JP2008039014A - Fluid pressure mechanical power transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission which is excellent in power transmission efficiency, and reduced in size/weight. <P>SOLUTION: The fluid pressure mechanical power transmission comprises an input member 2 power-transmitted from a power source 1, a combined planetary gear mechanism 3 disposed coaxially with the input member 2, and composed of two input elements and one output element, and one repulsion element by mutually connecting a carrier C1 and a ring gear R1 of a first planetary gear mechanism, and a carrier C2 and a ring gear R2 of a second planetary gear mechanism, a first connecting mechanism 4 to selectively connect one input element and the input member 2, a second connecting mechanism 5 to selectively connect the other input element and the input member 2, a third connecting mechanism 7 so as to be able to selectively transmit torque between the output element and the output shaft 8, a first pump motor 6 connected to an output shaft 8, and a second pump motor 9 connected to the repulsion element and communicating with a first pump motor 6 so as to be able to transfer a pressure fluid with the first pump motor 6. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a power transmission device configured to change a transmission path for transmitting power output from a power source to an output member and a state of the transmission according to a pressure of fluid such as hydraulic pressure.

  2. Description of the Related Art A vehicle transmission is known as an example of a power transmission device configured to output power transmitted from a power source by changing a rotation speed and torque. As with other general industrial power transmission devices, there are demands for vehicle transmissions such as small size and good power transmission efficiency. There are demands for a large number of gear ratios and for the gear ratios to be continuously changed.

  A twin-clutch stepped transmission is known as a transmission that meets such demands in a transmission, and an example thereof is described in Patent Document 1. The transmission described in Patent Document 1 includes a first input shaft connected to the engine via a first clutch, a second input shaft connected to the engine via a second clutch, an output shaft, A counter shaft connected to the first input shaft via a gear pair, a plurality of gear pairs provided between the first input shaft and the counter shaft and selectively connected by a meshing clutch mechanism; And a plurality of gear pairs which are provided between the two input shafts and the output shaft and are selectively connected by the meshing clutch mechanism. The transmission includes a gear stage that transmits torque from any one of the input shafts to the output shaft through a predetermined gear pair, and any output shaft from the input shaft to the output shaft through the predetermined gear pair and the sub shaft. It is configured to set a gear stage for transmitting torque, and as a result, it is configured to set seven or more gear stages including the reverse gear.

Japanese Patent Application Laid-Open No. 2003-120764

  In the transmission described in Patent Document 1 described above, since the number of shift speeds that can be set is large, the engine can be operated in a state with good fuel efficiency, and the auxiliary shaft is effectively used. The transmission is reduced in size and weight as a whole, and as a result, the fuel consumption of the vehicle can be improved. However, when setting a predetermined gear ratio, one of the input clutches is maintained in the engaged state. Since the clutch functions as a so-called starting clutch, a friction clutch is used so as to allow a difference in rotational speed. Therefore, power such as hydraulic pressure is consumed to maintain the engaged state, There is a possibility that the power loss accompanying this will occur and the fuel efficiency of the vehicle will deteriorate. Also, various configurations of input clutches and gear mechanisms in vehicle transmissions are conventionally known. However, in any conventional configuration, in terms of improvement in fuel consumption, in-vehicle performance, or quietness, etc. There was still plenty of room for improvement.

  The present invention has been made paying attention to the above technical problem, is excellent in power transmission efficiency, is easy to be miniaturized, and is mounted in the front-rear direction of the vehicle when applied to a vehicle. An object of the present invention is to provide a power transmission device that is excellent in on-vehicle performance.

  In order to achieve the above object, the present invention provides two sets of power transmission systems that receive power from a power source and set a predetermined gear ratio by receiving a reaction force from a variable displacement fluid pressure pump motor. It is characterized in that it is mainly composed of a compound planetary gear mechanism combining three planetary gear mechanisms and three coupling mechanisms. Specifically, the invention according to claim 1 inputs the power transmitted from the power source to the planetary gear mechanism, changes the reaction force against the planetary gear mechanism according to the fluid pressure, and changes the gear ratio, In the hydrodynamic mechanical power transmission device that outputs power corresponding to the gear ratio to the output member, the input member to which power is transmitted from the power source, and the input member are disposed on the same axis, and the first A carrier and a ring gear of two sets of planetary gear mechanisms including a planetary gear mechanism and a second planetary gear mechanism are connected to each other, and the sun gear of the first planetary gear mechanism serves as one input element, and the first planetary gear mechanism The ring gear of the second planetary gear mechanism and the carrier of the second planetary gear mechanism are the other input elements, the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism are the output elements, and the first A compound planetary gear mechanism configured such that a sun gear of the planetary gear mechanism is a reaction force element, a first connection mechanism that selectively connects the one input element and the input member, and the other input element; A second coupling mechanism that selectively couples the input member; a third coupling mechanism that selectively enables torque transmission between the output element and the output member; and a variable coupled to the output member. A variable first fluid pressure pump motor connected to the first fluid pressure pump motor, and connected to the reaction force element, and communicated with the first fluid pressure pump motor so as to exchange pressure fluid with the first fluid pressure pump motor. A fluid pressure mechanical power transmission device comprising a displacement type second fluid pressure pump motor.

  The invention according to claim 2 is the invention according to claim 1, wherein the first fluid pressure pump motor is a double swing type fluid pressure pump motor capable of changing the extrusion volume in both positive and negative directions across zero. The fluid pressure machine is characterized in that the second fluid pressure pump motor is constituted by a single swing type fluid pressure pump motor capable of changing the extrusion volume from zero to either positive or negative. Type power transmission device.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, the first fluid pressure pump motor and the output member are opposite to the input member with the composite planetary gear mechanism interposed therebetween and the input. The hydrodynamic mechanical power transmission is disposed on the same axis as the member and the compound planetary gear mechanism, and the second fluid pressure pump motor is disposed in parallel with the first fluid pressure pump motor. Device.

  According to a fourth aspect of the invention, there is provided a transmission mechanism for transmitting power from the reaction force element to the second fluid pressure pump motor in the invention of the third aspect. A fluid pressure mechanical power transmission device comprising a speed increasing mechanism for transmitting power by increasing speed toward a two-fluid pressure pump motor.

  According to a fifth aspect of the present invention, in the third or fourth aspect of the invention, the first fluid pressure pump motor is disposed on the outer peripheral side of the second fluid pressure pump motor. It is a power transmission device.

  According to a sixth aspect of the invention, in the third or fourth aspect of the invention, the first fluid pressure pump motor is disposed so as to be shifted in the axial direction with respect to the second fluid pressure pump motor. This is a fluid pressure mechanical power transmission device.

  The invention of claim 7 can be set to maximize the extrusion volume of at least one of the fluid pressure pump motors and set the other extrusion volume to zero or maximum in the invention of any one of claims 1 to 6. The hydrodynamic mechanical power transmission device is characterized in that the fixed gear ratio is three steps on the forward side and one step on the reverse side.

  Therefore, according to the first aspect of the present invention, power is input from the power source to any one of the input elements of the compound planetary gear mechanism. When the second fluid pressure pump motor functions as a pump in this state, a reaction force corresponding to the extrusion volume acts on the reaction force element. As a result, torque corresponding to the input torque and reaction force appears in the output element. In addition, the pressure fluid generated by the second fluid pressure pump motor is supplied to the first fluid pressure pump motor, which functions as a motor, and the output power is applied to the output member. That is, mechanical power transmission via the complex planetary gear mechanism and power transmission via the fluid occur. Therefore, in a state where power is transmitted via the fluid, the gear ratio is continuously changed, and so-called continuously variable transmission is possible. In addition, by switching the input element that transmits power from the input member, there are three fixed gear ratios that are set to maximize the extrusion volume of at least one of the fluid pressure pump motors, the maximum fixed gear ratio and the minimum fixed gear ratio. The gear ratio can be continuously changed between the gear ratio.

  In addition, the predetermined fixed speed ratio is such that either one of the fluid pressure pump motors is fixed or idling and does not transmit power, so that power is not particularly consumed to set the fixed speed ratio, Or power consumption can be suppressed. In particular, if each coupling mechanism is of a meshing type, power is not consumed to maintain the meshed state or engaged state, so that power consumption for setting the fixed gear ratio can be almost eliminated. As a result, power transmission efficiency can be improved. According to the first aspect of the present invention, since the power transmission path can be constituted mainly by a set of compound planetary gear mechanisms, which are a combination of two sets of planetary gear mechanisms, and three coupling mechanisms, the number of parts as a whole is reduced. Thus, the device can be easily miniaturized.

  Furthermore, the power source or the input member can be arranged so as to output power from the output member in the direction of the extension axis of the input member. As a result, when used in a vehicle, the power source such as an engine is directed in the longitudinal direction of the vehicle. A configuration suitable for a mounted FR (front engine / rear drive) vehicle can be obtained.

  The compound planetary gear mechanism connects the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism, and connects the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism. Since it is constituted by two sets of planetary gear mechanisms of CR-CR "coupling, the respective planetary gear mechanisms can be arranged close to each other. Therefore, the configuration of the entire apparatus can be reduced in size, which is particularly advantageous for shortening the length in the axial direction.

  According to the invention of claim 2, if the extrusion volume of the first fluid pressure pump motor is a negative volume while the extrusion volume of the second fluid pressure pump motor is a positive volume, these fluids Even when the pressure pump motor rotates in the same direction, the first fluid pressure pump motor can function as a pump, and the generated pressure fluid can be supplied to the second fluid pressure pump motor to function as a motor. With such a function, the rotation speed of each input element can be controlled to be the same. Therefore, when switching the engagement / release state between the first coupling mechanism and the second coupling mechanism, a so-called synchronization state is formed. Thus, the shock associated with switching can be prevented or suppressed. In other words, these coupling mechanisms can be meshing mechanisms.

  According to the invention of claim 3, since the power source, the compound planetary gear mechanism, and the first fluid pressure pump motor are arranged on the same axis, the configuration is more suitable for the above-described FR vehicle. It can be made good.

  According to the invention of claim 4, when the second fluid pressure pump motor functions as a pump, the rotation speed becomes a relatively high rotation speed, so that the extrusion capacity can be increased. It becomes possible to use a relatively small pump motor in order to obtain the required extrusion capacity, and accordingly, the apparatus can be miniaturized as a whole.

  According to the invention of claim 5, since the outer diameter of the fluid pressure pump motor is smaller than the outer diameter of the compound planetary gear mechanism, the first and second fluid pressure pump motors are arranged in the radial direction, and the input member By arranging them on the opposite side in the axial direction, the outer diameter on the output side can be reduced, and in particular, a configuration with good in-vehicle performance for FR vehicles can be achieved. Moreover, the structure of the fluid flow path between these fluid pressure pump motors can be simplified.

  Further, according to the invention of claim 6, since each fluid pressure pump motor is displaced in the axial direction, any one of the fluid pressure pump motors is disposed using a vacant space, and the entire apparatus is arranged. The outer diameter of the can be reduced.

  According to the invention of claim 7, in addition to the effects similar to the effects of the above-described inventions, since the fixed gear ratio is three forward speeds and one reverse speed, the gear ratio width is widened and put into practical use. It can be configured as a suitable transmission.

  Next, the present invention will be described based on specific examples. The example shown in FIG. 1 is an example configured as a transmission for a vehicle, and includes at least one of a planetary gear mechanism configured by combining two planetary gear mechanisms and two fluid pressure pump motors. This is an example in which three forward speeds and one reverse speed are set as a so-called fixed speed ratio that can be set to maximize the extrusion volume of the fluid pressure pump motor. Here, the compound planetary gear mechanism may be configured by connecting the rotating elements in the two sets of planetary gear mechanisms, or may be configured to share these rotating elements. The planetary gear mechanism to be combined may be either a single pinion type planetary gear mechanism or a double pinion type planetary gear mechanism. Further, the compound planetary gear mechanism is a mechanism including two input elements, and one reaction force element and an output element, respectively.

  And three connection mechanisms for selectively connecting the input member to the input element and selectively connecting the output member to the output element are provided. In short, these coupling mechanisms may be any mechanism that can selectively couple two members so that torque can be transmitted, and can use a meshing clutch, a synchronous coupling mechanism (synchronizer), a friction clutch (multi-plate clutch), or the like. . Among them, a meshing clutch or a synchronous coupling mechanism is advantageous in improving power transmission efficiency as a whole because it does not require power for maintaining the coupled state (engaged state).

  The fluid pressure pump motor according to the present invention is a fluid device that functions as a pump by receiving power from the outside, and also functions as a motor by being supplied with fluid pressure from the outside, and in particular, a variable that can change the extrusion volume. It is a capacitive type. At least one of the fluid pressure pump motors is of a double swing type that can change the extrusion volume in both positive and negative directions. These fluid pressure pump motors communicate with each other so as to exchange pressure fluid with each other. As this type of fluid pressure pump motor, a hydraulic pump motor such as an oblique shaft pump, a swash plate pump, or a radial piston pump can be employed.

  The configuration shown in FIG. 1 will be described more specifically. A compound planetary gear mechanism 3 is disposed on the same axis as the input member 2 to which power is transmitted from the power source 1. The power source 1 may be a general power source used in a vehicle such as an internal combustion engine, an electric motor, or a combination thereof, and an appropriate transmission such as a damper, a clutch, or a torque converter is provided on the output side thereof. Means can be interposed.

  The compound planetary gear mechanism 3 shown in FIG. 1 is composed of two sets of planetary gear mechanisms, a first planetary gear mechanism 3A and a second planetary gear mechanism 3B. The first and second planetary gear mechanisms 3A and 3B are both configured by a single pinion type planetary gear mechanism in this specific example. That is, the first planetary gear mechanism 3A is provided with a sun gear S1 that is an external gear, and a ring gear R1 that is an internal gear is disposed concentrically with the sun gear S1. A plurality of pinion gears P1 are engaged with each of the sun gear S1 and the ring gear R1, and the pinion gears P1 are held by the carrier C1 so as to rotate and revolve freely.

  On the other hand, the second planetary gear mechanism 3B is provided with a sun gear S2 that is an external gear, and a ring gear R2 that is an internal gear is arranged concentrically with the sun gear S2. A plurality of pinion gears P2 are engaged with each of the sun gear S2 and the ring gear R2, and these pinion gears P2 are held by a carrier C2 so as to rotate and revolve freely.

  Then, the ring gear R1 of the first planetary gear mechanism 3A and the carrier C2 of the second planetary gear mechanism 3B are connected, and the carrier C1 of the first planetary gear mechanism 3A and the ring gear R2 of the second planetary gear mechanism 3B are connected. Thus, the compound planetary gear mechanism 3 is configured. That is, the compound planetary gear mechanism 3 includes two sets of so-called “CR-CR” coupled planets in which the carriers C1 and C2 of the first and second planetary gear mechanisms 3A and 3B and the ring gears R2 and R1 are connected to each other. It is constituted by a gear mechanism.

  The sun gear S1 and the ring gear R1 (that is, the carrier C2) are input elements in the compound planetary gear mechanism 3. Among these, the first connection for selectively connecting the sun gear S1 and the input member 2 is provided. A mechanism 4 is provided, and a second connecting mechanism 5 is provided between the ring gear R1 and the input member 2 for selectively connecting them. In short, these coupling mechanisms 4 and 5 are mechanisms that can be switched between a state in which torque can be transmitted and a state in which torque is not transmitted, and a meshing clutch (dog clutch), a synchronous coupling mechanism (synchronizer), or a friction clutch ( A multi-plate clutch) can be used. Among these, the meshing clutch and the synchronous coupling mechanism are excellent in that no power is required to maintain the engaged state for transmitting torque. In addition to this, the synchronous coupling mechanism is excellent in that a synchronous action occurs during engagement and a shock can be avoided or reduced.

  A fluid pressure pump motor 6 is disposed on the opposite side of the input planetary gear mechanism 3 from the input planetary gear mechanism 3 and on the same axis as the compound planetary gear mechanism 3 and the input member 2. This fluid pressure pump motor 6 is of a variable displacement type capable of changing the extrusion volume in both positive and negative directions, and is constituted by a variable displacement hydraulic pump such as a swash plate pump, a slant shaft pump or a radial piston pump. Has been. In the following description, the fluid pressure pump motor 6 is referred to as a first pump motor 6 and is also described as “PM1” in the drawing. The "forward" extrusion volume in the first pump motor 6 is that when the rotor is rotated in the opposite direction to the input member 2, the pressure oil is sucked from the suction port 6S and the pressure oil is discharged from the discharge port 6D. Direction. Accordingly, when the pump functions in a state where the extrusion volume is reversed so as to set a negative extrusion volume, the pressure oil is sucked from the discharge port 6D and the pressure oil is discharged from the suction port 6S. Therefore, the first pump motor 6 is described as “both vibrations” in the drawing.

  A third coupling mechanism 7 is disposed between the first pump motor 6 (more specifically, its rotor) and the carrier C1 (that is, the ring gear R2) that is an output element in the compound planetary gear mechanism 3. That is, the first pump motor 6 and the carrier C <b> 1 are connected via the third connection mechanism 7. Similar to the first and second connection mechanisms 4 and 5 described above, the third connection mechanism 7 is a mechanism that can be switched between a state in which torque is transmitted and a state in which torque is not transmitted. A dog clutch), a synchronous coupling mechanism (synchronizer) or a friction clutch (multi-plate clutch) can be used.

  An output shaft 8 corresponding to the output member in the present invention is connected to the rotor shaft (or output shaft) of the first pump motor 6, and the rotor shaft penetrates the first pump motor 6 in the axial direction. Projecting in both the front and rear directions. Therefore, the third connecting mechanism 7 is configured to selectively connect the rotor shaft and the carrier C1. The output shaft 8 outputs torque in the extending direction of the central axis of the input member 2 (left direction in FIG. 1).

  Another fluid pressure pump motor 9 is arranged adjacent to the first pump motor 6 and on the outer peripheral side thereof with the central axis parallel to the first pump motor 6. The fluid pressure pump motor 9 is of a variable capacity type capable of changing the extrusion volume from zero to a predetermined positive direction. Like the first pump motor 6, the swash plate pump, the oblique shaft pump, It is composed of a variable displacement hydraulic pump such as a radial piston pump. Here, the “forward direction” is a setting state of the extrusion volume that sucks the pressure oil from the suction port 9S and discharges the pressure oil from the discharge port 9D when the rotor rotates in the same direction as the input member 2. In the following description, the fluid pressure pump motor 9 is referred to as a second pump motor 9 and is also described as “PM2” in the drawing. Further, since the change direction of the extrusion volume is a one-way swing type from zero, it is described as “one swing” in the figure.

  A counter gear pair 10 corresponding to the transmission mechanism in the present invention is provided between the second pump motor 9 and the sun gear S2 which is a reaction force element in the compound planetary gear mechanism 3. The counter gear pair 10 includes a drive gear 10A connected to the sun gear S2 and a driven gear 10B meshing with the drive gear 10A. Since the drive gear 10A has a larger diameter than the driven gear 10B, It has become.

  Said 1st and 2nd pump motors 6 and 9 are comprised so that power may be transmitted between both by supplying the pressure oil which one discharged to the other. Specifically, the suction ports 6 </ b> S and 9 </ b> S and the discharge ports 6 </ b> D and 9 </ b> D are communicated with each other through the circulation oil passage 11. Therefore, when the extrusion volume of one of the pump motors 6 and 9 is set to zero, the circulating oil passage 11 is blocked, and the pressure oil cannot flow in the other pump motors 9 and 6. 6 is configured to be in a locked state where it cannot rotate. Since there is an unavoidable leakage of hydraulic pressure, a charge pump (not shown) for replenishing pressure oil may be connected to the circulating oil passage 11.

  Next, the operation of the transmission described above will be described. FIG. 2 is a chart collectively showing the operation states of the pump motors (PM1, PM2) 6, 9 and the coupling mechanisms 4, 5, 7 when setting the respective gear positions. “M” for pump motors 6 and 9 indicates that the extrusion volume in the so-called positive direction is maximum (Max), and “−M” indicates that the extrusion volume in the so-called negative direction is maximum. Further, “0” indicates that the extrusion volume is minimum or zero. Further, “◯” for each of the coupling mechanisms 4, 5, 7 indicates an engaged state in which torque is transmitted, and “x” indicates a released state in which torque is not transmitted. Furthermore, “S” indicates that the vehicle speed is starting from zero, the number indicates the gear position at which each fixed gear ratio is set, “R” indicates the reverse speed (reverse) in which the vehicle moves backward, Further, the connection with a hyphen such as “S-1” indicates a state in which a so-called intermediate speed ratio that reaches each fixed speed ratio immediately after starting is set.

  In the neutral (N) state in which the neutral position is selected, the pump motors 6 and 9 are set to the “OFF” state in which the extrusion volume is zero, and the coupling mechanisms 4, 5 and 7 are set to the released state. When each of these coupling mechanisms 4, 5, and 7 is constituted by a synchronous coupling mechanism (so-called synchro), each sleeve is set at the center position. In addition, it can also set to the engagement / release state in preparation for the starting state mentioned later. Therefore, no power is input to the compound planetary gear mechanism 3, or the power of the power source 1 is not transmitted to the output shaft 8.

  When the vehicle starts by switching the shift position to the drive position or the like, first, the first coupling mechanism 4 and the third coupling mechanism 7 are switched to the engaged state, and the input member 2 and the sun gear S1 are coupled. In addition, the output shaft 8 is coupled to the carrier C1. If this state is shown in a collinear diagram for the compound planetary gear mechanism 3, it is as shown by a straight line L1 in FIG. That is, the sun gear S1 connected to the input member 2 rotates (forward rotation) in the same direction as the power source 1 or the input member 2, and is connected to the output shaft 8 and the first pump motor 6 via the third connection mechanism 7. The connected carrier C1 remains stopped because the vehicle has not yet started. Therefore, the ring gear R1 rotates in the direction opposite to the input member 2 (reverse rotation), and the sun gear S2 to which the second pump motor 9 is connected rotates further at a higher speed (idle in the reverse direction). Since the extrusion volume q1 of the first pump motor 6 is set to the maximum (M) and the extrusion volume q2 of the second pump motor 9 is set to zero (0), no pressure oil flows. .

  At the time of starting, the extrusion volume q1 of the first pump motor 6 is gradually decreased from the maximum to zero, and the extrusion volume q2 of the second pump motor 9 is gradually increased from zero to the maximum. Therefore, when the extrusion volume q2 of the second pump motor 9 which is set to zero and is idling in the reverse rotation direction is gradually increased, the second pump motor 9 starts to discharge the pressure oil, Torque required for discharging acts on the sun gear S2 as a reaction force. This is an upward force in the sun gear S2 and the second pump motor 9 (PM2) connected to the sun gear S2 in the collinear diagram of FIG. 3, so that the rotational speed of the second pump motor 9 gradually decreases and the carrier A torque for positively rotating it acts on C1, and its rotational speed gradually increases. Then, torque is transmitted from the carrier C1 to the output shaft 8.

  Further, since the second pump motor 9 rotates in the reverse direction, the pressure oil is discharged from the suction port 9S and supplied to the suction port 6S of the first pump motor 6. The first pump motor 6 functions as a motor and rotates forward in combination with the progressive reduction of the extrusion volume q1 of the first pump motor 6, and the rotor shaft and the output shaft 8 integrated therewith are positively connected. Torque in the rotational direction is applied. That is, power is transmitted from the second pump motor 9 to the first pump motor 6 via pressure oil (fluid). Therefore, in the state of the so-called intermediate stage (intermediate gear ratio) from the start to the setting of the first speed that is the fixed gear ratio, mechanical power transmission via the compound planetary gear mechanism 3 and pressure oil are performed. Power is transmitted to the output shaft 8 by so-called fluid transmission. The speed ratio in the process (ratio of the rotational speed of the input member 2 to the rotational speed of the output shaft 8) is determined according to the ratio of these two power transmissions, and the power transmitted by the fluid transmission is determined by each pump. Since the motors 6 and 9 continuously change depending on the extrusion volumes q1 and q2, the gear ratio changes continuously (steplessly), and so-called continuously variable transmission becomes possible.

  When the extrusion volume q2 of the second pump motor 9 is maximized, the rotation of the second pump motor 9 is almost stopped, and in this state, the extrusion volume q1 of the first pump motor 6 is made zero, thereby stopping the flow of pressure oil. Then, the second pump motor 9 is stopped. The first pump motor 6 idles in the forward rotation direction. This state is indicated by a straight line L2 in the alignment chart of FIG. In this case, no fluid transmission occurs, and power is transmitted from the input member 2 to the output shaft 8 via mechanical means (mechanism) in the compound planetary gear mechanism 3. Therefore, the gear ratio is a gear ratio according to the gear ratio (ratio of the number of teeth of each sun gear and ring gear) in the compound planetary gear mechanism 3. This is the first speed which is the fixed gear ratio.

  Therefore, at the first speed, which is a fixed gear ratio, pressure oil is not circulated between the pump motors 6 and 9, so that no power loss occurs at this point except for the unavoidable leakage of pressure oil. . Further, by configuring each coupling mechanism 4, 7 with a meshing clutch, a synchronous coupling mechanism, etc., energy is not consumed to transmit power from the power source 1, and therefore power loss and consumption are small. Efficient power transmission can be performed.

  When upshifting from the first speed, which is the fixed gear ratio, toward the second speed, the engagement / release states of the coupling mechanisms 4, 5, and 7 are not changed, and the pushing volume q2 of the second pump motor 9 is not changed. Is maintained at the maximum, and the extrusion volume q1 of the first pump motor 6 is gradually changed from zero toward the negative maximum (-M). As described above, at the first speed, the first pump motor 6 is idling in the positive rotation direction (the same rotation direction as that of the input member 2). Therefore, by setting the extrusion volume q1 to the negative direction, the discharge port 6D The pressure oil is sucked and the pressure oil is discharged from the suction port 6S. Since the suction port 6S communicates with the suction port 9S of the second pump motor 9, pressure oil is supplied from the first pump motor 6 to the second pump motor 9, and as a result, the second pump motor 9 is driven by the motor. Functions as a forward rotation.

Therefore, in the process of upshifting from the first speed to the second speed, the sun gear S1 and the counter gear pair 10 are connected to each other while the torque is transmitted from the power source 1 to the sun gear S1. The rotational speed of the second pump motor 9 is gradually increased. That is, the intermediate transmission gear ratio is set by power transmission via the pressure oil (fluid) between the pump motors 6 and 9, and the transmitted power changes according to the change in the extrusion volume q1, so that The ratio changes continuously. That is, continuously variable transmission can be performed. Thus, when the gear ratio of the counter gear pair 10 is “1”, when the extrusion volume q1 of the first pump motor 6 reaches the maximum (−M) in the negative direction, the rotational speeds of the carrier C1 and the sun gear S2 (each pump The rotational speeds of the motors 6 and 9 become equal, and the entire compound planetary gear mechanism 3 rotates as a unit. This state is indicated by a straight line L3 in FIG. When the gear ratio of the counter gear pair 10 is not “1”, if the gear ratio is K,
K = -q1 / q2
When is established, the entire compound planetary gear mechanism 3 rotates as a unit. The second forward speed is set by maximizing the extrusion volume of each of the pump motors 6 and 9, so the second forward speed is one of the fixed gear ratios in the present invention.

  At the second speed (directly connected stage), the rotational speed of the sun gear S1 and the rotational speed of the ring gear R1 match, so the rotational speed of the input side member and the rotational speed of the output side member in the second coupling mechanism 5 are the same. And are consistent. That is, since the second coupling mechanism 5 is in a so-called rotationally synchronized state, the engagement / release state of the first coupling mechanism 4 and the second coupling mechanism 5 is switched without causing a change in the rotational speed. Can do. The second connecting mechanism 5 is engaged when the second speed is set. When upshifting from the second speed to the third speed, the first coupling mechanism 4 is released. The extrusion volume q1 of the first pump motor 6 is gradually changed from the maximum in the negative direction to zero while the extrusion volume q2 of the second pump motor 9 is maintained at the maximum.

  In that case, the pump motor with a large extrusion volume discharges the pressure oil, and the pump motor with a small extrusion volume receives the pressure oil and functions as a motor. Therefore, the second pump motor 9 generates hydraulic pressure and functions as a pump. . Therefore, the rotational speed of the sun gear S <b> 2 connected to the second pump motor 9 gradually decreases together with the rotational speed of the second pump motor 9. Therefore, since the rotational speed of the sun gear S2 is gradually decreased in a state where the ring gear R1 is rotating forward together with the input member 2 or the power source 1, the rotational speed of the carrier C1 and the output shaft 8 connected thereto is gradually increased. To do. In that case, the first pump motor 6 is supplied with the pressure oil discharged from the second pump motor 9 and functions as a motor, so that torque is added to the output shaft 8. Therefore, also in this case, power transmission and fluid transmission are performed by mechanical means, and the gear ratio continuously changes.

  When the extrusion volume q1 of the first pump motor 6 becomes zero, the flow of pressure oil stops, the second pump motor 9 enters a so-called locked state, the sun gear S2 is fixed, and the first pump motor 6 runs idle. . This state is indicated by a straight line L4 in FIG. This is the third speed which is a fixed gear ratio, and the rotation speed of the output shaft 8 is larger than the rotation speed of the input member 2 as shown in FIG. It becomes. Also in this case, there is no fluid transmission, only the power transmission by the mechanical means of the compound planetary gear mechanism 3 occurs, and each coupling mechanism 5, 7 is constituted by a meshing clutch or a synchronous coupling mechanism. Since power is not particularly consumed to maintain the transmission state, power transmission efficiency can be improved.

  Next, the reverse gear will be described. When the reverse gear is set, the first and second coupling mechanisms 4 and 5 are engaged, the extrusion volume q1 of the first pump motor 6 is set to the maximum and the first gear is set. The extrusion volume q2 of the two-pump motor 9 is gradually increased from zero to the maximum. Therefore, since the ring gear R1 and the sun gear S1 of the compound planetary gear mechanism 3 are connected by engaging the first and second connecting mechanisms 4 and 5, the entire compound planetary gear mechanism 3 is integrated. , The whole is rotated as a unit. This is a state in which the second pump motor 9 is directly connected to the input member 2 via the counter gear pair 10, and the second pump motor 9 has a rotational speed of the input member 2 in accordance with the gear ratio of the counter gear pair 10. It is accelerated and rotates forward.

  Therefore, when the extrusion volume q2 of the second pump motor 9 is gradually increased from zero, this functions as a pump and generates hydraulic pressure. The pressure oil is discharged from the discharge port 9 </ b> D because the second pump motor 9 is rotating forward, and is supplied to the discharge port 6 </ b> D of the first pump motor 6. And since the extrusion volume q1 of the 1st pump motor 6 is set to the maximum in the positive direction, the 1st pump motor 6 reversely rotates by supplying pressure oil from the discharge port 6D. In this way, power is transmitted from the second pump motor 9 to the first pump motor 6 via pressure oil, and when the first pump motor 6 rotates in reverse, the output shaft 8 connected thereto rotates in reverse. You will drive backwards. Accordingly, the speed ratio from the start to the reverse speed is set only by fluid transmission after being increased by the counter gear pair 10 and is continuously variable.

  As described above, in the configuration shown in FIG. 1, the compound planetary gear mechanism 3 in which two sets of planetary gear mechanisms 3A and 3B are combined and the three coupling mechanisms 4, 5, and A gear ratio can be set, and a shift between these gear ratios can be a so-called continuously variable transmission. Moreover, a so-called two-axis configuration in which the rotating shafts are arranged on two parallel axes without using so-called multiple shafts that are rotatably fitted to each other, a compact configuration with a small number of parts. The hydraulic pressure mechanical power transmission device can be used. Further, in the configuration shown in FIG. 1, the output shaft 8 can be extended in the direction in which the axis of the power source 1 or the input member 2 is extended, and a propeller shaft (not shown) or the like can be connected thereto for output. It can be set as the apparatus with the favorable vehicle mounting property. Furthermore, since no power is consumed particularly when the fixed gear ratio is set, power transmission efficiency can be improved.

  Next, another example of the present invention will be described. The example shown in FIG. 4 is an example in which the configuration and arrangement of the second pump motor 9 are changed from the configuration shown in FIG. 1 described above. That is, in the configuration shown in FIG. 4, the second pump motor 9 is arranged to be shifted in the axial direction with respect to the first pump motor 6, and more specifically, the outer peripheral side of the compound planetary gear mechanism 3 or the first coupling mechanism 4. It is arranged at a position close to. The rotor shaft extends to the first pump motor 6 side (the side opposite to the power source 1) (left side in FIG. 4), and a driven gear 10B in the counter gear pair 10 is attached to the rotor shaft. Since the other configuration is the same as the configuration shown in FIG. 1, the same reference numerals as those in FIG. In FIG. 4, the power source 1 and the circulating oil passage 11 are omitted.

  Even in the configuration shown in FIG. 4, the gear ratios of the three forward speeds and the first reverse speed can be set continuously (infinitely) as in the apparatus having the configuration shown in FIG. 1 described above. Moreover, it can be set as the apparatus with the favorable vehicle-mounted property with respect to FR vehicle by the compact structure with few number of parts. In addition to this, in the configuration shown in FIG. 4, it is not necessary to arrange two pump motors side by side in the radial direction, and the second pump motor 9 can be arranged in a so-called empty space. The overall configuration can be made compact. Or the freedom degree of design improves.

  The present invention is not limited to the specific examples described above, and the transmission mechanism in the present invention may be configured by a winding transmission mechanism using a belt, a chain, or the like, instead of the counter gear pair 10 described above. Alternatively, a mechanism using a friction wheel or the like may be used.

It is a skeleton figure which shows typically an example of the power transmission device concerning this invention. It is a table | surface which shows collectively the operation state of each pump motor and each connection mechanism in the process of setting a fixed gear ratio. It is a collinear diagram about a compound planetary gear mechanism for explaining an operating state when setting each gear ratio. It is a skeleton figure which shows typically the other example of the power transmission device which concerns on this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Power source, 2 ... Input member, 3 ... Compound planetary gear mechanism, 3A ... 1st planetary gear mechanism, 3B ... 2nd planetary gear mechanism, S1, S2 ... Sun gear, R1, R2 ... Ring gear, C1, C2 ... Carrier 4 ... 1st connection mechanism, 5 ... 2nd connection mechanism, 7 ... 3rd connection mechanism, 6 ... 1st fluid pressure pump motor (1st pump motor), 9 ... 2nd fluid pressure pump motor (2nd pump motor) 8 ... Output member (output shaft), 10 ... Transmission mechanism (counter gear pair).

Claims (7)

The power transmitted from the power source is input to the planetary gear mechanism, and the gear ratio is changed by changing the reaction force against the planetary gear mechanism according to the fluid pressure, and the power corresponding to the gear ratio is output to the output member. In the hydraulic pressure mechanical power transmission device,
An input member to which power is transmitted from the power source;
The first planetary gear mechanism is disposed on the same axis as the input member, and the carrier and the ring gear of the two planetary gear mechanisms including the first planetary gear mechanism and the second planetary gear mechanism are connected to each other. The sun gear is one input element, the ring gear of the first planetary gear mechanism and the carrier of the second planetary gear mechanism are the other input elements, and the carrier of the first planetary gear mechanism and the ring gear of the second planetary gear mechanism are A compound planetary gear mechanism configured to be an output element and the sun gear of the second planetary gear mechanism to be a reaction force element;
A first coupling mechanism that selectively couples the one input element and the input member;
A second coupling mechanism that selectively couples the other input element and the input member;
A third coupling mechanism that selectively enables torque transmission between the output element and the output member;
A variable displacement first fluid pressure pump motor coupled to the output member;
A variable capacity second fluid pressure pump motor connected to the reaction force element and communicated with the first fluid pressure pump motor so as to exchange pressure fluid with the first fluid pressure pump motor; A fluid pressure mechanical power transmission device comprising:   The first fluid pressure pump motor is composed of a double-swing type fluid pressure pump motor capable of changing the extrusion volume in both positive and negative directions with zero interposed therebetween, and the second fluid pressure pump motor has an extrusion volume. 2. The hydro-mechanical power transmission device according to claim 1, wherein the hydro-mechanical power transmission device is constituted by a single swing type fluid pressure pump motor that can be changed from zero to either positive or negative.   The first fluid pressure pump motor and the output member are disposed on the opposite side of the input member and on the same axis as the input member and the compound planetary gear mechanism with the compound planetary gear mechanism interposed therebetween, and 3. The hydraulic mechanical power transmission device according to claim 1, wherein the second fluid pressure pump motor is arranged in parallel with the first fluid pressure pump motor. 4.   A transmission mechanism for transmitting power from the reaction force element to the second fluid pressure pump motor is provided, and the transmission mechanism increases power from the reaction force element toward the second fluid pressure pump motor to transmit power. 4. The hydraulic mechanical power transmission device according to claim 3, wherein the hydraulic pressure mechanical power transmission device is constituted by a speed increasing mechanism.   5. The hydraulic mechanical power transmission device according to claim 3, wherein the first fluid pressure pump motor is disposed on an outer peripheral side of the second fluid pressure pump motor. 6.   5. The hydromechanical power transmission device according to claim 3, wherein the first fluid pressure pump motor is disposed so as to be shifted in an axial direction with respect to the second fluid pressure pump motor. 6.   The fixed gear ratio that can be set by maximizing the extrusion volume of at least one of the fluid pressure pump motors and setting the other extrusion volume to zero or maximum is three stages on the forward side and one stage on the reverse side. The fluid pressure mechanical power transmission device according to any one of claims 1 to 6.

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