a circumferential stroke.

[0040] During operation, when there is a fluctuating torque on the turbine disk 2, the roller 16, the second track 17, and the first track 18 cooperate to cause the pair of mass blocks 11 and 12 to swing relative to the turbine disk 2 under the action of inertia. During this period, the mass blocks 11 and 12 apply fluctuating torques in opposite directions to the turbine disk 2 via the roller 16, thereby at least partially offsetting the fluctuating torque on the turbine disk 2 and achieving a vibration reduction effect.

[0041] like Figure 3A As shown, six pairs of masses are evenly arranged along the circumferential direction on the flange portion 9 of the wheel disc 2, wherein each pair of masses 11 and 12 is connected by two spacers 13. The structures of the two spacers 13 and the associated through-holes 15 and rollers 16 are identical, and they are staggered at a certain angle along the circumferential direction to promote smooth swinging of the masses 11 and 12 relative to the turbine disc 2.

[0042] like Figure 3B As shown, twelve through holes 15 are formed on the flange portion 9 on the outer periphery of the turbine disk 2. In other embodiments, other numbers of through holes 15 may be provided on the flange portion 9 for mounting other numbers and arrangements of masses 11, 12.

[0043] Second embodiment

[0044] Figures 4A to 4C A second exemplary embodiment is shown, in which the vibration damping device 8 is a riveted centrifugal pendulum 20 .

[0045] like Figure 4CAs shown, the centrifugal pendulum 20 includes a pair of masses 21 and 22 located on either side of the flange portion 9 of the turbine disk 2, which are fixedly connected to each other by rivets 23. A rivet mounting hole 24 is formed in each mass 21 and 22, and a rivet guide groove 25 is formed in the flange portion 9. The rivet 23 passes through the rivet guide groove 25, and its two ends are respectively engaged in the rivet mounting holes 24 of the masses 21 and 22 by an interference fit.

[0046] 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. In the illustrated embodiment, the outer waist-shaped hole 26 is arched toward the radial inside, while the inner waist-shaped hole 27 is arched toward the radial outside. The roller 28 is arranged through the outer waist-shaped holes 26 on both sides and the inner waist-shaped hole 27 in the middle. The middle part of the roller 28 engages with the inner waist-shaped hole 27, and its two end parts respectively engage with the corresponding outer waist-shaped holes 26. The inner waist-shaped hole 27 and the outer waist-shaped hole 26 arranged in this way allow the roller 28 to roll simultaneously along the outer waist-shaped hole 26 and the inner waist-shaped hole 27 over a circumferential stroke. In addition, as Figure 4B As shown, each rivet guide groove 25 also has a waist shape to prevent the rivet 23 from interfering with the rolling of the roller 28 .

[0047] During operation, when there is a fluctuating torque on the turbine disk 2, the outer waist-shaped hole 26, the inner waist-shaped hole 27 and the roller 28 cooperate to make the pair of mass blocks 21 and 22 swing relative to the turbine disk 2 under the action of inertia. During this period, the mass blocks 21 and 22 apply fluctuating torques in opposite directions to the turbine disk 2 via the roller 28, thereby at least partially offsetting the fluctuating torque on the turbine disk 2 and achieving a vibration reduction effect.

[0048] like Figure 4A As shown, four pairs of masses are evenly arranged in the circumferential direction along the flange portion 9 of the wheel disc 2. Each pair of masses 21 and 22 is connected to each other by three rivets 23 and has two rollers 28, each roller 28 being disposed between two adjacent rivets 23. The two rollers 28 and their associated inner and outer waist-shaped holes 27 and 26 are identical in structure and are staggered at a certain angle in the circumferential direction to facilitate smooth swinging of the masses 21 and 22 relative to the turbine disc 2.

[0049] like Figure 4B As shown, four groups of holes are formed on the flange portion 9 on the outer periphery of the turbine disk 2. Each group of holes includes three rivet guide grooves 25 and two inner waist-shaped holes 27. Each inner waist-shaped hole 27 is located between two adjacent rivet guide grooves 25. In other embodiments, other numbers and arrangements of inner waist-shaped holes 27 and rivet guide grooves 25 may be provided on the flange portion 9.

[0050] Third embodiment

[0051] Figures 5A to 5C A third embodiment is shown, in which the vibration damping device 8 is a dynamic vibration damper 30 with a spring.

[0052] like Figure 5C As shown, the dynamic vibration damper 30 includes a pair of masses 31 and 32 located on either side of the flange portion 9 of the turbine disk 2, fixedly connected to each other by rivets 33. A rivet mounting hole is formed in each mass 31 and 32, and a rivet guide slot 34 is formed in the flange portion 9. Rivet 33 passes through the rivet guide slot 34, with its ends riveted to the rivet mounting holes in the masses 31 and 32, respectively. The middle portion of rivet 33 can slide along the rivet guide slot 34, allowing the masses 31 and 32 connected to rivet 33 to swing over a circumferential travel.

[0053] An outer spring slot 35 is also formed in each mass 31 and 32, and an inner spring slot 36 is also formed in the flange portion 9. The inner and outer spring slots 36 and 35 both extend circumferentially and are aligned with each other, having the same circumferential length. A spring member (not shown), such as a helical straight spring, is disposed within the inner and outer spring slots 36 and 35. In a static state, one end of the spring member abuts against both the first end of the inner and outer spring slots 36 and 35, while the other end abuts against both the opposite second ends of the inner and outer spring slots 36 and 35.

[0054] During operation, when a fluctuating torque is applied to turbine disk 2, masses 31 and 32 swing relative to disk 2 under the influence of inertia, causing one end of the spring element to disengage from the inner spring slot 36 of disk 2 and contact only the end of the outer spring slot 35 of masses 31 and 32. Simultaneously, the opposite end of the spring element disengages from the outer spring slot 35 of masses 31 and 32 and contacts only the end of the inner spring slot 36 of disk 2. This compresses and deforms the spring element. During this period, masses 31 and 32 apply fluctuating torques in opposite directions to disk 2 via the spring element, thereby at least partially offsetting the fluctuating torque on disk 2 and achieving a vibration reduction effect.

[0055] like Figure 5A As shown, four pairs of masses are evenly arranged circumferentially along the flange 9 of the turbine disk 2. Each pair of masses 31 and 32 is connected by two rivets 33, located on opposite circumferential sides of the spring element. The two rivets 33 and their associated rivet guide slots 34 are identical in structure and staggered circumferentially to facilitate smooth swinging of the masses 31 and 32 relative to the turbine disk 2.

[0056] like Figure 5BAs shown, four groups of holes are formed on the flange portion 9 on the outer periphery of the turbine disk 2. Each group of holes includes two rivet guide grooves 34 and one inner spring groove 36. Each inner spring groove 36 is located between two rivet guide grooves 34. In other embodiments, other numbers of inner spring grooves 36 and rivet guide grooves 34 may be provided on the flange portion 9.

[0057] In practice, vehicles such as automobiles, construction vehicles, and agricultural vehicles can include a torque converter such as the one described above. Because the torque converter incorporates a vibration damper on the turbine disc, this damper provides additional vibration damping, eliminating torque vibrations generated by the vehicle's internal combustion engine. This has benefits such as fuel efficiency, noise reduction, and improved vehicle reliability.

[0058] While certain preferred embodiments and other embodiments for implementing the present invention have been described in detail above, it should be understood that these embodiments are provided for illustrative purposes only and are not intended to limit the scope, applicability, or configuration of the present invention in any way. The scope of protection of the present invention is defined by the appended claims and their equivalents. Those skilled in the art may make numerous modifications to the aforementioned embodiments in light of the teachings of the present invention, and such modifications are intended to fall within the scope of protection of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0060] 1 pump impeller

[0061] 2 turbine discs

[0062] 3 guide wheels

[0063] 4 spring shock absorbers

[0064] 5 Lock-up clutch

[0065] 6 back shell

[0066] 7 Pump impeller hub

[0067] 8 vibration damping device

[0068] 9 Flange

[0069] 201 wheel hub

[0070] 202 support part

[0071] 203 connection

[0072] 204 Folding Department

[0073] 10 Centrifugal Pendulum

[0074] 11 mass blocks

[0075] 12 mass blocks

[0076] 13 pads

[0077] 14 openings

[0078] 15 through holes

[0079] 16 rollers

[0080] 17 Second Track

[0081] 18 First Track

[0082] 20 Centrifugal Pendulum

[0083] 21 mass blocks

[0084] 22 mass blocks

[0085] 23 rivets

[0086] 24 rivet mounting holes

[0087] 25 rivet guide grooves

[0088] 26 outer waist-shaped holes

[0089] 27 inner waist-shaped hole

[0090] 28 rollers

[0091] 30 dynamic shock absorber

[0092] 31 mass blocks

[0093] 32 mass blocks

[0094] 33 rivets

[0095] 34 rivet guide groove

[0096] 35 outer spring slot

[0097] 36 inner spring slot

Claims

1. A torque converter comprising: A pump impeller disc (1) having pump impeller blades; A turbine disk (2) having a support portion (202) for supporting turbine blades, the turbine blades being driven by the pump blades via the fluid to rotate around a rotation axis (X); The turbine disc (2) further comprises a flange portion (9), the flange portion being located radially outside the support portion and extending outward, the flange portion (9) being integrally formed with the support portion (202); and The torque converter further comprises a vibration damping device (8), a mass block of the vibration damping device (8) being mounted on the flange portion and configured to be movable relative to the flange portion (9) and capable of absorbing torque fluctuations on the turbine disk (2). The support portion (202) is provided with a folding portion (204) at the radial outer edge, the folding portion (204) overlaps with a portion of the support portion (202) in the axial direction, the proximal end of the folding portion (204) is connected to the radial outer edge of the support portion (202), and the distal end of the folding portion (204) is connected to the radial inner edge of the flange portion (9).

2. The torque converter according to claim 1, wherein: The flange portion and the support portion are integrally formed by stamping.

3. The torque converter according to claim 1, wherein: The flange portion (9) extends outward from a radially outer edge of the support portion (202).

4. The torque converter according to claim 3, wherein: The flange portion extends in a plane perpendicular to the axial direction.

5. The torque converter according to claim 3, wherein: The flange portion (9) is inclined at a certain angle relative to a plane perpendicular to the axial direction.

6. The torque converter according to claim 5, wherein: The flange portion (9) is inclined in a direction away from the pump impeller disc (1).

7. The torque converter according to claim 1, in, comprising two mass blocks, which are located on both sides of the flange portion; and The two mass blocks are fixedly connected to each other by a connecting member (13, 23, 33), and the connecting member passes through a through hole on the flange portion and can move along the through hole.

8. The torque converter according to claim 7, in, The connecting member is a boat-shaped pad (13) which is interference-fitted with the openings (14) on the two mass blocks; wherein the pad defines a first track (18), the through hole defines a second track (17) radially opposite to the first track, and the roller is disposed between the first track and the second track; and The roller is configured to roll along the first track and the second track simultaneously, and the two mass blocks can apply torque to the turbine disc via the roller.

9. The torque converter according to claim 7, in, Each mass block has an outer waist-shaped hole (26), and the flange portion has an inner waist-shaped hole (27), the outer waist-shaped hole and the inner waist-shaped hole are oriented in opposite radial directions, and the roller passes through the outer waist-shaped holes and the inner waist-shaped holes of the two mass blocks in the axial direction; and The roller is configured to roll along the outer waist-shaped hole and the inner waist-shaped hole simultaneously, and the two mass blocks can apply torque to the turbine disc via the roller.

10. The torque converter according to claim 7, in, Each mass block has an outer spring slot (35), the flange portion has an inner spring slot (36), the outer spring slot and the inner spring slot have the same circumferential length, and the spring member is arranged in the outer spring slot and the inner spring slot; and The spring element is configured to contact only the outer spring slot at one end and only the inner spring slot at the opposite end during compression deformation, and the two masses can apply torque to the turbine disk via the spring element.

11. A vehicle, wherein: Comprising a torque converter according to any one of claims 1 to 10.

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