Unit

Abstract

In a unit internally provided with a power transmission mechanism, the inter-stage ratio during gear shifting is reduced. The unit has: an input member; an output member; and a gear device configured so that the rotating members of the first planetary gear mechanism and the second planetary gear mechanism are coupled at two locations, and a first rotating portion, a second rotating portion, a third rotating portion, and a fourth rotating portion are arranged side by side in this order on a collinear graph. The input part can be connected with the first rotating part and can be connected with the second rotating part, the output part is connected with the third rotating part, and the fourth rotating part can be switched between a rotating state and a non-rotating state.

Description

Technical Field

[0001] The present invention relates to a unit having a power transmission mechanism therein. Background Art

[0002] Patent Document 1 discloses a two-speed forward electric vehicle automatic transmission unit. In this unit, by switching the engagement states of two friction clutches, a first speed and a second speed with a smaller speed ratio (=input rotation speed / output rotation speed) than the first speed can be realized.

[0003] The same unit is also disclosed in Patent Documents 2 to 4.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent document 1: German Patent Application Publication No. 102019116360

[0007] Patent document 2: German Patent Application Publication No. 102019119951

[0008] Patent Document 3: Chinese Patent No. 106195194

[0009] Patent Document 4: Chinese Utility Model Specification No. 206000959 Summary of the invention

[0010] Technical problem to be solved by the invention

[0011] In an automatic transmission unit for electric vehicles with two forward gears, the larger the speed ratio of the first gear, the better the torque amplification effect caused by deceleration. Therefore, the larger the speed ratio of the first gear, the smaller the maximum torque of the motor can be, and the smaller the motor can be selected. In contrast, the smaller the speed ratio of the second gear, the lower the rotation speed of the motor when achieving a certain vehicle speed, which is beneficial when cruising at high speed.

[0012] However, when the speed ratios of the first gear and the second gear are set separately based on the above design concept, the inter-stage ratio when switching between the first gear and the second gear (= first gear speed ratio / second gear speed ratio) increases, and the speed change shock increases.

[0013] The present invention has been made in view of the above-mentioned technical problems, and an object of the present invention is to reduce the step ratio during speed change in a unit having a power transmission mechanism therein.

[0014] Technical solutions for solving technical problems

[0015] According to one aspect of the present invention, there is provided a unit having:

[0016] Input components;

[0017] Output components;

[0018] A gear device, wherein the rotating parts of the first planetary gear mechanism and the second planetary gear mechanism are connected at two locations, and a first rotating part, a second rotating part, a third rotating part, and a fourth rotating part are arranged in order on a collinear diagram;

[0019] The input member is connectable to the first rotating part and is connectable to the second rotating part.

[0020] The output member is connected to the third rotating part,

[0021] The fourth rotating portion can switch between a rotating state and a non-rotating state.

[0022] Effects of the Invention

[0023] According to the above-mentioned method, three speed stages can be realized by switching the connection destination of the input member (either one or both of the first rotating part and the second rotating part) and the rotation state of the fourth rotating part. Since the inter-stage ratio is reduced, an appropriate speed ratio can be set according to the speed range. In addition, since the speed ratio is 1 in the third gear, the power transmission loss caused by the rotation difference between the rotating parts can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a skeleton diagram of the units according to the embodiment of the present invention.

[0025] Figure 2 This is an engagement table showing the engagement state of each engagement member at each speed stage.

[0026] Figure 3 is the collinearity diagram of the unit.

[0027] Figure 4A This is a framework diagram of a modified example.

[0028] Figure 4B This is a framework diagram of a modified example.

[0029] Figure 5A It is a framework diagram of other modified examples.

[0030] Figure 5B yes Figure 5A Collinear diagram of the variation shown.

[0031] Figure 6 This is a framework diagram of yet another modified example.

[0032] Figure 7 This is a framework diagram of yet another modified example.

[0033] Figure 8 This is a framework diagram of yet another modified example.

[0034] Fig. 9 This is a framework diagram of yet another modified example.

[0035] Fig.10 This is a framework diagram of yet another modified example.

[0036] Fig.11 This is a framework diagram of yet another modified example.

[0037] Fig.12 This is a framework diagram of yet another modified example.

[0038] Fig.13 This is a framework diagram of yet another modified example.

[0039] Fig.14 This is a framework diagram of yet another modified example.

[0040] Fig.15 This is a framework diagram of yet another modified example.

[0041] Fig.16 This is a framework diagram of yet another modified example.

[0042] Fig.17 This is a framework diagram of yet another modified example.

[0043] Fig.18 This is a framework diagram of yet another modified example.

[0044] Fig.19 This is a framework diagram of yet another modified example.

[0045] Fig. 20 This is a framework diagram of yet another modified example.

[0046] Fig.21 This is a framework diagram of yet another modified example.

[0047] Fig. 22 This is a framework diagram of yet another modified example.

[0048] Fig.23 This is a framework diagram of yet another modified example.

[0049] Fig.24 This is a framework diagram of yet another modified example.

[0050] Fig.25 This is a framework diagram of yet another modified example.

[0051] Fig.26 This is a framework diagram of yet another modified example.

[0052] Fig. 27 This is a framework diagram of yet another modified example.

[0053] Fig.28 This is a framework diagram of yet another modified example.

[0054] Fig.29 This is a framework diagram of yet another modified example.

[0055] Fig.30 This is a framework diagram of yet another modified example.

[0056] Fig.31 This is a framework diagram of yet another modified example.

[0057] Fig.32 This is a framework diagram of yet another modified example. DETAILED DESCRIPTION

[0058] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. It should be noted that the terms used in this specification are defined as follows.

[0059] The term "unit" refers to a device as a whole that has a power transmission mechanism such as a gear mechanism or a differential gear mechanism inside, and includes a motor unit having a motor and a power transmission mechanism, an automatic transmission unit, a speed reducer unit, and the like.

[0060] The “speed ratio” is a value obtained by dividing the input rotational speed of the unit by the output rotational speed. The “input rotation” includes not only the rotation input to the unit from a power source outside the unit but also the rotation input to the unit from a power source inside the unit.

[0061] The “step ratio” is a value obtained by dividing the larger speed ratio (for low speed) by the smaller speed ratio (for high speed) of two speed ratios realized in the unit.

[0062] “Axial direction” refers to the axial direction of the rotation axis of a component constituting a unit. The component is a motor, a gear mechanism, a differential gear mechanism, etc. “Radial direction” refers to the radial direction from the central axis of the rotation axis.

[0063] The "housing" is a housing that houses the motor, inverter, and power transmission mechanism, and is composed of one or more housings. The method of integrally forming a housing for the motor, a housing for the inverter, and a housing for the power transmission mechanism is called "3in1".

[0064] The term "motor" refers to a rotating electrical machine having a motor function, and may have a generator function in addition to the motor function.

[0065] “Component A is connected to component B” means that component A is connected to component B upstream or downstream in a manner that power can be transmitted between component A and component B. The input side of power is upstream, and the output side of power is downstream. The method of connecting component A to component B directly or via other components is not limited, and the connection may be via a clutch or the like.

[0066] “Part A and part B are connected” refers to a state where parts A and B are connected directly or indirectly via other parts, so that parts A and B are integrated. In other words, it can also be said that parts A and B rotate integrally. In addition, it refers to a state where parts A and B are connected without a brake or a clutch, and it can also be said that parts A and B are always connected.

[0067] “Component A is fixed to component B” includes two types: component A is directly fixed to component B, and component A is fixed to component B via another component C other than components A and B. “Component A is fixed” means that component A is fixed to another component and cannot rotate.

[0068] “Component A and component B overlap when viewed in a prescribed direction” means that component A and component B are arranged side by side in a prescribed direction (axial direction, radial direction, gravity direction, etc.), and when viewed from the prescribed direction, component A and component B at least partially overlap. This has the same meaning as “component A and component B overlap in a prescribed direction”. When component A and component B overlap when viewed in the axial direction, component A and component B are coaxial. When component A and component B are drawn side by side in a prescribed direction in a drawing, component A and component B overlap when viewed in the prescribed direction.

[0069] In contrast, “components A and B do not overlap when viewed in a prescribed direction” means that components A and B are not arranged side by side in a prescribed direction (axial direction, radial direction, gravity direction, vehicle travel direction, etc.), and there is no overlapping portion between components A and B when viewed from the prescribed direction. This is the same as “components A and B do not overlap in a prescribed direction”. In the drawings, components A and B are not drawn side by side in a prescribed direction, which means that components A and B do not overlap when viewed in the prescribed direction.

[0070] “Component A is arranged between component B and component C when viewed in a prescribed direction” means that component A is observed to be between component B and component C when viewed from a prescribed direction (axial direction, radial direction, gravity direction, etc.). For example, when component B, component A, and component C are arranged in order in the axial direction, component A is observed to be between component B and component C when viewed in the radial direction, so component A can be said to be located between component B and component C. Component A does not need to overlap with components B and C when viewed in the axial direction. The case where component A is drawn between component B and component C in the drawings means that component A is located between component B and component C when viewed in the prescribed direction.

[0071] “Component A is arranged on the axially outer side of component B” means that component A is arranged on one axial side or the other axial side of component B. In addition to the case where component A and component B overlap when viewed axially, it also includes the case where component A and component B have different radial positions and component A and component B do not overlap.

[0072] “Component A is arranged radially outside (or inside) component B” means that the radial position of component A is closer to the outside (or inside) than the radial position of component B. In addition to the case where component A and component B overlap when viewed radially, it also includes the case where component A and component B have different axial positions and component A and component B do not overlap.

[0073] "Closely arranged" means that two components have overlapping portions when viewed axially or radially, and no other components are inserted between the two components. For example, "two engaging components are closely arranged" means that no planetary gear mechanism is arranged between the two engaging components. In the drawings, when no other components are drawn between component A and component B, it means that component A and component B are closely arranged.

[0074] “One side of the engaging component” and “the other side of the engaging component” refer to two components included in the engaging component that cannot rotate relative to each other when the engaging component is in the engaged state and can rotate relative to each other when the engaging component is in the released state. “One side of the engaging component” and “the other side of the engaging component” can be a combination of rotating components, or a combination of a rotating component and a non-rotating component. Usually, the former is called a clutch, and the latter is called a brake. In addition, “one side of the engaging component” refers to any one of “one side of the engaging component” and “the other side of the engaging component”.

[0075] Other terms are defined as appropriate in the main text of the specification.

[0076] Figure 11 is a frame diagram showing the basic structure of a unit 100 according to an embodiment of the present invention. The unit 100 is a three-speed forward automatic transmission unit for electric vehicles that changes the speed of the rotation input from the motor (not shown) as a power source to the input component IN at a speed ratio corresponding to the speed change stage, and transmits it from the output component OUT to the drive wheel (not shown). The input component IN and the output component OUT are each composed of gears, a rotating shaft, etc. Since the motor can switch between forward rotation and reverse rotation, the unit 100 does not have a reverse stage, and the design concept is significantly different from that of a vehicle unit using an internal combustion engine as a power source.

[0077] The unit 100 is a so-called 3-in-1 unit in which an input member IN, a gear device 2, first to third engagement members CL1, CL2, B1, an output member OUT, a motor and an inverter (not shown) are accommodated in a housing 1. The housing 1 is fixed to the vehicle in a non-rotatable manner.

[0078] One end of the input component IN is connected to the output shaft of the motor, and the input component IN rotates using the power input from the motor. The rotation speed of the input component IN is the input rotation speed of the unit 100. The motor functions as an electric motor, and is electrically connected to a battery (not shown) outside the unit 100 via an inverter, and receives power supply from the battery. In addition, the motor can also function as a generator.

[0079] The gear device 2 is configured as a rotating member in which a first planetary gear mechanism PG1 and a second planetary gear mechanism PG2 are arranged close to each other and connected to each other at two locations.

[0080] The first planetary gear mechanism PG1 is a single pinion planetary gear mechanism having a first sun gear S1 as a first rotating component, a plurality of first pinion gears (not shown), a first planet carrier C1 as a second rotating component that rotatably supports the plurality of first pinion gears, and a first internal ring gear R1 as a third rotating component. The first sun gear S1 meshes with the plurality of first pinion gears, and the plurality of first pinion gears mesh with the first internal ring gear R1.

[0081] The second planetary gear mechanism PG2 is a single pinion planetary gear mechanism having a second sun gear S2 as a fourth rotating member, a plurality of second pinion gears (not shown), a second planet carrier C2 as a fifth rotating member for rotatably supporting the plurality of second pinion gears, and a second internal ring gear R2 as a sixth rotating member. The second sun gear S2 meshes with the plurality of second pinion gears, and the plurality of second pinion gears mesh with the second internal ring gear R2.

[0082] The S in the parentheses next to the reference numerals PG1 and PG2 in the drawings indicates that the planetary gear mechanism is a single pinion planetary gear mechanism. It should be noted that although it does not appear in the present embodiment, when the planetary gear mechanism is a double pinion planetary gear mechanism, a parenthesis D is added next to PG1 and PG2.

[0083] The first sun gear S1 is coupled to the second sun gear S2. The first planetary carrier C1 is coupled to the second inner ring gear R2 and the output member OUT. By coupling the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 at two locations, the first rotating portion P1 is composed of the first sun gear S1 and the second sun gear S2, the second rotating portion P2 is composed of the second planetary carrier C2, the third rotating portion P3 is composed of the first planetary carrier C1 and the second inner ring gear R2, and the fourth rotating portion P4 is composed of the first inner ring gear R1.

[0084] The rotation speed of the output component OUT is the output rotation speed of the unit 100 .

[0085] The first engagement member CL1 is a hydraulic or electric clutch. When the first engagement member CL1 is in an engagement state, when the two parts of the first engagement member CL1 to be engaged are one side and the other side, one side is connected to the input member IN via the connecting member M passing through the inner circumference of the gear device 2, and the other side is connected to the second rotating part P2 formed by the second planetary carrier C2. Therefore, as long as the first engagement member CL1 is engaged, the input member IN can be connected to the second rotating part P2 formed by the second planetary carrier C2.

[0086] The second engaging component CL2 is a hydraulic or electric clutch. When the second engaging component CL2 is engaged, when the two parts of the engaged second engaging component CL2 are regarded as one side and the other side, one side is connected to the input component IN, and the other side is connected to the first rotating part P1 formed by the first sun gear S1 and the second sun gear S2. Thus, as long as the second engaging component CL2 is engaged, the input component IN can be connected to the first rotating part P1 formed by the first sun gear S1 and the second sun gear S2.

[0087] By connecting one side of the first engaging component CL1 to the input component IN via the connecting component M passing through the inner peripheral side of the gear device 2, the first engaging component CL1 and the second engaging component CL2 can be dispersedly arranged on both sides of the axial direction relative to the gear device 2, that is, the gear device 2 is arranged between the first engaging component CL1 and the second engaging component CL2 when viewed in the radial direction.

[0088] When the first engagement member CL1 and the second engagement member CL2 are arranged on the same side in the axial direction relative to the gear device 2, one is arranged on the inner peripheral side of the other, and the necessity of using an actuator (such as a hydraulic actuator supplied with hydraulic pressure from a control valve unit) that is not easily restricted by layout increases.

[0089] In contrast, when the first engaging member CL1 and the second engaging member CL2 are dispersedly arranged on both sides of the axial direction relative to the gear device 2, a layout in which one is not arranged on the inner peripheral side of the other can be adopted. As a result, as the actuators of the first engaging member CL1 and the second engaging member CL2, it is convenient to adopt an actuator that is easily restricted by the layout (an electric actuator that is fixed to the housing 1 or the like by the relationship of the reaction force and needs to be connected to the power line, or a hydraulic actuator that is installed on the housing 1 or the like and needs to be connected to the hydraulic supply unit by piping, etc.), and the freedom of selection of the actuators used for the first engaging member CL1 and the second engaging member CL2 is improved.

[0090] In addition, since one side of the first engaging member CL1 and one side of the second engaging member CL2 are connected to the input member IN and rotate integrally, they can be shared, that is, configured as an integrated part. For example, when the first engaging member CL1 and the second engaging member CL2 are respectively configured by a multi-plate clutch having a plurality of friction plates arranged between a drum and a hub, by forming the hub of the other on the outer periphery of the drum of one, it is possible to configure an integrated part. Thus, the number of parts of the unit 100 can be reduced.

[0091] The third engaging member B1 is a hydraulic or electric brake. When the third engaging member B1 is in an engaged state, when two parts of the engaged third engaging member B1 are used as one side and the other side, one side is connected to the fourth rotating part P4 formed by the first internal gear ring R1, and the other side is fixed to the housing 1. Thus, as long as the third engaging member B1 is engaged, the fourth rotating part P4 formed by the first internal gear ring R1 can be fixed to the housing 1.

[0092] Since the third engagement member B1 is arranged radially outwardly of the first engagement member CL1 and the second engagement member CL2, an actuator that is not easily restricted by layout or an actuator that is easily restricted by layout can be adopted as the third engagement member B1.

[0093] The third engaging member B1 may also be constituted by a selectable one-way clutch. The selectable one-way clutch is constituted by a pair of ratchet mechanisms that can switch the operating state by an electric actuator and limit the rotation in different directions. When only one of the pair of ratchet mechanisms is operated, it is in the one-way clutch state, and when both of the pair of ratchet mechanisms are operated, it is a clutch in the engaged state.

[0094] By having the first to third engaging parts CL1, CL2, and B1, one of the first engaging part CL1 and the second engaging part CL2 is engaged, and the other is released, thereby selectively connecting the input part IN to the first rotating part P1 formed by the first sun gear S1 and the second sun gear S2, or the second rotating part P2 formed by the second planetary carrier C2. In addition, by engaging both the first engaging part CL1 and the second engaging part CL2, the input part IN can be connected to the first rotating part P1 and the second rotating part P2.

[0095] Furthermore, by changing the engagement state of the third engagement member B1, the fourth rotational portion P4 formed by the first ring gear R1 can be switched between a rotational state and a non-rotational state.

[0096] In addition, when viewed in the radial direction, the first to third engaging parts CL1, CL2, B1 are arranged on the axially outer side of the gear device 2. Since no engaging parts are arranged between the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, the layout freedom of the first to third engaging parts CL1, CL2, B1 is increased, and the axial dimension of the unit 100 can be reduced.

[0097] Furthermore, when viewed in the axial direction, the first to third engagement members CL1, CL2, and B1 can be overlapped with the gear device 2. When the above members are overlapped, the radial dimension of the unit 100 can be reduced.

[0098] Figure 2 : is an engagement table showing the relationship between the engagement states of the first to third engagement members CL1, CL2, and B1 and the speed stages achieved in the unit 100. In the table, a black circle indicates an engaged state, and a blank indicates a released state.

[0099] As shown in the engagement table, the first gear is achieved by engaging the second engagement member CL2 and the third engagement member B1, and releasing the first engagement member CL1. The second gear is achieved by engaging the first engagement member CL1 and the third engagement member B1, and releasing the second engagement member CL2. The third gear is achieved by engaging the first engagement member CL1 and the second engagement member CL2, and releasing the third engagement member B1.

[0100] Any speed change stage is realized by engaging two engagement parts among the first to third engagement parts CL1, CL2, and B1, and the engagement part to be released is one. In the case where the engagement parts to be released are in contact with each other and generate traction torque even in the released state, such as a multi-plate clutch, the fewer the number of engagement parts to be released in the process of realizing the speed change stage, the more the mechanical loss can be reduced. In the present embodiment, since the engagement part to be released in any speed change stage is one, even when the engagement parts that generate traction torque are used as the first to third engagement parts CL1, CL2, and B1, the mechanical loss can be suppressed and the power efficiency of the vehicle equipped with the unit 100 can be improved.

[0101] in addition, Figure 3 It is a collinear diagram of the unit 100. On the collinear diagram, the first to fourth rotational positions P1 to P4 are arranged in sequence, and each rotational position corresponds to the longitudinal lines l1 to l4.

[0102] Since the first planetary gear mechanism PG1 is a single pinion planetary gear mechanism, a first carrier C1 is disposed between the first sun gear S1 and the first ring gear R1. Since the second planetary gear mechanism PG2 is also a single pinion planetary gear mechanism, a second carrier C2 is disposed between the second sun gear S2 and the second ring gear R2.

[0103] When the first engagement member CL1 is engaged and the second engagement member CL2 is released, the input member IN is connected to the second rotational portion P2, and thus the vertical line l2 corresponds to the input member IN. Conversely, when the first engagement member CL1 is released and the second engagement member CL2 is engaged, the input member IN is connected to the first rotational portion P1, and thus the vertical line l1 corresponds to the input member IN.

[0104] Since the output member OUT is connected to the third rotation point P3, the vertical line l3 corresponds to the output member OUT.

[0105] When the interval between the longitudinal line l1 and the longitudinal line l3 is set to 1, the interval α1 between the longitudinal line l3 and the longitudinal line l4 is the value obtained by dividing the number of teeth of the first sun gear S1 by the number of teeth of the first inner ring gear R1. In addition, when the interval between the longitudinal line l1 and the longitudinal line l2 is set to 1, the interval α2 between the longitudinal line l2 and the longitudinal line l3 is the value obtained by dividing the number of teeth of the second sun gear S2 by the number of teeth of the second inner ring gear R2.

[0106] The collinear diagram plots straight lines L1 to L3 corresponding to the respective speed stages. The rotation speeds of the respective rotational parts P1 to P4 at the respective speed stages are represented by the ordinates of the intersections of the straight lines L1 to L3 corresponding to the respective speed stages and the ordinates l1 to l4.

[0107] In the first gear, the second engagement member CL2 and the third engagement member B1 are engaged, and the first engagement member CL1 is released. As a result, the rotation speed of the input member IN is the same as that of the first rotational portion P1, and the rotation speed of the fourth rotational portion P4 is zero, so that the straight line L1 corresponding to the first gear is a straight line passing through the point X3 and the point X2. The rotation speed of the output member OUT is the ordinate r1 of the intersection of the straight line L1 and the longitudinal line l3. Therefore, when the rotation speed of the input member IN is rin, the speed ratio of the first gear is rin / r1.

[0108] In the second gear, the first engagement member CL1 and the third engagement member B1 are engaged, and the second engagement member CL2 is released. As a result, the rotation speeds of the input member IN and the second rotational portion P2 are the same, and the rotation speed of the fourth rotational portion P4 is zero, so that the straight line L2 corresponding to the second gear is a straight line passing through the points X1 and X2, and having a greater inclination than the straight line L1. The rotation speed of the output member OUT is the ordinate of the intersection of the straight line L2 and the longitudinal line l3, i.e., r2. Therefore, when the rotation speed of the input member IN is rin, the speed ratio of the second gear is rin / r2. Since r2 is greater than r1, the speed ratio of the second gear is smaller than the speed ratio of the first gear.

[0109] In the third gear, the first engagement member CL1 and the second engagement member CL2 are engaged, and the third engagement member B1 is released. As a result, the rotation speeds of the input member IN, the first to fourth rotational portions P1 to P4, and the output member OUT are the same, so that the straight line L3 corresponding to the third gear is a straight line passing through the point X3 and the point X1, and the inclination is zero. Since the rotation speeds of the input member IN and the output member OUT are the same, the speed ratio of the third gear is 1, which is smaller than the speed ratios of the first gear and the second gear.

[0110] Therefore, since three speed stages can be realized in the unit 100, the step ratio is reduced compared with the unit with two-speed forward movement, and the shock during the speed change can be suppressed to be smaller than that of the unit with two-speed forward movement. In addition, since the first to third gears can be used for low speed, medium speed, and high speed, respectively, an appropriate speed ratio can be set according to the speed range.

[0111] In addition, the speed ratio is 1 in the third gear. That is, since all the rotating parts P1 to P4 constituting the gear device 2 rotate at the same rotation speed, the power transmission loss caused by the rotation difference between the rotating parts can be reduced. Since the third gear for high-speed cruising is frequently used, by achieving a speed ratio of 1 in the third gear, a high power efficiency improvement effect can be obtained.

[0112] Next, modifications of the embodiment of the present invention will be described.

[0113] Figure 4A It is a skeleton diagram of a unit 100 according to a modified example.

[0114] The first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 are Figure 1 The unit 100 shown is identical to the single pinion planetary gear mechanism.

[0115] In the unit 100, the first rotating part P1 is composed of the first sun gear S1 and the second sun gear S2, the second rotating part P2 is composed of the second planetary carrier C2, the third rotating part P3 is composed of the first planetary carrier C1 and the second inner ring gear R2, and the fourth rotating part P4 is composed of the first inner ring gear R1.

[0116] Moreover, one side of the first engaging component CL1 is connected to the input component IN, the other side of the first engaging component CL1 is connected to the second planetary carrier C2 which is the second rotating part P2, one side of the second engaging component CL2 is connected to the input component IN, the other side of the second engaging component CL2 is connected to the first sun gear S1 and the second sun gear S2 which are the first rotating part P1, one side of the third engaging component B1 is connected to the first internal gear ring R1 which is the fourth rotating part P4, and the other side of the third engaging component B1 is fixed to the housing 1.

[0117] like Figure 4B As shown, one side of the second engagement member CL2 may be connected to the input member IN via a connecting member M passing through the inner peripheral side of the gear device 2 .

[0118] according to Figure 4A , Figure 4B In the illustrated modification, since the first to third engagement members CL1, CL2, B1 are respectively arranged axially outside the gear device 2, the layout freedom of the first to third engagement members CL1, CL2, B1 is increased, and the axial dimension of the unit 100 can be reduced.

[0119] Furthermore, when viewed in the axial direction, the first to third engagement members CL1, CL2, and B1 can be overlapped with the gear device 2. When the above members are overlapped, the radial dimension of the unit 100 can be reduced.

[0120] Furthermore, one side of the first engagement member CL1 and one side of the second engagement member CL2 can be made common (integrated parts), thereby reducing the number of parts of the unit 100 .

[0121] Card table and Figure 2The same engagement table as shown in FIG. 1 is used. By changing two of the first to third engagement components CL1, CL2, and B1 that are engaged, three speed stages can be achieved. Since the inter-stage ratio is reduced, an appropriate speed ratio can be set according to the speed range. In addition, since the speed ratio is 1 in the third gear, the power transmission loss caused by the rotation difference between the rotating parts can be reduced.

[0122] Since only one engagement member is released in any speed stage, even when the first to third engagement members CL1, CL2, B1 that generate traction torque are used, mechanical loss can be suppressed and the power efficiency of the vehicle equipped with the unit 100 can be improved.

[0123] In addition, according to Figure 4B The modified example shown can adopt the following layout, that is, the first engaging part CL1 and the second engaging part CL2 are dispersedly arranged on both sides of the axial direction relative to the gear device 2, instead of arranging the second engaging part CL2 on the inner peripheral side of the first engaging part CL1. As a result, as the actuator of the first to third engaging parts CL1, CL2, B1, it is convenient to adopt an actuator that is easily restricted by the layout, and the freedom of choice of the actuator is improved.

[0124] Collinearity plot and Figure 3 The collinear plots shown are identical.

[0125] Figure 5A It is a skeleton diagram of the unit 100 according to another modified example.

[0126] and Figure 1 Unlike the unit 100 shown in FIG. 1 , the first planetary gear mechanism PG1 is a double pinion planetary gear mechanism. That is, the first planet carrier C1 rotatably supports a plurality of inner pinions (not shown) meshing with the first sun gear S1 and a plurality of outer pinions (not shown) meshing with the first inner ring gear R1. In addition, the plurality of inner pinions mesh with the plurality of outer pinions. The second planetary gear mechanism PG2 is a double pinion planetary gear mechanism. Figure 1 The unit 100 shown is identical to the single pinion planetary gear mechanism.

[0127] In the unit 100, the first rotating part P1 is composed of the first sun gear S1 and the second sun gear S2, the second rotating part P2 is composed of the first planetary carrier C1, the third rotating part P3 is composed of the first inner ring gear R1 and the second inner ring gear R2, and the fourth rotating part P4 is composed of the second planetary carrier C2.

[0128] Moreover, one side of the first engaging component CL1 is connected to the input component IN, the other side of the first engaging component CL1 is connected to the first planetary carrier C1 which is the second rotating part P2, one side of the second engaging component CL2 is connected to the input component IN, the other side of the second engaging component CL2 is connected to the first sun gear S1 and the second sun gear S2 which are the first rotating part P1, one side of the third engaging component B1 is connected to the second planetary carrier C2 which is the fourth rotating part P4, and the other side of the third engaging component B1 is fixed to the housing 1.

[0129] according to Figure 5A In the illustrated modification, since the first to third engagement members CL1, CL2, B1 are respectively arranged axially outside the gear device 2, the layout freedom of the first to third engagement members CL1, CL2, B1 is increased, and the axial dimension of the unit 100 can be reduced.

[0130] Furthermore, when viewed in the axial direction, the first to third engagement members CL1, CL2, and B1 can be overlapped with the gear device 2. When the above members are overlapped, the radial dimension of the unit 100 can be reduced.

[0131] Furthermore, one side of the first engagement member CL1 and one side of the second engagement member CL2 can be made common (integrated parts), thereby reducing the number of parts of the unit 100 .

[0132] Card table and Figure 2 The same engagement table as shown in FIG. 1 is used. By changing two of the first to third engagement components CL1, CL2, and B1 that are engaged, three speed stages can be achieved. Since the inter-stage ratio is reduced, an appropriate speed ratio can be set according to the speed range. In addition, since the speed ratio is 1 in the third gear, the power transmission loss caused by the rotation difference between the rotating parts can be reduced.

[0133] Since only one engagement member is released in any speed stage, even when the first to third engagement members CL1, CL2, B1 that generate traction torque are used, mechanical loss can be suppressed and the power efficiency of the vehicle equipped with the unit 100 can be improved.

[0134] Figure 5B yes Figure 5A Since the first planetary gear mechanism PG1 is a double pinion planetary gear mechanism, the first ring gear R1 is arranged between the first sun gear S1 and the first carrier C1 on the collinear diagram. That is, the second rotating element and the third rotating element are opposite to those of the single pinion planetary gear mechanism.

[0135] The intervals between the rotating parts constituting the first to fourth rotating parts P1 to P4 and the longitudinal lines l1 to l4 are Figure 3 Although the illustrated situations are different, the connection relationship between the first to fourth rotational portions P1 to P4 and the first to third engagement members CL1 , CL2 , and B1 is the same, and therefore substantially the same diagram can be obtained as a collinear diagram.

[0136] Next, the effects of the embodiment of the present invention will be described.

[0137] (1) In an embodiment of the present invention,

[0138] exist Figure 1 , Figure 4A , Figure 4B , Figure 5A In the example shown, unit 100 has:

[0139] Input component IN;

[0140] Output component OUT;

[0141] The gear device 2 is configured by connecting the rotating parts of the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2 at two locations, and a first rotating part P1, a second rotating part P2, a third rotating part P3, and a fourth rotating part P4 are arranged in sequence on the collinear diagram ( Figure 3 Figure 4C Figure 5B ).

[0142] The input member IN can be connected to either or both of the first rotating portion P1 and the second rotating portion P2.

[0143] The output component OUT is connected to the third rotating part P3.

[0144] The fourth rotating portion P4 can switch between a rotating state and a non-rotating state.

[0145] According to the present embodiment, three speed stages can be realized by switching the connection destination of the input member IN (either one or both of the first rotating part P1 and the second rotating part P2) and the rotation state of the fourth rotating part P4. Since the inter-stage ratio is reduced, an appropriate speed ratio can be set according to the speed range. In addition, since the speed ratio is 1 in the third gear, the power transmission loss caused by the rotation difference between the rotating parts can be reduced.

[0146] (2) The gear device 2 can be Figure 1 , Figure 4A , Figure 4B As shown.

[0147] exist Figure 1 , Figure 4A , Figure 4B In the example shown,

[0148] The first planetary gear mechanism PG1 is a single pinion planetary gear mechanism having a first sun gear S1, a first planet carrier C1, and a first inner ring gear R1, and the first planet carrier C1 is arranged between the first sun gear S1 and the first inner ring gear R1 on the collinear diagram ( Figure 3 ).

[0149] The second planetary gear mechanism PG2 is a single pinion planetary gear mechanism having a second sun gear S2, a second planet carrier C2, and a second inner ring gear R2, and the second planet carrier C2 is arranged between the second sun gear S2 and the second inner ring gear R2 on the collinear diagram ( Figure 3 ).

[0150] The first rotating part P1 is composed of the first sun gear S1 and the second sun gear S2.

[0151] The second rotating part P2 is formed by the second planet carrier C2.

[0152] The third rotating part P3 is formed by the combination of the first planet carrier C1 and the second inner ring gear R2.

[0153] The fourth rotational portion P4 is formed by the first ring gear R1.

[0154] exist Figure 5A In the example shown,

[0155] The first planetary gear mechanism PG1 is a single pinion planetary gear mechanism having a first sun gear S1, a first planet carrier C1, and a first inner ring gear R1, and the first planet carrier C1 is arranged between the first sun gear S1 and the first inner ring gear R1 on the collinear diagram ( Figure 5B ).

[0156] The second planetary gear mechanism PG2 is a double pinion planetary gear mechanism having a second sun gear S2, a second inner ring gear R2, and a second planet carrier C2, and the second inner ring gear R2 is arranged between the second sun gear S2 and the second planet carrier C2 on the co-linear diagram ( Figure 5B ).

[0157] The first rotating part P1 is composed of the first sun gear S1 and the second sun gear S2.

[0158] The second rotating part P2 is formed by the first planet carrier C1.

[0159] The third rotating part P3 is composed of the first inner ring gear R1 and the second inner ring gear R2.

[0160] The fourth rotation point P4 is formed by the second carrier C2.

[0161] (3) The connection destination of the input member IN and the switching of the rotation state of the fourth rotation portion P4 can be realized by the first to third engagement members CL1, CL2, and B1.

[0162] exist Figure 1 , Figure 4A , Figure 4B , Figure 5A In the example shown,

[0163] The unit 100 has:

[0164] A first engaging member CL1;

[0165] A second engaging member CL2;

[0166] The third engaging part B1.

[0167] One side of the first engagement member CL1 is connected to the input member IN.

[0168] The other side of the first engagement member CL1 is connected to the second rotational portion P2.

[0169] One side of the second engagement member CL2 is connected to the input member IN.

[0170] The other side of the second engagement member CL2 is connected to the first rotation portion P1.

[0171] One side of the third engaging member B1 is connected to the fourth rotating portion P4.

[0172] The other side of the third engagement member B1 is fixed.

[0173] According to this structure, when viewed in the axial direction, the first to third engagement members CL1, CL2, and B1 can be overlapped with the gear device 2. When the above members are overlapped, the radial dimension of the unit 100 can be reduced.

[0174] (4) Figure 1 , Figure 4A , Figure 4B , Figure 5A In the example shown, the first to third engagement members CL1, CL2, B1 are respectively arranged axially outside the gear device 2. This increases the degree of freedom in layout of the first to third engagement members CL1, CL2, B1 and reduces the axial dimension of the unit 100.

[0175] (5) Figure 1 , Figure 4BIn the example shown, one side of the first engagement member CL1 or one side of the second engagement member CL2 is connected to the input member IN via the connection member M passing through the inner circumference of the gear device 2. As a result, a layout can be adopted in which the first engagement member CL1 and the second engagement member CL2 are dispersedly arranged on both sides of the axial direction with respect to the gear device 2, rather than one being arranged on the inner circumference of the other. As the actuator of the first to third engagement members CL1, CL2, B1, an actuator that is easily restricted by the layout can be easily adopted, and the freedom of selection of the actuator is improved.

[0176] (6) Figure 1 , Figure 4A , Figure 4B , Figure 5A In the example shown, three speed stages ( Figure 2 Since only one engagement member is released in any gear stage, even when the first to third engagement members CL1, CL2, and B1 are engagement members that generate traction torque, mechanical loss can be suppressed and the power efficiency of the vehicle equipped with the unit 100 can be improved.

[0177] (7) Figure 1 , Figure 4A , Figure 4B , Figure 5A In the example shown, one side of the first engagement member CL1 and one side of the second engagement member CL2 may be formed of an integrated component. This can reduce the number of components of the unit 100.

[0178] As mentioned above, although the embodiment of the present invention has been described, the above embodiment is only an application example of the present invention, and it is not intended that the technical scope of the present invention is limited to the specific structure of the above embodiment.

[0179] Figure 1 , Figure 4A , Figure 4B , Figure 5A The illustrated block diagram is a part of an application example of the present invention, and the block diagram of the unit to which the present invention is applied is not limited thereto.

[0180] Figure 6 to Figure 32 This is an example of a skeleton diagram of a unit included in the technical scope of the invention of claims 1, 4, 7, and 8. Figure 1 The same reference numerals are used for the same components in the embodiments shown. Figure 2 In addition, since the connection relationship between the first to fourth rotation parts P1 to P4 and the first to third engagement parts CL1, CL2, B1 is the same in each collinear diagram, it is actually the same as Figure 3Same picture.

[0181] In addition, as the first planetary gear mechanism PG1 and the second planetary gear mechanism PG2, either a single pinion planetary gear mechanism or a double pinion planetary gear mechanism may be used.

[0182] Description of Reference Numerals

[0183] 1 housing; 2 gear device; 100 units; CL1 first engaging component; CL2 second engaging component; B1 third engaging component; S1 first sun gear; S2 second sun gear; C1 first planetary carrier; C2 second planetary carrier; R1 first internal ring gear; R2 second internal ring gear; M connecting component; P1 first rotating part; P2 second rotating part; P3 third rotating part; P4 fourth rotating part; IN input component; OUT output component; PG1 first planetary gear mechanism; PG2 second planetary gear mechanism.

Claims

1. A unit, characterized in that have: Input components; Output components; A gear device, wherein the rotating parts of the first planetary gear mechanism and the second planetary gear mechanism are connected at two locations, and a first rotating part, a second rotating part, a third rotating part, and a fourth rotating part are arranged in order on a collinear diagram; The input member is connectable to the first rotating part and is connectable to the second rotating part. The output member is connected to the third rotating part, The fourth rotating portion can switch between a rotating state and a non-rotating state.

2. The unit according to claim 1, characterized in that The first planetary gear mechanism is a planetary gear mechanism having a first rotating member, a second rotating member, and a third rotating member, and the second rotating member is arranged between the first rotating member and the third rotating member on a collinear diagram, The second planetary gear mechanism is a planetary gear mechanism having a fourth rotating member, a fifth rotating member, and a sixth rotating member, and the fifth rotating member is arranged between the fourth rotating member and the sixth rotating member on a collinear diagram. The first rotating part is composed of the first rotating part and the fourth rotating part. The second rotating part is constituted by the fifth rotating member, The third rotating part is formed by combining the second rotating part and the sixth rotating part. The fourth rotating portion is constituted by the third rotating member.

3. A unit according to claim 1 or 2, characterized in that have: a first engaging member; a second engaging member; a third engaging member; One side of the first engaging member is connected to the input member. The other side of the first engaging member is connected to the second rotating portion. One side of the second engagement member is connected to the input member. The other side of the second engaging member is connected to the first rotating portion. One side of the third engaging member is connected to the fourth rotating portion. The other side of the third engagement member is fixed.

4. The unit according to claim 3, characterized in that The first to third engagement members are respectively arranged on the axially outer side of the gear device.

5. The unit according to claim 3, characterized in that The one side of the first engagement member or the one side of the second engagement member is connected to the input member via a connection member passing through the inner peripheral side of the gear device.

6. The unit according to claim 3, characterized in that Three speed change stages are achieved by changing the two members that are engaged among the first to third engaging members.

7. The unit according to claim 3, characterized in that The one side of the first engaging member and the one side of the second engaging member are formed by an integrated component.

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