JP2019138332A - Torque converter - Google Patents

Abstract

To improve transmission efficiency and a torque ratio while miniaturizing a torque converter.SOLUTION: A torque converter includes a pump impeller including a pump shell, and a plurality of pump blades disposed on the pump shell, a turbine liner including a turbine shell and a plurality of turbine blades disposed on the turbine shell, and a stator including a stator blade. The pump blade includes a pressure face positioned at a front side in a main rotating direction of the pump impeller, and a suction face positioned at a rear side in the main rotating direction, the suction face includes an inclined face positioned at a turbine line side and inclined at an acute inclination angle to the pressure face, at either one of a fluid inlet and a fluid outlet of the pump impeller, and a boundary portion of the pressure face and the inclined face forms a peripheral edge portion at the turbine liner side, of the pump blade.SELECTED DRAWING: Figure 4

Description

  The present disclosure relates to a torque converter including a pump impeller, a turbine runner, and a stator.

  Conventionally, as a torque converter, the pump shell of the pump impeller, adjacent pump blades, and the maximum and minimum values of the cross-sectional area of the pump flow path perpendicular to the center line of the pump flow path defined between the pump cores When the average is the reference area Sref, the cross-sectional area St of the turbine flow path perpendicular to the center line of the turbine flow path defined between the turbine shell, the adjacent turbine blades, and the turbine core is | St-Sref | A structure configured to satisfy /Sref≦0.2 is known (see, for example, Patent Document 1). In this torque converter, the entire device can be reduced in size by flattening the torus while ensuring a practically sufficient torque capacity according to the outer diameter of the torus.

Japanese Patent No. 5246345

  Here, in the torque converter as described above, it is necessary to secure a clearance between the pump impeller and the turbine runner in consideration that the turbine runner is inclined to the pump impeller side due to negative pressure. For this reason, even if it is a torque converter comprised as mentioned above, if further miniaturization (flattening, diameter reduction) is aimed at, the said clearance in a torque converter will increase relatively, torque ratio and transmission Efficiency will decrease.

  Therefore, the main object of the present disclosure is to further improve the torque ratio and transmission efficiency while reducing the size of the torque converter.

  A torque converter according to the present disclosure includes a pump impeller including a pump shell and a plurality of pump blades disposed in the pump shell, a turbine runner including the turbine shell and the plurality of turbine blades disposed in the turbine shell, In the torque converter including a stator including a stator blade, the pump blade includes a pressure surface located on the front side in the main rotation direction of the pump impeller, and a suction surface located on the rear side in the main rotation direction, The suction surface includes an inclined surface that is located on the turbine runner side and is inclined at an acute angle with respect to the pressure surface on at least one of a fluid inlet and a fluid outlet of the pump impeller, and the pressure The boundary between the surface and the inclined surface is the pump block. And it forms a peripheral edge portion of the turbine runner side over de.

  In the torque converter according to the present disclosure, the suction surface of the pump blade is inclined at an acute inclination angle with respect to the pressure surface and located on the turbine runner side on at least one of the fluid inlet and the fluid outlet of the pump impeller. Including face. And the boundary part of a pressure surface and an inclined surface forms the peripheral part by the side of the turbine runner of a pump blade. As a result, the area of the pressure surface of the pump blade of the pump impeller that scrapes out the fluid can be increased as compared with the case where the inclined surface is not formed on the suction surface, and the turbine runner turbine is scraped off by the pump impeller. It becomes possible to increase the flow velocity of the fluid flowing through the flow path. As a result, even if the clearance between the pump impeller and the turbine runner is relatively increased due to the downsizing (flattening, small diameter) of the torque converter, the energy imparted from the pump impeller to the turbine runner is ensured satisfactorily. At the same time, the increase in the flow velocity of the fluid flowing through the turbine flow path can suppress the change in the inflow angle of the fluid to the stator blade according to the increase in the rotational speed of the turbine blade. Therefore, in the torque converter according to the present disclosure, it is possible to further improve the torque ratio and the transmission efficiency while reducing the size.

It is sectional drawing which shows the starting apparatus containing the torque converter of this indication. It is a perspective view which shows the pump blade of the pump impeller contained in the torque converter of this indication. It is an expanded sectional view showing a pump blade of a pump impeller included in a torque converter of this indication. FIG. 4 is a schematic diagram illustrating a configuration around a fluid outlet of a pump impeller and a fluid inlet of a turbine runner included in a torque converter according to the present disclosure. It is a schematic diagram which shows the flow of the fluid in the fluid outlet periphery of the turbine runner contained in the torque converter of this indication. It is a graph which shows the characteristic of the torque converter of this indication. It is an expanded sectional view which shows the deformation | transformation aspect of the inclined surface contained in the suction surface of a pump blade. It is a schematic diagram which shows the flow of the fluid in the fluid exit of the turbine runner which concerns on a deformation | transformation aspect.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view illustrating a starting device 1 including a torque converter according to the present disclosure. The starting device 1 shown in the figure is mounted on a vehicle equipped with an engine (internal combustion engine) as a prime mover. As shown in the figure, a starting device 1 includes a front cover 2 as an input member that is connected to a crankshaft of an engine and transmits torque from the engine, and a pump impeller (input-side fluid transmission) fixed to the front cover 2. Element) 3, a turbine runner (output-side fluid transmission element) 4 that can rotate coaxially with the pump impeller 3, and a torque converter (fluid transmission device) 6 of the present disclosure including a stator 5, and an automatic transmission (AT) or nothing, for example. It includes a damper hub 7 as an output member fixed to an input shaft IS of a transmission which is a step transmission (CVT), a lock-up clutch 8, and a damper device 10 connected to the damper hub 7.

  The pump impeller 3 of the torque converter 6 is tightly fixed to the front cover 2 and defines a fluid chamber 9 through which hydraulic oil (working fluid) flows together with the front cover 2, and an inner surface of the pump shell 30. It has a plurality of pump blades 31 disposed and a pump core 32 fixed to the plurality of pump blades 31. Pump shell 30, adjacent pump blades 31, and pump core 32 define a plurality of fluid inlets, pump flow paths, and fluid outlets, respectively. The turbine runner 4 includes a turbine shell 40 fixed to the damper hub 7 through a plurality of rivets, a plurality of turbine blades 41 disposed on the inner surface of the turbine shell 40, and a turbine core fixed to the plurality of turbine blades 41. 42. The turbine shell 40, the adjacent turbine blades 41, and the turbine core 42 define a plurality of fluid inlets, turbine flow paths, and fluid outlets, respectively. The stator 5 is coaxially disposed between the pump impeller 3 and the turbine runner 4 facing each other, and rectifies the flow of hydraulic oil from the turbine runner 4 toward the pump impeller 3 to amplify the torque. The pump impeller 3, the turbine runner 4 and the stator 5 form a torus (annular flow path) for circulating hydraulic oil. In the present embodiment, the pump impeller 3 and the turbine runner 4 are formed so as to constitute a torus that is slightly smaller in diameter and flattened than a conventional torque converter.

  Each pump blade 31 is tilted and fixed to the pump shell 30 at a predetermined mounting angle (see FIG. 4), and each pump blade 31 is twisted. Further, the mounting angle of each turbine blade 41 with respect to the turbine shell 40 is determined to be smaller than the mounting angle of each pump blade 31 with respect to the pump shell 30 (see FIG. 4), and each turbine blade 41 is also twisted. Is granted. The number of pump blades 31 of the pump impeller 3 and the number of turbine blades 41 of the turbine runner 4 may be the same. In order to suppress the occurrence of unexpected resonance, the pump blades 31 of the pump impeller 3 The number and the number of turbine blades 41 of the turbine runner 4 may be different. For example, the number of pump blades 31 may be slightly larger than the number of turbine blades 41 in order to increase the amount of hydraulic oil scraped.

  The stator 5 is manufactured by casting a metal material, and has a plurality of integrally formed stator blades 50, an inner ring portion 51, and an outer ring portion 52. The plurality of stator blades 50 are arranged radially between the outer peripheral surface of the inner ring portion 51 and the inner peripheral surface of the outer ring portion 52. The inner ring portion 51 supports the blade root (radially inner end, that is, the outer periphery of the torus) of each stator blade 50, and the outer ring portion 52 supports the blade tip (radially outer end, That is, the inner peripheral side of the torus is supported. The inner ring portion 51 of the stator 5 is fixed to the outer race 56 of the one-way clutch 55, and the inner race 57 of the one-way clutch 55 is fixed to the case of the transmission via a stator shaft (not shown).

  The rotation direction of the stator 5 is set to one direction, that is, only in the same direction as the pump impeller 3 and the turbine runner 4 by the one-way clutch 55, and the speed ratio e of the torque converter 6 (the rotation speed of the turbine runner 4 / the rotation of the pump impeller 3). When the speed is large, the stator 5 rotates with the pump impeller 3 and the turbine runner 4. Further, when the speed ratio is reduced, the rotation of the stator 5 is restricted by the action of the one-way clutch 55, and the hydraulic oil from the turbine runner 4 is rectified by the stator blades 50 and returned to the pump impeller 3. As a result, the torque ratio t (output torque / input torque) of the torque converter 6 can be increased.

  The lock-up clutch 8 performs lock-up that connects the front cover 2 and the damper hub 7 via the damper device 10 and releases the lock-up. In the present embodiment, the lock-up clutch 8 is configured as a single-plate hydraulic clutch, and is disposed in the front cover 2 and in the vicinity of the inner wall surface on the engine side in the front cover 2 and with respect to the damper hub 7. It has a lock-up piston 80 that is rotatably and axially movable. A friction material 81 is attached to the outer peripheral side of the lockup piston 80 and the surface on the front cover 2 side. Further, a lockup chamber (engagement oil chamber) connected between a lockup piston 80 and the front cover 2 is connected to a hydraulic control device (not shown) via a hydraulic oil supply passage and an oil passage formed in the input shaft IS. ) 85 is defined.

  The hydraulic oil from a hydraulic control device (not shown) can flow into the lockup chamber 85, and if the lockup chamber 85 and the fluid chamber 9 are kept at the same pressure, the lockup piston 80 is moved to the front cover. The lockup piston 80 does not frictionally engage with the front cover 2 without moving to the second side. On the other hand, when the hydraulic pressure in the fluid chamber 9 is made higher than the hydraulic pressure in the lockup chamber 85 by a hydraulic control device (not shown), the lockup piston 80 moves toward the front cover 2 due to the pressure difference and moves to the front. The cover 2 is frictionally engaged. As a result, the front cover 2 (engine) is connected to the damper hub 7 via the lock-up piston 80 and the damper device 10. The lockup clutch 8 may be a multi-plate hydraulic clutch including at least one friction engagement plate (a plurality of friction materials).

  As shown in FIG. 1, the damper device 10 includes, as rotating elements, a drive member (input element) 11 connected to a lockup piston 80, a first intermediate member (first intermediate element) 12, and a first connected to each other. And a second intermediate member (second intermediate element) 14 having second plate members 141 and 142, and a driven member (output element) 15 connected to the damper hub 7. Further, the damper device 10 is a torque transmission element (torque transmission elastic body) that is disposed in the vicinity of the outer periphery of the damper device 10 and transmits a torque between the drive member 11 and the first intermediate member 12. First outer springs SP11 and a plurality of second outer springs that are arranged in a circumferential direction with the first outer springs SP11 and transmit torque between the first intermediate member 12 and the second intermediate member 14 ( And a plurality of inner springs SP2 that are disposed radially inward of the first and second outer springs SP11 and the like and that transmit torque between the second intermediate member 14 and the driven member 15.

  FIG. 2 is a perspective view showing the pump blade 31 of the pump impeller 3 included in the torque converter 6, and FIG. 3 is an enlarged sectional view showing the pump blade 31. FIG. 4 is a schematic diagram showing the configuration around the fluid outlet 3o of the pump impeller 3 and around the fluid inlet 4i of the turbine runner 4. As shown in FIG. As shown in these drawings, each pump blade 31 of the pump impeller 3 includes a pressure surface 31p positioned on the front side in the main rotation direction of the pump impeller 3 (the rotation direction of the engine, see FIG. 4), and the main rotation direction. And a suction surface 31s located on the rear side. Further, the suction surface 31s extends along the edge on the turbine runner 4 side from the end on the fluid inlet 3i (see FIG. 1) side of the pump impeller 3 (lower end in FIG. 2) to the end on the fluid outlet 3o side (FIG. 2). And an inclined surface 31t having a narrow band shape that is inclined at an acute inclination angle θ with respect to the pressure surface 31p. The inclination angle θ is selected from a range of about 10 ° to 60 °, for example.

  In the present embodiment, the pump blade 31 is formed in a flat plate shape prior to the application of torsion, and the pressure surface 31p and the suction surface 31s extend in parallel to each other. Further, the inclined surface 31t is formed flat, for example, by coining before the pump blade 31 is twisted, and as shown in FIG. 2, the inlet of the inclined surface 31t that defines the fluid inlet 3i of the pump impeller 3 is formed. The side end portion 31ti and the outlet side end portion 31to of the inclined surface 31t defining the fluid outlet 3o extend even after the pump blade 31 is twisted. Further, as shown in FIG. 3, the boundary portion between the pressure surface 31p and the inclined surface 31t is rounded to have an R shape, and the boundary portion has a peripheral edge portion 31e on the turbine runner 4 side of the pump blade 31. Form. Each pump blade 31 is a plane perpendicular to the axis of the pump impeller 3 and has a peripheral portion from a reference surface that is defined so as to define a position where the pump blade 31 does not interfere with the turbine blade 41 during operation of the torque converter 6. 31e is fixed to the pump shell 30 so as not to protrude toward the turbine runner 4 side.

  In the pump impeller 3 configured as described above, as can be seen from FIGS. 3 and 4, the pressure surface 31p of each pump blade 31 is the fluid outlet 3o of the pump impeller 3, and the outlet side end 31to of the inclined surface 31t. And the outlet side end portion 31to of the suction surface 31s protrudes to the turbine runner 4 side from the boundary between the portion separated from the turbine runner 4 (the side opposite to the turbine runner 4 and the fluid inlet 3i side). Further, the pressure surface 31p of each pump blade 31 is a fluid inlet 3i of the pump impeller 3 and is a side away from the turbine runner 4 than the inlet side end 31ti of the inclined surface 31t and the inlet side end 31ti of the suction surface 31s. It protrudes to the turbine runner 4 side from the boundary with the part (on the side opposite to the turbine runner 4 and the fluid outlet 3o side).

  Therefore, the total surface area of the pressure surface 31p of the pump blade 31 in the pump impeller 3 is formed such that the inclined surface is not formed on the suction surface, for example, the end surface on the turbine runner side is orthogonal to the pressure surface and the suction surface. It increases compared with a pump impeller including a pump blade (see a broken line in FIG. 4). As a result, the amount of hydraulic oil scraped by the pump impeller 3 and flowing from the fluid outlet 3o into the fluid inlet 4i of the turbine runner 4 can be increased, so that the hydraulic oil flowing through the turbine flow path of the turbine runner 4 can be increased. The flow rate can be increased. As a result, even if the clearance between the pump impeller 3 and the turbine runner 4 is relatively increased due to the flattening and small diameter (downsizing) of the torque converter 6, the energy applied from the pump impeller 3 to the turbine runner 4. Can be secured satisfactorily.

  And the centrifugal force which acts on hydraulic oil according to the increase in the rotational speed of the turbine runner 4 by increasing the flow velocity of the hydraulic oil which circulates through the turbine flow path of the turbine runner 4, especially in the high speed ratio region where the speed ratio e is increased. Even if the force increases, the amount of hydraulic oil circulating in the torus can be kept sufficiently, and the energy imparted from the pump impeller 3 to the turbine runner 4 can be secured satisfactorily. Further, as can be seen from FIG. 5, the rotational speed of the turbine blade 41 (turbine runner 4) is increased by increasing the flow velocity of the hydraulic oil flowing through the turbine flow path of the turbine runner 4 (see the broken line in FIG. 5). It is possible to suppress a change in the inflow angle of the hydraulic oil with respect to the stator blade 50 in accordance with the increase in the dotted line).

  As a result, in the torque converter 6, as shown by a solid line in FIG. 6, the torque ratio t in the high speed ratio region, in particular, includes a pump impeller in which no inclined surface is formed on the suction surface of the pump blade (in FIG. (See broken line). Further, in the torque converter 6, as shown by a solid line in FIG. 6, the transmission efficiency η in the high speed ratio region is a torque converter including a pump impeller in which an inclined surface is not formed on the suction surface of the pump blade (see the broken line in FIG. 6). For example, it can be increased by about 2 to 3%.

  Further, if the narrow strip-like inclined surface 31t extending along the edge on the turbine runner 4 side is formed on the suction surfaces 31s of the plurality of pump blades 31, an increase in the area of the pressure surface 31p in each pump blade 31 is slight. However, in the pump impeller 3 as a whole, the total surface area of the pressure surface 31p can be sufficiently increased. Therefore, the use of the pump blade 31 as described above is extremely useful in improving the efficiency of the torque converter 6 in which the torus is flattened and / or reduced in diameter. Note that an inclined surface 31t is formed on the suction surface 31s of the above-described pump blade 31 so as to extend from the fluid inlet 3i side of the pump impeller 3 to the fluid outlet 3o side along the edge on the turbine runner 4 side. However, there is nothing limited to this. That is, the inclined surface 31t may be formed only on one side of the fluid inlet 3i and the fluid outlet 3o of the pump impeller 3. Moreover, the above-mentioned pump impeller 3 may be applied to a fluid coupling that does not include a stator.

  Furthermore, as shown in FIG. 7, the inclined surface 31t of the pump blade 31 may be a curved surface that smoothly continues to a portion of the suction surface 31s on the pump shell 30 side. That is, the outlet side end portion of the inclined surface 31t may be a curved surface that smoothly continues to a portion (the fluid inlet side) that is farther from the turbine runner 4 than the outlet side end portion of the suction surface 31s. The inlet-side end portion of the surface 31t may be a curved surface that smoothly continues to a portion (the fluid outlet side) that is farther from the turbine runner 4 than the inlet-side end portion of the suction surface 31s. In this case, the curved inclined surface 31t has an angle formed between the pressure surface 31p and the flat surface in contact with the inclined surface 31t in the vicinity of the peripheral edge 31e before the pump blade 31 is twisted, as shown in FIG. It only has to be an acute angle. Further, the boundary portion between the pressure surface 31p and the inclined surface 31t, that is, the peripheral portion 31e on the turbine runner 4 side of the pump blade 31 does not necessarily have to be rounded by molding, and crushing processing such as coining processing is performed. It may be what was done.

  Further, as shown by a two-dot chain line in FIG. 4, an inclined surface 41 t may be formed in a portion that defines the fluid inlet 4 i of the suction surface 41 s located on the front side of the turbine blade 41 in the main rotation direction. As shown in FIG. 4, the inclined surface 41t is inclined at an acute inclination angle with respect to the pressure surface 41p located on the pump impeller 3 side and located on the rear side of the turbine blade 41 in the main rotation direction. A boundary portion between the surface 41t and the pressure surface 41p forms a peripheral portion 41e of the turbine blade 41 on the pump impeller 3 side. As a result, the hydraulic oil flowing out from the fluid outlet 3o of the pump impeller 3 can be smoothly flowed into the fluid inlet 4i of the turbine runner 4 to further increase the flow velocity of the fluid flowing through the turbine flow path.

  Further, as shown in FIG. 8, an inclined surface 41 t may be formed in a portion defining the fluid outlet 4 o of the suction surface 41 s of the turbine blade 41. As shown in FIG. 8, the inclined surface 41t is located on the stator 5 (pump impeller 3) side and is inclined at an acute inclination angle with respect to the pressure surface 41p of the turbine blade 41, and the inclined surface 41t and the pressure surface 41p are inclined. The boundary part of the turbine blade 41 forms a peripheral part 41e of the turbine blade 41 on the stator 5 (pump impeller 3) side. As a result, the hydraulic oil flows out smoothly from the fluid outlet 4o of the turbine runner 4 to increase the flow speed of the hydraulic oil flowing through the turbine flow path, and as shown by the solid line in FIG. 8, the suction surface 41s is inclined to the inclined surface 41t. Compared with the case where the is not formed (refer to the broken line in the figure), the hydraulic oil can flow out from the fluid outlet 4o of the turbine runner 4 toward the stator blade 50 in a direction in which the stator torque is further increased. As a result, the torque ratio t and the transmission efficiency η of the torque converter 6 can be further improved.

  As described above, the torque converter according to the present disclosure includes the pump impeller (3) including the pump shell (30) and the plurality of pump blades (31) disposed in the pump shell (30), and the turbine shell (40). And a turbine runner (4) including the plurality of turbine blades (41) fixed to the turbine shell (40), and a stator (5) including a stator blade (50). The pump blade (31) includes a pressure surface (31p) located on the front side in the main rotation direction of the pump impeller (3) and a suction surface (31s) located on the rear side in the main rotation direction, The suction surface (31s) has a small number of fluid inlets (3i) and fluid outlets (3o) of the pump impeller (3). Both include an inclined surface (31i) located on the turbine runner (4) side and inclined at an acute inclination angle (θ) with respect to the pressure surface (31p) on either side of the pressure surface (31p). ) And the inclined surface (31t) form a peripheral portion (31e) on the turbine runner (4) side of the pump blade (3).

  In the torque converter according to the present disclosure, the suction surface of the pump blade is inclined at an acute inclination angle with respect to the pressure surface and located on the turbine runner side on at least one of the fluid inlet and the fluid outlet of the pump impeller. Including face. And the boundary part of a pressure surface and an inclined surface forms the peripheral part by the side of the turbine runner of a pump blade. As a result, the area of the pressure surface of the pump blade of the pump impeller that scrapes out the fluid can be increased as compared with the case where the inclined surface is not formed on the suction surface, and the turbine runner turbine is scraped off by the pump impeller. It becomes possible to increase the flow velocity of the fluid flowing through the flow path. As a result, even if the clearance between the pump impeller and the turbine runner is relatively increased due to the downsizing (flattening, small diameter) of the torque converter, the energy imparted from the pump impeller to the turbine runner is ensured satisfactorily. At the same time, the increase in the flow velocity of the fluid flowing through the turbine flow path can suppress the change in the inflow angle of the fluid to the stator blade according to the increase in the rotational speed of the turbine blade. Therefore, in the torque converter according to the present disclosure, it is possible to further improve the torque ratio and the transmission efficiency while reducing the size.

  Further, the inclined surface (31t) of the pump blade (31) may extend flat.

  Further, the inclined surface (31t) of the pump blade (31) may be a curved surface smoothly continuing to a portion of the suction surface (31s) on the side away from the turbine runner (4).

  Moreover, the boundary part of the said pressure surface (31p) and the said inclined surface (31t) may be rounded.

  Further, the turbine blade (41) may include a pressure surface (41p) positioned on the rear side in the main rotation direction and a suction surface (41s) positioned on the front side in the main rotation direction. The suction surface (41s) of (41) is located on the pump impeller (3) side on at least one of the fluid inlet (4i) and the fluid outlet (4o) of the turbine runner (4). The turbine blade (41) may include an inclined surface (41t) inclined at an acute angle with respect to the pressure surface (41p) of the turbine blade (41), and the pressure surface (41p) and the inclined surface ( 41t) may form a peripheral edge (41e) of the turbine blade (41) on the pump impeller (3) side. As a result, the fluid flowing out from the fluid outlet of the pump impeller flows smoothly into the fluid inlet of the turbine runner to increase the flow velocity of the fluid flowing through the turbine flow path, or the fluid smoothly flows out from the fluid outlet of the turbine runner. This increases the flow rate of the fluid flowing through the turbine flow path and allows the fluid to flow out from the turbine runner fluid outlet toward the stator blade in the direction of increasing the stator torque. This can be further improved.

  And the invention of this indication is not limited to the above-mentioned embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the above-described embodiment is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column.

  The invention of the present disclosure can be used in the field of manufacturing torque converters.

  1 starter device, 2 front cover, 3 pump impeller, 3i fluid inlet, 3o fluid outlet, 30 pump shell, 31 pump blade, 31e peripheral edge, 31p pressure surface, 31s suction surface, 31t inclined surface, 31ti inlet side end, 31 to outlet side end, 32 pump core, 4 turbine runner, 4i fluid inlet, 4o fluid outlet, 40 turbine shell, 41 turbine blade, 41e peripheral edge, 41p pressure surface, 41s suction surface, 41t inclined surface, 42 turbine core, 5 Stator, 50 Stator blade, 51 Inner ring, 52 Outer ring, 55 One-way clutch, 56 Outer race, 57 Inner race, 6 Torque converter, 7 Damper hub, 8 Lock-up clutch, 80 Lock-up piston, 8 DESCRIPTION OF SYMBOLS 1 Friction material, 85 Lockup chamber, 9 Fluid chamber, 10 Damper apparatus, 11 Drive member, 12 1st intermediate member, 14 2nd intermediate member, 141 1st plate member, 142 2nd plate member, 15 Driven member, SP11 First outer spring, SP2 inner spring.

Claims (5)

A pump impeller including a pump shell and a plurality of pump blades disposed on the pump shell, a turbine shell and a turbine runner including the plurality of turbine blades disposed on the turbine shell, and a stator including a stator blade. In the provided torque converter,
The pump blade includes a pressure surface located on the front side in the main rotation direction of the pump impeller, and a suction surface located on the rear side in the main rotation direction,
The suction surface includes, on at least one of a fluid inlet and a fluid outlet of the pump impeller, an inclined surface that is located on the turbine runner side and is inclined at an acute angle with respect to the pressure surface,
A torque converter in which a boundary portion between the pressure surface and the inclined surface forms a peripheral portion of the pump blade on the turbine runner side.   The torque converter according to claim 1, wherein the inclined surface of the pump blade extends flat. The torque converter according to claim 1,
The torque converter is a torque converter in which the inclined surface of the pump blade is a curved surface that is smoothly continuous with a portion of the suction surface that is separated from the turbine runner.   4. The torque converter according to claim 1, wherein a boundary portion between the pressure surface and the inclined surface is rounded. 5. In the torque converter as described in any one of Claim 1 to 5,
The turbine blade includes a pressure surface located on the rear side in the main rotation direction, and a suction surface located on the front side in the main rotation direction,
The suction surface of the turbine blade is inclined at an acute inclination angle with respect to the pressure surface of the turbine blade located on the pump impeller side on at least one of the fluid inlet and the fluid outlet of the turbine runner. Including an inclined surface
A torque converter in which a boundary portion between the pressure surface and the inclined surface of the turbine blade forms a peripheral portion on the pump impeller side of the turbine blade.

Images