JP2017129199A - Variable inertia flywheel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To attain a structure of a variable inertia flywheel capable of changing inertial moment regardless of a rotational speed.SOLUTION: In a plurality of places in a circumferential direction of a flywheel body 4 rotating together with a driving shaft, weights 5, 5 are held so as to enable change of a radial position. At a radial central part of the flywheel body 4, held is a rotationally driving mechanism 6 having a vane rotor 12, as a movable part, to enable rotational driving to the flywheel body 4. The respective weights 5, 5 and the vane rotor 12 are coupled with link mechanisms 7, 7. Consequently, based on the rotational driving of the vane rotor 12, the respective link mechanisms 7, 7 can synchronize the respective weights 5, 5 with each other to move them in a radial direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a variable inertia flywheel that is configured to rotate with a crankshaft of an engine for a vehicle, for example, and has a configuration capable of changing a moment of inertia.

  For example, in an engine for a vehicle such as an automobile, a flywheel as an inertial body is attached to the end of the crankshaft in order to suppress rotational fluctuations at the time of starting, idling, etc., especially at low speed rotation, The engine output is transmitted to the transmission and clutch. Such a flywheel desirably has a moment of inertia as large as possible from the viewpoint of suppressing engine rotation fluctuations, but is as small as possible from the viewpoint of improving engine startability and acceleration response. It is desirable to have a moment of inertia.

In view of such circumstances, flywheels capable of changing the moment of inertia have been developed in recent years.
For example, Patent Document 1 has weights arranged at a plurality of locations in the circumferential direction as components of a flywheel, and each of these weights is utilized by utilizing a centrifugal force that changes according to the rotational speed of the flywheel. A structure is described in which the moment of inertia of the flywheel is made variable by moving it in the radial direction.
However, in the case of such a conventional structure, since each weight is moved by utilizing a centrifugal force that changes according to the rotational speed of the flywheel, each weight is directed radially outward when the engine rotates at a low speed. There is a possibility that the flywheel cannot be moved sufficiently and the moment of inertia of the flywheel cannot be increased sufficiently. In particular, during acceleration at medium and high speeds, each weight may stick to the leaf spring attached to the outer diameter side surface of the guide groove, and the moment of inertia of the flywheel may not be sufficiently reduced.

JP 2003-206992 A

  The present invention has been invented to realize a variable inertia flywheel structure capable of changing the moment of inertia regardless of the rotational speed of the engine in view of the above circumstances.

The variable inertia flywheel of the present invention includes a flywheel body, a plurality of weights, a rotation drive mechanism, and power transmission means.
Of these, the flywheel body rotates together with a drive shaft such as an engine crankshaft.
Each of the weights is held at a plurality of locations in the circumferential direction of the flywheel body so that its radial position can be changed.
Moreover, the said rotational drive mechanism is hold | maintained at the radial direction center part of the said flywheel main body, and has a movable part which can be rotationally driven with respect to the said flywheel main body.
In addition, the power transmission means changes the radial positions of the weights in synchronization with each other as the movable part is rotationally driven with respect to the flywheel body.

When carrying out the present invention, for example, as in the invention described in claim 2, the power transmission means can be a link mechanism that connects the movable part and the weights.
Alternatively, for example, the power transmission means can be a power transmission member that changes the contact position with each weight in the radial direction as it rotates together with the movable portion.

  In carrying out the present invention, for example, as in the third aspect of the present invention, it is possible to employ a configuration including an elastic member that biases each of the weights radially outward.

  According to the variable inertia flywheel of the present invention having the above-described configuration, the moment of inertia can be changed regardless of the rotational speed.

The schematic block diagram which shows the variable inertia flywheel regarding the 1st example of embodiment of this invention in the state assembled | attached to the crankshaft of the engine. Similarly, the figure which looked at the mechanism part which changes an inertia moment from the axial direction one side. The figure similar to FIG. 2 which shows the 2nd example of embodiment of this invention. The figure similar to FIG. 2 which shows the 3rd example of embodiment of this invention.

[First example of embodiment]
A first example of the embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, the variable inertia flywheel 1 of this example is attached to the end of a crankshaft 3 that is a drive shaft that constitutes an engine 2 for a vehicle such as an automobile. Rotate.

  Such a variable inertia flywheel 1 of this example includes a flywheel body 4, a plurality of weights 5, 5, a rotation drive mechanism 6, and a plurality of link mechanisms 7, 7 as power transmission means.

  The flywheel body 4 is configured in a disc shape. When the flywheel main body 4 is arranged coaxially with the crankshaft 3 in the assembled state to the engine 2, a plurality of bolts or the like are provided with respect to the flange portion 8 provided at the end of the crankshaft 3. The coupling members 9 and 9 are coupled and fixed. Further, the circumferential direction among the radially outer end portion or intermediate portion of one side surface in the axial direction of the flywheel body 4 (the left side surface or the right side surface in FIG. 1, the side surface on the front side in FIG. 2). Guide recesses 10 and 10 extending in the radial direction (radial direction) of the flywheel body 4 are provided at a plurality of locations (three locations in the illustrated example) that are equally spaced.

  Each of the weights 5 and 5 is held inside the guide recesses 10 and 10 so as to be movable along the guide recesses 10 and 10. In other words, the respective weights 5 and 5 are held at a plurality of positions at equal intervals in the circumferential direction of the flywheel body 4 so that the radial position can be changed (movable in the radial direction).

  The rotational drive mechanism 6 is a hydraulic rotary actuator, and is held at the radial center of the flywheel body 4. Such a rotational drive mechanism 6 includes a housing 11 fixed to the flywheel body 4 and is accommodated in the housing 11, and the center axis of the flywheel body 4 a is set to the housing 11. A vane rotor 12 which is a movable part and is held so as to be able to rotate around the center. The vane rotor 12 can be rotationally driven with respect to the housing 11 by the hydraulic pressure generated based on the supply and discharge of the pressure oil to and from the hydraulic chamber provided inside the housing 11. With respect to such a hydraulic rotary actuator, various types of conventionally known structures can be employed.

  Each of the link mechanisms 7, 7 connects the weights 5, 5 and one axial end portion of the first connecting pin 13 that is a central axis fixed to the central portion of the vane rotor 12. Each of the link mechanisms 7 and 7 includes a first link arm 14 and a second link arm 15. Of these, the base end portion of the first link arm 14 is coupled and fixed to one end portion in the axial direction of the first connecting pin 13. The distal end portion of the first link arm 14 and the proximal end portion of the second link arm 15 are connected to the second connecting pin 16 by a second connecting pin 16 provided in parallel with the first connecting pin 13. Are coupled so as to be able to swing relative to each other. The tip end of the second link arm 15 is centered on the third connecting pin 17 with respect to the third connecting pin 17 projecting from the central portion of one side surface of the weights 5 and 5 in the axial direction. It is coupled so as to be capable of swinging displacement. In the case of this example, the first link arms 14 and 14 constituting the link mechanisms 7 and 7 are arranged at equal intervals in the circumferential direction. Further, the inclination direction and the inclination angle of the second link arms 15 and 15 with respect to the first link arms 14 and 14 constituting the link mechanisms 7 and 7 are the same direction and the same angle, respectively.

  In the case of the variable inertia flywheel 1 of the present example having the above-described configuration, for example, as shown in FIG. 2A, the weights 5 and 5 are radially outer ends in the guide recesses 10 and 10, respectively. When the vane rotor 12 is rotated with respect to the housing 11 in the direction of the arrow α in a state where the rotor is located at a portion, that is, in a state where the inertia moment of the variable inertia flywheel 1 is maximized, As shown in A) → (B), the first link arms 14, 14 constituting each of the link mechanisms 7, 7 rotate together with the vane rotor 12 in the direction of the arrow α, so that the first link arms 14, 14, 14 and the respective second link arms 15 and 15 are increased, the respective weights 5 and 5 are synchronized with each other in the respective guide recesses 10 and 10 radially inward (in the radial direction). Move to the inner edge). With such movement, the inertia moment of the variable inertia flywheel 1 continuously decreases {minimum in the state shown in FIG. 2B}. On the contrary, as shown in FIG. 2B, the weights 5 and 5 are located at the radially inner ends of the guide recesses 10 and 10, that is, the variable inertia flywheel 1 of the variable inertia flywheel 1. When the vane rotor 12 is rotated in the arrow β direction (the direction opposite to the arrow α direction) with respect to the housing 11 in a state where the moment of inertia is minimized, as shown in FIG. 2 (B) → (A). Similarly, when the first link arms 14, 14 constituting the link mechanisms 7, 7 rotate in the arrow β direction together with the vane rotor 12, the first link arms 14, 14 and the second link arms As the inclination angle with respect to 15 and 15 decreases, the weights 5 and 5 move radially outward (to the radially outer end) in the guide recesses 10 and 10 in synchronization with each other. With such movement, the inertia moment of the variable inertia flywheel 1 continuously increases {maximum in the state shown in FIG. 2A}.

  As described above, in the case of the variable inertia flywheel 1 of this example, regardless of the rotational speed of the engine 2 (the crankshaft 3), the pressure oil to the hydraulic chamber constituting the rotational drive mechanism 6 The moment of inertia of the variable inertia flywheel 1 can be changed by changing the rotation angle of the vane rotor 12 with respect to the housing 11 by controlling the supply / discharge state. Therefore, for example, the acceleration of the engine 2 is detected by an appropriate method known in the art, and when the engine 2 is accelerated (including when it is started), as shown in FIG. The acceleration performance of the engine 2 is improved by sufficiently reducing (minimizing) the moment of inertia of the variable inertia flywheel 1 by moving the weights 5 and 5 to the radially inner end. In addition, the fuel consumption can be improved. Similarly, when the engine 2 is at a constant speed and is decelerated (including during low-speed rotation), the weights 5 and 5 are moved to the radially outer end as shown in FIG. Thus, by sufficiently increasing (maximizing) the moment of inertia of the variable inertia flywheel 1, the rotational fluctuation of the engine 2 can be sufficiently suppressed.

  In the case of this example, the weights 5 and 5 are moved in the radial direction by utilizing not only the oil pressure by the rotary drive mechanism 6 but also the lever force by the link mechanisms 7 and 7. The configuration of the rotational drive mechanism 6 (hydraulic equipment including the rotary drive mechanism) can be made compact.

In addition, although illustration is abbreviate | omitted, in the 1st example of embodiment mentioned above, elastic members, such as a spring which urges | biases each said weight 5 and 5 to a radial direction outer side, can also be provided. By adopting such a configuration, the driving force of the rotational drive mechanism 6 only needs to be generated when the weights 5 and 5 are moved radially inward, so that the running cost can be suppressed.
When carrying out the structure of this example, the flywheel body 4 includes the weights 5, 5, the link mechanisms 7, 7, etc. covering the one side surface in the axial direction of the flywheel body 4. A cover that prevents exposure to the outside can also be fixed.

[Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIG.
In the case of this example, the configuration of the flywheel body 4a, the plurality of weights 5a, 5a, the rotation drive mechanism 6a, and the plurality of link mechanisms 7a, 7a serving as power transmission means is the first example of the above-described embodiment. It is different from the case of.

  In the case of this example, the rotation drive mechanism 6a is an electric rotary actuator, and is held at the radial center of the flywheel body 4a. Such a rotational drive mechanism 6a supports a stator portion 18 fixed to the flywheel main body 4a and allows the stator portion 18 to rotate around the central axis of the flywheel main body 4a. And a rotor portion 19 which is a movable portion. And it has the structure which can drive the said rotor part 19 with respect to the said stator part 18 with the electromagnetic force which generate | occur | produces with the electricity supply to either one of these stator parts 18 and the rotor parts 19. Yes. With respect to such an electric rotary actuator, various types of conventionally known structures can be employed.

  The plurality (eight in the illustrated example) of the weights 5a and 5a are each formed in an oval plate shape, and are arranged on one side in the axial direction of the flywheel main body 4a (front side in FIG. 3). 1 are arranged at equal intervals in the circumferential direction at positions facing (adjacent) the radial outer end or intermediate portion of the side surface, the left side surface or the right side surface in the use state shown in FIG.

  The link mechanisms 7a and 7a connect the weights 5a and 5a to the rotor portion 19 that constitutes the rotation drive mechanism 6a. Each of the link mechanisms 7 a and 7 a includes an annular link plate 20 and a link arm 21. Of these, the link plate 20 is a member shared by the link mechanisms 7a and 7a, and has a central portion in the radial direction coupled and fixed to a rotor portion 19 constituting the rotation drive mechanism 6a. Further, the base end portions of the link arms 21, 21 constituting the link mechanisms 7 a, 7 a are respectively provided at a plurality of locations at equal intervals in the circumferential direction of the radially outer end portion of the link plate 20. The coupling pins 22 and 22 provided in parallel with the central axis of 4a are coupled so as to be capable of swinging displacement. Further, the distal ends of the link arms 21 and 21 are integrally coupled and fixed to one end of the weights 5a and 5a in the major axis direction (the end located on the inner side with respect to the radial direction of the flywheel body 4a). ing. Further, guide pins 23, 23 projecting to the other side in the axial direction (the back side in the drawing in FIG. 3) are provided at the end portions of the link arms 21, 21, and these guide pins 23, 23 is engaged with each guide groove 24, 24 formed in an open state on one side surface in the axial direction of the flywheel body 4a so that the guide groove 24, 24 can be moved. These guide grooves 24, 24 extend (inclined) in a direction toward one side in the circumferential direction of the flywheel body 4a (counterclockwise side in FIG. 3) as it goes inward in the radial direction of the flywheel body 4a. ).

  In the case of the variable inertia flywheel of this example having the above-described configuration, for example, as shown in FIG. 3A, the guide pins 23, 23 are arranged at the radially outer ends of the guide grooves 24, 24. (The angle of inclination of the long axes of the link arms 21 and the weights 5a and 5a with respect to the radial direction is zero, and the weights 5a and 5a are positioned radially outward). State), that is, in a state where the inertia moment of the variable inertia flywheel is maximized, when the rotor portion 19 constituting the rotational drive mechanism 6a is rotated in the arrow α direction with respect to the stator portion 18, As shown in FIG. 3 (A) → (B), the link plate 20 rotates in the direction of the arrow α together with the rotor portion 19, so that the guide pins 23, 23 are inserted into the guide grooves 24, 24. Move radially inward along At the same time, as the inclination angle of the long axis of each link arm 21 and each weight 5a, 5a with respect to the radial direction increases, each weight 5a, 5a moves radially inward in synchronization with each other. With such movement, the inertia moment of the variable inertia flywheel continuously decreases {minimum in the state shown in FIG. 3B}. On the contrary, as shown in FIG. 3B, the respective guide pins 23, 23 are located at the radially inner ends of the respective guide grooves 24, 24 (the respective link arms 21 with respect to the radial direction). In addition, the inclination angle of the major axis of each of the weights 5a and 5a is maximized, and the respective weights 5a and 5a are positioned radially inward), that is, the inertia moment of the variable inertia flywheel is minimized. 3 (B) → (A) in FIG. 3 when the rotor portion 19 constituting the rotational drive mechanism 6a is rotated in the arrow β direction (the direction opposite to the arrow α direction) with respect to the stator portion 18 in the state As shown in FIG. 4, when the link plate 20 rotates in the direction of the arrow β together with the rotor portion 19, the guide pins 23, 23 move radially outward along the guide grooves 24, 24. , Each Click arm 21 and the respective weights 5a, along with reducing the inclination angle of the long axis of 5a, each spindle 5a, 5a are moved in synchronization with the radially outward from each other. With such movement, the inertia moment of the variable inertia flywheel continuously increases {maximum in the state shown in FIG. 3A}.

  As described above, in the case of the variable inertia flywheel of this example, the stator portion is energized by energization of the rotational drive mechanism 6a regardless of the rotational speed of the engine 2 (crankshaft 3, see FIG. 1). The moment of inertia of the variable inertia flywheel can be changed by changing the rotation angle of the rotor portion 19 with respect to 18.

Although illustration is omitted, in the second example of the above-described embodiment, an elastic member such as a spring for urging the weights 5a and 5a outward in the radial direction can be provided. If such a configuration is adopted, the driving force of the rotational drive mechanism 6a only needs to be generated when the weights 5a and 5a are moved radially inward, so that the running cost can be suppressed.
Also when the structure of this example is implemented, the flywheel body 4a covers the one side in the axial direction of the flywheel body 4a, and the weights 5a, 5a, the link mechanisms 7a, 7a, etc. It is also possible to fix a cover that prevents exposure to the outside.
Other configurations and operations are the same as those in the first example of the embodiment described above.

[Third example of embodiment]
A third example of the embodiment of the present invention will be described with reference to FIG.
In the case of this example, the configuration of the flywheel body 4b, the plurality of weights 5b, 5b, the rotation drive mechanism 6a, and the power transmission member 25 that is the power transmission means is the same as in the case of the first example of the above-described embodiment. Different.

  In the case of this example, the rotational drive mechanism 6a is an electric rotary actuator having the same configuration as that of the second example of the embodiment described above, and in the case of the second example of the embodiment described above. Similarly, the flywheel main body 4b is held at the center in the radial direction.

  Further, of the radial outer end portion to the intermediate portion of one side surface in the axial direction of the flywheel main body 4b (the side surface in front of the paper surface in FIG. 4, the left side surface or the right side surface in the use state shown in FIG. 1), At a plurality of locations that are equally spaced in the circumferential direction (the same number of the weights 5b and 5b), each of them extends in the direction toward one side in the circumferential direction (counterclockwise in FIG. 4) as it goes radially inward. (Inclined) guide recesses 10a and 10a are provided. Each of the weights 5b and 5b is held inside the guide recesses 10a and 10a so as to be movable along the guide recesses 10a and 10a. Further, inside the guide recesses 10a and 10a, between the weights 5b and 5b, the weights 5b and 5b are placed between the guide recesses 10a and 10a. Coil springs 26 and 26, which are elastic members, are provided to be urged radially outward in 10a and 10a.

  The power transmission member 25 includes a cylindrical base portion 27 that is coupled and fixed coaxially with the rotor portion 19 with respect to the rotor portion 19 that constitutes the rotational drive mechanism 6a, and a circumferential direction of the outer peripheral surface of the base portion 27 Arm portions 28 and 28 provided in a state of extending radially outward from a plurality of locations (the same number of the weights 5b and 5b) at equal intervals. Then, one circumferential side surface (side surface facing in the counterclockwise direction in FIG. 4) of each arm portion 28, 28 is axially extended from each guide recess 10a, 10a of each weight 5b, 5b. It is made to contact | abut to the axial direction one end part which protruded. In the case of this example, in this state, when the power transmission member 25 is rotated in one circumferential direction (in the direction of arrow α in FIG. 4), from the circumferential one side surface of each of the arm portions 28 and 28. The respective weights 5b and 5b are diametrically extended along the guide recesses 10a and 10a (against the urging force of the coil springs 26 and 26) with respect to one axial end portion of the weights 5b and 5b. The shape and forming direction of each part are regulated so that a force (component force) having a direction and a size to move inward is applied.

  In the case of the variable inertia flywheel of this example having the above-described configuration, for example, as shown in FIG. 4A, the weights 5b and 5b are radially outer ends in the guide recesses 10a and 10a. The rotor portion 19 constituting the rotary drive mechanism 6a is moved in the direction of the arrow α with respect to the stator portion 18 in a state where the rotor portion 19 is located at a portion, that is, in a state where the inertia moment of the variable inertia flywheel 1 is maximized. 4 (A) → (B), when the power transmission member 25 rotates in the direction of the arrow α together with the rotor portion 19, one end in the axial direction of each of the weights 5b and 5b. The weights 5b and 5b are applied to the urging forces of the coil springs 26 and 26 based on the pressing of the portion to one side surface in the circumferential direction of the arm portions 28 and 28 constituting the power transmission member 25. Against the guide recesses 10a and 10a) And move inward in the radial direction (to the inner end in the radial direction) (according to this, contact of one side in the circumferential direction of each arm 28, 28 with one end in the axial direction of each of the weights 5b, 5b) Position changes radially inward). As the weights 5b and 5b move as described above, the inertia moment of the variable inertia flywheel continuously decreases {minimum in the state shown in FIG. 4B}. On the contrary, as shown in FIG. 4B, the weights 5b and 5b are located at the radially inner ends of the guide recesses 10a and 10a, that is, the variable inertia flywheel 1 4 is rotated in the arrow β direction (the direction opposite to the arrow α direction) with respect to the stator portion 18 in a state where the inertia moment is minimized, As shown in (B) → (A), when the power transmission member 25 rotates together with the rotor portion 19 in the direction of the arrow β, the circumferential directions of the arm portions 28 and 28 constituting the power transmission member 25 are as follows. By releasing the force applied to one end in the axial direction of each of the weights 5b and 5b from one side, the respective weights 5b and 5b are guided by the respective guides based on the biasing force of the coil springs 26 and 26. Synchronously with each other in the recesses 10a and 10a Move outward (to the radially outer end) (according to this, the contact position of one side in the circumferential direction of each arm 28, 28 with respect to the one axial end of each of the weights 5b, 5b is radially outward) Change towards). As the weights 5b and 5b move as described above, the inertia moment of the variable inertia flywheel continuously increases {maximum in the state shown in FIG. 4A}.

  As described above, in the case of the variable inertia flywheel of this example, the stator portion is energized by energization of the rotational drive mechanism 6a regardless of the rotational speed of the engine 2 (crankshaft 3, see FIG. 1). The moment of inertia of the variable inertia flywheel can be changed by changing the rotation angle of the rotor portion 19 with respect to 18.

In the case of this example, coil springs 26 and 26 for urging the weights 5b and 5b outward in the radial direction are provided. Therefore, since the driving force of the rotational drive mechanism 6a only needs to be generated when the weights 5b and 5b are moved radially inward, the running cost can be suppressed.
Even when the structure of this example is implemented, the flywheel body 4b covers the one side of the flywheel body 4b in the axial direction, and the weights 5b and 5b, the power transmission member 25, and the like are external. It is also possible to fix a cover that prevents exposure.
Other configurations and operations are the same as those in the first example of the embodiment described above.

The present invention is implemented by replacing the rotary drive mechanism 6 of the first example of the above-described embodiment with an electric rotary actuator such as the rotary drive mechanism 6a of the second to third examples of the above-described embodiment. You can also do it.
In the present invention, the second to third examples of the rotational drive mechanism 6a of the above-described embodiment are replaced with a hydraulic rotary actuator such as the first example of the rotational drive mechanism 6 of the above-described embodiment. Can also be implemented.

DESCRIPTION OF SYMBOLS 1 Variable inertia flywheel 2 Engine 3 Crankshaft 4, 4a, 4b Flywheel main body 5, 5a, 5b Weight 6, 6a Rotation drive mechanism 7, 7a Link mechanism 8 Flange part 9 Coupling member 10, 10a Guide recessed part 11 Housing 12 Vane rotor DESCRIPTION OF SYMBOLS 13 1st connection pin 14 1st link arm 15 2nd link arm 16 2nd connection pin 17 3rd connection pin 18 Stator part 19 Rotor part 20 Link plate 21 Link arm 22 Connection pin 23 Guide pin 24 Guide groove 25 Power transmission member 26 Coil spring 27 Base 28 Arm

Claims (3)

A flywheel body that rotates with the drive shaft;
A plurality of weights held in a plurality of locations in the circumferential direction of the flywheel body so that the radial position can be changed;
A rotary drive mechanism that is held at the center in the radial direction of the flywheel body and has a movable part that can be rotationally driven with respect to the flywheel body;
And a power transmission means for changing a radial position of each of the weights in synchronization with the rotational drive of the movable part with respect to the flywheel body. A variable inertia flywheel.   The variable inertia flywheel according to claim 1, wherein the power transmission means is a link mechanism that connects the movable part and the weights.   The variable inertia flywheel according to claim 1, further comprising an elastic member that urges each of the weights outward in the radial direction.

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