TORQUE CONVERTER AND VEHICLE CONTAINS THE TORQUE CONVERTER

Abstract

Torque converter, containing: a pump housing (1) which has pump blades; a turbine housing (2) which has a support section (202) which supports turbine blades, wherein the turbine blades are driven by the pump blades via a fluid to rotate about an axis of rotation (X); wherein the turbine housing (2) further comprises a flange section (9), wherein the flange section (9) is arranged radially outside the support section (202) and extends outwards, and wherein the flange section (9) is formed integrally with the support section (202), wherein the support section (202) and the flange section (9) are formed integrally by stamping; wherein the torque converter further comprises a vibration damping device (8), wherein a mass (11, 12; 21, 22; 31, 32) of the same is attached to the flange section (9) and is configured to be movable relative to the flange section (9) and to apply a torque to the turbine casing; and wherein the torque converter further comprises two masses (11, 12; 21, 22; 31, 32) which are arranged on both sides of the flange section (9), wherein the two masses (11, 12; 21, 22; 31, 32) are fixed to each other by means of a connecting element (13, 23, 33), and the connecting element (13, 23, 33) passes through a through hole (15, 25, 34) in the flange section (9) and is movable along the through hole (15, 25, 34).

Description

TECHNICAL FIELD

[0001] The present application relates to a torque converter, in particular a torque converter with an integrated vibration damping device on the turbine housing. The present application relates to a vehicle which incorporates the torque converter. BACKGROUND

[0002] In the vehicle's transmission system, a torque converter is installed between the internal combustion engine and the transmission. A fluid is used as the working medium for transmitting torque, changing torque, and engaging the clutch. The torque converter may include a vibration damping device (e.g., a centrifugal pendulum) to eliminate torsional vibrations present in the output of the internal combustion engine.

[0003] There is a need to reduce torsional vibrations by improving the structure of the torque converter.

[0004] Most prior art vibration damping devices are independent units, separate from the turbine housing and other torque converter components. Installing a separate vibration damping device on the turbine housing requires additional parts and complex processes such as welding. Furthermore, prior art vibration damping devices typically occupy a large axial distance and take up axial space within the torque converter, which is detrimental to achieving a compact torque converter design.For example, DE 112013 004 892 T5 describes a torque converter comprising a torus with a pump and a turbine, each having a cover, a housing, and a first damper disk, wherein the pump cover has a radial wall arranged radially outside the torus, and wherein the turbine cover also has a radial wall for frictional contact with the radial wall of the pump cover. Furthermore, US 2017 / 0 002 908 A1 describes a fluid transmission device comprising a dynamic vibration damper and belonging to the technical field of power transmission for vehicles. Finally, DE 10 2012 212 125 A1 describes a torsional vibration damper for a coupling device used to establish a functional connection between a drive and an output.

[0005] Therefore, it is desirable to provide a torque converter with an improved structure in order to overcome at least many problems existing in the prior art. SUMMARY

[0006] The aim of the present invention is to reduce or eliminate the torsional vibrations transmitted by the torque converter.

[0007] In one aspect of the present invention, a torque converter is provided comprising a pump housing having pump blades; and a turbine housing having a support section that supports turbine blades, wherein the turbine blades are driven by a fluid via the pump blades to rotate about an axis of rotation. The turbine housing further comprises a flange section, the flange section extending outwards radially outside the support section and being formed integrally with the support section. The torque converter further includes a vibration damping device, wherein a mass of the device is attached to the flange section and is configured to be able to move relative to the flange section and to apply a torque to the turbine housing.According to this technical solution, when there is a torque fluctuation at the turbine housing, the mass of the vibration damping device oscillates relative to the turbine housing under the effect of inertia, applying a torque in the opposite direction to the turbine housing, thus achieving the vibration damping effect. Additionally, the mass of the vibration damping device is installed directly on the turbine housing, eliminating the need for any further components, and thus enabling convenient and simple installation.

[0008] According to the invention, the flange section and the support section are formed in one piece by means of stamping. According to this technical solution, the flange section and the support section are stamped in one piece and formed using the same metal plate, so that the bond strength between the flange section and the support section is high, and the precise positioning of the flange section and the mass located on it is easy to achieve.

[0009] In some embodiments, the flange section extends outwards from the radially outer edge of the support section.

[0010] In some embodiments, the support section is provided with a folded section at its radially outer edge, and the folded section axially overlaps a section of the support section; the proximal end of the folded section is connected to the radially outer edge of the support section, and the distal end of the folded section is connected to the radially inner edge of the flange section. According to this design, the flange section is offset axially by a certain distance from the pump housing, which allows the mass to be positioned further away from the pump housing, thus reducing the axial size of the torque converter.

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

[0012] In some embodiments, the flange section is inclined at an angle with respect to a plane perpendicular to the axial direction. Advantageously, the flange section is inclined in a direction away from the pump housing. According to this technical solution, the flange section is inclined away from the pump housing over a certain distance in the axial direction, which makes it possible to position the mass further away from the pump housing, thus reducing the axial size of the torque converter.

[0013] According to the invention, the torque converter comprises two masses which are arranged on both sides of the flange section; wherein the two masses are rigidly coupled to each other by means of a connecting element, and the connecting element passes through the through-hole in the flange section and is movable along the through-hole.

[0014] In some embodiments, the connecting element can be a boat-shaped spacer which is interference-fitted with openings in the two masses. The spacer defines a first track, the through-hole defines a second track radially opposite the first, and a roller is positioned between the first and second tracks. The roller is configured to roll simultaneously along both the first and second tracks, and the two masses are able to transmit torque to the turbine housing via the roller.

[0015] In some embodiments, each mass has an outer waisted hole, the flange section has an inner waisted hole, the outer waisted holes and the inner waisted hole are oriented in opposite radial directions, and the roller passes through the outer waisted holes and the inner waisted hole of the two masses in the axial direction. The roller is configured to roll along the outer waisted holes and the inner waisted hole simultaneously, and the two masses are able to apply torque to the turbine casing via the roller.

[0016] In some embodiments, each mass has an outer spring groove, the flange section has an inner spring groove, the outer and inner spring grooves have the same circumferential lengths, and a spring element is arranged in the outer and inner spring grooves. The spring element is configured to contact only the outer spring grooves at one end and only the inner spring groove at the opposite end to effect compression deformation, and the two masses are able to apply torque to the turbine housing via the spring element.

[0017] In another aspect of the present invention, a vehicle is provided which contains one of the torque converters described above. BRIEF SUMMARY OF THE FIGURES Fig. Figure 1 is a general side view of a torque converter according to the present invention; Fig. Figures 2A-D are schematic views of the structure of the flange section of the turbine casing according to different embodiments; Fig. Figures 3A-3C are schematic views of the turbine housing of the torque converter according to the first embodiment; Fig. Figures 4A-4C are schematic views of the turbine housing of a torque converter according to a second embodiment; Fig. Figures 5A-5C are schematic views of the turbine housing of the torque converter according to the third embodiment. DETAILED DESCRIPTION OF THE EXECUTION FORMS

[0018] The specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. Components with the same or similar reference numerals in the drawings have the same or similar functions.

[0019] In the following description, “axial direction” refers to the direction parallel to the axis of rotation X of the torque converter; “circumferential direction” refers to the direction around the axis of rotation X; “radial direction” refers to the direction perpendicular to the axis of rotation X, where “outside”, “outside”, etc. refer to the direction radially outward away from the axis of rotation X, and “inside” and “within” refer to the direction radially inward in the direction of the axis of rotation X.

[0020] Fig. Figure 1 is a general side view of a torque converter according to the present invention. As shown in Fig. As shown in Figure 1, the torque converter comprises a pump housing 1, a turbine housing 2, a guide wheel 3, a spring damper 4, a locking 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 pump housing 1 to rotation via a pump housing hub 7. Since the pump housing 1 and the rear housing 6 are welded together, they can rotate together. On the output side of the torque converter, the turbine housing 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 toothed connection located on the hub to transmit torque to the downstream transmission. The pump housing 1 and the turbine housing 2 are positioned opposite each other and define a fluid chamber. The pump housing 1 has pump blades, and the turbine housing 2 has turbine blades.The pump blades can drive the turbine blades via a fluid in the fluid chamber to rotate, and then drive the turbine housing 2 to rotate.

[0021] When the locking clutch 5 is actuated to open, the power transmission between the housing 6 and the spring damper 4 is interrupted. At this point, the pump housing 1 drives the turbine housing 2 to rotate solely via the fluid, and the turbine housing 2 drives the output shaft to rotate. This is advantageous when starting the car and can effectively increase torque.

[0022] When the locking clutch 5 is actuated to close, the power transmission between the housing 6 and the spring damper 4 is engaged. At this point, the torque of the pump housing 1 is sequentially transmitted through the rear housing 6, the locking clutch 5, and the spring damper 4 to the output shaft, and the spring damper 4 drives the turbine housing 2 to rotate. In this case, the torque fluctuation of the internal combustion engine is transmitted to the downstream transmission. Although the spring damper 4 can partially absorb this torque fluctuation, problems with vibration, noise, and fuel consumption still occur.

[0023] Against this background, the present invention proposes that an extended annular flange section 9 is formed on the radial outside of the turbine housing 2 and that a vibration damping device 8 (e.g. a centrifugal pendulum or a dynamic vibration absorber) is installed on the flange section 9 in order to realize the integration of the vibration damping device 8 and the turbine housing 2.

[0024] In this case, when the locking clutch 5 is closed, the vibration damping device 8, which is integrated into the turbine housing 2, is used for further damping based on the damping by the spring damper 4, which enables locking at low speed and, meanwhile, improves fuel economy and the comfort of the entire vehicle.

[0025] In addition, the vibration damping device 8 is integrated into the turbine housing 2, which reduces the number of parts and improves ease of use when operating the system as well as the reliability of the overall performance.

[0026] Furthermore, the vibration damping device 8 is located on the radial outside of the turbine housing 2 and does not occupy any additional axial space, which avoids interference with other components and helps to form a compact overall structure.

[0027] As in the Fig. As shown in Figures 2A-D, the turbine casing 2 comprises a hub section 201, a support section 202, and a connecting section 203 between them. The support section 202 has an arc profile that defines a fluid chamber, and the turbine blades are mounted on its concave side. The support section 202 is connected to the inner edge of the annular flange section 9 near the outer edge facing away from the axis of rotation X. The turbine casing 2 can be stamped in one piece to form the flange section 9 with different structures, as shown in the Fig. 2A-D shown.

[0028] In the Fig. 2A and Fig. In 2B, the flange section 9 extends outwards from the outer edge of the support section 202. At this point, the inner edge of the flange section 9 and the outer edge of the support section 202 are directly connected. In contrast, the flange section 9 extends into the Fig. 2C and Fig. 2D from a folded section 204, which is located near the outer edge of the support section 202, outwards. The folded section 204 overlaps with a section near the outer edge of the support section 202 in the axial direction. The proximal end of the folded section 204 (the end that is closer to the axis of rotation X) is connected to the radial outer edge of the support section 202, and the distal end of the folded section 204 (the end that is farther from the axis of rotation X) is connected to the radial inner edge of the flange section 9. The flange section 9 in the Fig. 2C and Fig. 2D can be set so that, compared to the case without the folded section, it is a certain distance from the pump housing 1 (see Fig. 1) is offset. This allows the vibration damping device 8 on the flange section 9 to be offset away from the pump housing 1, which makes it possible for the pump housing 1 to be positioned closer to the enclosure 6, thereby reducing the volume of the torque converter.

[0029] In the Fig. 2A and Fig. In section 2C, flange section 9 extends along a plane perpendicular to the axis of rotation X. In the Fig. 2B and Fig. In contrast, in 2D, the flange section 9 is inclined at a specific angle with respect to a plane perpendicular to the axis of rotation X. Preferably, the inclination on the side facing away from the pump housing 1 is less than or equal to 5°. Compared to the case without an inclination angle, the vibration damping device 8 on the flange section 9 can be positioned in the Fig. 2B and Fig. 2D is positioned so that it is inclined away from the pump housing 1, which allows the pump housing 1 to be positioned closer to the enclosure 6, thereby further reducing the volume of the torque converter.

[0030] 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 show those skilled in the art some possible ways of implementing the present invention. Those skilled in the art may make modifications to these embodiments, all of which fall within the scope of protection of the present invention. THE FIRST VERSION

[0031] The Fig. Figures 3A to 3C show the first embodiment in which the vibration damping device 8 is a centrifugal pendulum 10 in the form of an interference fit.

[0032] As in Fig. As shown in Figure 3C, the centrifugal pendulum 10 contains a pair of masses 11 and 12 on each side of the flange section 9 of the turbine casing 2, and the pair of masses 11 and 12 is rigidly coupled to each other by means of a boat-shaped spacer 13. Openings 14 are formed in each mass 11 and 12, and through-holes 15 are formed in the flange section 9. The boat-shaped spacer 13 passes through the through-hole 15, and both ends of the boat-shaped spacer 13 are each fitted into the openings 14 of the masses 11 and 12 in a type of interference fit.

[0033] 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 housing 2 defines a second track 17. A roller 16 is arranged between the first track 18 and the second track 17, which is able to oscillate simultaneously along both of them in a circumferential path.

[0034] During operation, when a fluctuating torque acts on the turbine housing 2, the roller 16, the second track 17 and the first track 18 work together to cause the pair of masses 11 and 12 to oscillate relative to the turbine housing 2 under the effect of inertia, while the masses 11 and 12 apply a fluctuating torque in the opposite direction to the turbine housing 2 via the roller 16 in order to at least partially compensate for the fluctuating torque on the turbine housing 2 and to achieve the vibration damping effect.

[0035] As in Fig. As shown in Figure 3A, six pairs of masses are arranged uniformly along the circumferential direction on the flange section 9 of the turbine casing 2, with each pair of masses 11 and 12 being connected by two spacers 13. The structures of these two spacers 13 and the structures of the associated through holes 15 and rollers 16 are identical, and they are offset circumferentially by a specific angle to allow the masses 11 and 12 to oscillate smoothly relative to the turbine casing 2.

[0036] As in Fig. As shown in Figure 3B, twelve through-holes 15 are formed in the flange section 9 of the outer periphery of the turbine housing 2. In other embodiments, a different number of through-holes 15 may be provided in the flange section 9 to mount a different number and arrangement of masses 11 and 12. SECOND VERSION

[0037] The Fig. Figures 4A to 4C show the second embodiment, in which the vibration damping device 8 is a riveted centrifugal pendulum 20.

[0038] As in Fig. As shown in Figure 4C, the centrifugal pendulum 20 contains a pair of masses 21 and 22 on each side of the flange section 9 of the turbine casing 2, and the pair of masses 21 and 22 is rigidly coupled to each other by a rivet 23. Rivet mounting holes 24 are formed in each mass 21 and 22, and rivet guide grooves 25 are formed in the flange section 9. The rivet 23 passes through the rivet guide grooves 25, and both ends of the rivet 23 are each fitted into the rivet mounting holes 24 of the masses 21 and 22 in a type of interference fit.

[0039] Outer waisted holes 26 are also formed in each mass 21 and 22, and inner waisted holes 27 are also formed in the flange section 9. The outer waisted holes 26 and the inner waisted holes 27 have opposite orientations. In the illustrated embodiment, the outer waisted holes 26 are convex towards the radially inner side, while the inner waisted holes 27 are convex towards the radially outer side. A roller 28 is arranged to pass through the outer waisted holes 26 on both sides and the inner waisted hole 27 in the middle. The middle section of the roller 18 engages with the inner waisted hole 27, and its two end sections each engage in the corresponding outer waisted holes 26.The inner waist-shaped hole 27 and the outer waist-shaped holes 26, which are arranged as follows, allow the roller 28 to roll along the outer waist-shaped holes 27 and the inner waist-shaped hole 26 simultaneously in a circumferential path. Additionally, as shown in . Fig. As shown in Figure 4B, each rivet guide groove 25 also has a waist-shaped form to prevent the rivet 23 from hindering the rolling of the roller 28.

[0040] During operation, when a fluctuating torque acts on the turbine housing 2, the outer waist-shaped holes 26, the inner waist-shaped hole 27 and the roller 28 work together to cause the pair of masses 21 and 22 to oscillate relative to the turbine housing 2 under the effect of inertia, while the masses 21 and 22 apply a fluctuating torque in the opposite direction to the turbine housing 2 via the roller 28 in order to at least partially compensate for the fluctuating torque on the turbine housing 2 and to achieve the vibration damping effect.

[0041] As in Fig. As shown in Figure 4A, four pairs of masses are arranged evenly distributed circumferentially along the flange section 9 of the turbine casing 2, each pair of masses 21 and 22 being coupled to one another by means of three rivets 23 and comprising two rollers 28, each roller 28 being positioned between two adjacent rivets 23. The two rollers 28 and their associated inner waisted holes 26 and outer waisted holes 27 are identical in structure and are offset circumferentially by a specific angle to allow the masses 21 and 22 to oscillate smoothly relative to the turbine casing 2.

[0042] As in Fig. As shown in Figure 4B, four groups of holes are formed on the flange section 9 of the outer periphery of the turbine housing 2, each group of holes containing three rivet guide grooves 25 and two inner waisted holes 26, and each inner waisted hole 26 being arranged between two adjacent rivet guide grooves 25. In other embodiments, different numbers and arrangements of the inner waisted holes 26 and the rivet guide grooves 25 can also be provided on the flange section 9. The third embodiment

[0043] Fig. Figures 5A to 5C show the third embodiment, in which the vibration damping device 8 is a dynamic vibration absorber 30 with a spring.

[0044] As in Fig. As shown in Figure 5C, the dynamic vibration absorber 30 comprises a pair of masses 31 and 32, which are arranged on each side of the flange section 9 of the turbine casing 2, and the pair of masses 31 and 32 is rigidly coupled to each other by a rivet 33. Rivet mounting holes are formed in each mass 31 and 32, and rivet guide grooves 34 are formed in the flange section 9. The rivet 33 passes through the rivet guide grooves 34, and both ends of the rivet 33 are riveted to the rivet mounting holes in the masses 31 and 32. The central part of the rivet 33 can slide along the rivet guide groove 34, so that the masses 31 and 32, which are coupled to the rivet 33, can oscillate in a circumferential path.

[0045] An outer spring groove 35 is also formed on each mass 31 and 32, and an inner spring groove 36 is also formed on the flange section 9. The inner spring groove 36 and the outer spring groove 35 both extend along the circumferential direction and are aligned with each other, and they have the same circumferential length. A spring element (not shown), such as a straight coil spring, is provided in the inner spring groove 36 and the outer spring groove 35. In the rest state, one end of the spring element simultaneously abuts the first ends of the inner spring groove 36 and the outer spring groove 35, and the other end of the spring element simultaneously abuts the opposite second ends of the inner spring groove 36 and the outer spring groove 35.

[0046] During operation, when a fluctuating torque acts on the turbine housing 2, the masses 31 and 32 oscillate relative to the turbine housing 2 under the effect of inertia. This causes one end of the spring element to be separated from the inner spring groove 36 on the turbine housing 2 and to be in contact only with the ends of the outer spring grooves 35 of the masses 31 and 32. Meanwhile, the opposite end of the spring element is separated from the outer spring grooves 35 of the masses 31 and 32 and is in contact only with the end of the inner spring groove 36 on the turbine housing 2. This deforms the spring element under pressure. During this period, the masses 31 and 32 exert a fluctuating torque in the opposite direction on the turbine housing 2 via the spring element, thus at least partially compensating for the fluctuating torque and achieving the vibration damping effect.

[0047] As in Fig. As shown in Figure 5A, four pairs of masses are arranged evenly in the circumferential direction along the flange section 9 of the turbine housing 2, each pair of masses 31 and 32 being connected by two rivets 33 located on the circumferentially opposite sides of the spring element. The two rivets 33 and their associated rivet guide grooves 34 are identical in structure and are offset circumferentially by a specific angle to allow the masses 31 and 32 to oscillate smoothly relative to the turbine housing 2.

[0048] As in Fig.As shown in Figure 5B, four groups of holes are formed on the flange section 9 of the outer periphery of the turbine housing 2, each group of holes containing two rivet guide grooves 34 and one inner spring groove 36, and each inner spring groove 36 being arranged between the two rivet guide grooves 34. In other embodiments, a different number of inner spring grooves 36 and rivet guide grooves 34 may be provided on the flange section 9.

[0049] In fact, vehicles such as automobiles, technical vehicles, agricultural vehicles, and the like can incorporate the torque converter as described above. Because the torque converter integrates a vibration damping device on the turbine housing, this device can provide an additional damping effect to eliminate torque vibrations generated by the vehicle's internal combustion engine. This is beneficial for reducing fuel consumption, noise, and vehicle reliability.

[0050] Some advantageous embodiments and other embodiments for implementing the present invention have been described in detail above, but it is understood that these embodiments serve only as examples and are not intended to limit the scope, applicability, or configuration of the present invention in any way. The scope of the present invention is defined by the appended claims and their equivalents. A person skilled in the art can make numerous modifications to the aforementioned embodiments within the scope of the present invention, and all such modifications fall within the scope of the present invention. Reference symbol list 1 Pump housing 2 turbine housings 3 Guide wheel 4 spring dampers 5 locking coupling 6 Rear Enclosure 7 Pump housing hub 8 Vibration damping device 9 Flange section 201 Hub section 202 Support section 203 Connecting section 204 folded section 10 Centrifugal pendulums 11 Mass 12 Masse 13 spacers 14 Opening 15 through hole 16 rolls 17 second lane 18 first track 20 centrifugal pendulums 21 Mass 22 Masse 23 rivets 24 rivet mounting holes 25 rivet guide groove 26 outer waist-shaped hole 27 inner waist-shaped hole 28 rolls 30 Dynamic vibration absorber 31 mass 32 Masse 33 rivets 34 Rivet guide groove 35 inner spring groove 36 outer spring groove

Claims

[1] Torque converter, containing: a pump housing (1) which has pump blades; a turbine housing (2) which has a support section (202) which supports turbine blades, wherein the turbine blades are driven by the pump blades via a fluid to rotate about an axis of rotation (X); wherein the turbine housing (2) further comprises a flange section (9), wherein the flange section (9) is arranged radially outside the support section (202) and extends outwards, and wherein the flange section (9) is formed integrally with the support section (202), wherein the support section (202) and the flange section (9) are formed integrally by stamping; wherein the torque converter further comprises a vibration damping device (8), wherein a mass (11, 12; 21, 22; 31, 32) of the same is attached to the flange section (9) and is configured to be movable relative to the flange section (9) and to apply a torque to the turbine casing; and wherein the torque converter further comprises two masses (11, 12; 21, 22; 31, 32) which are arranged on both sides of the flange section (9), wherein the two masses (11, 12; 21, 22; 31, 32) are fixed to each other by means of a connecting element (13, 23, 33), and the connecting element (13, 23, 33) passes through a through hole (15, 25, 34) in the flange section (9) and is movable along the through hole (15, 25, 34). [2] Torque converter according to claim 1, wherein the flange section (9) extends outwards from the radially outer edge of the support section (202). [3] Torque converter according to claim 1, wherein the support section (202) is provided at its radially outer edge with a folded section (204), and the folded section (204) axially overlaps with a section of the support section (202); and wherein the proximal end of the folded section (204) is connected to the radial outer edge of the support section (202), and the distal end of the folded section (202) is connected to the radial inner edge of the flange section (9). [4] Torque converter according to claim 2 or 3, wherein the flange section (9) extends in a plane which is perpendicular to the axial direction. [5] Torque converter according to claim 2 or 3, wherein the flange section (9) is inclined at an angle with respect to a plane which is perpendicular to the axial direction. [6] Torque converter according to claim 5, wherein the flange section (9) is inclined in a direction away from the pump housing (1). [7] Torque converter according to claim 1, wherein the connecting element is a boat-shaped spacer (13) which fits together with openings (14) in the two masses (11, 12) in a kind of press fit; wherein the spacer (13) defines a first track (18), the through-hole (15) defines a second track (17) which is radially opposite the first track (18), and a roller (16) is arranged between the first and the second track (18, 17); and wherein the roller (16) is configured to roll along both the first and second track (18, 17), and the two masses (11, 12) are able to apply the torque via the roller (16) to the turbine housing (2). [8] Torque converter according to claim 1, wherein each mass (21, 22) has an outer waist-shaped hole (26), the flange section (9) has an inner waist-shaped hole (27), the outer waist-shaped holes (26) and the inner waist-shaped hole (27) are oriented in opposite radial directions, and a roller (28) passes through the inner waist-shaped hole (27) and the outer waist-shaped holes (26) of the two masses (21, 22); and wherein the roller (28) is configured to roll along the outer waist-shaped holes (26) and the inner waist-shaped hole (27) simultaneously, and the two masses (21, 22) are able to apply the torque to the turbine casing (2) via the roller (28). [9] Torque converter according to claim 1, wherein each mass (31, 32) has an outer spring groove (35), the flange section (9) has an inner spring groove (36), the outer spring grooves (35) and the inner spring groove (36) have equal circumferential lengths, and a spring element is arranged within the outer spring grooves (35) and the inner spring groove (36); and wherein the spring element is configured to touch only the outer spring grooves (36) at one end and only the inner spring groove (36) at the opposite end during compression deformation, and the two masses (31, 32) are able to apply the torque to the turbine housing (2) via the spring element. [10] Vehicle which includes a torque converter according to any one of claims 1-9.

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