JP2005042820A - Fluid torque transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid torque transmission device by which torque transmission efficiency can be improved. <P>SOLUTION: A boundary between respective blades 16, 26 in a pump impeller 10 and a turbine runner 20 is inclined to the turbine runner 20 as it accesses an outer periphery. Inside a shell 15, movement toward a shell 25 side from the side of the outer periphery of a hydraulic fluid is facilitated by a centrifugal force generated by the rotation of the pump impeller 10 so that the hydraulic fluid can be smoothly circulated. As a result, inertial torque is increased to improve the transmission efficiency of torque. The hydraulic fluid is mightily circulated to make the turbine runner 20 surely follow, even if the rotation of the pump impeller 10 is accelerated. By this, the torque is surely transmitted, thus offering remarkable effectiveness. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a fluid torque transmission device.

  BACKGROUND ART Conventionally, a fluid coupling is generally known as a fluid torque transmission device that transmits torque via a fluid (see, for example, Patent Document 1).

  The fluid coupling includes a drive-side pump impeller and a driven-side turbine runner, and circulates hydraulic oil between the shells provided by the rotation of the pump impeller and operates during circulation. This is a structure in which a rotating torque is generated by the viscosity of the oil and the turbine runner is also rotated, thereby transmitting the driving side torque to the driven side.

According to this fluid coupling, a slight torque fluctuation on the driving side is absorbed by the slip between the pump impeller and the turbine runner, so that a stable output torque with little fluctuation can be obtained from the driven side.
Japanese Utility Model Publication No. 56-101227 (FIG. 1)

  By the way, in such a fluid coupling, improvement in torque transmission efficiency from the driving side to the driven side is required, and development for that purpose is underway. In this regard, according to Patent Document 1, an annular core ring is attached across each blade that partitions the shell, and the hydraulic oil smoothly circulates around the core ring to increase the follow-up torque. , Improving torque transmission efficiency.

  However, although the transmission efficiency is improved by providing the coring, there is a limit to this and further improvement is required.

  An object of the present invention is to provide a fluid torque transmission device capable of improving torque transmission efficiency.

  A fluid torque transmission device according to a first aspect of the present invention includes a drive-side pump impeller and a driven-side turbine runner, and a boundary portion where the blades of the pump impeller and the blades of the turbine runner face each other is at least an outer periphery. The side is inclined with respect to a plane orthogonal to the torque transmission axis.

  A fluid torque transmission device according to a second aspect of the present invention is the fluid torque transmission device according to the first aspect, wherein boundary portions of the blades are complicated.

  According to a third aspect of the present invention, there is provided a fluid torque transmission device including a driving-side pump impeller and a driven-side turbine runner, and the boundary portions where the blades of the pump impeller and the blades of the turbine runner face each other are complicated. It is characterized by that.

  According to the first aspect of the present invention, for example, the boundary portion of each blade is inclined toward the turbine runner side toward the outer periphery, so that the centrifugal force generated by the rotation of the pump impeller causes the outer periphery of the fluid inside the pump impeller shell. The movement toward the side is promoted so that the circulation is performed smoothly, the accompanying torque is increased, and the torque transmission efficiency is improved. On the other hand, when the boundary portion is inclined toward the pump impeller side toward the outer peripheral side, the mass on the outer peripheral side of the turbine runner increases and the inertial force increases, making it less susceptible to torque fluctuations on the driving side. After all, torque transmission efficiency is improved.

  According to the second aspect of the present invention, the boundary portions of the blades are formed in a wave shape or the like so as to be intertwined with each other. Since the length of the coil becomes longer and the resistance at the time of shearing increases, the accompanying torque increases and the torque transmission efficiency is further improved.

  According to the invention of claim 3, the boundary part is complicated with a wave shape or the like regardless of the inclination of the boundary part. Even in such a case, the same action as in claim 2 can be obtained, and torque transmission can be achieved. Efficiency is improved.

Hereinafter, each embodiment of the present invention will be described with reference to the drawings. In the second and third embodiments and the first to fifth modifications, which will be described later, constituent members having the same functions as those of the first embodiment described below are denoted by the same reference numerals, and description thereof is omitted.
[First Embodiment]
FIG. 1 is a cross-sectional view showing a fluid coupling (fluid torque transmitting device) 1 according to a first embodiment of the present invention.

  In FIG. 1, the fluid coupling 1 includes a drive-side pump impeller 10 and a driven-side turbine runner 20, and the whole is covered with a split-type mounting housing 30 fixed to a housing (not shown). Yes.

  Specifically, a large-diameter input gear 11 that meshes with an external drive gear (not shown) is bolted to the outer surface of the pump impeller 10, and the pump impeller 10 is connected to the main shaft (torque as the input gear 11 rotates. Slide around 22 transmission shafts. An annular housing 12 is bolted to the outer peripheral side of the pump impeller 10, thereby covering the turbine runner 20. A liner type bearing 13 is disposed between the pump impeller 10 and the main shaft 22.

  One turbine runner 20 is bolted to the outer periphery of the main shaft 22 together with a small-diameter output gear 21. One end of the main shaft 22 is not shown, but the other end is rotatably attached to the mounting housing 30 via a ball bearing 23. The ball bearing 23 is sandwiched between the contact portion of the mounting housing 30 and the plate 24 inserted through the main shaft 22 and is pressed by the cover 31 that hides the end of the main shaft 22 so that the main shaft 22 cannot be removed. It is attached as follows.

  Shells 15 and 25 are formed in the pump impeller 10 and the turbine runner 20 so as to be opposed to each other. Each of the shells 15 and 25 has a fan shape when viewed from the axial direction, and the adjacent shells 15 and 25 are partitioned by blades 16 and 26 provided radially from the center of rotation. When the pump impeller 10 rotates, the hydraulic oil circulates between the shells 15 and 25 (see arrows), and the turbine runner 20 also rotates due to the rotating torque caused by the viscosity of the hydraulic oil (fluid), and consequently the main shaft 22. Then, the output gear 21 rotates and torque is transmitted to the output side.

  The hydraulic oil at this time is sent to a communication hole 22A formed in the center of the main shaft 22 along the axial direction, and is supplied into the shells 15 and 25 through a radial supply hole 22B. The other supply holes 22C and 22D are holes for supplying hydraulic oil for lubricating the bearings 13 and 23. The hydraulic oil leaking from the shells 15 and 25 and the bearings 13 and 23 once flows down to the bottom of the mounting housing 30 and is then collected and turned to the supply side again.

  By the way, in the fluid coupling 1 of the present embodiment, the boundary portion between the blade 16 and the blade 26 that partitions the shells 15 and 25 is formed with a certain gap, and is a surface S (that is perpendicular to the axis C of the main shaft 22. It is inclined with respect to the virtual plane. That is, the boundary portion between the blades 16 and 26 is linearly inclined toward the turbine runner 20 toward the outer periphery.

  Thus, on the outer peripheral side of the pump impeller 10, the shell 15 is pushed out so as to cover the shell 25 and is continuous, so that when the pump impeller 10 is rotated and centrifugal force is applied, the hydraulic oil is supplied to the shell 15. It is easy to move to the outer peripheral side and consequently to the shell 25 side along the continuous inner surface of the shell, and the circulation between the insides of the shells 15 and 25 is performed smoothly. The inclination angle of the boundary portion, the sizes of the shells 15 and 25 when inclined, and the like are arbitrary, and may be appropriately determined in consideration of the sizes of the pump impeller 10 and the turbine runner 20.

  According to the present invention, there are the following effects.

  That is, the boundary portion between the blades 16 and 26 in the pump impeller 10 and the turbine runner 20 is inclined toward the turbine runner 20 toward the outer periphery, so that the centrifugal force generated by the rotation of the pump impeller 10 causes the inside of the shell 15. Further, the movement of the hydraulic oil from the outer peripheral side toward the shell 25 side is promoted, the hydraulic oil can be smoothly circulated, and the accompanying torque can be increased to improve the torque transmission efficiency. In particular, in such a configuration, even when the rotation of the pump impeller 10 is accelerated, the hydraulic oil is circulated vigorously and the turbine runner 20 reliably follows, so that the torque is reliably transmitted and is particularly effective. It is.

Further, unlike the prior art, it is possible to improve the torque transmission efficiency without using a coring, so that the pump impeller 10 and the turbine runner 20 can be easily manufactured and the cost can be reduced.
[Second Embodiment]
FIG. 2 shows a fluid coupling 2 according to a second embodiment of the present invention.

  In this fluid coupling 2, the boundary portions of the blades 16 and 26 of the shells 15 and 25 are wave-shaped and are intricate with each other. These wave-shaped boundary portions are provided along the radial direction of the main shaft 22, and the clearance between the boundary portions is constant. However, the shape of the wave is arbitrary such as a triangular shape or a rectangular shape in addition to the sine wave shape shown in FIG. 2, and the number and size of the waves may be arbitrarily determined in the implementation. Further, the wave shape may be a part of the boundary portion, or may be a part thereof. In that case, the wave shape is preferably provided near the outer periphery where the centrifugal force is large.

  In such a configuration, the boundary portions of the blades 16 and 26 are waved and are intertwined with each other, and at the boundary portions, the opposed end edges 16A and 26A that attempt to exert a shearing force on the circulating hydraulic oil. Since the resistance when attempting to shear can be increased, the accompanying torque can be increased and the torque transmission efficiency can be improved.

It should be noted that the present invention is not limited to the above-described embodiments, and modifications, improvements, and the like within the scope that can achieve the object of the present invention are included in the present invention.
[First Modification]
FIG. 3 shows a cross section of the main part of the fluid coupling as a first modification of the present invention.

  In FIG. 3, the boundary portions of the blades 16 and 26 of the pump impeller 10 and the turbine runner 20 are inclined toward the turbine runner 20 toward the outer peripheral side as in the first embodiment, and are the same as in the second embodiment. Moreover, they are in a wave shape and are intricate.

With such a configuration, the effects of both the first and second embodiments can be obtained, and the torque transmission efficiency can be further improved.
[Second Modification]
In the second modification shown in FIG. 4, the boundary portions of the blades 16 and 26 are linearly inclined toward the pump impeller 10 side toward the outer peripheral side. As a result, on the outer peripheral side of the turbine runner 20, the shell 25 protrudes so as to cover the shell 15 and is continuous.

According to such a configuration, the mass on the outer peripheral side of the turbine runner 20 is increased and the inertial force is increased, so that the driven side can be made less susceptible to torque fluctuations on the driving side, and the torque transmission efficiency is also improved. be able to.
[Third Modification]
In the third modified example shown in FIG. 5, in addition to the configuration described in the first embodiment, annular core rings 17 and 27 straddling the blades 16 and 26 are attached. The core rings 17 and 27 are fixed to the groove portions of the blades 16 and 26 by brazing or the like. In this modification, the cross-sectional shape of the core rings 17 and 27 is substantially similar to the side surface shape of each blade 16 and 26, but is not limited to this, and can be any shape in its implementation. .

In such a configuration, since the core rings 17 and 27 are provided, the hydraulic oil inside the shells 15 and 25 can be circulated more smoothly, and the torque transmission efficiency can be further improved.
[Fourth Modification]
In the fourth modification shown in FIG. 6, the core rings 17 and 27 are attached in addition to the configuration described in the second embodiment. Even in such a configuration, the torque transmission efficiency is achieved by the action of the core rings 17 and 27. Can be further improved.
[Fifth Modification]
In the fifth modification shown in FIG. 7, the boundary portions of the blades 16 and 26 are linearly inclined, but the inclination directions are different between the outer peripheral side and the inner peripheral side, It is slanted into an open “<” shape. Even in this case, the same configuration as in the first embodiment can be obtained.

Although not shown, the boundary portion is inclined in a “<” shape that opens to the pump impeller 10 side, or as shown by a two-dot chain line in FIG. 7, only the outer peripheral side is inclined, and the inner peripheral side is inclined. Without being provided along the surface S, it is included in the present invention.
[Sixth Modification]
In the sixth modified example shown in FIG. 8, the blades 16 and 26 are arranged in a wave shape, but at this time, the blades of the pump impeller 10 with respect to the surface S perpendicular to the axis C of the main shaft 22. Only 16 has a structure that protrudes toward the turbine runner 20 and is intricate with the blade 26.

  Of course, conversely, only the blade 26 of the turbine runner 20 may protrude toward the pump impeller 10 and be intricate with the blade 16.

  Furthermore, even when a part of each structure of 1st, 2nd embodiment and the 1st-6th modification is combined and it is set as another structure, it is contained in this invention.

  In addition, the best configuration for carrying out the present invention is disclosed in the above description, but the present invention is not limited to this. That is, the invention has been illustrated and described primarily with respect to particular embodiments, but may be configured for the above-described embodiments without departing from the scope and spirit of the invention. Various modifications can be made by those skilled in the art in terms of quantity, other details, and the like.

  Therefore, the description limited to the shape, quantity and the like disclosed above is an example for easy understanding of the present invention, and does not limit the present invention. The description by the name of the member which remove | excluded the limitation of one part or all of such restrictions is included in this invention.

  The present invention can be used for a fluid coupling as described in the above embodiment, and can also be used for, for example, a torque converter constituting a transmission mechanism of a vehicle.

Sectional drawing which shows the fluid torque transmission apparatus which concerns on 1st Embodiment of this invention. Sectional drawing which shows the fluid torque transmission apparatus which concerns on 2nd Embodiment of this invention. Sectional drawing which shows the 1st modification of this invention. Sectional drawing which shows the 2nd modification of this invention. Sectional drawing which shows the 3rd modification of this invention. Sectional drawing which shows the 4th modification of this invention. Sectional drawing which shows the 5th modification of this invention. Sectional drawing which shows the 6th modification of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 2 ... Fluid coupling (fluid torque transmission device), 10 ... Pump impeller, 16, 26 ... Blade, 20 ... Turbine runner, 22 ... Main shaft (torque transmission shaft), C ... Axis, S ... Surface.

Claims (3)

In the fluid torque transmission device (1),
A drive-side pump impeller (10);
A driven turbine runner (20),
The boundary portion where the blade (16) of the pump impeller (10) and the blade (26) of the turbine runner (20) face each other is at least at the outer peripheral side with respect to a surface (S) perpendicular to the torque transmission shaft (22). A fluid torque transmission device (1) characterized by being inclined. The fluid torque transmission device according to claim 1,
The fluid torque transmitting device, wherein boundary portions of the blades (16, 26) are complicated. In the fluid torque transmission device (2),
A drive-side pump impeller (10);
A driven turbine runner (20),
The fluid torque transmission device (2), wherein the opposing boundary portions of the blade (16) of the pump impeller (10) and the blade (26) of the turbine runner (20) are complicated.

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