JP2011252579A - Power device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a power device which combines an engine with a reciprocating-type continuously variable transmission.SOLUTION: A crank shaft 14 of an engine E and an output shaft 15 of the continuously variable transmission T are arranged in parallel. Connecting rod 13 and the output shaft 15 are connected via a first two-pairing-elements joint L1, a second two-pairing-elements joint L2, a three-pairing-elements joint L3, and a one-way clutch 16. By changing the length of at least one joint of three joints of the three-pairing-elements joint L3 by a gear ratio change means V or by changing a fixed position of a third turning pair P3, the rotational motion of the crank shaft 14 can be converted by a gear change into an intermittent rotational motion of the output shaft 15. Because the axis of the engine E and that of the continuously variable transmission T can be arranged in parallel, dimension in the axial direction of the power device can be miniaturized and in addition, an input shaft of the continuously variable transmission T becomes unnecessary so that dimension in the direction perpendicular to the shaft of the power device can be miniaturized.

Description

  The present invention relates to an engine that converts a reciprocating motion of a piston into a rotational motion of a crankshaft through a connecting rod, and a shift that converts the rotational motion of the crankshaft into an intermittent rotational motion of an output shaft through a link mechanism and a one-way clutch. The present invention relates to a power unit comprising a motor and a gear ratio changing means for changing a gear ratio of the transmission.

  In a reciprocating continuously variable transmission that converts the rotational movement of the input shaft into the reciprocating movement of the connecting rod with an eccentric disk with variable eccentricity, and the reciprocating movement of the connecting rod into the intermittent rotational movement of the output shaft with a one-way clutch. Patent Document 1 listed below discloses that an engine crankshaft and an input shaft of the continuously variable transmission are connected in series.

JP-T-2005-502543

  By the way, in the above-mentioned conventional one, since the crankshaft of the engine and the input shaft of the continuously variable transmission are connected in series, the axial dimension of the power unit constituted by the engine and the continuously variable transmission is increased. Inevitably, it may be difficult to secure a space when the power device is mounted on a vehicle or the like.

  In order to solve this problem, it is conceivable that the crankshaft of the engine and the input shaft of the continuously variable transmission are arranged in parallel, and the crankshaft and the input shaft are connected by a gear or a chain. However, since the crankshaft, the input shaft, and the output shaft are arranged in parallel in this way, there is a problem that the dimension in the direction perpendicular to the axis of the power unit increases.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to reduce the size of a power unit that combines an engine and a reciprocating transmission.

  In order to achieve the above object, according to the first aspect of the present invention, an engine that converts the reciprocating motion of the piston into the rotational motion of the crankshaft via the connecting rod, and the rotational motion of the crankshaft are linked mechanisms. And a transmission for converting to intermittent rotation motion of the output shaft via a one-way clutch, and a gear ratio changing means for changing a gear ratio of the transmission, wherein the link mechanism is rotated by the engine. A first pair that moves; a second pair that is provided on the one-way clutch; a third pair that is fixed in position; a fourth pair that swings around the third pair; and the third pair A fifth pair even swinging about the first pair, a first second pair even clause connecting the first pair and the fourth pair, and connecting the second pair and the fifth pair A second two-pair even-numbered clause and a three-pair even-numbered clause for connecting the third, even-numbered fourth and even-numbered fifth-even numbers, and By changing the length of at least one of the nodes or changing the fixed position of the third pair, the stroke of the reciprocating swing of the second pair is increased or decreased to change the transmission ratio of the transmission. A power plant characterized by this is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the transmission ratio changing means is configured such that the volume increases in the opposite direction in accordance with the rotation of the rotating shaft and the rotating shaft. The first and second oil chambers to be reduced, the first oil passage connected to the first oil chamber, the second oil passage connected to the second oil chamber, and between the first oil passage and the second oil passage. A check valve that is disposed, a switching valve that is disposed between the first oil passage and the second oil passage, and switches a connection direction of the check valve with respect to the first and second oil chambers; A first speed change link connected; and a second speed change link having one end connected to the other end of the first speed change link and the other end connected to the second two-paired elemental node. During rotation, the angle formed between the second shift link and the second two-paired element node is Power unit is proposed, wherein a switch between acute and obtuse.

  According to a third aspect of the invention, in addition to the configuration of the second aspect, a driving force adjustment that adjusts a positive / negative driving force that is input from the first transmission link to the rotary shaft of the transmission ratio changing unit. A power plant is proposed, characterized in that means are provided.

  According to the invention described in claim 4, in addition to the configuration of any one of claims 1 to 3, at least one of the third pair, the fourth pair, and the fifth pair is slippery. A power plant characterized by being an even number is proposed.

  According to the invention described in claim 5, in addition to the configuration of any one of claims 1 to 4, a plurality of one-way clutches are provided for one of the first pairs. Proposed a power plant characterized in that the one first pair and the plurality of one-way clutches are connected by a plurality of the link mechanisms, and the phases of the plurality of second pairs are different from each other. Is done.

  According to the invention described in claim 6, in addition to the configuration of any one of claims 1 to 5, a plurality of one-way clutches are provided for one fifth pair, A plurality of the second pair evenly provided in the plurality of one-way clutches so as to have different phases are connected to the one fifth pair even by a plurality of the second two-pair even nodes. A power plant is proposed.

  According to a seventh aspect of the present invention, in addition to the structure of any one of the first to sixth aspects, the first pair is provided on the crankshaft. Is proposed.

  According to the invention described in claim 8, in addition to the structure of any one of claims 1 to 6, the first pair is provided on the cap portion of the connecting rod. A power plant is proposed.

  According to the invention described in claim 9, in addition to the configuration of any one of claims 2 to 8, a plurality of the first speed change links are connected to the single rotating shaft. In addition, there is proposed a power unit in which the transmission ratio changing means is disposed between the plurality of first transmission links with respect to the axial direction of the rotating shaft.

  The torsion spring 42 of the embodiment corresponds to the driving force adjusting means of the present invention, and the continuously variable transmission T of the embodiment corresponds to the transmission of the present invention.

  According to the configuration of the first aspect, the link mechanism of the transmission of the power unit includes the first pair that is rotated by the engine, the second pair that is provided on the one-way clutch, and the third pair that is fixed in position. , A fourth pair that swings around the third pair, a fifth pair that swings around the third pair, a first second pair even clause connecting the first pair and the fourth pair, A second pair of even-numbered clauses that connect the two-paired and even-numbered even-numbered couples, and a third pair of even-numbered clauses that connect the third, even-numbered, even-numbered, even-numbered even-numbered pairs; By changing the length of at least one of the two nodes or changing the fixed position of the third pair, the rotational motion of the crankshaft of the engine is converted into a reciprocating motion with a variable stroke. Convert to intermittent rotation of output shaft with one-way clutch It is possible to carry out the shift Te.

  Since the engine axis and the transmission axis can be arranged in parallel, the axial dimension of the power unit can be reduced, and the driving force of the engine crankshaft or connecting rod can be used as the transmission link mechanism. Since direct input is performed, the input shaft of the transmission becomes unnecessary, and the size of the power unit in the direction perpendicular to the axis can be reduced.

  Further, when the gear ratio changing means matches the position of the fifth pair with the position of the third pair, the speed ratio of the transmission can be made infinite, and a large speed ratio variable region can be secured. . In addition, since a torque converter and a multi-plate clutch of a normal automatic transmission are not required, it is possible to reduce the elements that lower the transmission efficiency and to enable highly efficient power transmission.

  In addition, the triple pair even clause is more likely to be heavy because there are more even pairs than the two pair even clause, but the inertial force during the operation of the link mechanism is reduced by fixing the position of the third pair even of the triple pair even clause. In addition, the followability when the input to the link mechanism fluctuates can be improved.

  According to the second aspect of the present invention, the transmission ratio changing means includes the rotating shaft, the first and second oil chambers whose volumes expand and contract in opposite directions in accordance with the rotation of the rotating shaft, and the first oil. A first oil passage connected to the chamber, a second oil passage connected to the second oil chamber, a check valve disposed between the first oil passage and the second oil passage, and between the first oil passage and the second oil passage. A switching valve arranged to switch the connecting direction of the check valve to the first and second oil chambers, a first speed change link having one end connected to the rotating shaft, and one end connected to the other end of the first speed change link. A second shift link having an end connected to the second two-pair even node, a state in which the switching valve allows only the movement of the hydraulic oil from the first oil chamber to the second oil chamber, and the second oil It is possible to switch between a state in which only movement of hydraulic oil from the chamber to the first oil chamber is allowed.

  While the crankshaft makes one revolution, the angle formed between the second shift link and the second two-paired element node is switched between an acute angle and an obtuse angle, so that the rotating shaft receives a load that alternately switches the rotation direction. Thus, the volumes of the first and second oil chambers are alternately expanded / reduced, so that the rotation shaft can be rotated in the forward rotation direction or the reverse rotation direction depending on the position of the switching valve. As a result, it is possible to control the transmission gear ratio by operating the transmission gear ratio changing means without requiring a special drive source.

  According to the third aspect of the present invention, since the driving force adjusting means adjusts the positive / negative driving force input from the first speed change link to the rotating shaft of the speed ratio changing means, the required operating speed of the speed ratio changing means is When the rotation axis varies depending on the forward / reverse rotation of the rotation shaft or the rotation angle of the rotation shaft, the driving force input to the gear ratio changing means can be adjusted accordingly.

  Further, according to the configuration of claim 4, since at least one of the third pair, the fourth pair, and the fifth pair is composed of a slip pair, the simple pair structure of the triple pair node itself is used as a guide. The length of can be changed.

  According to the configuration of claim 5, a plurality of one-way clutches are provided for one first pair, and one first pair and a plurality of one-way clutches are connected by a plurality of link mechanisms, Since the phases of the plurality of second pairs are made different from each other, the driving force taken out from one place or one connecting rod of the crankshaft can be transmitted to the output shaft at different phases via a plurality of link mechanisms. The output shaft can be obtained by engaging a plurality of one-way clutches with a phase difference while reducing the axial dimension of the power unit as compared with the case where the driving force is input from the first pair provided for each link mechanism. Torque fluctuations can be reduced.

  According to the structure of claim 6, a plurality of one-way clutches are provided for one fifth pair, and a plurality of second pairs provided in the plurality of one-way clutches so that phases are different from each other. Since the plurality of second second-pair even nodes are connected to one fifth pair, the torque fluctuation of the output shaft can be reduced by engaging the plurality of one-way clutches with a phase difference.

  Further, according to the configuration of the seventh aspect, since the first pair is provided on the crankshaft, the torque variation of the output shaft can be reduced by making the phases of the plurality of first pairs corresponding to the plurality of link mechanisms different from each other. Can be reduced.

  According to the structure of claim 8, since the first pair is provided on the cap portion of the connecting rod, the cap portion of the connecting rod is assembled in advance to the link mechanism that has been assembled, and the cap portion is attached to the crank pin. By assembling and connecting to the main body of the connecting rod, the assembly of the power unit is improved.

  According to the ninth aspect of the present invention, the plurality of first speed change links are connected to a single rotation shaft, and the gear ratio changing means is provided for the plurality of first speed change links with respect to the axial direction of the rotation shaft. Therefore, it is possible to further reduce the size of the transmission by reducing the number of parts compared to the case where each link mechanism is operated by the corresponding gear ratio changing means. The transmission characteristics can be made uniform by minimizing the influence of twisting of the path through which the load generated by the second oil chamber is transmitted to the first transmission links via the rotary shaft.

The skeleton figure of a power unit. (First embodiment) The figure which shows the hydraulic circuit of a gear ratio change means. (First embodiment) The figure explaining the structure and effect | action of a gear ratio change means. (First embodiment) The side view of a power unit. (First embodiment) 5 (A) -5 (A) sectional view taken on the line of FIG. 4 and 5 (B) -5 (B) sectional view taken on the line. (First embodiment) The perspective view of a gear ratio change means. (First embodiment) The skeleton figure of a power unit. (Second Embodiment) The skeleton figure of a power unit. (Third embodiment) The skeleton figure of a power unit. (Fourth embodiment) The skeleton figure of a power unit. (Fifth embodiment)

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, for example, a power device used as a power source for driving an automobile includes a reciprocating engine E such as a gasoline engine, a reciprocating continuously variable transmission T, and a continuously variable transmission. Gear ratio changing means V for changing the gear ratio of T is provided.

  The engine E includes a cylinder 11, a piston 12, a connecting rod 13, and a crankshaft 14. The connecting rod 13 includes a main body portion 13a and a cap portion 13b, and a crank pin 14b of the crankshaft 14 that rotates about the crank journal 14a is rotatably held between the main body portion 13a and the cap portion 13b of the connecting rod 13. The The first turning pair P1 provided on the cap portion 13b of the connecting rod 13 serves as an input portion for driving force from the engine E to the continuously variable transmission T.

  A one-way clutch 16 is provided on the output shaft 15 of the continuously variable transmission T, and the output shaft 15 rotates intermittently in one direction by reciprocatingly swinging the second counter-pair P2 provided on the one-way clutch 16. To do.

  The link mechanism 17 that connects the first turning pair P1 and the second turning pair P2 includes the third turning pair P3, the fourth turning pair P4, and the fifth in addition to the first turning pair P1 and the second turning pair P2. A sliding pair P5 is provided. The third turning pair P3 is fixed in position, and the fourth turning pair P4 and the fifth sliding pair P5 can swing around the third turning pair P3. The first turn pair P1 and the fourth turn pair P4 are connected by a first second pair even element node L1, and the second turn pair P2 and the fifth slip pair P5 are connected by a second second pair element node L2. The third turning pair P3 and the fourth turning pair P4 are connected by a triple pair even node L3, and the fifth sliding pair P5 can slide on the triple pair element L3.

  The transmission gear ratio changing means V changes the operation ratio of the link mechanism 17 and changes the transmission gear ratio of the continuously variable transmission T by changing the position of the fifth slip pair P5 on the three-pair element node L3.

  FIG. 1A shows an OD (overdrive) state in which the speed ratio is minimized, and the fifth slip pair P5 of the triple pair element L3 is moved by a predetermined distance from the third turn pair P3 by the speed ratio changing means V. It is set at a separated position.

  In this OD state, when the first turning pair P1 provided on the cap portion 13b of the connecting rod 13 moves along an elliptical locus along with the rotation of the crankshaft 14, the first second pairing element P1 is connected to the first turning pair P1. The triple pair even node L3 connected to the fourth turning pair P4 via the node L1 reciprocally swings around the third turning pair P3, and the second second pair even to the fifth sliding pair P5 on the triple turning even node L3. The output shaft 15 is intermittently rotated in one direction via the one-way clutch 16 by the second reciprocating pair P2 connected via the element L2 reciprocally swinging.

  At this time, the fifth slip pair P5 is adjusted to the farthest position from the third turn pair P3 by the gear ratio changing means V, so that the stroke of the reciprocating motion of the second second pair node element L2 is maximized, and the one-way clutch 16, the rotational speed of the output shaft 15 driven through 16 is maximized, and the gear ratio becomes OD.

  FIG. 1B shows a UD (underdrive) state in which the gear ratio is maximum (infinite), and the fifth slip pair P5 of the three-pair even node L3 is changed to the third counter-pair P3 by the gear ratio changing means V. It is set to a position that overlaps with.

  In this UD state, even if the three-pair even node L3 reciprocally swings around the third turning pair P3 via the first two-pairing element node L1 by the connecting rod 13, the fifth slipping pair P5 remains the third turning pair. Since it overlaps P3, the stroke of the reciprocating motion of the second two-paired element node L2 becomes zero, the output shaft 15 does not rotate, and the output shaft 15 remains stopped even when the crankshaft 14 rotates. Gear ratio becomes infinite.

  When the engine E is a single cylinder, the output shaft 15 rotates intermittently. However, when the multi-cylinder engine E including a plurality of pistons 12 having different reciprocating phases is used, the output shaft 15 corresponds to the plurality of pistons 12. The output shaft 15 can be continuously rotated by intermittently inputting driving force from the plurality of one-way clutches 16 to the output shaft 15 at different phases.

  2 and 3 show the structure of the gear ratio changing means V. FIG. The shape of the link mechanism 17 in FIG. 3 is different from that in FIG. 1, but the principle and operation are the same.

  As is apparent from FIG. 2, two vanes 22 and 22 are fixed to a rotating shaft 21 that penetrates the housing 20, and each vane 22 is formed with a first oil chamber 23 and a second oil formed inside the housing 20. It arrange | positions so that between the chambers 24 may be partitioned off. When the rotating shaft 21 rotates clockwise in the figure, the volume of the first oil chamber 23 increases and the volume of the second oil chamber 24 decreases, and when the rotating shaft 21 rotates counterclockwise in the figure, the first oil chamber 23. And the volume of the second oil chamber 24 increases.

  A first oil passage 25 connected to the two first oil chambers 23, 23 and a second oil passage 26 connected to the two second oil chambers 24, 24 are connected via a check valve 27. The A switching valve 28 is disposed in the first and second oil passages 25, 26 between the first and second oil chambers 23, 23; 24, 24 and the check valve 27. When the switching valve 28 is at the center position 28C, the first oil chambers 23, 23 and the second oil chambers 24, 24 are closed. When the switching valve 28 is in the left position 28L, the first and second oil chambers 23, 23; 24, 24 communicate with each other via the check valve 27, and the first oil chambers 23, 23 are communicated from the second oil chambers 24, 24. Only the distribution of hydraulic oil to When the switching valve 28 is in the right position 28R, the first and second oil chambers 23, 23; 24, 24 communicate with each other via the check valve 27, and the first oil chambers 23, 23 to the second oil chambers 24, 24 are communicated. Only the distribution of hydraulic oil to

  A third oil passage 29 and an oil tank connected to the first and second oil passages 25 and 26 in order to replenish hydraulic oil that has leaked from the first and second oil chambers 23 and 23; 30, an oil pump 31 and two check valves 32, 32 are arranged.

  As is apparent from FIG. 3, one end of the second speed change link L5 is connected to the other end of the first speed change link L4 whose one end is fixed to the rotating shaft 21 (see FIG. 2) via a sixth turning pair P6. The other end of the second shift link L5 is connected to the fifth slip pair P5. Therefore, when the rotary shaft 21 rotates, the fifth slip pair P5 slides on the triple pair element node L3 via the first shift link L4 and the second shift link L5, and the transmission ratio of the continuously variable transmission T changes. To do.

  FIG. 3A shows a state in which the piston 12 is in the vicinity of the top dead center. At this time, the angle θ formed by the second transmission link L5 and the second two-paired element node L2 becomes an obtuse angle. For example, when the one-way clutch 16 is set to transmit power when receiving a compressive force from the second two-paired elemental node L2, the second two-paired elemental node L2 receives only a compressive load and receives a tensile load. Therefore, the fifth slip pair P5 receives only the leftward compressive load from the second second pair even node L2, but at this time, the angle θ formed between the second shift link L5 and the second second pair node L2 is an obtuse angle. Therefore, the rotating shaft 21 receives only the moment M in the clockwise direction in the figure.

  FIG. 3B shows a state in which the piston 12 is in the vicinity of the bottom dead center. At this time, the angle θ formed by the second transmission link L5 and the second two-paired element node L2 is an acute angle. Due to the power transmission characteristic of the one-way clutch 16 described above, the second two-pair element node L2 receives only a compressive load and not a tensile load. Therefore, the fifth slip pair P5 is directed leftward in the figure from the second two-pair element node L2. Only the compressive load is received. At this time, since the angle θ formed between the second transmission link L5 and the second two-paired elemental node L2 is an acute angle, the rotating shaft 21 receives only the moment M in the counterclockwise direction in the figure. Become.

  Thus, the link mechanism 17 and the gear ratio changing means V are configured such that the rotating shaft 21 alternately receives clockwise and counterclockwise moments while the crankshaft 14 rotates once.

  In FIG. 2, when the switching valve 28 is at the center position 28C, the communication between the first and second oil chambers 23, 23; 24, 24 is blocked, and the rotary shaft 21 is restrained to be non-rotatable. The transmission ratio of the transmission T is fixed.

  When the switching valve 28 is in the left position 28L, the first and second oil chambers 23, 23; 24, 24 communicate with each other via the check valve 27, and the first oil chambers 23, 23 are communicated from the second oil chambers 24, 24. Therefore, only the clockwise rotation of the rotating shaft 21 is allowed, and the counterclockwise rotation is prevented. The rotating shaft 21 alternately receives clockwise and counterclockwise moments as the crankshaft 14 rotates. However, the rotating shaft 21 rotates only when it receives a clockwise moment, and the rotating shaft 21 is intermittently repeated. Rotate in the direction.

  When the switching valve 28 is in the right position 28R, the first and second oil chambers 23, 23; 24, 24 communicate with each other via the check valve 27, and the first oil chambers 23, 23 to the second oil chambers 24, 24 are communicated. Therefore, the rotation shaft 21 is only allowed to rotate counterclockwise and is prevented from rotating clockwise. The rotating shaft 21 alternately receives clockwise and counterclockwise moments as the crankshaft 14 rotates. However, the rotating shaft 21 rotates only when the counterclockwise moment is received, and the rotating shaft 21 is intermittently repeated. Rotates counterclockwise.

  As described above, since one of the forward and reverse moments transmitted from the link mechanism 17 via the second speed change link L5 and the first speed change link L4 is extracted and the rotating shaft 21 is rotated, it is like an electric motor. This eliminates the need for a special actuator and simplifies the structure.

  As described above, according to the present embodiment, the engine E and the continuously variable transmission T are connected in parallel in the direction perpendicular to the axis without connecting the engine E and the continuously variable transmission T in series in the axial direction. Since it can connect, the axial direction dimension of a power plant can be reduced in size. Further, the continuously variable transmission T does not have an input shaft, and the crankshaft 14 of the engine E functions as the input shaft of the continuously variable transmission T. Therefore, the size of the power unit in the direction perpendicular to the axis can be reduced. It becomes easy to mount on the vehicle.

  In addition, the triple-even node L3 includes three pairs P3, P4, and P5, so that the triple-even node L3 is likely to increase in size, and the inertial mass of the triple-even node L3 may increase, and the follow-up performance to engine speed fluctuations may decrease. However, the increase in the inertial mass can be minimized by setting the position of the third pair P3 of the triple pair even node L3 to be fixed.

  When the continuously variable transmission T is connected to the multi-cylinder engine E and a plurality of link mechanisms 17 are juxtaposed, the torque fluctuation of the output shaft 15 can be achieved by changing the phase of the first turning pair P1 of each link mechanism 17. However, since the connecting rods 13 reciprocate at different phases, the torque fluctuation of the output shaft 15 can be reduced by changing the phase of the first turning pair P1 of each link mechanism 17.

  4 to 6 show a specific structure of the power plant described in FIGS. 2 and 3. 4 to 6 correspond to the reference numerals in FIGS. 2 and 3.

  The first turning pair P1 of the link mechanism 17 is provided at the lower end of the cap portion 13b that is coupled to the main body portion 13a of the connecting rod 13 and rotatably holds the crank pin 14b of the crankshaft 14. Therefore, the first turning pair P1 of the link mechanism 17 assembled in advance as a subassembly is assembled to the cap portion 13b of the connecting rod 13, and the cap portion 13b is coupled to the main body portion 13a of the connecting rod 13, thereby Assembling of E and continuously variable transmission T can be easily completed, and assembling performance is improved.

  The fifth sliding pair P5 is a sleeve that is slidably fitted to the outer periphery of the shaft-shaped three-pair even element L3 pivotally supported by the mission case 40 (see FIG. 5B) via the third turning pair P3. 41, and the sleeve 41 is provided with a slit 41a for avoiding interference with the first two-paired elemental node L1 pivotally supported by the fourth turning pair P4 at the upper end of the three-paired elemental node L3 in the axial direction. Is open. A pin 41b is implanted on the side surface of the sleeve 41, and two second second-paired elements L2 and L2 and a second speed change link L5 are pivotally supported on the pin 41b. Since the fifth sliding pair P5 includes the sleeve 41 that slides with the triple pair element L3 as a guide, the length of the triple pair element L3 can be changed with a simple structure.

  FIG. 4 shows the OD state. At this time, the position of the sixth turning pair P6 that pivotally supports the first transmission link L4 and the second transmission link L5 is such that the lower end of the triple pairing element L3 is pivotally supported by the housing. It is set so as to coincide with the position of the 3-turn pair P3. As a result, when the triple pair element L3 reciprocally swings around the third turning pair P3 as the crankshaft 14 rotates, the fifth slipping pair P5 is not pushed or pulled by the second shift link L5. The distance between the fourth turning pair P4 and the fifth slipping pair P5 is kept constant.

  The link mechanism 17 is connected to the two one-way clutches 16 and 16, and the two second turning pairs P2 and P2 of the one-way clutches 16 and 16 are arranged so as to have different phases. One fifth sliding pair P5 and two second turning pairs P2, P2 are connected by two second second pair even nodes L2, L2. As a result, the output force is transmitted to the output shaft 15 when at least one of the two one-way clutches 16 and 16 is engaged, and the torque fluctuation of the output shaft 15 can be reduced.

  It should be noted that a plurality of link mechanisms 17 for reciprocatingly swinging the second turning pair P2 with mutually different phases and a plurality of one-way clutches 16 are juxtaposed in the axial direction, and these are connected to a single connecting rod 13. When connected to a single first turn pair P1, the number of first turn pairs P1 is reduced as compared with the case where each link mechanism 17 is connected to the first turn pair P1 of the corresponding connecting rod 13. The torque fluctuation of the output shaft 15 can be reduced while reducing the axial dimension of the device.

  The engine E according to the present embodiment is an in-line four cylinder, and the power unit includes four link mechanisms 17 and four one-way clutches 16 corresponding to the four connecting rods 13. The single gear ratio changing means V is shared by the four link mechanisms 17. As is apparent from FIG. 6, the rotation shaft 21 of the gear ratio changing means V extends from the housing 20 to both sides in the axial direction, and two first transmission links L4, L4 are connected to one and the other respectively. In this way, the four first speed change links L4... Are arranged separately on both sides of the rotary shaft 21 with the housing 20 interposed therebetween, that is, the four link mechanisms 17 in which the housings 20 of the speed change ratio changing means V are juxtaposed. Since it is arranged at the center of the ..., the influence of the twist of the rotary shaft 21 can be minimized and the operating characteristics of the link mechanisms 17 can be made uniform.

  A torsion spring 42 (see FIG. 6) is disposed between the rotation shaft 21 of the gear ratio changing means V and the housing 20, and the rotation shaft 21 is urged in one direction by its elastic force. As a result, the positive / negative driving force input from the first speed change link L4 to the rotary shaft 21 of the gear ratio changing means V is adjusted by the torsion spring 42, and the required operating speed of the speed ratio changing means V is adjusted to the rotary shaft 21. When the forward / reverse rotation and the rotation angle of the rotary shaft 21 vary, the driving force input to the gear ratio changing means V can be adjusted accordingly.

  Further, when the engine E is stopped in a state where the speed ratio of the continuously variable transmission T is infinite (a state where the driving force is not transmitted) and then the engine E is started, the rotation shaft of the speed ratio changing means V is transmitted from the link mechanism 17. There is a problem that the gear ratio is fixed to an infinite state because no driving force is input to 21. However, if the rotational shaft 21 is urged by the torsion spring 42 in the direction of decreasing the transmission ratio, the transmission can be started from the state where the transmission ratio is infinite.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the first turning pair P1 of the link mechanism 17 is provided on the cap portion 13b of the connecting rod 13. However, in the second embodiment, the first turning pair P1 of the link mechanism 17 is A crank web 14c of the crankshaft 14 is provided. The structure of the other link mechanism 17 is the same as that of the first embodiment described with reference to FIG. 3 except that two second paired even nodes L2 and L2 and two one-way clutches 16 and 16 are provided. It is.

  The first turning pair P1 provided on the cap portion 13b of the connecting rod 13 rotates on a horizontally long elliptical locus, whereas the first turning pair P1 provided on the crankshaft 14 moves on a circular locus. It rotates but there is no difference in its function. The position of the first turning pair P1 on the crankshaft 14 can be any position other than the crank journal 14a, but it is suitable to be provided on the crank web 14c that connects the crank journal 14a and the crank pin 14b. .

  When the continuously variable transmission T is connected to the multi-cylinder engine E and a plurality of link mechanisms 17 are juxtaposed, the torque fluctuation of the output shaft 15 can be achieved by changing the phase of the first turning pair P1 of each link mechanism 17. However, since the crank web 14c of the crankshaft 14 is formed to have a different phase for each piston 12, the phase of the first turning pair P1 of each link mechanism 17 is made different so that the output shaft 15 torque fluctuations can be reduced.

  Next, a third embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the third turn pair P3, the fourth turn pair P4, and the fifth slip pair P5 of the triple pair even node L3 are arranged in a straight line, but in the third embodiment, they are triangular. The fifth slip pair P5 in the first embodiment is replaced with the fifth counter pair P5 in the third embodiment. The gear ratio changing means V can change the length of the node a connecting the third turning pair P3 and the fifth turning pair P5 from zero to a predetermined value.

  As shown in FIG. 8A, when the length of the node a is maximized, the transmission ratio of the continuously variable transmission T becomes OD, and as shown in FIG. When becomes zero, the gear ratio of the continuously variable transmission T becomes UD (infinite), and the output shaft 15 stops rotating. In order to make the length of the node a zero, that is, to overlap the third turn pair P3 and the fifth turn pair P5, the length of the node b connecting the fourth turn pair P4 and the third turn pair P3, The lengths of the nodes c connecting the fourth turning pair P4 and the fifth turning pair P5 must be the same.

  Next, a fourth embodiment of the present invention will be described with reference to FIG.

  In the first embodiment, the fifth sliding pair P5 is arranged between the third round pair P3 and the fourth round pair P4 of the triple pair even node L3, but in the fourth embodiment, the triple pair even node. The third turn pair P3 is arranged between the fourth turn pair P4 and the fifth turn pair P5 of L3, and the fifth slip pair P5 of the first embodiment is the first turn pair P5 in the fourth embodiment. It has been replaced with a 5-turn pair P5. Then, the gear ratio changing means V determines the length of the node connecting the fifth counter-couple P5 and the third counter-couple P3 while keeping the length of the node connecting the fifth counter-couple P5 and the fourth counter-couple P4 constant. It can be changed between zero and a predetermined value.

  As shown in FIG. 9A, when the length of the node connecting the fifth turning pair P5 and the third turning pair P3 is maximized, the transmission ratio of the continuously variable transmission T becomes OD, and FIG. As shown in B), when the length of the node connecting the fifth turning pair P5 and the third turning pair P3 becomes zero, that is, when the fifth turning pair P5 and the third turning pair P3 overlap each other, The transmission ratio of the transmission T becomes UD (infinite), and the output shaft 15 stops rotating.

  Next, a fifth embodiment of the present invention will be described with reference to FIG.

  In the fifth embodiment, the fourth turning pair P4 of the first embodiment is replaced with the fourth sliding pair P4, and the node connecting the fourth sliding pair P4 and the fifth sliding pair P5 of the triple pair even node L3. And the second 2nd even-numbered segment L2 are formed of one member forming a straight line. The gear ratio changing means V can change the length of a node connecting the fourth slip pair P4 and the fifth slip pair P5 of the triple pair even node L3.

  As shown in FIG. 10A, when the length of the node connecting the fourth slip pair P4 and the fifth slip pair P5 is minimized, that is, the length of the second second pair even node L2 is maximized. When the transmission ratio of the continuously variable transmission T becomes OD, as shown in FIG. 10B, when the length of the node connecting the fourth slip pair P4 and the fifth slip pair P5 becomes maximum, that is, When the length of the second 2nd even number node L2 is minimized and the fifth slipping pair P5 is overlapped with the second turning pair P2, the transmission ratio of the continuously variable transmission T becomes UD (infinite) and the output shaft 15 stops the rotation.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the gear ratio changing means V may be one that uses an actuator such as an electric motor as a drive source, or may directly drive the vane by hydraulic pressure, and the gear ratio changing means V of the embodiment. These may be added to.

  Further, the gear ratio changing means V may be any means that changes the length of at least one of the three nodes of the three-pair even node L3 or changes the fixed position of the third pair P3.

12 Piston 13 Connecting rod 13b Cap portion 14 Crankshaft 15 Output shaft 16 One-way clutch 17 Link mechanism 21 Rotating shaft 23 First oil chamber 24 Second oil chamber 25 First oil passage 26 Second oil passage 27 Check valve 28 Switching valve 42 Torsion spring (drive force adjustment means)
E Engine L1 1st 2nd even number node L2 2nd 2nd number even element L3 3nd number even node L4 1st speed change link L5 2nd speed change link P1 1st number even number P2 2nd number even number P3 3rd number even number P4 4th number even number P5 5th Even number T continuously variable transmission (transmission)
V Gear ratio changing means

Claims (9)

An engine (E) that converts the reciprocating motion of the piston (12) into the rotational motion of the crankshaft (14) via the connecting rod (13), and the rotational motion of the crankshaft (14) is linked to the link mechanism (17) and the one-way. A power plant comprising: a transmission (T) that converts to intermittent rotation motion of the output shaft (15) via a clutch (16); and a gear ratio changing means (V) that changes the gear ratio of the transmission (T). Because
The link mechanism (17)
A first pair (P1) that is rotated by the engine (E);
A second pair (P2) provided on the one-way clutch (16);
A third pair (P3) of fixed position;
A fourth pair (P4) swinging about the third pair (P3);
A fifth pair (P5) swinging about the third pair (P3);
A first two-pair even clause (L1) connecting the first pair (P1) and the fourth pair (P4);
A second second pair even clause (L2) connecting the second pair (P2) and the fifth pair (P5);
A third pair even clause (L3) connecting the third pair (P3), the fourth pair (P4) and the fifth pair (P5);
The speed change ratio changing means (V) changes the length of at least one of the three nodes of the triple pair node (L3) or changes the fixed position of the third pair (P3). The power device is characterized by changing the speed ratio of the transmission (T) by increasing / decreasing the stroke of the reciprocating swing of the second pair (P2). The gear ratio changing means (V)
A rotating shaft (21);
First and second oil chambers (23, 24) whose volumes expand and contract in opposite directions according to the rotation of the rotating shaft (21);
A first oil passage (25) connected to the first oil chamber (23);
A second oil passage (26) connected to the second oil chamber (24);
A check valve (27) disposed between the first oil passage (25) and the second oil passage (26);
A switching valve (between the first oil passage (25) and the second oil passage (26) for switching the connecting direction of the check valve (27) to the first and second oil chambers (23, 24). 28)
A first speed change link (L4) having one end connected to the rotating shaft (21);
A second shift link (L5) having one end connected to the other end of the first shift link (L4) and the other end connected to the second two-paired element node (L2);
The angle formed between the second transmission link (L5) and the second two-pair elemental node (L2) is switched between an acute angle and an obtuse angle during one rotation of the crankshaft (14). The power plant according to claim 1, wherein the power plant is characterized.   A driving force adjusting means (42) for adjusting a positive / negative driving force input to the rotating shaft (21) of the speed ratio changing means (V) from the first speed change link (L4) is provided. The power plant according to claim 2.   4. The method according to claim 1, wherein at least one of the third pair (P3), the fourth pair (P4), and the fifth pair (P5) is a slip pair. The power plant described.   A plurality of one-way clutches (16) are provided for one first pair (P1), and a plurality of one-pair clutches (P1) and a plurality of one-way clutches (16) are connected to a plurality of one-way clutches (16). The power according to any one of claims 1 to 4, wherein the power is connected by the link mechanism (17), and the phases of the plurality of second pairs (P2) are different from each other. apparatus.   A plurality of the one-way clutches (16) are provided for one fifth pair (P5), and a plurality of the first-way clutches (16) provided in such a manner that the phases are different from each other. The two-paired even number (P2) is connected to the one fifth paired-even number (P5) by a plurality of the second paired-even elements (L2). The power plant according to item 1.   The power plant according to any one of claims 1 to 6, wherein the first pair (P1) is provided on the crankshaft (14).   The power unit according to any one of claims 1 to 6, wherein the first pair (P1) is provided on a cap portion (13b) of the connecting rod (13).   A plurality of the first speed change links (L4) are connected to a single rotating shaft (21), and the speed ratio changing means (V) is arranged in the axial direction of the rotating shaft (21). The power plant according to any one of claims 2 to 8, wherein the power plant is arranged between the first shift links (L4).

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