JP2005308098A - Hydraulic power transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic power transmission capable of improving transmission efficiency by effectively using energy of working fluid. <P>SOLUTION: A torque converter 1 is provided with a pump impeller 3 attached to a front cover 2, a turbine runner 4 attached to a turbine hub 5 facing the pump impeller 3, and a stator 6 for guiding fluid flowing out of the turbine runner 4 to the pump impeller 3. An annular recess part 61 and an injection hole 62 for injecting working fluid toward the pump impeller 3 to assist rotation of the pump impeller 3 is formed on a blade support part 6a of a stator 6. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a fluid transmission device that transmits power from an input member to an output member via a working fluid.

  Conventionally, a torque converter (fluid transmission device) having a pump impeller and a turbine runner facing each other and a stator disposed therebetween is known (see, for example, Patent Document 1). In this torque converter, a stator for guiding hydraulic oil from a turbine runner to a pump impeller is splined to a fixed member connected to a transmission housing via a one-way clutch. Further, in general torque converters such as this torque converter, hydraulic oil is supplied at a predetermined pressure toward a pump impeller or the like during its operation.

JP-A-9-100954

  Here, the energy of the hydraulic oil that functions as a power transmission medium and further as a cooling medium or a lubrication medium is basically converted into heat during the operation of the torque converter. From the viewpoint of effective use of energy. As can be seen, there is still room for improvement in the conventional torque converter.

  Therefore, an object of the present invention is to provide a fluid transmission device capable of improving transmission efficiency by effectively using energy of a working fluid.

  A fluid transmission device according to the present invention is a fluid transmission device that transmits power from an input member to an output member via a working fluid, a pump impeller attached to the input member, a pump impeller attached to the output member, And an opposing turbine runner, wherein a working fluid is supplied to the pump impeller so as to assist the rotation of the pump impeller.

  In this fluid transmission device, a working fluid that functions as a power transmission medium and further as a cooling medium or a lubricating medium is supplied to the pump impeller. At this time, the working fluid assists the rotation of the pump impeller. To the pump impeller. Accordingly, it is possible to promote the rotation of the pump impeller by using the energy of the working fluid supplied toward the pump impeller, and it is possible to increase the pump torque and improve the transmission efficiency of the fluid transmission device. .

  The fluid transmission device according to the present invention further includes a stator for guiding the fluid flowing out from the turbine runner to the pump impeller, and the stator operates toward the pump impeller so as to assist the rotation of the pump impeller. It is preferable that a working fluid channel for ejecting fluid is formed.

  By adopting such a configuration, it is possible to easily realize a configuration for assisting the rotation of the pump impeller using the energy of the working fluid. In this case, the reaction force generated by assisting the rotation of the pump impeller by the working fluid is received by the stator, and the influence of the reaction force on the fluid characteristics is minimized.

  Furthermore, it is preferable that the working fluid flow path includes a region inclined in the rotation direction of the pump impeller.

  Further, the working fluid flow path is preferably formed so as to eject the working fluid along the flow direction of the working fluid flowing out from the turbine runner and flowing into the pump impeller.

  By adopting such a configuration, it is possible to increase the flow rate of the working fluid circulating between the pump impeller and the turbine runner, and to increase the capacity coefficient of the fluid transmission device.

  According to the present invention, it is possible to realize a fluid transmission device that can improve the transmission efficiency by effectively using the energy of the working fluid.

  Hereinafter, the best mode for carrying out the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a partial cross-sectional view showing a torque converter as an example of a fluid transmission device according to the present invention. The torque converter 1 is applied to a vehicle equipped with an engine. As shown in FIG. 1, a front cover (input member) 2, a pump impeller (fluid transmission element) 3, a turbine runner (fluid transmission element) 4, including a turbine hub (output member) 5, a stator 6, a damper unit 7, and a lockup clutch mechanism 8. An engine rotation shaft (not shown) is fixed to the front cover 2. In addition, an input shaft Si of an automatic transmission (AT) or a continuously variable transmission (CVT) (not shown) is fixed to the turbine hub 5 (spline fitting).

  The pump impeller 3 has a pump shell 3 a and a plurality of blades 3 b, and the pump shell 3 a is closely fixed to the front cover 2. Similarly, the turbine runner 4 has a turbine shell 4 a and a plurality of blades 4 b, and the turbine shell 4 a is fixed to the turbine hub 5. The pump impeller 3 on the front cover 2 side and the turbine runner 4 on the turbine hub 5 side face each other, and a stator 6 that can rotate coaxially with the input shaft Si is disposed between them. The pump impeller 3, the turbine runner 4 and the stator 6 form a torus (annular flow path) for circulating the working oil (working fluid).

  The stator 6 includes an annular blade support 6a and a plurality of blades 6b fixed to the outer peripheral surface of the blade support 6a. In addition, a one-way clutch 9 that sets the rotation direction of the stator 6 to only one direction is disposed inside the blade support portion 6a. The one-way clutch 9 includes an inner race 91, an outer race 92, and a plurality of sprags 93 disposed between the inner race 91 and the outer race 92.

  The inner race 91 is fixed (spline fitting) to the outer periphery of the hollow shaft Sh arranged around the input shaft Si, and the outer race 92 is integrated with the blade support portion 6a in the rotation direction. Further, the inner race 91, the outer race 92, and the sprag 93 are sandwiched from both sides by annular washers 94 and 95 positioned on the inner periphery of the blade support portion 6a. The stator 6 (one-way clutch 9) is positioned between the sleeve 3c and the turbine hub 5 in the axial direction by the thrust bearings 10a and 10b via the bearing race 96.

  On the other hand, the damper unit 7 of the torque converter 1 is coupled to the turbine hub 5 together with the turbine shell 4a. As shown in FIG. 1, the damper unit 7 includes an intermediate plate 71, a plurality of springs (elastic bodies) 72, and guide plates 73 and 74. The intermediate plate 71 is formed as an annular member in which substantially trapezoidal protrusions are extended outward from a plurality of locations in the circumferential direction of the outer peripheral edge thereof, and the inner peripheral portion thereof is connected via a rivet or the like. The turbine hub 5 is fixed. A predetermined number of springs 72 are arranged between the protrusions of the intermediate plate 71, and the intermediate plate 71 and the springs 72 are sandwiched from both sides by the guide plates 73 and 74.

  The guide plates 73 and 74 are formed in an annular shape, and have spring holding portions 73a and 74a formed by opening a part of the plate outward and opening at a plurality of locations in the circumferential direction. The guide plate 73 and the guide plate 74 are connected (fixed) to each other by rivets or the like at a plurality of locations in the circumferential direction of the respective outer peripheral side edges. The intermediate plate 71 is held between the guide plates 73 and 74 so as to be rotatable relative to the guide plates 73 and 74, and the springs 72 arranged between the protrusions of the intermediate plate 71 are respectively corresponding spring holding portions. 73a and 74a. At this time, one outer end (the end opposite to the protrusion) of the spring 72 comes into contact with one end of the spring holding portions 73a and 74a.

  The lockup clutch mechanism 8 of the torque converter 1 is disposed between the above-described damper unit 7 and the front cover 2. As shown in FIG. 1, the lockup clutch mechanism 8 includes an annular lockup piston 80 and an annular member 81 fixed to the front cover 2. As shown in FIG. 1, a plurality of splines are provided on the inner peripheral surface of the annular member 81, and a plurality of friction plates 82 are slidably fitted into these splines. A plurality of splines are also provided on the outer peripheral portion of the guide plate 73 constituting the damper unit 7, and a plurality of friction disks 83 are slidable on these splines and the friction plate 82 on the annular member 81 side. It is fitted so that it is located between them.

  The central opening of the lock-up piston 80 is slidably fitted around the piston receiving member 2 a fixed to the front cover 2, and the outer peripheral portion of the lock-up piston 80 is located inside the annular member 81. The peripheral surface is slidably supported. Further, the free end of the outer peripheral portion of the lock-up piston 80 can be brought into contact with the friction plate 82 disposed closest to the front cover 2 side.

  In the torque converter 1 configured as described above, when an engine (not shown) is operated and the front cover 2 and the pump impeller 3 rotate, the turbine runner 4 starts to be dragged by the flow of hydraulic oil. When the rotational speed difference between the pump impeller 3 and the turbine runner 4 is large, the stator 6 converts the flow of hydraulic oil into a direction that assists the rotation of the pump impeller 3. Thus, the torque converter 1 operates as a torque amplifier when the rotational speed difference between the pump impeller 3 and the turbine runner 4 is large. Further, when the difference in rotational speed between the pump impeller 3 and the turbine runner 4 becomes small, the stator 6 idles via the one-way clutch 9, whereby the torque converter 1 operates as a fluid coupling.

  When a predetermined condition is satisfied after the vehicle starts (for example, when the vehicle speed reaches a predetermined value), the lock-up clutch mechanism 8 is activated, and the power transmitted from the engine to the front cover 2 is used as an output member. Is directly transmitted to the turbine hub 5 (mechanically [directly transmitted)], whereby the engine and the input shaft of the transmission are mechanically directly connected. Further, the fluctuation of torque transmitted from the front cover 2 to the turbine hub 5 is absorbed by the damper unit 7.

  At the time of such lock-up, it is defined between the front cover 2 and the lock-up piston 80 via an oil passage Sid formed in the input shaft Si and an oil passage 2b formed in the piston receiving member 2a. Hydraulic oil is supplied into the oil chamber R1. As a result, the lock-up piston 80 moves toward the damper unit 7 and presses the friction plate 82 and the friction disk 83, so that the front cover 2 and the damper unit 7 (guide plate 73) are firmly connected. Rotate together. Further, when the hydraulic oil supply pressure to the oil chamber R1 is lowered below the hydraulic oil supply pressure to the oil chamber R2, the lock-up piston 80 moves toward the front cover 2, thereby the oil chamber R1. As a result, the hydraulic oil is discharged, and the connection between the front cover 2 and the lock-up piston 80 is broken, and a difference in rotation occurs between the two.

  In the torque converter 1 configured as described above, as a power transmission medium for circulating a torus (annular flow path) formed by the pump impeller 3, the turbine runner 4, and the stator 6, a lock-up clutch mechanism 8 is further provided. The hydraulic oil as a medium used for cooling and lubrication is supplied to the pump impeller 3. For this reason, a hydraulic fluid passage 60 for ejecting the working fluid toward the pump impeller 3 is formed in the blade support portion 6 a of the stator 6 disposed between the pump impeller 3 and the turbine runner 4. . As shown in FIGS. 1 and 2, the hydraulic oil flow path 60 includes an annular recess 61 formed in the inner peripheral portion of the blade support portion 6 a and a plurality of jets extending outward from the annular recess 61. Hole 62.

  As can be seen from FIG. 1, the annular recess 61 is formed to extend in the radial direction of the input shaft Si. On the other hand, each ejection hole 62 is inclined toward the pump impeller 3 and extends while being inclined in the rotation direction of the pump impeller 3 (see the white arrow in FIG. 2). That is, as can be seen from FIG. 1, each ejection hole 62 is inclined in the direction from the turbine runner 4 toward the pump impeller 3 in the axial direction of the stator 6 (input shaft Si), and as shown in FIG. As seen from the axial direction of the stator 6 (input shaft Si), it extends in a state of being inclined in the rotational direction of the pump impeller 3.

  In addition, a washer 95 disposed in the vicinity of the pump impeller 3 in order to supply hydraulic oil to the hydraulic oil flow path 60 formed in the blade support portion 6a of the stator 6 is shown in FIGS. It is formed as shown in FIG. That is, the surface of the washer 95 on the pump impeller 3 side has a plurality of recesses 95a extending outwardly and radially from the inner periphery thereof (in this embodiment, at intervals of 90 °, as shown in FIGS. 3 and 4). 4) formed. Each recess 95 a terminates on the inner side of the outer peripheral edge of the washer 95.

  Further, as shown in FIG. 3 and FIG. 5, a plurality of (this embodiment) is provided on the surface of the washer 95 on the turbine runner 4 side so as to be located on the back side of each recess 95a formed on the surface of the pump impeller 3 side. In the embodiment, four concave portions 95b are formed at intervals of 90 °. Each concave portion 95 b extends inward and radially from the outer peripheral edge of the washer 95, and terminates outside the inner peripheral edge of the washer 95. The recesses 95b and the recesses 95a located on the back sides of the recesses 95b communicate with each other through the communication holes 95c.

  When the washer 95 configured as described above is positioned with respect to the blade support portion 6a, the recess 95a adjacent to the pump impeller 3 communicates with an oil passage defined between the sleeve 3c and the hollow shaft Sh. In addition, the outer peripheral end of the recess 95 b adjacent to the turbine runner 4 communicates with the annular recess 61 formed in the blade support portion 6 a of the stator 6. Moreover, the recessed part 95a which adjoins the turbine runner 4 is connected also with the space between the inner race 91 and the outer race 92, as FIG. 1 shows.

  Therefore, if hydraulic oil is supplied at a predetermined pressure to the oil passage defined between the sleeve 3c and the hollow shaft Sh via the oil passage Sia and the hole Sib formed in the input shaft Si, the hydraulic oil is Then, it flows into the annular recess 61 of the blade support portion 6a through the recess 95a, the communication hole 95c, and the recess 95b, and further flows into the ejection holes 62 from the annular recess 61. Since each ejection hole 62 is inclined in the rotational direction of the pump impeller 3, the hydraulic oil ejected from each ejection hole 62 collides with the blade 3 b of the pump impeller 3 to rotate the pump impeller 3. I will assist.

  Thus, in the torque converter 1 according to the present invention, it is possible to promote the rotation of the pump impeller 3 by using the energy of the working fluid supplied toward the pump impeller 3 with a certain pressure. The transmission efficiency can be improved by increasing the pump torque.

  In addition, by forming the hydraulic oil flow path 60 including the annular recess 61 and the plurality of ejection holes 62 in the blade support portion 6a of the stator 6, the rotation of the pump impeller 3 is assisted using the energy of the hydraulic oil. This configuration can be easily realized. In this case, the reaction force generated by assisting the rotation of the pump impeller 3 by the hydraulic oil is received by the stator 6. However, in the region where the stator 6 idles, the amount of heat generated in the torque converter 1 is reduced, and the torque converter 1 Since the amount of hydraulic oil in the interior can be reduced, the reaction force received by the stator 6 itself is reduced, so that the influence of the reaction force on the fluid characteristics is minimized. Further, when the stator 6 is fixed by the one-way clutch 9 (when the stator 6 does not rotate), the reaction force does not affect the fluid characteristics.

  Further, in the present embodiment, each ejection hole 62 constituting the hydraulic oil flow path 60 is inclined from the turbine runner 4 toward the pump impeller 3, so that it flows out from the turbine runner 4 and flows into the pump impeller 3. The hydraulic oil (see the two-dot chain line in FIG. 1) can be ejected from each of the ejection holes 62 so as to substantially follow the flow direction of the hydraulic oil (see the one-dot chain line in FIG. 1). That is, in the present embodiment, the hydraulic oil ejected from each ejection hole 62 has not only the radial component of the input shaft Si but also the axial component of the input shaft Si. Thereby, it becomes possible to increase the flow rate of the hydraulic oil circulating between the pump impeller 3 and the turbine runner 4, and to increase the capacity coefficient of the torque converter 1.

  Part of the hydraulic oil that has reached the recess 95a of the washer 95 flows into the periphery of the sprag 93 of the one-way clutch 9 from the recess 95a, lubricates and cools the one-way clutch 9, and then a hole 94a formed in the washer 94. And it flows into oil chamber R4 defined between turbine shell 4a and damper unit 7 via crevice 94b and hole 4c formed in turbine shell 4a. A part of the hydraulic oil also flows into the oil chamber R4 from the pump impeller 3, and the hydraulic oil is used for cooling the lockup clutch mechanism 8 and the like. Further, when the lockup clutch mechanism 8 is released from the lockup, the hydraulic oil supply pressure to the oil chamber R1 is made lower than the hydraulic oil supply pressure to the oil chamber R2, and the lockup piston 80 is directed toward the front cover 2. To move. Further, the hydraulic oil in the oil chamber R2 flows through an oil path between the turbine hub 5 and the piston receiving member 2a and an oil path (not shown) formed in the input shaft Si via a hole Sic formed in the input shaft Si. Returned to.

It is sectional drawing which shows the fluid transmission apparatus by this invention. It is sectional drawing which shows the stator contained in the fluid power transmission apparatus of FIG. It is sectional drawing which shows the washer provided with respect to the stator contained in the fluid power transmission apparatus of FIG. It is the front view which looked at the washer of FIG. 3 from the VI direction in FIG. It is the rear view which looked at the washer of FIG. 3 from the V direction in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 3 Pump impeller 4 Turbine runner 5 Turbine hub 6 Stator 6a Blade support part 6b Blade 60 Hydraulic oil flow path 61 Annular recessed part 62 Injection hole 7 Damper unit 71 Intermediate | middle plate 72 Spring 73, 74 Guide plate 8 Lock up Clutch mechanism 80 Lock-up piston 81 Annular member 82 Friction plate 83 Friction disk 9 One-way clutch 91 Inner race 92 Outer race 93 Sprag 94, 95 Washer 95a, 95b Recess 95c Communication hole R1, R2, R3, R4 Oil chamber Si Input shaft

Claims (4)

In a fluid transmission device that transmits power from an input member to an output member via a working fluid,
A pump impeller attached to the input member;
A fluid transmission mounted on the output member, comprising a turbine runner facing the pump impeller, wherein working fluid is supplied to the pump impeller so as to assist the rotation of the pump impeller. apparatus.   A stator for guiding the fluid flowing out from the turbine runner to the pump impeller; and an operation for ejecting the working fluid toward the pump impeller so as to assist the rotation of the pump impeller. The fluid transmission device according to claim 1, wherein a fluid flow path is formed.   The fluid transmission device according to claim 2, wherein the working fluid flow path includes a region inclined in a rotation direction of the pump impeller. The said working fluid flow path is formed so that a working fluid may be ejected along the flow direction of the working fluid which flows out from the said turbine runner, and flows in into the said pump impeller. The fluid transmission device described.

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