JP6668809B2 - Coreless torque converter and method of manufacturing the same - Google Patents

Description

  The present invention relates to a coreless torque converter in which a core member for fixing a blade of a torque converter is eliminated, and a method for manufacturing the same.

  Patent Literature 1 discloses a technique in which an endless ring that engages with a plurality of blades is provided with the abolition of a core member.

JP-A-9-137856

In the technology of Patent Literature 1, since the recess of the endless ring is configured to engage with the plurality of blades in the axial direction of the torque converter, play is provided between the recess and the blade in the circumferential direction and in the radial direction. Installation and assembling properties must be ensured. However, when fixing the endless ring to the blade, it is necessary to perform a centering step of the endless ring in order to eliminate deviation due to play in the circumferential direction and the radial direction, and there is a problem that an assembling man-hour is increased. Was.
An object of the present invention is to provide a coreless torque converter capable of eliminating a centering step and a method for manufacturing the same.

  In order to achieve the above object, the coreless torque converter of the present invention has a ring-shaped member that engages with a plurality of blades arranged in a shell having a concave curved surface covering the outer diameter side. The radially outward elastic force is generated by radially engaging with an engaging portion formed on the blade.

  Therefore, when assembling the ring-shaped member, the ring-shaped member can be assembled without requiring a centering step, and an increase in the number of assembling steps can be prevented.

FIG. 2 is a cross-sectional view illustrating the coreless torque converter according to the first embodiment. FIG. 2 is a schematic perspective view illustrating a pump impeller according to the first embodiment. FIG. 2 is a schematic perspective view illustrating a ring-shaped member according to the first embodiment. FIG. 2 is a schematic diagram illustrating an impeller blade according to the first embodiment. FIG. 3 is a schematic diagram illustrating a force acting on the pump impeller according to the first embodiment. FIG. 3 is an enlarged schematic view of an assembly portion between the impeller blade and the ring-shaped member according to the first embodiment. FIG. 7 is a partially enlarged view of a ring-shaped member according to a second embodiment. FIG. 13 is a partially enlarged view of an engagement portion according to the third embodiment. FIG. 13 is a partially enlarged view of the vicinity of an end of a ring-shaped member according to a fourth embodiment.

[Example 1]
FIG. 1 is a sectional view illustrating the coreless torque converter according to the first embodiment. The coreless torque converter is disposed at a position facing the converter cover 1 to which engine torque is input, a pump impeller 2 connected to the converter cover 1 in the axial direction of the pump impeller 2, and a transmission input shaft (not shown). A turbine runner 4 connected via a turbine hub 3 and a stator 6 disposed on an inner diameter portion between the pump impeller 2 and the turbine runner 4 and connected to a case (not shown) via a one-way clutch 5. Have. Further, a lock-up clutch 7 for mechanically connecting the pump impeller 2 and the turbine runner 4 is provided.

  FIG. 2 is a schematic perspective view illustrating the pump impeller of the first embodiment. The pump impeller 2 includes a pump shell 20, an impeller blade 21, and a ring-shaped member 30 connecting the impeller blades 21 on the inner diameter side. The pump shell 20 extends in the radial direction, bulges toward the axial transmission (see FIG. 1), and has a concave curved surface 20 a that covers the outer diameter side of the impeller blade 21. The concave curved surface 20a is formed with a fixing groove 20b into which a plurality of fixing claws 21a formed on the shell-side contact surface of the impeller blade 21 fit. When installed in the concave curved surface 20a of the pump shell 20, the impeller blade 21 is fixed to the pump shell 20 by fitting the fixing claw 21a into the fixing groove 20b and brazing.

  FIG. 3 is a schematic perspective view illustrating the ring-shaped member of the first embodiment. The ring-shaped member 30 is an end ring formed by forming plate-shaped steel into a C-shape, and has an inner peripheral surface and an outer peripheral surface substantially parallel to the rotation axis. A gap s1 having a predetermined interval in a natural state is provided between the first end 31 and the second end 32. When the gap s1 becomes narrow, an urging force is generated so that the diameter increases toward the outer diameter side. The ring-shaped member 30 has a plurality of slits 300 into which claw portions 22a of the impeller blade 21 described later are inserted. Although not shown in FIG. 3, a plurality of slits 300 corresponding to the number of impeller blades 21 are formed over the entire circumference of the ring-shaped member 30.

  Here, the slit 300 adjacent to the first end 31 is referred to as a first slit 31a, and the slit 300 adjacent to the second end 32 is referred to as a second slit 32a. When the ring-shaped member 30 is attached to the impeller blade 21, the distance between the first slit 31 a and the second slit 32 a matches the interval when the impeller blade 21 is installed on the pump shell 20. At this time, the gap s1 is attached so as to be narrower than the natural state. Further, the impeller blade 21 engaging with the first slit 31a has a pressure surface on which the fluid pressure acts on the second slit 32a side. The impeller blade 21 engaged with the second slit 32a has a back surface of a pressure surface on which no fluid pressure acts on the first slit 31a side. In other words, the distance from the first end 31 to the first slit 31a is longer than the distance from the second end 32 to the second slit 32a. Therefore, the gap s1 is disposed at a position closer to the back surface of the pressure surface of the adjacent impeller blade 21 than the pressure surface of the impeller blade 21. Thereby, since the gap s1 is not located near the pressure surface where the pressure difference becomes large, fluid leakage is suppressed, and a decrease in fluid performance is avoided.

  FIG. 4 is a schematic diagram illustrating the impeller blade of the first embodiment. FIG. 4A is a perspective view of the pump impeller 2 as viewed from the inner diameter side, and FIG. 4B is a perspective view of the pump impeller 2 as viewed from the circumferential direction. In addition, the fixing claw 21a is not shown for simplification. The impeller blade 21 has an engaging portion 22 that engages with the ring-shaped member 30 in the radial direction. The engaging portion 22 includes a contact surface 22b that radially contacts the ring-shaped member 30; a claw portion 22a that extends in a substantially radial direction (see FIG. 2) and is inserted into the slit 300 of the ring-shaped member 30; Having. The claw portion 22a is formed on the side opposite to the pump shell 20 in the direction of the rotation axis, that is, on the engine side. Therefore, even after the impeller blade 21 is assembled and before brazing, the ring-shaped member 30 can be prevented from falling off. When the impeller blade 21 is fixed to the pump shell 20, the engaging portion 22 is formed so as to be aligned on the circumference concentric with the center of the pump shell 20 on the inner diameter side radially opposed to the concave curved surface 20 a. Have been.

  When assembling the impeller blades 21 to the pump shell 20, the engaging portions 22 are evenly arranged in the concave curved surface 20 a of the pump shell 20 such that the engaging portions 22 are arranged on a circle concentric with the center of the pump shell 20, and a ring shape is formed. By applying a compressive force to the member 30 to reduce the gap s1, the outer diameter of the ring-shaped member 30 is reduced. The diameter of the reduced ring-shaped member 30 is designed to be smaller than the diameter of an imaginary circle passing through the tip of the claw portion 22a. Then, the reduced diameter ring-shaped member 30 is arranged on the inner diameter side of the engagement portion 22, and the circumferential position of the ring-shaped member 30 is adjusted so that the slit 300 and the claw portion 22a coincide with each other. Release the compression force of 30.

  At this time, since the claw portion 22a extends substantially in the radial direction, the ring-shaped member 30 expands in diameter while the slit 300 is inserted into the claw portion 22a, and the contact surface 22b and the outer periphery of the ring-shaped member 30 Expand until the abutment is reached. After the ring-shaped member 30 contacts the contact surface 22b, the ring-shaped member 30 generates a radially outward pressing force F against the plurality of impeller blades 21.

  FIG. 5 is a schematic diagram illustrating a force acting on the pump impeller of the first embodiment. As shown in FIG. 5, a pressing force F acts on the impeller blade 21 radially outward of the ring-shaped member 30. In addition, since the position of the engaging portion 22 is arranged so as to be aligned on the circumference concentric with the center of the pump shell 20, the ring-shaped member 30 is adjusted only by releasing the compressive force of the ring-shaped member 30. Be hearted. Therefore, there is no need to perform the centering step of the ring-shaped member 30, and the assembling step can be simplified.

  FIG. 6 is an enlarged schematic view of an assembly portion between the impeller blade and the ring-shaped member according to the first embodiment. FIGS. 6A to 6C are perspective views in which the viewpoints are changed, and the hatched portions in the drawings are brazing portions. The stator 6 is located below the inner peripheral surface 30 a which is the radially inner end of the ring-shaped member 30, and it is necessary to secure a flow path cross-sectional area of a gap between the impeller blade 21 and the stator 6. Therefore, the radial position of the radially inner end portion 22a1 of the claw portion 22a is formed to be the same as the radial position of the inner peripheral surface 30a of the ring-shaped member 30. Thus, the influence of the claw portion 22a on the cross-sectional area of the flow path can be avoided, and a decrease in fluid performance can be avoided. Note that if the radially inner end 22a1 of the claw portion 22a is radially outside the inner circumferential surface 30a of the ring-shaped member 30, the same operation and effect can be obtained even if they are not the same.

  In the first embodiment, after the claw portion 22a of the impeller blade 21 is brought into contact with the slit 300 of the ring-shaped member 30, the gap between the slit 300 and the claw portion 22a is brazed over the entire circumference. , To ensure strength. Here, when the ring-shaped member 30 is engaged with the impeller blade 21 due to an assembling error of the impeller blade 21 with respect to the pump shell 20, the gap between the engagement portion 22 of some of the impeller blades 21 and the ring-shaped member 30. There may be a gap in However, as shown in FIG. 4, since a radially outward pressing force F acts on the impeller blade 21 from the ring-shaped member 30, the ring-shaped member 30 is pressed against the impeller blade 21. Thereby, the gap between the engagement portion 22 and the claw portion 22a can be suppressed, and the mechanical engagement state can be easily ensured, so that the rigidity of the impeller blade 21 after assembly can be ensured. Further, since the gap between the slit 300 and the claw portion 22a can be reduced, a reduction in brazing strength can be suppressed by suppressing the thickness of the brazing at the time of brazing.

  Next, the turbine runner 4 will be described. The turbine runner 4 has a turbine shell 4a, a turbine blade 4c, and a ring-shaped member 30. The turbine blade 4c has an engagement portion 22 similar to the impeller blade 21. The ring-shaped member 30 provided on the turbine runner 4 has the same shape as the ring-shaped member 30 provided on the pump impeller 2. Basically, when the turbine runner 4 is manufactured, the turbine runner 4 can be manufactured by the same manufacturing process as the manufacturing method of the pump impeller 2 described above.

  However, in the case of the turbine runner 4, the turbine shell 4a and the turbine blade 4c are not fixed by brazing. Specifically, a plurality of fixing claws 41a formed on the shell-side contact surface of the turbine blade 4c are merely fitted into and held in the fixing grooves 40b formed in the turbine shell 4a. Therefore, when the compression force of the ring-shaped member 30 is released when the ring-shaped member 30 is assembled, each turbine blade 4c is pressed against the turbine shell 4a by the pressing force F of the ring-shaped member 30. At this time, even if there is a slight gap between the ring-shaped member 30 and the engagement portion 22 of the turbine blade 4c, the position or the direction of the turbine blade 4c is finely adjusted so that the gap is minimized by the pressing force F. Is done. Therefore, the mechanical coupling force of the turbine shell 4a, the turbine blade 4c, and the ring-shaped member 30 increases, and the rigidity of the turbine blade 4c can be increased.

As described above, the first embodiment has the following advantages.
(1) A circular pump shell 20, a turbine shell 4a (shell) having concave curved surfaces 20a, 40a covering the outer diameter side, and a plurality of impeller blades 21 uniformly arranged in the circumferential direction within the concave curved surfaces 20a, 40a. , A turbine blade 4c (blade), a plurality of impeller blades 21, and a ring-shaped member 30 that engages with the turbine blade 4c. The impeller blade 21 and the turbine blade 4c are radially aligned with the concave curved surfaces 20a and 40a. On the inner diameter side opposed to the center, the pump shell 20 and the turbine shell 4a are arranged on a circle concentric with the center, and have an engaging portion 22 radially opposed to the ring-shaped member 30. And a radially outward pressing force F against the plurality of impeller blades 21 and turbine blades 4c. Occurs, it engages the engaging portion 22 and the radial direction.
Therefore, when assembling the ring-shaped member 30, the ring-shaped member 30 can be assembled without requiring a centering step, and an increase in the number of assembling steps can be prevented.

(2) The ring-shaped member 30 has a plurality of slits 300 formed at positions corresponding to the engaging portions 22, and the engaging portions 22 extend substantially in the radial direction and are inserted into the slits 300a. It is.
Accordingly, by matching the direction in which the pressing force F of the ring-shaped member 30 generates the engagement direction with the engagement direction, even when the diameter is increased from the reduced diameter state during the assembling, the claw portion 22a smoothly enters the slit 300, so that the assembling is easy. be able to.

(3) The claw portion 22a is formed on the opposite side of the pump shell 20 and the turbine shell 4a in the rotation axis direction of the coreless torque converter.
Therefore, after the ring-shaped member 30 is assembled, even before the brazing, the ring-shaped member 30 can be prevented from falling off, and the ease of assembly can be ensured.

(4) The radial position of the radial inner peripheral end 22a1 of the claw portion 22a is the same as the radial position of the inner peripheral surface 30a, which is the radial inner peripheral end of the ring-shaped member 30, or is radially outward. is there.
Therefore, the influence on the flow path cross-sectional area can be suppressed, and a decrease in fluid performance can be suppressed.

(5) The slit 300 and the claw portion 22a are fixed by brazing.
Generally, when the gap between the members is large, it is difficult to secure sufficient strength even when brazing. On the other hand, the gap can be reduced by effectively performing mechanical coupling between the slit 300 and the claw portion 22a by the pressing force F of the ring-shaped member 30. Therefore, even when both are brazed, the gap is stably filled with the brazing material, and sufficient strength can be obtained.

(6) The first end 31 and the second end 32 (both ends) of the ring-shaped member 30 are higher than the pressure surface of any one of the plurality of impeller blades 21 and turbine blades 4c. Is located at a position close to the back surface of the pressure surface of the blade adjacent to the blade.
Therefore, since the gap s1 is not located near the pressure surface where the pressure difference becomes large, fluid leakage is suppressed, and a decrease in fluid performance is suppressed.

(7) Circular pump shell 20, turbine shell 4a having concave curved surfaces 20a and 40a covering the outer diameter side, ring-shaped member 30 which is a C-shaped end ring, and inside concave curved surfaces 20a and 40a. And a plurality of impeller blades 21 and a turbine blade 4c having an engagement portion 22 radially opposed to the ring-shaped member 30 on an inner diameter side radially opposed to the concave curved surfaces 20a and 40a. A method of manufacturing a torque converter, wherein the plurality of blades are evenly arranged in concave curved surfaces of a pump shell 20 and a turbine shell 4a such that the engaging portions are arranged on a circle concentric with the center of the shell. A step of reducing the diameter of the ring-shaped member 30 by applying a compressive force to the ring-shaped member 30 and disposing the ring-shaped member 30 on the inner diameter side of the engagement portion in a reduced-diameter state; Releasing the contraction force, and a step of assembling as ring-shaped member 30 are a plurality of impeller blades 21, to generate the elastic force of the radially outward relative to the turbine blades 4c, the.
Therefore, when the ring-shaped member 30 is assembled, the ring-shaped member 30 can be assembled without requiring a centering step, and an increase in the number of assembling steps can be prevented.

[Example 2]
Next, a second embodiment will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 7 is a partially enlarged view of the ring-shaped member according to the second embodiment. In the slit 300 of the second embodiment, the slit opening width L1 on the outer peripheral surface 30b on the outer diameter side of the ring-shaped member 30 is larger than the slit opening width L2 on the inner peripheral surface 30a on the inner diameter side of the ring-shaped member 30. It is formed so that it becomes. Thereby, after reducing the diameter of the ring-shaped member 30 and assembling it with the engaging portion 22 of the impeller blade 21 or the turbine blade 4c, when the compression force is released and the diameter of the ring-shaped member 30 is expanded, the claw portion 22a is slit. By performing a guide function of smoothly inserting into the 300, ease of assembly can be ensured. In addition, as a method of forming the widths L1 and L2, for example, in the initial stage of manufacturing the ring-shaped member 30, the slit 300 is formed by punching the plate-shaped member from the outer peripheral surface 30b side. I just need. As a result, the width L1 increases due to drooping during processing (a phenomenon in which the surrounding base material is involved when the pressed teeth cut into the plate). By utilizing this characteristic, the widths L1 and L2 can be easily formed.

As described above, in the second embodiment, the following operational effects can be obtained.
(8) The circumferential width of the slit 300 is larger on the radially outer side than on the radially inner side.
Therefore, when assembling the ring-shaped member 30, a guide function for smoothly inserting the claw portion 22a into the slit 300 can be obtained, and assembling easiness can be secured.

[Example 3]
Next, a third embodiment will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 8 is a partially enlarged view of the engaging portion according to the third embodiment. In the claw portion 22a according to the third embodiment, the circumferential width P2 of the radially outer end 22a2 is larger than the circumferential width P1 of the radially inner end 22a1. With this, the ring-shaped member 30 is reduced in diameter and assembled to the engagement portion 22 of the impeller blade 21 or the turbine blade 4c. Thereafter, when the compression force is released and the diameter of the ring-shaped member 30 is increased, the claw portion 22a is By performing a guide function when inserting into the slit 300, ease of assembly can be ensured.

As described above, in the third embodiment, the following operational effects can be obtained.
(9) The circumferential width of the claw portion 22a is larger on the radially outer side than on the radially inner side.
Therefore, when assembling the ring-shaped member 30, a guide function for inserting the claw portion 22 a into the slit 300 can be obtained, and assembling easiness can be secured.

[Example 4]
Next, a fourth embodiment will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 9 is a partially enlarged view of the vicinity of the end of the ring-shaped member according to the fourth embodiment. In the first embodiment, each of the first end 31 and the second end 32 has an end surface cut at a substantially right angle. On the other hand, the first end 31 of the fourth embodiment has a first inclined surface 310 inclined toward the inner diameter side in the circumferential direction, and the second end 32 has the second inclined surface inclined toward the outer diameter side in the circumferential direction. It has an inclined surface 320.

  When the diameter of the ring-shaped member 30 is reduced and assembled to the engagement portion 22 of the impeller blade 21 or the turbine blade 4c, as shown in FIG. 9A, the first end 31 and the second end 32 are in the radial direction. Slide to overlap. Therefore, the diameter of the ring-shaped member 30 can be easily reduced, and the gap s1 in the natural state of the ring-shaped member 30 can be reduced. Further, since the gap s1 after the diameter expansion can be reduced, a decrease in fluid performance can be suppressed. Further, after the compression force is released and the diameter is expanded after being assembled to the engagement portion 22, the first inclined surface 310 and the second inclined surface 320 overlap in the radial direction as shown in FIG. 9B. With regions. As a result, the gap s1 can be reduced, fluid leakage is suppressed, and a decrease in fluid performance is suppressed.

As described above, in the fourth embodiment, the following operational effects can be obtained.
(10) The first end 31 (one end) of the ring-shaped member has a first inclined surface 310 that is inclined inward in the circumferential direction, and the second end 32 (the other end) is It has a second inclined surface 320 inclined to the outer diameter side in the circumferential direction, and the first inclined surface 310 and the second inclined surface 320 have a region overlapping in the radial direction.
Therefore, the gap s1 at the end can be reduced, and a decrease in fluid performance can be suppressed by suppressing fluid leakage.

[Other embodiments]
Although the present invention has been described based on the embodiments, the specific configuration may be another configuration. For example, in the embodiment, the ring-shaped member 30 has a shape having an inner circumferential surface and an outer circumferential surface substantially parallel to the rotation axis, but may have a shape having an inner circumferential surface and an outer circumferential surface inclined with respect to the rotation axis. In this case, the inclination direction is preferably inclined such that the outer peripheral surface faces a portion extending in the radial direction of the shell. In this case, the pressing force F of the ring-shaped member 30 is generated on the axial shell side in addition to the radial direction, so that the blade can be fixed more effectively.
Further, the cross-sectional shape of the ring-shaped member 30 is not limited to a square shape, but may be an elliptical shape, a circular shape, or the like. At this time, mechanical engagement can be ensured by forming the shape of the engagement portion in accordance with the cross-sectional shape of the ring-shaped member 30.
Further, the inventions of the embodiments may be appropriately combined.

DESCRIPTION OF SYMBOLS 1 Converter cover 2 Pump impeller 3 Turbine hub 4 Turbine runner 4a Turbine shell 4c Turbine blade 20 Pump shell 20a Concave curved surface 20b Fixed groove 21 Impeller blade 22 Engaging part 22a Claw part 22a1 Radial inner peripheral end 22a2 Radial outer periphery Side end 22b Contact surface 30 Ring-shaped member 30a Inner peripheral surface 30b Outer peripheral surface 31 First end 31a First slit 32 Second end 32a Second slit 40a Concave curved surface 300 Slit 310 First inclined surface 320 Second Slope

Claims (10)

A circular shell having a concave curved surface covering the outer diameter side,
A plurality of blades evenly arranged in the circumferential direction in the concave curved surface,
A ring-shaped member engaged with the plurality of blades,
Has,
The blade has an engagement portion radially opposed to the ring-shaped member, arranged on a circumference concentric with the center of the shell, on an inner diameter side radially opposed to the concave curved surface,
The ring-shaped member is a C-shaped end ring, which generates a radially outward elastic force on the plurality of blades and radially engages with the engaging portion. And a coreless torque converter. The coreless torque converter according to claim 1,
The ring-shaped member has a plurality of slits formed at positions corresponding to the engagement portion,
The coreless torque converter, wherein the engagement portion is a claw portion extending in a substantially radial direction and inserted into the slit. The coreless torque converter according to claim 2,
The coreless torque converter, wherein the claw portion is formed on a side opposite to the shell in a rotation axis direction of the coreless torque converter. The coreless torque converter according to claim 2 or 3,
A coreless torque converter, wherein a radial position of a radially inner end of the claw portion is the same as or radially outward of a radially inner end of the ring-shaped member. The coreless torque converter according to any one of claims 2 to 4,
A coreless torque converter, wherein a circumferential width of the slit is larger on a radially outer side than on a radially inner side. The coreless torque converter according to claim 2, wherein
A coreless torque converter, wherein a circumferential width of the claw portion is larger on a radially outer side than on a radially inner side. The coreless torque converter according to any one of claims 2 to 6,
The slit and the claw part are fixed by brazing. The coreless torque converter according to any one of claims 1 to 7 ,
Both end portions of the ring-shaped member, out of the plurality of blades, are arranged at positions closer to the back surface of the pressure surface of a blade adjacent to the arbitrary blade than the pressure surface of an arbitrary blade. Coreless torque converter.


The coreless torque converter according to any one of claims 1 to 8,
One end of the ring-shaped member has a first inclined surface inclined to the inner diameter side in the circumferential direction, and the other end has a second inclined surface inclined to the outer diameter side in the circumferential direction. A coreless torque converter, wherein the first inclined surface and the second inclined surface have a region overlapping in a radial direction. A circular shell having a concave curved surface covering the outer diameter side,
A ring-shaped member that is a C-shaped end ring;
A plurality of blades arranged in the concave curved surface and having an engagement portion radially opposed to the ring-shaped member on an inner diameter side radially opposed to the concave curved surface,
A method for manufacturing a coreless torque converter comprising:
In the concave curved surface of the shell, a step of uniformly disposing the plurality of blades such that the engagement portion is arranged on a circumference concentric with the center of the shell,
A step of reducing the diameter by applying a compressive force to the ring-shaped member, and disposing the ring-shaped member on the inner diameter side of the engagement portion in a reduced diameter state,
On the inner diameter side of the engagement portion, releasing the compressive force of the ring-shaped member, assembling the ring-shaped member so as to generate a radially outward elastic force on the plurality of blades,
A method for manufacturing a coreless torque converter, comprising:

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