JP2013133850A - Torque converter - Google Patents

Abstract

A torque converter in which a plurality of stators are arranged with a reduced length in the axial direction is provided.
A stator 16 of a torque converter 10 includes a first stator 17 and a second stator arranged in parallel in the direction of the rotation axis O. The torque converter 10 is formed on a plurality of dog teeth 41 a formed on a lock plate 41 fixed to the first stator 17 so as not to rotate relative to the first stator 17, and a side plate 42 fixed on the second stator 18 so as not to rotate relatively. The first one-way clutch 40 and the second stator 18 that have a plurality of dog teeth 42a and allow the first stator 17 to rotate in only one direction with respect to the second stator 18 in a state where the dog teeth 41a and 42a mesh. And a second one-way clutch 50 that is disposed between the first stator and the fixed shaft 31 that is fixed radially inward of the one-way clutch 40, and that allows the second stator 18 to rotate in only one direction relative to the fixed shaft 31; 1 A pressing member 43 that presses the stator 17 toward the dog teeth 42a is provided.
[Selection] Figure 1

Description

  The present invention relates to a torque converter in which a plurality of stators are arranged.

  In recent years, with the aim of improving fuel efficiency, in order to satisfy both the reduction of engine speed during cruise driving and the improvement of climbing and starting performance, the number of reciprocal oranges has been expanded by increasing the number of automatic transmissions. However, it may not be possible from the viewpoint of cost and weight increase only by expanding the ratio orange of the automatic transmission main body.

  Therefore, it is desired to increase the ratio of the orange by increasing the torque ratio of the torque converter, particularly in the low speed ratio region. Further, in order to reduce slip loss of the torque converter during cruise traveling, it is desired to increase the capacity coefficient particularly in the high speed ratio region. Against this background, torque converters are required to have a performance that achieves both a high torque ratio and a high capacity.

  In order to satisfy such requirements, a torque converter has been proposed in which a plurality of stators are arranged and the direction of the flow of hydraulic oil from the turbine runner can be appropriately changed by the stator according to the speed ratio range. Yes. For example, in Patent Document 1, in order to achieve both a high torque ratio in a low speed ratio range and a high capacity in a high speed ratio range, two stators are connected to a fixed shaft that does not rotate via separate one-way clutches. A torque converter is disclosed.

  Patent Document 2 discloses a torque converter in which a single stator is connected to a fixed shaft via a dog-tooth type one-way clutch. This one-way clutch is connected to the inner peripheral side of the stator so as not to rotate and to be movable in the axial direction, and has an outer race (outer ring) having dog teeth on the side surface and a cylindrical flange connected to the fixed shaft so as not to be relatively rotatable. An inner race (inner ring) having dog teeth formed on the inner race, and a biasing member that biases the outer race and the inner race toward each other.

Japanese Utility Model Publication No. 62-100365 Utility Model Registration No. 2550976

  However, in the torque converter of Patent Document 1, the one-way clutch of each stator is arranged side by side in the axial direction of the torque converter, so that the axial length of the torque converter becomes long. For this reason, the axial length of the entire automatic transmission including the torque converter becomes long, and there is a problem that the weight of the entire automatic transmission increases.

  An object of the present invention is to provide a torque converter in which a plurality of stators are arranged with a reduced axial length.

  The present invention is a torque converter that transmits a rotational force input to a pump impeller to the turbine runner using a fluid circulating between the pump impeller, the turbine runner, and the stator as a transmission medium, and the stator includes: A first stator disposed on the turbine runner side and a second stator disposed on the pump impeller side are arranged in parallel in the rotational axis direction of the pump impeller, and the torque converter further includes the first stator A plurality of first dog teeth formed in a circumferential direction on a surface orthogonal to the rotational axis of one stator or a member fixed to the first stator so as not to rotate relative to the first stator; and the second stator or the second A member fixed to the stator so as not to rotate relative to the rotation axis is opposed to the plurality of first dog teeth in a circumferential direction. The first stator is rotated in only one direction with respect to the second stator in a state where the first dog teeth and the second dog teeth mesh with each other. A first one-way clutch that allows rotation about an axis, and the second stator, and a fixed member that is fixed radially inward of the one-way clutch, and the second stator is positioned with respect to the fixed member. A second one-way clutch that allows rotation about the rotation axis only in the direction, and a pressing member that presses the first stator toward the second dog teeth are provided.

  According to the present invention, the second one-way clutch is fixed radially inward from the first one-way clutch. Therefore, the axial length of the torque converter can be reduced as compared with the torque converter described in Patent Document 1 in which two one-way clutches are arranged in the axial direction.

  Further, unlike the one-way clutch described in Patent Document 2 described above, the first one-way clutch is idling unlike the case where it slides against the force that is biased in the axial direction during the idling. Sometimes the first and second dog teeth do not mesh. Therefore, since the stator idles smoothly, there is little fluid loss and the transmission efficiency is good. Furthermore, when the first stator and the second stator are idling in the most frequently used coupling range state, the difference in rotation between the two stators is small, so that during idling as in the one-way clutch described in Patent Document 2. Since there are few volume changes of the uneven | corrugated | grooved part pinched by a dog tooth, there is little stirring of a transmission medium and there are few temperature rises and deterioration of a transmission medium.

  The first dog teeth and the second dog teeth preferably have inclined surfaces that are inclined in the circumferential direction.

  In the present invention, the pressing member is preferably a spring.

  In this case, when there is no rotational difference between the first stator and the second stator in the coupling range state where the usage frequency is high, the first stator or the member fixed to the first stator so as not to rotate relative to the second stator or Since it rotates in the same direction with no separation from the member fixed to the second stator so as not to be relatively rotatable, there is no relative rotation, so the drag torque generated by the first one-way clutch is very small. As a result, power loss in the first one-way clutch is reduced, and transmission efficiency is improved.

Sectional drawing which shows the upper half of the torque converter which concerns on embodiment of this invention. The expanded sectional view which shows the periphery of the 1st and 2nd one-way clutch of FIG. The graph which shows the relationship between a speed ratio, a torque ratio, and a volume coefficient. It is a figure explaining the relationship between the flow of hydraulic oil and the force which acts on a stator blade, (a) shows a low speed ratio area, (b) shows a medium speed ratio area, (c) shows a high speed ratio area, respectively. .

  Hereinafter, a torque converter 10 according to an embodiment of the present invention will be described.

  As shown in FIG. 1, the torque converter 10 includes three types of impellers, that is, a pump impeller 12, a turbine runner 14, a stator 16, and a front cover 21. An annular path for circulating hydraulic oil is formed by the pump impeller 12, the turbine runner 14, and the stator 16.

  The torque converter 10 further includes two one-way clutches 40 and 50 and a lock-up clutch 22 disposed between the turbine runner 14 and the front cover 21.

  The pump impeller 12 is attached to a flywheel (not shown) connected to a drive shaft (engine crankshaft) (not shown) to which an engine output (not shown) is transmitted.

  The turbine runner 14 is disposed to face the pump impeller 12, has an annular fluid inflow port disposed in proximity to the annular fluid discharge port of the pump impeller 12, and is coupled to the speed change mechanism. The stator 16 deflects the flow of hydraulic oil that flows into the pump impeller 12 from the turbine runner 14.

  The pump impeller 12 includes an outer pump shell 12a formed in a bowl shape, an inner pump core ring 12b, and a plurality of pump blades 12c having base ends attached to the pump core ring 12b.

  The outer peripheral end of the pump shell 12a is attached to a front cover 21 connected to the drive shaft that rotates along the rotation axis O. The inner peripheral end of the pump shell 12 a is fixed to the pump hub 13. Accordingly, the pump impeller 12 is formed in an annular shape and is configured to rotate along the rotation axis O. An output shaft 30 is disposed in the pump hub 13 so as to be rotatable about the rotation axis O.

  The turbine runner 14 includes an outer turbine shell 14a formed in a bowl shape, an inner turbine core ring 14b, and a plurality of turbine blades 14c whose base ends are attached to the turbine core ring 14b.

  An inner peripheral end of the turbine shell 14 a is fixed to the turbine hub 15 by a rivet 23. The turbine hub 15 is coupled to the output shaft 30, and the turbine runner 14 rotates integrally with the output shaft 30.

  The stator 16 is disposed so as to be sandwiched between the pump impeller 12 and the turbine runner 14.

  The stator 16 includes a first stator (first stage stator) 17 and a second stator (second stage stator) 18 that are arranged side by side in the axial direction of the torque converter 10. The axial direction of the torque converter 10 is a direction in which the rotation axis O extends, and is also simply referred to as “axial direction” hereinafter.

  The first stator 17 is composed of an outer first shell side ring 17a, an inner first core side ring 17b, and a plurality of first stator blades 17c whose base ends are attached to the first shell side ring 17a. ing. The first stator 17 is movable in the axial direction with respect to the second stator 18.

  The second stator 18 is configured similarly to the first stator 17. The second stator 18 is composed of an outer second shell side ring 18a, an inner second core side ring 18b, and a plurality of second stator blades 18c having base ends attached to the second shell side ring 18a. ing.

  The stator blades 17c and 18c are fixed to the outer peripheral surfaces of the shell-side rings 17a and 18a, respectively, and extend outward in the radial direction.

  Referring also to FIG. 4 (a), the first stator blade 17c has a thick blade-shaped cross section, the turbine runner 14 side end is a large rounded head, and the pump impeller 12 side end. Has a small rounded tail. The surface of the first stator blade 17c (the lower right surface in FIG. 4A) has a slightly curved concave shape, and the back surface (the upper left surface in FIG. 4A) has a slightly curved convex shape.

  The second stator blade 18c has a thin wing-shaped cross section, the turbine runner 14 side end is a small rounded head, and the pump impeller 12 side end is a slightly rounded tail. Yes. The surface of the second stator blade 18c (the left lower surface in FIG. 4A) is formed in a slightly curved concave shape, and the back surface (the right upper surface in FIG. 4A) is formed in a slightly curved convex shape.

  The first stator 17 is supported by the second stator 18 via the first one-way clutch 40. On the other hand, the second stator 18 is supported by a fixed shaft 31 that is supported by a housing (not shown) via a second one-way clutch 50 so as not to rotate. The first one-way clutch 40 is disposed on the outer peripheral side of the second one-way clutch 50.

  As shown in FIG. 2, the second one-way clutch 50 is provided between the inner ring 51 that is spline-fitted to the fixed shaft 31, the outer ring 52 that is disposed around the inner ring 51, and the inner ring 51 and the outer ring 52. And an engaging body 53. The outer ring 52 is fixed to the second stator 18.

  In the embodiment, the second shell side ring 18a is formed with a hub 18d that protrudes in the axial direction toward the first stator 17 at the radially intermediate portion. The outer ring 52 is fixed to the second stator 18 by fitting the spline formed on the outer peripheral side of the outer ring 52 with the spline formed on the inner peripheral side of the hub 18d.

  As the first one-way clutch 40 is turned on / off, the first stator 17 is rotatable upward in FIGS. 4A to 4B with respect to the second stator 18.

  The first one-way clutch 40 is a dog-tooth clutch, a lock plate 41 fixed to the first shell side ring 17a on the turbine runner 14 side so as not to rotate relative to the first shell side ring 17a, and a turbine of the outer ring 52. The outer ring 52 and the side plate 42 fixed so as not to rotate relative to the runner 14 are formed.

  Although not shown, the first shell side ring 17a and the lock plate 41 are fixed by fitting a key groove formed on the lock plate 41 to a key-shaped protrusion formed on the first shell side ring 17a. .

  A plurality of dog teeth 41a are continuously formed in the circumferential direction on the surface of the lock plate 41 on the turbine runner 14 side. Each dog tooth 41a is formed such that one side is perpendicular to the axial direction and the other side is inclined in the circumferential direction, and the dog tooth 41a has a sawtooth shape as a whole.

  Although not shown, the outer ring 52 and the side plate 42 are fixed by fitting a key groove on one side to a key-shaped protrusion formed on one side. The outer ring 52 and the side plate 42 may be fixed by serration press-fitting or the like.

  On the surface of the side plate 42 on the pump impeller 12 side, a plurality of dog teeth 42a that can mesh with the dog teeth 41a are continuously formed in the circumferential direction. Each dog tooth 42a is formed such that one side is perpendicular to the axial direction and the other side is inclined in the circumferential direction at the same angle as the inclined side of the dog tooth 41a, and the dog tooth 42a has a sawtooth shape as a whole. ing.

  When the lock plate 41 and the side plate 42 are close to each other, that is, when the first stator 17 is close to the second stator 18, the dog teeth 41 a and 42 a are engaged, and the first one-way clutch 40 is as shown in FIG. It becomes a meshing state. In the meshed state, the first stator 17 and the second stator 18 are difficult to rotate in the opposite directions.

  On the other hand, when the lock plate 41 and the side plate 42 are separated from each other, that is, when the first stator 17 is separated from the second stator 18, the engagement of the dog teeth 41 a and 42 a is released and the state shown in FIG. 4B or FIG. As shown, the first one-way clutch 40 is in a mesh release state. In the mesh release state, the first stator 17 and the second stator 18 are relatively rotatable.

  Further, a pressing member 43 that presses the first shell side ring 17 a toward the turbine runner 14 is disposed between the first stator 17 and the second stator 18. Here, the pressing member 43 is an urging member made of a known spring such as a wave spring or a disc spring. However, you may comprise the press member 43 from the hydraulic device etc. which were connected to the control apparatus.

  Further, a first thrust bearing 24 is disposed between the axial direction of the pump hub 13 and the second shell side ring 18a. A second thrust bearing 25 is arranged between the turbine hub 15 and the first shell side ring 17a in the axial direction. A third thrust bearing 26 is disposed between the first shell side ring 17a and the second shell side ring 18a in the axial direction.

(Torque converter operation)
In the torque converter 10 configured as described above, when a condition such as the vehicle speed reaching a predetermined value is satisfied, the pump impeller 12 is turned on by operating a hydraulic device (not shown) to turn on the lock-up clutch 22. The turbine runner 14 is held in a directly connected state, and the power of the drive shaft (not shown) is directly transmitted to the automatic transmission side.

  On the other hand, when the lockup clutch 22 is off (lockup release), torque transmission between the front cover 21 and the turbine runner 14 is performed by fluid transmission between the pump impeller 12 and the turbine runner 14.

  When the drive shaft rotates and the front cover 21 rotates, the pump shell 12a attached thereto also rotates at the same time. Due to the rotation of the pump impeller 12, a flow indicated by an arrow in FIG. 1 is generated in the hydraulic oil, and this flow is transmitted through the stator 16 to rotate the turbine runner 14. The output shaft 30 also rotates integrally with the rotation of the turbine runner 14, and an input shaft of a transmission (not shown) connected to the output shaft 30 is rotationally driven.

  The hydraulic fluid flowing from the pump impeller 12 to the turbine runner 14 rotates the turbine runner 14 and then moves toward the stator 16. When passing through the stator 16, the hydraulic oil abuts on the stator blades 17 c and 18 c to change its direction, and is returned to the pump impeller 12.

  The turbine runner 14 generates torque by the flow of hydraulic oil, and this torque is transmitted to the input shaft of a transmission mechanism (not shown) via the turbine hub 15 and the output shaft 30. During this operation, the stator 16 functions to amplify the torque transmitted from the pump impeller 12 to the turbine runner 14 by changing the flow direction of the hydraulic oil. The hydraulic oil corresponds to a torque transmission medium that circulates between the pump impeller 12 and the turbine runner 14.

  The hydraulic oil flows from the turbine runner 14 to the stator 16 by the swirl flow generated according to the operating state of the torque converter 10. The hydraulic oil abuts on the first and second stator blades 17 c and 18 c, flows along these, and flows into the pump impeller 12.

  The inflow angle of the hydraulic oil flowing from the turbine runner 14 to the stator 16 greatly depends on the speed ratio e, that is, the speed ratio between the turbine runner 14 and the pump impeller 12, and the lower the speed ratio e, the more the hydraulic oil generates in the stator 16. The thrust force to be increased.

  Here, as shown in FIG. 3, the operation of the torque converter 10 in each region will be described in three regions R <b> 1 to R <b> 3 according to the speed ratio e.

(Low speed ratio range)
In the low speed ratio region R1 where the speed ratio e is about 0 to 0.5, for example, as shown in FIG. 4A, the hydraulic oil from the turbine runner 14 flows into the stator 16 toward the upper right in the figure. Therefore, the hydraulic oil hits the surface of the first stator blade 17c, and a thrust force S1 is generated on the first stator blade 17c in the left direction in the figure.

  Due to the thrust force S1 and the pressing force P of the pressing member 43, the first stator 17 moves to the turbine runner 14 side, and the lock plate 41 and the side plate 42 are brought close to each other.

  As a result, the dog teeth 41a of the lock plate 41 of the first one-way clutch 40 and the dog teeth 42a of the side plate 42 mesh with each other to prevent the first stator 17 from rotating relative to the second stator 18 in the upward direction in the figure. Is done. At this time, since the second stator 18 cannot rotate in the upward direction in the figure due to the engagement of the second one-way clutch 50 and is in the stopped state, the first stator 17 is also maintained in the stopped state.

  Therefore, the hydraulic oil that hits the surface of the first stator blade 17c flows along the surface, then flows along the surface of the second stator blade 18c, and flows out toward the pump impeller 12 toward the lower right in the drawing. .

  Due to the hydraulic oil hitting the surface, a leftward thrust force S1 is generated in the first stator blade 17c, and a rightward thrust force S2 is generated in the second stator blade 18c. Along with this, a force is generated in the first and second stator blades 17c and 18c in the upward direction in the figure by the hydraulic oil hitting the surface. However, since the first and second stators 17 and 18 cannot rotate upward in the drawing and are kept stationary, the first and second stator blades 17c and 18c have the reaction force of the force as a reaction force. Torques T1 and T2 are generated in the upward direction in the figure.

  The hydraulic oil whose direction of flow is changed in contact with the stator blades 17c, 18c flows into the pump impeller 12, and boosts the rotation of the pump impeller 12. Thus, in the low speed ratio region R1, the torque increasing action is performed, and the torque ratio K becomes high.

(Medium speed ratio range)
As the speed ratio e increases, the inclination of the hydraulic oil flowing from the turbine runner 14 side into the stator 16 from the axial direction decreases.

  When the speed ratio e becomes a medium speed ratio region R2 of about 0.5 to about 0.8, for example, as shown in FIG. The first stator blade 17c hits the back surface, and a rightward thrust force S1 is generated in the drawing.

  When the thrust force S1 becomes larger than the pressing force P of the pressing member 43 opposite to the thrust force S1, the thrust force S1 that exceeds the pressing force P becomes a thrust, and the first stator 17 moves toward the pump impeller 12 side. Moving. Thereby, since the lock plate 41 and the side plate 42 are separated from each other, the engagement between the first stator 17 and the second stator 18 by the first one-way clutch 40 is released.

  In addition, when the pressing member 43 consists of springs, such as a wave spring and a disk spring, cancellation | release of the engagement by the 1st one-way clutch 40 is decided according to the magnitude of the pressing force P which is the urging | biasing force of a spring, and thrust force S1. The responsiveness at the time of release is good, and the first stator 17 in the fixed state starts to rotate smoothly. Further, drag torque in the first one-way clutch 40 by the rotating first stator 17 is also small.

  The hydraulic oil that flows into the stator 16 from the turbine runner 14 side hits the back surface of the first stator blade 17c and acts to rotate the first stator 17. And since the engagement by the 1st one-way clutch 40 is cancelled | released, the 1st stator 17 rotates freely in the outline arrow direction of FIG.4 (b).

  On the other hand, even at this time, the second stator 18 is still stopped. The hydraulic oil flowing from the turbine runner 14 side hits the surface of the second stator blade 18c, and a force is generated in the second stator blade 18c in the upward direction in the figure. However, since the second stator 18 cannot rotate upward in the figure due to the engagement of the second one-way clutch 50 and is kept stationary, the second stator 18 has a reaction force as the reaction force. Torque T2 is generated in the upward direction in the figure.

(High speed ratio range)
As the speed ratio e further increases, the inclination of the hydraulic oil flowing from the turbine runner 14 side into the stator 16 increases in the axial direction.

  When the speed ratio e becomes a high speed ratio range R3 of about 0.8 to 1, for example, as shown in FIG. 4C, the hydraulic oil flowing from the turbine runner 14 side hits the back surface of the second stator blade 18c. The second stator 18 is rotated. As a result, the engagement of the second one-way clutch 50 is released, and the second stator 18 also rotates in the direction of the white arrow in FIG.

  In particular, when the speed ratio e is 1, that is, when the torque converter 10 approaches the coupling state, the rotational difference between the first stator 17 and the second stator 18 disappears, and the rotational difference between the first stator 17 and the second stator 18 is Get smaller. Accordingly, the drag torque is very small, so that the power loss is small and the transmission efficiency is good.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to this. For example, although the case where the stator 16 is composed of two stators 17 and 18 has been described, the stator may be composed of three or more stators. The type of the second one-way clutch 50 is not limited, and may be a one-way clutch such as a ratchet type, a sprag type, or a roller type.

  As described above, the second one-way clutch 50 is disposed radially inward from the first one-way clutch 40. Accordingly, the axial length of the torque converter 10 can be reduced as compared with the torque converter described in Patent Document 1 in which two one-way clutches are arranged in the axial direction.

  Further, unlike the one-way clutch described in the above-mentioned Patent Document 2, when the first one-way clutch 40 is idling, unlike the one-way clutch that slides against the force that is biased in the axial direction during the idling, The dog teeth 41a and 42a do not mesh with each other. Therefore, since the stator 16 idles smoothly, there is little fluid loss and the transmission efficiency is good. Then, when there is no rotational difference between the first stator 17 and the second stator 18 in the high speed ratio region R3, as compared with the one-way clutch described in Patent Document 2, the uneven portion sandwiched between the dog teeth 41a and 42a. Since there is little change in volume, there is little agitation of the transmission medium, and there is little temperature rise or deterioration of the transmission medium.

  Further, the first one-way clutch 40 engages or disengages the first stator 17 with respect to the second stator 18 based on the thrust force S1 generated in the first stator 17 by the swirling flow according to the operating state of the torque converter 10. Do.

  Therefore, it is not necessary to provide a special oil passage for engaging or releasing the first stator 17, and the number of parts can be reduced as compared with the conventional one-way clutch illustrated in Patent Document 1. . Therefore, the cost of the torque converter 10 can be suppressed.

  DESCRIPTION OF SYMBOLS 10 ... Torque converter, 12 ... Pump impeller, 12a ... Pump shell, 12b ... Pump coring, 12c ... Pump blade, 13 ... Pump hub, 14 ... Turbine runner, 14a ... Turbine shell, 14b ... Turbine coring, 14c ... Turbine blade 15 ... Turbine hub, 16 ... Stator, 17 ... First stator, 17a ... First shell side ring, 17b ... First core side ring, 17c ... First stator blade, 18 ... Second stator, 18a ... Second shell Side ring, 18b ... second core side ring, 18c ... second stator blade, 18d ... hub, 21 ... front cover, 22 ... lock-up clutch, 24 ... first thrust bearing, 25 ... second thrust bearing, 26 ... first 3 thrust bearings DESCRIPTION OF SYMBOLS 30 ... Output shaft 31 ... Fixed shaft (fixed member), 40 ... 1st one-way clutch, 41 ... Lock plate (member fixed to the 1st stator so that relative rotation is impossible), 41a ... Dog tooth (1st dog tooth) 42... Side plate (member fixed to the second stator so as not to rotate relative to the second stator) 42 a. Dog teeth (second dog teeth) 43. Pressing members 50. Second one-way clutch 51. ... outer ring, 53 ... engagement body.

Claims (3)

A torque converter that transmits a rotational force input to a pump impeller to the turbine runner using a fluid circulating between the pump impeller, the turbine runner, and a stator as a transmission medium;
The stator is configured such that a first stator disposed on the turbine runner side and a second stator disposed on the pump impeller side are arranged side by side in the rotation axis direction of the pump impeller.
The torque converter further includes a plurality of first dog teeth formed in a circumferential direction on a surface orthogonal to the rotation axis of the first stator or a member fixed to the first stator so as not to be relatively rotatable. The second stator or a member fixed to the second stator in a relatively non-rotatable manner is formed to face the plurality of first dog teeth in a circumferential direction on a surface orthogonal to the rotation axis. A plurality of second dog teeth, wherein the first stator rotates about the rotation axis in only one direction relative to the second stator in a state where the first dog teeth and the second dog teeth mesh with each other. The first one-way clutch to allow,
Arranged between the second stator and a fixing member fixed radially inward of the one-way clutch, the second stator is allowed to rotate about the rotation axis in only one direction with respect to the fixing member. A second one-way clutch, and
A torque converter comprising a pressing member that presses the first stator toward the second dog teeth.   The torque converter according to claim 1, wherein the first dog teeth and the second dog teeth have inclined surfaces that are inclined in a circumferential direction.   The torque converter according to claim 1, wherein the pressing member includes a spring.

Images