Electric lathe and vehicle drive device

Abstract

An electric lathe comprising a rotor rotatably supported radially inside a stator via a rotor support element, which has winding end sections on both sides in an axial direction, and which is constructed such that oil is supplied from an axially to a first direction-facing side, which is a side in the axial direction of the rotor, to the winding end sections on both sides in the axial direction, with: an oil collection section provided at one end of the rotor support element, which is arranged on the side facing axially to the first direction; and a communication oil channel which is provided in at least either the rotor and / or the rotor support element and communicates with a first opening and a second opening of the oil collection section, wherein the first opening is radially open on the inside of the winding end section on the side axially pointing towards the first direction, and the second opening is radially open on the inside of the winding end section on the side pointing axially towards the second direction, which is the other side in the axial direction of the rotor.

Description

TECHNICAL AREA

[0001] The present invention relates to electric lathes having a rotor rotatably supported radially inside a stator via a rotor support element, which has winding end sections on both sides in the axial direction, and which are constructed such that oil is supplied from an axially to a first direction-facing side, which is a side in the axial direction of the rotor, to the winding end sections on both sides in the axial direction, and to vehicle drive devices having such an electric lathe. BACKGROUND TO THE STATE OF THE TECHNOLOGY

[0002] An electric lathe described below in patent document 1 is already known as an electric lathe having the construction described above. The electric lathe (a generator motor 2) of patent document 1 has a recess 10 configured to be open at a side surface 6a located on an axially oriented side of the rotor 6, and has a communication hole 12 that connects a bottom section 10a of the recess 10 to another side surface 6b located on an axially oriented side of the rotor. In this electric lathe, oil is supplied to the recess 10 from an end piece of a nozzle 11 located on the axially oriented side of the rotor.The oil collected in the recess 10 flows through the opening of the recess 10 on the axial side of the rotor (facing first direction) and falls onto a winding end section (a winding section 8) on the axial side (facing first direction), which is arranged radially on the outside of the recess 10, thereby cooling the winding end section. The oil collected in the recess 10 can also be discharged from the axial side of the rotor (facing second direction) through the communication hole 12 and can fall onto a winding end section on the axial side (facing second direction), which is arranged radially on the outside of the recess 10, thereby cooling the winding end section.

[0003] In the electric lathe described in patent document 1, however, the opening area of ​​the communication hole 12 on the axial side of the rotor facing the second direction is significantly smaller than that of the recess 10 on the axial side facing the first direction. Thus, most of the oil accumulated in the recess 10 flows through the opening of the recess 10 on the axial side facing the first direction of the rotor, and it is less likely that the oil will be supplied to the axial side facing the second direction through the communication hole 12. Accordingly, it is less likely that the cooling oil will be supplied to the cooling end section on the axial side facing the second direction, and the winding end section on the axial side facing the second direction may not be adequately cooled. Related state of the art documents, patent documents Patent document 1: Japanese published patent application JP 2008-007023 A Patent document 2: DE 34 90 363 T5 Patent document 3: US 2011 / 0 121 692 A1

[0004] DE 34 90 363 T5 discloses an electric lathe having a rotor with a bearing at each end, each bearing being supported on a rotor support element on a housing. Furthermore, a chamber is provided inside the rotor, to which a fluid is supplied by means of a pump via pipes and inlet openings.

[0005] US patent 2011 / 0 121 692 A1 discloses a vehicle propulsion device with a hybrid drive unit and a housing with a radially extending support wall. The housing contains an electric lathe and a torque converter. DISCLOSURE OF THE INVENTION Problem to be solved by the invention

[0006] Therefore, the object of the invention is to implement a design in which it is possible to adequately cool the winding end section on the axial side facing the second direction in addition to the winding end section on the axial side facing the first direction in electric lathes designed in such a way that the oil is supplied from the axial side of the rotor facing the first direction to the winding end sections. Solution to the task

[0007] This problem is solved by an electric lathe with the features of claim 1. Advantageous further developments are the subject of the dependent claims.

[0008] It should be noted that the term "electric lathe" is used here as a concept that includes a motor (an electric motor), a generator (an electric generator) and a motor-generator that functions as both a motor and a generator when required.

[0009] According to the characteristic design described above, the oil supplied from the axial side of the rotor, facing the first direction, can be collected and stored by the oil collection section provided at the end of the rotor support element on the axial side facing the first direction. The stored oil is discharged from the first and second openings through the communication oil channel, which is provided at least on the rotor and / or the rotor support element. Since the cross-sectional area of ​​the flow path of the communication oil channel, which connects the oil collection section to the first and second openings, can be made to be approximately equal to the area of ​​the communication oil channel opening, the quantity of oil discharged from the first opening can be made to be approximately equal to that discharged from the second opening.Furthermore, the first and second openings are radially open on the inside of the winding end sections, both on the side facing axially to the first direction and on the side facing axially to the second direction. Accordingly, approximately the same amount of oil is supplied to the winding end sections on both the side facing axially to the first direction and the side facing axially to the second direction, thus ensuring adequate cooling of these winding end sections.

[0010] Thus, according to the aforementioned characteristic design of the electric lathe, which is designed so that the oil is supplied from the axial side of the rotor pointing towards the first direction to the winding end sections, the design can be implemented in which it is possible to adequately cool the winding end section on the axial side pointing towards the second direction in addition to the winding end section on the axial side pointing towards the first direction.

[0011] It is preferred that the rotor support element has a cylindrical axially projecting section that projects towards the axial side facing the first direction, a recess is formed such that it is deepened towards the axial side facing the second direction with respect to a side end surface of the axially projecting section which is arranged on the axial side facing the first direction and is open on an inner side in a radial direction, and a cover section is provided such that it is in contact with and fixed to one side end surface and covers the recess on the axial side facing the first direction, and the oil collection section is formed as a pocket-shaped space defined by the recess and the cover element.

[0012] According to the aforementioned design, the oil collection section can be implemented with a relatively simple structure, utilizing the recess provided on one end face of the axially projecting section and the cover element that covers the recess on the side facing axially. Furthermore, the area occupied by the oil collection section can be reduced compared to, for example, a design where a component forming the oil collection section is provided separately on the end face of the rotor support element located on the side facing axially. Thus, an increase in the overall size of the electric lathe can be avoided.

[0013] It is preferred that the communication oil channel has a common oil channel extending from the oil collecting section, an oil channel branching off from the common oil and communicating with the first opening, and an oil channel branching off from the common oil channel and communicating with the second opening.

[0014] According to the setup described above, the oil channel communicating with the first opening of the oil collection section and the oil channel communicating with the second opening of the oil collection section are formed using the common oil channel section. This can relatively simplify the overall design of the communicating oil channel. Furthermore, in the aforementioned setup, by appropriately incorporating the branch section between the oil channel communicating with the first opening and the oil channel communicating with the second opening, the oil can be distributed evenly to the first and second openings, regardless of the oil collection state of the oil collection section. Thus, the winding end sections can be cooled uniformly on both the axially oriented side and the axially oriented side.

[0015] It is preferred that the rotor support element has a cylindrical inner support section that supports the rotor radially from the inside and an annular single-sided support section that extends radially outward from the inner support section and supports the rotor from the axial side facing the first direction; a first oil channel is configured to extend axially inside the single-sided support section from the oil collecting section to the axial side facing the second direction; a second oil channel is configured to branch off from the first oil channel and extend radially outward inside the single-sided support section and communicate with the first opening, which is open in an outer circumferential surface of the single-sided support section; and a third oil channel is configured to extend further from the first oil channel to the axial side facing the second direction.and is in communication with the second opening, which is open at an end face of the rotor or rotor support element located on the side facing axially towards the second direction.

[0016] According to the design described above, the communication oil channel, which is configured to include the common oil channel extending from the oil collecting section and the two oil channels branching off from the common oil channel and communicating with the first and second openings respectively, can be suitably formed by the first, second, and third oil channels. Furthermore, the use of the design in which both the first and second oil channels are formed together in the single-sided support section is advantageous in that machining to form these oil channels can be carried out relatively easily.

[0017] It is preferred that the third oil channel is formed along a connecting surface between an inner circumferential surface of the rotor and an outer circumferential surface of the inner support section.

[0018] According to the above-described design, the third oil channel can be formed simply and appropriately by machining one or both of the circumferential surfaces, i.e., the inner circumferential surface of the rotor and the outer circumferential surface of the rotor support section, in such a way as to form a groove extending in the axial direction.

[0019] Furthermore, in the above-described setup, even if the rotor has a large number of permanent magnets arranged in such a way that they are distributed in the circumferential direction and extend along the axial direction, the influence of the third oil channel on a magnetic field formed by the permanent magnets can be reduced.

[0020] It is preferred that the electric lathe further comprises: a ring-shaped rotor holding element arranged to be in contact with the rotor from the axial to the second direction-facing side and to hold the rotor from the axial to the second direction-facing side; and a crimped section which presses the rotor holding element, which is inserted with the inner support section, from the axial to the second direction-facing side, wherein the crimped section serves as a guide section which directs the oil supplied by the third oil channel to the winding end section.

[0021] According to the design described above, the rotor holding element, which is inserted with the inner support section, can be pressed through the crimped section from the axially oriented side to the second direction, and the rotor can be held appropriately against the rotor support element. Furthermore, the crimped section is designed to act as a guide section, efficiently directing the oil supplied by the third oil channel to the winding end sections. This allows for even more efficient cooling of the winding end sections.

[0022] It is preferred that the communication oil channel independently has an oil channel that communicates with the first opening of the oil collecting section and the oil channel that communicates with the second opening of the oil collecting section.

[0023] Since, according to the above-described design, the oil channel that communicates with the first opening of the oil collection section and the oil channel that communicates with the second opening of the oil collection section can be designed independently, the entire communication oil channel can be designed with relatively high flexibility.

[0024] A vehicle drive device with the electric lathe is the subject of claim 8.

[0025] According to the characteristic design described above, the friction engagement device is arranged inside the housing, which is formed by using at least part of the rotor support section, and the housing is filled with oil. Thus, the friction engagement device can be efficiently cooled by this oil.

[0026] In a setup where the housing is fluid-tight and filled with oil at a predetermined pressure or higher, it is difficult to directly channel the oil radially outward and use it to cool the winding end sections. However, in the characteristic setup described above, the support wall located on the axial side of the rotor is equipped with an oil flow section through which the oil flows to supply the winding end sections. Furthermore, an oil collection section is provided at the end of the rotor support element located on the axial side. Thus, the oil flowing through the oil flow section can be collected by the oil collection section and used to cool the winding end sections on both sides in the axial direction.Thus, even if the oil in the housing cannot be guided directly radially outwards, the winding end sections on both sides can be cooled appropriately in the axial direction. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 shows a schematic representation of a schematic setup of a hybrid drive device according to an exemplary embodiment. Fig. Figure 2 shows a partial cross-sectional view of the hybrid drive device of the exemplary embodiment. Fig. Figure 3 shows a cross-sectional view of a main section of the hybrid drive device of the exemplary embodiment. Fig. Figure 4 shows a front view when the oil collection sections of the embodiment are viewed from a side pointing axially towards the first direction. Fig. Figure 5 shows a cross-sectional view of a main section, showing an example of a structure of cooling oil channels according to another embodiment. Fig. Figure 6 shows a cross-sectional view of a main section, showing an example of a structure of cooling oil channels according to another embodiment. Fig. Figure 7 shows cross-sectional views of a main section, including an example of a cooling oil channel structure according to another embodiment. BEST MODE FOR EXECUTING THE INVENTION

[0027] An embodiment of the present invention is described below with reference to the accompanying drawings. This embodiment is described in relation to an example in which an electric lathe of the present invention is applied to an electric lathe used as a drive power source for a vehicle in a hybrid drive system. Fig. Figure 1 shows a schematic representation of the structure of a hybrid drive device H according to the present embodiment. The hybrid drive device H is a drive device for hybrid vehicles that uses an internal combustion engine E and / or an electric lathe MG as a drive power source for the vehicle. The hybrid drive device H is designed as a hybrid drive device of the so-called single-motor parallel type. The hybrid drive device H according to the present embodiment is described in detail below. 1. Overall structure of the hybrid drive system

[0028] First, the overall structure of the hybrid drive device H of the present embodiment is explained. As this is shown in Fig. As shown in Figure 1, the hybrid drive unit H comprises: an input shaft I, which is drive-coupled to the internal combustion engine E as a first drive power source of the vehicle; the electric lathe MG as a second drive power source of the vehicle; a speed-changing mechanism TM; an intermediate shaft M, which is drive-coupled to the electric lathe MG and to a speed-changing mechanism TM; and an output shaft O, which is drive-coupled to the wheels W. The hybrid drive unit H further comprises: a clutch CL, which is designed to switch between the transmission and interruption of the transmission of drive power between the input shaft I and the intermediate shaft M; a counter-gear mechanism C; and an output differential gear unit DF. These components are housed in a casing (a drive unit casing) 1.

[0029] It should be noted that the term "drive-coupled" here refers to a state in which two rotating elements are coupled to each other in such a way that they are capable of transmitting a driving force between them. This term is used as a concept encompassing the state in which the two rotating elements are coupled to each other in such a way that they rotate together, or the state in which the two rotating elements are coupled to each other in such a way that they are capable of transmitting a driving force between them via one or more transmission elements. Such transmission elements include various elements that transmit rotation at the same speed or after a change in speed and include, for example, a shaft, a gear mechanism (transmission mechanism), a belt, a chain, etc. The term "driving force" is used here as a synonym for torque.In the present embodiment, the “axial direction”, the “radial direction” and the “circumferential direction” are defined on the basis of a rotational center axis of the input shaft I, the intermediate axis M and the electric lathe MG, which are arranged on the same axis.

[0030] The internal combustion engine E is a device powered by the combustion of fuel within the engine to generate kinetic energy. Various well-known internal combustion engines, such as a gasoline engine and a diesel engine, can be used as examples of the internal combustion engine E. In this example, an output shaft, such as a crankshaft, of the internal combustion engine E is drive-coupled to the input shaft I via a damper D. The input shaft I is drive-coupled to the electric lathe MG and the intermediate shaft M via the coupling CL, and the input shaft I is selectively drive-coupled to the electric lathe MG and the intermediate shaft M via the coupling CL. When the coupling CL is engaged, the internal combustion engine E is drive-coupled to the electric lathe MG via the input shaft I.When the clutch CL is in a disengaged state, the internal combustion engine E is disconnected from the electric lathe MG.

[0031] The electric lathe MG has a stator St and a rotor Ro and is capable of functioning as a motor (an electric motor) supplied with electrical energy to generate kinetic energy, and as a generator (an electric generator) supplied with kinetic energy to generate electrical energy. Thus, the electric lathe MG is electrically connected to an electricity storage device (not shown). In this example, a battery is used as the electricity storage device. It should be noted that using a capacitor, etc., as the electricity storage device is also preferred.The electric lathe MG is supplied with electrical energy from the battery to perform an energy-driven movement, or it is supplied with torque from the internal combustion engine E or with electrical energy generated by the vehicle's inertia to store the electrical energy in the battery. The rotor Ro of the electric lathe MG is coupled to the drive shaft M so that they rotate together. The intermediate shaft M is an input shaft (a speed-changing input shaft) of the speed-changing mechanism TM.

[0032] The speed-changing mechanism TM is a mechanism that changes the speed of the intermediate shaft M at a predetermined speed ratio in order to transmit the resulting rotation to a speed-changing output gear G. In the present embodiment, an automatically stepped speed-changing mechanism is used as such a mechanism. This mechanism is constructed to include single-drive and Ravigneaux-type gear mechanisms and a plurality of engagement devices, such as a clutch, a brake, and a one-way clutch (freewheel), and has a plurality of switching stages with different speed ratios that can be selected between them.It should be noted that an automatically stepped speed-changing mechanism with a different specific design, an automatically continuously variable speed-changing mechanism capable of continuously changing the speed ratio, a manually stepped speed-changing mechanism with a multitude of switching stages with different speed ratios that can be switched between, etc., can all be used as the speed-changing mechanism TM. The speed-changing mechanism TM changes the speed of the intermediate shaft M at a predetermined speed ratio at any given time and converts the torque from this speed to transmit the resulting rotation and torque to the speed-changing output gear G.

[0033] The speed-changing output gear G is drive-coupled to the output differential gear unit DF via the counter-gear mechanism C. The output differential gear unit DF is drive-coupled to the wheels W via the output shaft O and distributes and transmits the rotation and torque input to the output differential gear unit DF to the two wheels W, namely the right and left wheels W. Thus, the hybrid drive device H can transmit the torque from either the internal combustion engine E and / or the electric motor MG to the wheels W to cause the vehicle to move.

[0034] It should be noted that the hybrid drive unit H of the present embodiment has a multi-axis design in which the input shaft I and the intermediate shaft M are arranged on the same axis, and the output shaft O is arranged on a different axis than those of the input shaft I and the intermediate shaft M, such that they extend parallel to each other. Such a design is suitable for the structure of the hybrid drive unit H, which is mounted, for example, on FF-type vehicles (front-engine, front-wheel-drive vehicles). 2. Construction of each section of the hybrid drive device

[0035] The construction of each section of the hybrid drive device H according to the present embodiment is described below. As shown in Fig. As shown in Figure 2, the housing 1 contains at least the electric lathe MG and the coupling CL. The housing 1 has the following: a housing circumferential wall 2, which covers the outer circumferences of the components contained in the housing 1, such as the electric lathe MG and the speed-changing mechanism TM; a first support wall 3, which has an opening in the housing circumferential wall 2 on the side facing axially towards the second direction A2 (the side of the internal combustion engine E, the right side in Figure 2). Fig. 2; the same applies in the description set out below); and a second support wall 8, which is located between the electric lathe MG and the speed-changing mechanism TM in the axial direction on a side pointing in an axial direction to the first direction A1 (on the opposite side from the internal combustion engine E, the left side in Fig. 2; the same applies in the description set out below) with respect to the first support wall 3. Although this is not shown in the drawing, the housing 1 further has an end support wall that closes one end of the housing circumferential wall 2, which is located on the other side in the axial direction.

[0036] The first support wall 3 is shaped such that it extends at least in the radial direction, and in the present embodiment, it extends in both the radial and circumferential directions. A through-hole in the axial direction is formed in the first support wall 3, and the input shaft I, which is inserted through the through-hole, is inserted into the housing 1 through the first support wall 3. The first support wall 3 is coupled to a hub-shaped cylindrical section 4, which projects towards the side facing the axial direction A1. The cylindrical section 4 is integrally coupled to the first support wall 3.The first support wall 3 is arranged on the axial side facing the second direction A2 with respect to the electric lathe MG and the coupling CL, and more precisely, it is adjacent to a rotor support element 30, which supports the rotor Ro of the electric lathe MG, on the axial side facing the second direction A2, with a predetermined gap between the first support wall 3 and the rotor support element 30. The first support wall 3 rotatably supports the rotor support element 30 on the axial side facing the second direction A2 of the electric lathe MG.

[0037] The second support wall 8 is shaped such that it extends at least in the radial direction, and in the present embodiment, it extends in both the radial and circumferential directions. A through-hole in the axial direction is formed in the second support wall 8, and the intermediate shaft M, which is inserted through the through-hole, extends through the second support wall 8. The second support wall 8 is coupled to a hub-shaped cylindrical section 9, which projects towards the side facing the second direction A2 in the axial direction. The cylindrical section 9 is integrally coupled to the second support wall 8.The second support wall 8 is arranged on the side axially facing the first direction A1 with respect to the electric lathe MG and the coupling CL, and more precisely, is arranged adjacent to the rotor support element 30 on the side axially facing the first direction A1, with a predetermined gap between the second support wall 8 and the rotor support element 30. The second support wall 8 rotatably supports the rotor support element 30 on the side of the electric lathe MG axially facing the first direction A1. In the present embodiment, the second support wall corresponds to a "support wall" in the present invention.

[0038] An oil pump 18 is housed in a pump chamber formed within the second support wall 8. In the present embodiment, the oil pump 18 is an internal gear pump with an inner rotor and an outer rotor. The inner rotor of the oil pump 18 is coupled to the rotor support element 30 at its radial center by a wedge such that it rotates together with it. The oil pump 18 draws oil from an oil pan (not shown) in accordance with the rotation of the rotor support element 30 and discharges the drawn-in oil to supply the clutch CL, the speed-changing mechanism TM, the electric lathe MG, etc. It should be noted that oil channels are formed within the second support wall 8, the intermediate shaft M, etc., and the oil discharged by the oil pump 18 is supplied to each section requiring oil via a hydraulic control device (not shown) and the oil channels.In the present embodiment, a portion of the oil in the pump chamber can escape step by step in the axial direction through a gap between the through-hole in the second support wall 8 and the rotor support element 30 and can be supplied to the electric lathe MG. The oil thus supplied to each section either lubricates or cools the section, or both lubricates and cools the section. The oil in the present embodiment acts as a "lubricating coolant" that can function as both a "lubricant" and a "coolant".

[0039] The input shaft I is a shaft element for transmitting torque from the internal combustion engine E to the hybrid drive device H. The input shaft I is drive-coupled to the internal combustion engine E at its end, which is located on the axial side facing the second direction A2. The input shaft I is designed to extend through the first support wall 3 and is, as shown in Fig. As shown in Figure 2, the output shaft of the internal combustion engine E is driven via the damper D on the axial side of the first support wall 3, facing the second direction A2, such that it rotates together with the output shaft. A sealing element 66 is provided in a region between the outer circumferential surface of the input shaft I and the inner circumferential surface of the through-hole provided in the first support wall 3 to form a fluid-tight seal between them and to suppress oil leakage to the axial side facing the second direction A2 (the side of the damper D).

[0040] In the present embodiment, an axially extending hole is formed in the radial center of one end of the input shaft I, located on the side facing the first direction A1. An end of the intermediate shaft M, which is arranged on the same axis as the input shaft I, is inserted axially into the hole, with the end located on the side facing the second direction A2. The end of the input shaft I located on the side facing the first direction A1 is coupled to a coupling hub 21, which extends radially outward. In the present embodiment, the rotor support element 30 is configured to cover the circumference of the coupling CL, as described below, and a housing (a coupling housing) in which the coupling CL is accommodated is formed by the rotor support element 30.In this example, the housing (the clutch housing) is formed by using the entire rotor support element 30. When the term "rotor support element 30" is used below in the description, the term includes the meaning of "housing (the clutch housing)."

[0041] The intermediate shaft M is a shaft element for transmitting either the torque of the electric lathe MG and / or the torque of the internal combustion engine E via the coupling CL to the speed-changing mechanism TM. The intermediate shaft M is coupled to the rotor support element 30 by a key. As shown in Fig. As shown in Figure 2, the intermediate shaft M is designed to extend through the second support wall 8. As described above, a through-hole is formed in the axial direction at the radial center of the second support wall 8, and the intermediate shaft M extends through the second support wall 8 via this through-hole. The intermediate shaft M is supported in the radial direction so that it is rotatable with respect to the second support wall 8. In the present embodiment, the intermediate shaft M has a plurality of oil channels, including a supply oil channel 15 and a discharge oil channel 16. The supply oil channel 15 extends in the axial direction and also extends radially at a predetermined position in the axial direction such that it communicates with a hydraulic oil chamber H1 of the coupling CL and is open at the outer circumferential surface of the intermediate shaft M.The delivery oil channel 16 extends in the axial direction and is open at an end face of the intermediate shaft M, which is located on the side pointing axially towards the second direction A2.

[0042] The clutch CL is a friction engagement device designed to switch between transmitting and interrupting the transmission of the drive force between the input shaft I and the intermediate shaft M, as described above, and to selectively couple the internal combustion engine E to the electric lathe MG. In the present embodiment, the clutch CL is constructed as a wet multi-disc clutch mechanism. As is shown in Fig. As shown in Figure 3, the clutch CL has a clutch hub 21, a clutch drum 22, a plurality of friction plates 24, and a piston 25. The clutch hub 21 is coupled to the end of the input shaft I on the side axially facing direction A1, such that it rotates together with the input shaft I. The clutch drum 22 is formed integrally with the rotor support element 30 and is coupled to the intermediate shaft M via the rotor support element 30, such that it rotates together with the intermediate shaft M. The friction plates 24 are provided between the clutch hub 21 and the clutch drum 22 and have hub-side and drum-side friction plates in pairs.

[0043] In the present embodiment, the hydraulic oil chamber H1 is formed in a fluid-tight state between the rotor support element 30, which is integrally formed with the clutch drum 22, and the piston 25. Pressurized oil, supplied by the oil pump 18 and adjusted to a predetermined oil pressure by the (not shown) hydraulic control device, is fed to the hydraulic oil chamber H1 through the supply oil channel 15, which is formed in the intermediate shaft M. The engagement and disengagement of the clutch CL is controlled according to the oil pressure supplied by the hydraulic oil chamber H1. A circulation oil chamber H2 is formed on the opposite side of the piston 25 from the hydraulic oil chamber H1.The pressurized oil, which is delivered by the oil pump 18 and set to a predetermined oil pressure by the (not shown) hydraulic control device, is supplied to the circulation oil chamber H2 through a circulation oil channel 48 which is formed in the rotor support element 30.

[0044] As this is Fig. As shown in Figure 2, the electric lathe MG is arranged radially on the outside of the coupling CL. The electric lathe MG and the coupling CL are positioned such that they overlap in a section when viewed in the radial direction. It should be noted that, with regard to the arrangement of the two elements, the phrase "overlapping in a section when viewed in a certain direction" indicates that if the certain direction is used as a viewing direction and a viewing point is moved in any direction perpendicular to that viewing direction, the viewing point from which the two visible elements overlap will be present in at least one region. Arranging the electric lathe MG and the coupling CL in such a positional relationship reduces the length in the axial direction, thereby reducing the overall size of the device.

[0045] The electric lathe MG has a stator St, which is fixed to the housing 1, and a rotor Ro, which is rotatably supported radially on the inside of the stator St via the rotor support element 30. The stator St and the rotor Ro are arranged so that they face each other radially, with a small gap between them. The stator St has a stator core, which is designed as a stacked structure formed by stacking a plurality of ring-shaped, disc-shaped electromagnetic steel plates, and which is fixed to the first support wall 3, and a winding wound around the stator core. It should be noted that the sections of the winding that project axially from the ends of the stator, located on both sides in the axial direction, serve as winding end sections Ce.In this example, of the winding end sections Ce located on both sides in the axial direction, the winding end section Ce on the side facing the first direction A1 is a first winding end section Ce1, and the winding end section Ce on the side facing the second direction A2 is a second winding end section Ce2. The rotor Ro of the electric lathe MG has a rotor core designed as a stacked structure formed by stacking a plurality of ring-shaped, disk-shaped electromagnetic steel plates, and permanent magnets PM embedded in the rotor core. In the present embodiment, the plurality of permanent magnets PM extending in the axial direction are arranged in the rotor Ro (in the rotor core) such that they are distributed in the circumferential direction.

[0046] As this is shown in the Fig. 2 and Fig. As shown in Figure 3, the hybrid drive device H of the present embodiment has the rotor support element 30, which supports the rotor Ro. The rotor support element 30 supports the rotor Ro so that it is rotatable with respect to the housing 1. More precisely, the rotor support element 30 is supported by the first support wall 3 via a first bearing 61 on the side facing axially towards the second direction A2, and is supported by the second support wall 8 via a second bearing 62 on the side facing axially towards the first direction A1, with the rotor Ro being fixed to the outer circumference of the rotor support element 30. The rotor support element 30 is designed such that it surrounds the coupling CL, which is arranged on the inside of the rotor support element 30, i.e., such that it covers the coupling CL on the side facing axially towards the first direction A1, on the side facing axially towards the second direction A2, and on the outside in the radial direction.Thus, the rotor support element 30 has a first radially extending section 31, which is arranged on the axial side of the coupling CL pointing towards the second direction A2 and extends in the radial direction, a second radially extending section 41, which is arranged on the axial side of the coupling CL pointing towards the first direction A1 and extends in the radial direction, and an axially extending section 51, which is arranged radially on the outside of the coupling CL and extends in the axial direction.

[0047] The first radially extending section 31 is shaped such that it extends at least in the radial direction, and in the present embodiment, it extends in both the radial and circumferential directions. A through-hole in the axial direction is formed in the radial center of the first radially extending section 31, and the input shaft I, inserted through the through-hole, extends through the first radially extending section 31 and is inserted into the rotor support element 30. In this example, the first radially extending section 31 is shaped as a whole in a plate form, and it is shaped such that a radially inner section is slightly offset from the axially oriented side (facing the first direction A1) with respect to a radially outer section.The first radially extending section 31 is coupled to a hub-shaped cylindrical section 32, which projects towards the side facing the second direction A2 axially. The cylindrical section 32 is coupled to the first radially extending section 31 at its radially inner end. The cylindrical section 32 is designed to surround the input shaft I. A third bearing 63 is provided between the cylindrical section 32 and the input shaft I. The first bearing 61 is provided between the inner circumferential surface of the cylindrical section 32 and the inner circumferential surface of the cylindrical section 4 of the first support wall 3. In this example, a ball bearing is used as such a first bearing 61. The first bearing 61 and the third bearing 63 are arranged to overlap each other in the radial direction.

[0048] The second radially extending section 41 is shaped such that it extends at least in the radial direction, and in the present embodiment, it extends in both the radial and circumferential directions. A through-hole in the axial direction is formed in the radial center of the second radially extending section 41, and the intermediate shaft M, which is inserted through the through-hole, extends through the second radially extending section 41 and is inserted into the rotor support element 30. In this example, the second radially extending section 41 is shaped as a whole in a plate form, and it is shaped such that a radially inner section is slightly offset with respect to a radially outer section on the side facing the second direction A2 axially.The second radially extending section 41 is coupled to a hub-shaped cylindrical section 42, which projects towards the axial side facing the first direction A1. The cylindrical section 42 is integrally coupled to the second radially extending section 41 at its radially inner end. The cylindrical section 42 is designed to surround the intermediate shaft M. A portion of the axial length of the inner circumferential surface of the cylindrical section 42 is in contact with the outer circumferential surface of the intermediate shaft M along its entire circumference. The second bearing 62 is located in a region between the outer circumferential surface of the cylindrical section 42 and the inner circumferential surface of the cylindrical section 9 of the second support wall 8. In this example, a ball bearing is used as such a second bearing 62.

[0049] The cylindrical section 42 is coupled to the intermediate shaft M in the inner circumferential surface of the end on the side axially facing the first direction A1 by means of a key, such that it rotates together with the intermediate shaft M. The cylindrical section 42 is also coupled to the inner rotor of the oil pump 18 in the outer circumferential surface of the end on the side axially facing the first direction A1 by means of a key, such that it rotates together with the inner rotor. The hydraulic oil chamber H1 is formed between the second radially extending section 41 and the piston 25.

[0050] In the present embodiment, the second radially extending section 41 has a cylindrical, axially projecting section 43 that projects towards the side facing the first direction A1. In this example, the axially projecting section 43 is shaped to have a specific thickness in both the axial and radial directions. Such an axially extending section 43 is formed in a radially outer region of the second radially extending section 41. A radially outer section of the axially projecting section 43 overlaps with the rotor Ro when viewed in the axial direction. A radially inner section of the axially projecting section 43 overlaps with the coupling drum 22 when viewed in the axial direction. The axially projecting section 43 is arranged such that it overlaps with the second bearing 62 and the first winding end section Ce1 when viewed in the radial direction.In the present embodiment, oil collection sections OC are located in an end surface 43a (see . Fig. 3) of the axially projecting section 43, which is provided on the side facing axially towards the first direction A1. The oil collecting sections OC are provided to collect the oil supplied by an oil delivery section SP, which is provided on the side of the rotor Ro facing axially towards the first direction A1. The oil collected by the oil collecting sections OC is supplied to the winding end sections Ce1 and Ce2 on both sides in the axial direction to cool the winding end sections Ce1 and Ce2. This is described in more detail below.

[0051] The axially extending section 51 is shaped such that it extends at least in the axial direction, and in the present embodiment, it extends in both the axial and circumferential directions. The axially extending section 51 has a cylindrical shape that surrounds the outer surface of the coupling CL in the radial direction. The axially extending section 51 couples the first radially extending section 31 and the second radially extending section 51 in the radial direction at their radially outer ends. In this example, the axially extending section 51 is formed integrally with the first radially extending section 31 on the side facing the second direction A2. The axially extending section 51 is coupled to the second radially extending section 41 on the side facing the first direction A1 by a fastening element such as a screw.It should be noted that the axially extending section 51 can be coupled to the second radially extending section 41 by welding, etc. The rotor Ro of the electric lathe MG is fixed to the outer circumference of the axially extending section 51.

[0052] In the present embodiment, the axially extending section 51 has a cylindrical inner support section 52 extending in the axial direction and an annular single-sided support section 53 extending radially outward from an end of the inner support section 52 located on the side facing the first direction A1. In this example, the single-sided support section 53 is shaped to have a specific thickness in both the axial and radial directions. The rotor Ro is in contact with and fixed to the outer circumferential surface of the inner support section 52, whereby the inner support section 52 supports the rotor Ro from the radial inside.The rotor Ro is in contact with and fixed to an end face of the single-sided support section 53, which is located on the side facing the second direction A2 axially. The single-sided support section 53 thus supports the rotor Ro from the side facing the first direction A1 axially. It should be noted that an annular rotor retaining element 56 with the inner support section 52 is inserted from the side of the rotor Ro facing the second direction A2 axially. The rotor retaining element 56 is arranged such that it is in contact with the rotor Ro from the side facing the second direction A2 axially, and it holds the rotor Ro from the side facing the second direction A2 axially.In this example, the rotor holding section 56 pushes and holds the rotor Ro from the axial side pointing towards the second direction A2, with the plurality of electromagnetic steel plates being held in the axial direction between the rotor holding section 56 and the single-sided support section 53.

[0053] As described above, the rotor support element 30 of the present embodiment is designed to also function as the housing (the coupling housing) in which the coupling CL is located. The majority of the space formed inside the rotor support element 30, with the exception of the hydraulic oil chamber H1, serves as the circulation oil chamber H2, as described above. In the present embodiment, the oil supplied by the oil pump 18, which is set to a predetermined oil pressure, is delivered to the circulation oil chamber H2 through the circulation oil channel 48.In the present embodiment, the third bearing 63, which is provided between the cylindrical section 32 of the first radially extending section 31 and the input shaft I, is a bearing that has a sealing function (in this example: a needle bearing with a sealing ring) and is designed to ensure a certain level of fluid tightness. Furthermore, a portion of the axial length of the inner circumferential surface of the cylindrical section 42 in the second radially extending section 41 is in contact with the outer circumferential surface of the intermediate shaft M along its entire circumference. Thus, the circulation oil chamber H2 in the rotor support element 30 is designed to be fluid-tight, and the oil is supplied to the circulation oil chamber H2, which is essentially filled with oil at a predetermined pressure or higher.Thus, in the hybrid drive device H of the present embodiment, the plurality of friction plates 24 provided in the clutch CL can be effectively cooled by a large quantity of oil that is filled into the circulation oil chamber H2.

[0054] It should be noted that most of the oil discharged from the circulation oil chamber H2 is discharged through the discharge oil channel 16, which is formed inside the intermediate shaft M, via a communication hole in the radial direction. This hole is open in the outer circumferential surface of the input shaft I and returns to the oil pan (not shown). However, some of the oil discharged from the circulation oil chamber H2 exits axially through the third bearing 63, which is provided between the outer circumferential surface of the input shaft I and the inner circumferential surface of the cylindrical section 32 of the first radially extending section 31, and lubricates the first bearing 61, which is arranged radially on the outside of the third bearing 63.

[0055] In the present embodiment, a rotation sensor 11 is provided between the first support wall 3 and the first radially extending section 31 on the axial side of the rotor support element 30 facing the second direction A2. The rotor sensor 11 is a sensor for detecting the rotational position of the rotor Ro relative to the stator St of the electric lathe MG. For example, a rotary encoder, etc., can be used as such a rotation sensor 11. In the present embodiment, the rotation sensor 11 is arranged radially on the outside of the first bearing 61, which is provided between the first support wall 3 and the first radially extending section 31, such that it overlaps the first bearing 61 when viewed in the radial direction. Furthermore, the rotation sensor 11 is arranged radially on the inside of the stator St such that it overlaps the second winding end section Ce2 of the stator St when viewed in the radial direction.This example shows how this is done in . Fig. Figure 3 shows a sensor rotor 12 fixed to a side surface of the first radially extending section 31, located on the side axially facing the second direction A2, and a sensor stator 13 fixed to a side surface of the first support wall 3, located on the side axially facing the first direction A1. In the present embodiment, the sensor rotor 12 is arranged radially on the inside of the sensor stator 13. 3. Cooling system of the electric lathe

[0056] A cooling system for the electric lathe MG of the present embodiment is described below with reference to the Fig. 2 and Fig. 3 described. The electric lathe MG of the present embodiment has a basic design in which the winding end sections Ce are cooled by the oil supplied from the side of the rotor Ro facing axially towards the first direction A1. This is described in detail below.

[0057] In the present embodiment, the oil supply section SP for supplying oil to the electric lathe MG is provided in the second support wall 8, which is arranged on the side facing axially towards the first direction A1 with respect to the rotor Ro. More precisely, the oil supply section SP of the present embodiment is provided as a small gap between the inner circumferential surface of the through-hole in the second support wall 8 and the outer circumferential surface of the cylindrical section 42 of the second radially extending section 41 on the side facing axially towards the second direction A2 of the oil pump 18, which is arranged inside the second support wall 8.A portion of the oil in the pump chamber, which houses the oil pump 18, escapes in small increments in the axial direction through the small gap as the oil supply section SP and lubricates the second bearing 62, which is located adjacent to the oil supply section SP (the small gap) on the side facing axially in the second direction A2. In the present embodiment, the small gap forming the oil supply section SP corresponds to an “oil flow section” in the present invention. After lubricating the second bearing 62, the oil flows downwards in the vertical direction (the lower side into the Fig. 2 and Fig. 3) along the second radially extending section 41 and is finally supplied to the winding end sections Ce of the electric lathe MG, which are arranged radially on the outside of the rotor support element 30.

[0058] The oil collection sections OC are provided radially on the outside of the small gap as an oil supply section SP and of the second bearing 62 adjacent to the small gap. Such oil collection sections OC are provided at the end of the rotor support element 30 that is located on the side axially facing the first direction A1. In the present embodiment, the oil collection sections OC are provided at the end that is located on the side axially facing the first direction A1 of the axially projecting section 43 of the second radially extending section 41, which forms part of the rotor support element 30.More precisely, the axially projecting section 43 is provided with recesses 44 which are shaped such that they are recessed on the side facing the second direction A2 with respect to the end surface 43a of the axially projecting section 43, which is located on the side facing the first direction A1, and which are open on the inside in the radial direction. Such recesses 44 are designed to be uniformly distributed at a plurality (six in this example) circumferential positions in the axially projecting section 43 (see ). Fig. 4) The recesses 44 are covered by a cover element 46 on the side facing the first direction A1 in the state where the cover element 46 is in contact with and fixed to the end surface 43a of the axially projecting section 43. The cover element 46 is fixed to the axially projecting section 43 by fasteners such as screws at a plurality (18 in this example) circumferential positions. At least the areas of the cover element 46 around the sections corresponding to the recesses 44 are formed in the form of a flat plate. Thus, a pocket-shaped space is formed between each recess 44 and the cover section 46, which is closed on both sides in the axial direction, on both sides in the circumferential direction, and on the outside in the radial direction, and is open only on the inside in the radial direction.In the present embodiment, the oil collecting sections OC are designed as pocket-shaped spaces, which are thus defined by the recesses 44 and the cover element 46. The oil collecting sections OC are arranged such that they are evenly distributed at a plurality (six in this example) of circumferential positions, corresponding to the arrangement of the recesses 44. The oil collecting sections OC are capable of collecting and storing the oil that flows downwards in the vertical direction along the second radially extending section 41 after the second bearing 62 has been lubricated.

[0059] The electric lathe MG of the present embodiment is constructed such that at least the winding end sections Ce (the first winding end section Ce1, the second winding end section Ce2) are cooled using the oil that is collected and stored by the oil collection sections OC. Thus, the electric lathe MG of the present embodiment has a communication oil channel L, which is provided in both the rotor Ro and the rotor support element 30 and which communicates with the oil collection section OC via two openings (i.e., a first opening P1 and a second opening P2) formed on both sides in the axial direction of the rotor Ro.An oil channel communicating with the first opening P1 on the side axially facing the first direction A1 from the oil collecting section OC is formed as part of the communication oil channel L, and the first opening P1 is radially open on the inside of the first winding end section Ce1. An oil channel communicating with the second opening P2 on the side axially facing the second direction A2 from the oil collecting section OC is formed as another part of the communication oil channel L, and the second opening P2 is radially open on the inside of the second winding end section Ce2. At this point, the first opening P1 is open at a position that overlaps with the first winding end section Ce1 when viewed in the radial direction, and the second opening P2 is open at a position that overlaps with the second winding end section Ce2 when viewed in the radial direction.

[0060] In the present embodiment, such a communication oil channel L has a common oil channel extending from each oil collecting section OC, an oil channel branching off from the common oil channel and communicating with the first opening P1, and an oil channel branching off from the common oil channel and communicating with the second opening P2. That is to say, in the present embodiment, the entire communication oil channel L is formed by the oil channel communicating with the first opening P1 of the oil collecting section OC and the oil channel communicating with the second opening P2 of the oil collecting section OC, using the common section on the upstream side (the side of the oil collecting section OC).

[0061] More precisely, an oil hole 45 in the axial direction, which communicates with the radially outer end of the recess 44, is formed in the axially projecting section 43 of the second radially extending section 41, and a first oil channel L1, which communicates with the oil hole 45 and extends along the axial direction to the side facing the second direction A2, is formed in the (inside of the) one-sided support section 53 of the axially extending section 51. In the present embodiment, as shown in Fig. As shown in Figure 4, a plurality (six in this example) of oil holes 45 and a plurality (six in this example) of first oil channels L1 are configured such that they are distributed circumferentially according to the arrangement of the oil collecting sections OC (the recesses 44). The first oil channels L1 are arranged radially on the outside and adjacent to the outer circumferential surface of the inner support section 52 and are open at the end face of the single-sided support section 53, which is located on the side axially facing the second direction A2. A second oil channel L2, branching off from the first oil channel L1 and extending radially outwards, is formed in the single-sided support section 53. In the present embodiment, a plurality (six in this example) of the second oil channels L2 are configured such that they are distributed circumferentially according to the arrangement of the first oil channels L1.Every second oil channel L2 is open in the outer circumferential surface of the single-sided section 53, and this opening serves as the first opening P1. In this example, the first opening P1 is open in directions along the radial direction. The first oil channels L1 and the second oil channels L2 can be formed in a relatively simple manner by a machining process such as drilling the single-sided support section 53.

[0062] In the present embodiment, a third oil channel L3, which communicates with the first oil channel L1 and extends axially from the first oil channel L1 to the side facing the second direction A2, is formed in the rotor Ro along the connecting surface between the outer circumferential surface of the inner support section 52 and the inner circumferential surface of the rotor Ro. In the present embodiment, a plurality (six in this example) of the third oil channels L3 are configured to be distributed circumferentially according to the arrangement of the first oil channels L1. In the present embodiment, the radially inner sections of the electromagnetic steel plates forming the rotor Ro are cut out at a plurality of circumferential positions, and these cutouts are successively aligned in the axial direction and fixed in this state.Thus, the third oil channels L3 are designed as axial grooves defined between the outer circumferential surface of the inner support section 52 and the cutouts on the radially inner side of the electromagnetic steel plates. Each third oil channel L3 is open in the end face of the rotor Ro, located on the side facing axially to the second direction A2, and this opening serves as the second opening P2. In this example, the second opening P2 is open in the direction that runs along the axial direction. It should be noted that such cutouts, designed as described above, can be formed simultaneously in a stamping process of the electromagnetic steel plates that form the rotor Ro.

[0063] The multitude of permanent magnets PM, arranged circumferentially within the rotor Ro, generate a magnetic field to produce a torque through interaction with a rotating magnetic field generated by the stator St. In the present embodiment, the third oil channels L3 in the radially inner end of the rotor Ro, forming a connection between the rotor Ro and the inner support section 52 located away from the permanent magnets PM, are designed such that an ideal magnetic flux path, as the passage of a magnetic flux through the permanent magnets PM, can be maintained as far as possible without disturbing the magnetic flux path. Thus, even if the third oil channels L3 are formed by cutting out a portion of the electromagnetic steel plates of the rotor Ro, the influence of the third oil channels L3 on the magnetic field generated by the permanent magnets can be reduced.Therefore, since the design of the present embodiment can reduce the hindrance of the formation of the magnetic field by the permanent magnets PM, it is also advantageous that the third oil channels L3 can be formed while maintaining the capability and performance of the electric lathe MG.

[0064] Thus, in the present embodiment, the aforementioned common oil channel is formed by the oil hole 45 in the axial direction, which communicates with the recess 44 that defines the oil collecting section OC, and by the section of the first oil channel L1 located on the axial side facing the first direction A1 with respect to the branching point from which the second oil channel L2 branches off. On the other hand, the oil channel branching off from the common oil channel and communicating with the first opening P1 is formed by the second oil channel L2. The oil channel branching off from the common channel and communicating with the second opening P2 is formed by the section of the first oil channel L1 located on the axial side facing the second direction A2 with respect to the branching point from which the second oil channel L2 branches off, and by the third oil channel L3.

[0065] In the electric lathe MG, which has a construction as described above, the winding end sections Ce1 and Ce2 are cooled as follows. First, the oil that escapes and is supplied in the axial direction from the oil supply section SP between the second support wall 8 and the cylindrical section 42 of the second radially extending section 41 on the side facing axially towards the first direction A1, is collected by the oil collection section OC. The oil collected by the oil collection section OC is supplied by the oil collection section OC to the common oil channel formed by the oil hole 45 and part of the first oil channel L1.Part of the oil supplied to the common oil channel is discharged from the first opening P1 through the second oil channel L2 and falls onto the first winding end section Ce1, which is arranged radially on the outside of the first opening P1, thus cooling the first winding end section Ce1. Another part of the oil supplied to the common oil channel is discharged from the second opening P2 through the first oil channel L1 and the third oil channel L3 and falls onto the second winding end section Ce2, which is arranged radially on the outside of the second opening P2, thus cooling the second winding end section Ce2. It should be noted that after the winding end sections Ce1 and Ce2 have been cooled, the oil returns to the oil pan (not shown).

[0066] In the present embodiment, the circulation oil chamber H2 in the rotor support element 30 is designed to be fluid-tight and is generally filled with oil at a predetermined pressure or higher in order to effectively cool the plurality of friction plates 24 enclosed in the coupling CL. In such a design, it is difficult to direct the oil in the circulation oil chamber H2 radially outwards and use this oil to cool the winding end sections Ce of the electric lathe MG.Furthermore, if the oil supply section SP is located on the side of the electric lathe MG facing axially towards the first direction A1, the second winding end section Ce2, located on the side opposite the side where the oil supply section SP is located (on the side facing axially towards the second direction A2), may not be adequately cooled. However, since the present embodiment utilizes the assembly equipped with the communication oil channel L, which communicates with both the first opening P1 and the second opening P2 of the oil collection section OC, both the first winding end section Ce1 and the second winding end section Ce2 can be adequately cooled. In particular, the assembly equipped with the oil collection section OC is used in the present embodiment.Thus, even if the amount of oil escaping in the axial direction through the space between the second support wall 8 and the cylindrical section 42 of the second radially extending section 41 is small, and the amount of oil supplied by the oil supply section SP is small, the oil can still be collected more efficiently by the oil collection section OC, and the winding end sections Ce1 and Ce2 can be cooled efficiently.

[0067] In the present embodiment, the second oil channel L2 is configured to have substantially the same flow path cross-sectional area as the first oil channel L1. The third oil channel L3 is configured to have a flow path cross-sectional area that is substantially equal to or greater than that of the first oil channel L1 and the second oil channel L2. Thus, the oil flow rate can be designed to be substantially the same in the two oil channels located downstream of the branch point from the common oil channel. Furthermore, in the present embodiment, the oil collected by the oil collection section OC is first supplied to the common oil channel and then distributed to the two oil channels branching off from the common oil channel.Thus, in the electric lathe MG of the present embodiment, the oil supplied by the oil delivery section SP, which is provided on the axial side of the rotor Ro facing the first direction A1, can be evenly distributed to the two oil channels communicating with the first opening P1 and the second opening P2, regardless of the oil collection state of the oil collection section OC (the amount of oil stored in the oil collection section OC). Therefore, the first winding end section Ce1 and the second winding end section Ce2 can be cooled in an equilibrium state (in a balanced manner).

[0068] In the present embodiment, the second oil channel L2 is an oil channel extending radially, and the first opening P1 of the second oil channel L2 is configured to be open in the middle of the area occupied by the first winding end section Ce1 in the axial direction. Thus, the entire first winding end section Ce1 can be efficiently cooled. On the other hand, the third oil channel L3 is an oil channel extending axially, and the second opening P2 of the third oil channel L3 is configured to be open at a position near the end face of the stator core in the area occupied by the second winding end section Ce2 in the axial direction.As described above, the rotor retaining element 56, which is inserted with the inner support section 52 and holds the rotor Ro from the side facing the second direction A2, is provided in the present embodiment. A plurality of through-holes, extending at least through the rotor retaining element 56 in the axial direction, are formed in the rotor retaining element 56 at circumferential positions corresponding to the third oil channels L3 and the second openings P2. Each opening of the rotor retaining element 56 on the side facing the second direction A2, formed by each through-hole 57 communicating with the third oil channel L3 and the second opening P2, is designed to be open in the middle of the area occupied by the second winding end section Ce2 in the axial direction.Thus, in the present embodiment, the entire second winding end section Ce2 can also be efficiently cooled.

[0069] The rotor retaining element 56 of the present embodiment is fixed by being riveted from the radial inside and from the side facing the second direction A2 in the state in which the rotor retaining element 56 is inserted into the inner support section 52. That is, the rotor retaining element 56 is fixed in the axial direction by a riveted section 54 formed between the rotor retaining element 56 and the inner support section 52. The riveted section 54, described above, is shaped such that the end of the cylindrical inner support section 52 is inclined radially outward on the side facing the second direction A2. As with the riveted section 54, each through-hole 57 formed in the rotor retaining element 56 is also inclined radially outward on the side facing the second direction A2.The crimped section 54 and the through-hole, which has this shape, act as a guide section that directs the oil supplied from the third oil channel L3 to the second winding end section Ce2. This allows the second winding end section Ce2 to be cooled even more efficiently. 4. Other examples of implementation

[0070] Finally, other embodiments of the electric lathe and the vehicle drive device of the present invention are described below. It should be noted that a characteristic structure disclosed in each of the embodiments described below is not only used in that embodiment, but can also be used in combination with the characteristic structures disclosed in the other embodiments, provided that no incompatibility arises. (1) The embodiment described above is described with regard to an example in which the communication oil channel L, which communicates with the first opening P1, and the second oil channel P2 of the oil collection section OC are provided inside the rotor support element 30 and between the rotor Ro and the rotor support element 30. However, the embodiments of the present invention are not limited thereto. That is to say, the communication oil channel L, which communicates with the first opening P1, and the second oil channel P2 of the oil collection section OC need only be provided in at least either the rotor Ro and / or the rotor support element 30, and, as is the case, for example, in Fig. As shown in Figure 4, it is also one of the preferred embodiments of the present invention that the entire communication oil channel L is formed inside the rotor support element 30. In this case, for example, the first oil channels L1 and the third oil channels L3, which are described in the embodiment explained above, can be formed in one piece, and the position of this oil channel (which is indicated by “L3” in Figure 4) can be determined by the fact that the entire communication oil channel L is formed inside the rotor support element 30. Fig. (as shown in Figure 5, representatively) can be displaced radially inwards compared to the position of the first oil channel L1 and the third oil channel L3 in the embodiment described above. In this case, the oil channel “L3” can extend along the axial direction inside the single-sided support section 53 and the inner support section 52, and the second opening P2 can be open in the end face of the rotor support element 30 (the inner support section 52), which is located on the side axially facing the second direction A2. (2) The embodiment described above is described with reference to an example in which each oil collecting section OC is formed as the pocket-shaped space defined in which the recesses 44 are covered. This pocket-shaped space is provided in the end surface 43a of the axially projecting section 43 of the second radially extending section 41 on the side facing the first direction A1 by the flat, plate-shaped cover element 46, which is in contact with and fixed to the end surface 43a. However, the embodiments of the present invention are not limited to this. That is to say, it is possible, as is the case, for example, in Fig. Figure 6 shows, also one of the preferred embodiments of the present invention, that the end surface 43a of the axially projecting section 43, which is located on the side facing the first direction A1 axially, is designed as a flat end surface, and a plate-shaped element 47, which is shaped to project towards the first side facing the axial direction A1 and is open on the inside in the radial direction, is fixed to the end surface 43a such that the oil collecting section OC is formed as a pocket-shaped space defined between them. (3) The embodiment described above relates to an example in which the oil collecting sections OC are formed between the second radially extending section 41 and the cover element 46. However, the embodiments of the present invention are not limited to this. That is to say, it is also, for example, one of the preferred embodiments of the present invention that pocket-shaped spaces, open only on the inside in the radial direction, are formed directly at a plurality of circumferential positions in the axially projecting section 43, which is located at the end of the rotor support element 30 on the side axially facing the first direction A1, and these pocket-shaped spaces are used as the oil collecting sections OC.Alternatively, it is also one of the preferred embodiments of the present invention that an oil collecting element in which a pocket-shaped space is formed which is open only on the inside in the radial direction is provided separately, and that this oil collecting element is provided such that it is fixed to the end surface 43a of the axially projecting section 43 of the second radially extending cut 41. (4) The embodiment described above refers to an example in which the plurality of oil collecting sections OC are arranged such that they are uniformly distributed at the plurality of circumferential positions. However, the embodiments of the present invention are not limited to this. That is to say, it is also, for example, a preferred embodiment of the present invention in which the plurality of oil collecting sections OC are arranged such that they are unevenly distributed in the circumferential direction. Alternatively, it is also a preferred embodiment of the present invention to provide a single oil collecting section OC that extends continuously along the entire circumference. (5) The embodiment described above refers to an example in which the first opening P1 is open in a direction along the radial direction and the second opening P2 is open in a direction along the axial direction. However, the embodiments of the present invention are not limited thereto. That is to say, with regard to the first opening P1, it is also a preferred embodiment of the present invention that, for example, the first opening P1 is open in a direction inclined with respect to the radial direction, if the first opening P1 is open at a position that overlaps with the first winding end section Ce1, at least in the radial direction.With regard to the second opening P2, it is also one of the preferred embodiments of the present invention that, for example, the second opening P2 is open in a direction which is inclined with respect to the axial direction or is inclined in a direction along the radial direction, if the second opening P2 is open at a position where it overlaps with the second winding end section Ce2, considering at least in the radial direction. (6) The embodiment described above is described with regard to an example in which, in the case where the third oil channel L3, which forms part of the communication oil channel L that communicates with the second opening P2 of the oil collecting section OC, is formed in the rotor Ro, the third oil channel L3 is formed along the connecting surface between the outer circumferential surface of the inner support section 52 and the inner circumferential surface of the rotor Ro. However, the embodiments of the present invention are not limited thereto. That is to say, it is also one of the preferred embodiments of the present invention that the third oil channels L3 in, for example, the rotor Ro are formed such that they extend along the axial direction between the permanent magnets that are arranged adjacent to each other in the circumferential direction.This design is advantageous in that the permanent magnets PM can be cooled by the oil flowing through the third oil channel L3. It should be noted that this reduces magnetic flux leakage from the permanent magnets PM through the third oil channel L3. Therefore, this design is also advantageous in that the magnetic flux distribution of the magnetic field generated by the permanent magnets PM can be satisfactorily optimized, thus maintaining the high capability and performance of the electric lathe MG. (7) The embodiment described above relates to an example in which the third oil channel L3 is formed along the connecting surface between the outer circumferential surface of the inner support section 52 and the inner circumferential surface of the rotor Ro, and the third oil channel L3 is formed as a space between the axial groove formed in the inner circumferential surface of the rotor Ro and the inner support section 52. However, the embodiments of the present invention are not limited thereto. That is to say, it is also, for example, one of the preferred embodiments of the present invention that an axial groove is provided in the outer circumferential surface of the inner support section 52, and the third oil channel L3 is formed as a space between the axial groove of the inner support section 52 and the inner circumferential surface of the rotor Ro. (8) The embodiment described above is described with reference to an example in which the communication oil channel L has the common oil channel extending from the oil collecting section OC and the two oil channels branching off from the common oil channel, each communicating with the first opening P1 and the second opening P2, respectively. However, the embodiments of the present invention are not limited thereto. That is to say, it is also one of the preferred embodiments of the present invention that the communication oil channel L does not have such a common oil channel, but rather, as described in Fig. As shown in Figure 5, the instrument has, independently, an oil channel communicating with the first opening P1 of the oil collecting section OC and an oil channel communicating with the second opening P2 of the oil collecting section OC. In this case, the oil channel communicating with the first opening P1 of the oil collecting section OC can extend radially outward from the radially outer bottom of the recess 44 at least in the axially projecting section 43 of the second radially extending section 41 and can be open in the outer circumferential surface of the axially projecting section 43 or the outer circumferential surface of the one-sided support section 53 of the axially extending section 51. Alternatively, it is also preferred that, as shown, for example, in Figure 5, the oil channel communicates with the first opening P1 of the oil collecting section OC. Fig. 7 is shown, at a circumferential position that differs from that of an oil channel (see Fig. 7B), which communicates with the second opening P2 from the oil collection section OC, distinguishes an oil channel (see Fig. 7A), which communicates with the first opening P1 of the oil collection section OC, extends in the (inside of the) single-sided support section 53 of the axially extending section 51 to the side facing the second direction A2 at the same radial position as the oil channel communicating with the second opening P2, and extends radially outward in the single-sided support section 53 from a predetermined position such that it is open in the outer circumferential surface of the single-sided support section 53. Thus, the oil can be distributed evenly to the first opening P1 and the second opening P2 regardless of the oil collection state of the oil collection section OC. (9) The embodiment described above is presented with reference to an example in which the six recesses 44, the six oil collecting sections OC, the six oil holes 45, the six first oil channels L1, the six second oil channels L2, and the six third oil channels L3 are formed. However, the embodiments of the present invention are not limited to this. That is to say, it is also one of the preferred embodiments of the present invention in which any of the respective numbers of the elements described above can be 1, 2, ..., 5, 7, ... It should be noted that in this case, the number of the elements described above need not necessarily be the same. (10) The embodiment described above refers to an example in which the oil supply section SP is formed as the small space between the inner circumferential surface of the through-hole in the second support section 8 and the outer circumferential surface of the cylindrical section 42 of the second radially extending section 41. However, the embodiments of the present invention are not limited to this. That is to say, in the present invention, it is only necessary that the oil be supplied from the side of the rotor Ro facing axially to the first direction A1, and it is also one of the preferred embodiments of the present invention that an assigned oil channel for supplying the oil delivered by the oil pump 18 is provided, for example, in the second support wall 8, and that the oil supply section SP is formed by the assigned oil channel. (11) The embodiment described above refers to an example in which the housing (the coupling housing) is formed by the entire rotor support element 30, which is configured to surround the coupling CL. However, the embodiments of the present invention are not limited to this. That is to say, the housing need only be formed by using at least a part of the rotor support element 30, and it is also one of the preferred embodiments of the present invention that the housing is formed by an interaction between the part of the rotor support element 30 and another element. (12) The embodiment described above relates to an example in which the hybrid drive unit H has a multi-axle design suitable for mounting on front-engine, front-wheel-drive vehicles (FF vehicles). However, the embodiments of the present invention are not limited to this. That is to say, it is also a preferred embodiment of the present invention that the hybrid drive unit has a uniaxial design in which, for example, the output shaft of the speed-changing mechanism TM is arranged coaxially with the input shaft I and the intermediate shaft M and is directly coupled to the output differential gear unit TF. The hybrid drive unit H having such a design is also suitable for mounting on front-engine, rear-wheel-drive vehicles (FR vehicles). (13) The embodiment described above relates to an example in which the vehicle drive device of the present invention is applied to the hybrid drive device H for hybrid vehicles, which have both the internal combustion engine E and the electric lathe MG as the vehicle's drive power source. However, the embodiments of the present invention are not limited thereto. That is to say, the present invention can also be applied to a drive device for electric vehicles which have only the electric lathe MG as the vehicle's drive power source. (14) The embodiment described above relates to an example in which the electric lathe of the present invention is applied to the electric lathe MG, which is used as the motive power source of the vehicle. However, the embodiments of the present invention are not limited to this. That is to say, the present invention can also be applied to the electric lathe MG, which is used for applications other than powering the vehicle. (15) With regard to other structures as well, the embodiments disclosed in the description are in all respects merely exemplary, and the embodiments of the present invention are not limited to them. That is to say, it should be clear that the configurations in which the structures not described in the claims are partially modified in a suitable manner also fall within the scope of the present invention, as long as these configurations include the structures described in the claims of the present invention and the structures that are equivalent to them. INDUSTRIAL APPLICABILITY

[0071] The present invention can preferably be applied to electric lathes having a rotor rotatably supported radially inside a stator by means of a rotor support element, having winding end sections on both sides in the axial direction, and being constructed such that oil is supplied from the axially oriented side (one side in the axial direction of the rotor) to the winding end sections on both sides in the axial direction. The present invention can also preferably be applied to vehicle drive systems that have such an electric lathe. List of reference symbols H Hybrid drive device (vehicle drive device) MG electric lathe St stator Ce winding end section Ce1 first winding end section Ce2 second winding end section Ro Rotor PM permanent magnet 1 case 8 second retaining wall (retaining wall) 30 Rotor support element (housing) 43 axially projecting section 43a End surface (end surface on one side) 44 In-depth study 46 Cover element 52 inner support section (interior support section) 53 Single-sided support section 54 caulked section 56 Rotor retaining element SP Oil Delivery Section (Oil Flow Section) OC Oil Collection Section L Communication oil channel L1 first oil channel L2 second oil channel L3 third oil channel P Opening P1 first opening P2 second opening A1 axial first direction A2 axial second direction

Claims

[1] A rotary electric machine comprising a rotor rotatably supported via a rotor support member radially inside a stator having winding end portions on both sides in an axial direction, and configured such that oil is supplied from an axial side facing a first direction, which is one side in the axial direction of the rotor, to the winding end portions on the two sides in the axial direction, comprising: an oil collecting portion provided at one end of the rotor support member located on the axial side facing the first direction; and a communication oil passage provided in at least one of the rotor and the rotor support member and communicating with a first opening and a second opening of the oil collecting portion, wherein the first opening is open radially on the inside of the winding end portion on the axial side facing the first direction, and the second opening is open radially on the inside of the winding end portion on the axial side facing the second direction, which is the other side in the axial direction of the rotor. [2] Electric rotary machine according to claim 1, wherein the rotor support element has a cylindrical axially projecting portion projecting toward the axial side facing the first direction, a recess is formed so as to be recessed toward the axial side facing the second direction with respect to a side end face of the axially projecting portion, which is arranged on the axial side facing the first direction, and is open on an inner side in a radial direction, and a cover portion is provided so as to be in contact with the one side end face and fixed and to cover the recess on the axial side facing the first direction, and the oil collecting portion is formed as a pocket-shaped space defined by the recess and the cover member. [3] The rotary electric machine according to claim 1 or 2, wherein the communication oil passage has a common oil passage extending from the oil collecting portion, an oil passage branching from the common oil and communicating with the first opening, and an oil passage branching from the common oil passage and communicating with the second opening. [4] Electric rotary machine according to claim 3, wherein the rotor support member has a cylindrical inner support portion that supports the rotor from radially inside and an annular one-side support portion that extends radially outward from the inner support portion and supports the rotor from the side facing the first axial direction, a first oil channel is formed so as to extend inside the one-side support portion in the axial direction from the oil collecting portion to the axial side facing the second direction, a second oil passage is formed so as to branch off from the first oil passage and extend radially outwardly inside the one-side support portion, and to communicate with the first opening open in an outer peripheral surface of the one-side support portion, and a third oil passage is formed to extend from the first oil passage further to the axial side facing the second direction and to communicate with the second opening open at an end surface of the rotor or the rotor support member located on the axial side facing the second direction. [5] The rotating electric machine according to claim 4, wherein the third oil passage is formed along a connecting surface between an inner peripheral surface of the rotor and an outer peripheral surface of the inner support portion. [6] An electric rotary machine according to claim 5, further comprising: a ring-like rotor holding member arranged to contact the rotor from the axial side facing the second direction and to hold the rotor from the axial side facing the second direction; and a caulked portion that presses the rotor holding member inserted with the inner support portion from the axial side facing the second direction, wherein the caulked portion serves as a guide portion that guides the oil supplied from the third oil passage to the coil end portion. [7] The rotary electric machine according to claim 1, 2 or 6, wherein the communication oil passage independently has an oil passage communicating with the first opening of the oil collecting portion and the oil passage communicating with the second opening of the oil collecting portion. [8] Vehicle drive device with: the electric rotary machine according to any one of claims 1 to 7; a friction engagement device; and a housing in which at least the electric rotary machine and the friction engagement device are accommodated, wherein the housing has a support wall which rotatably supports the rotor support element on the axial side of the rotor facing the first direction, a housing surrounding the friction engagement device is formed by using at least a part of the rotor support member, and the friction engagement device is arranged in a fluid-tight state inside the housing at a position radially inside the rotor, the housing is filled with oil at a predetermined pressure or more, and the support wall is provided with an oil flow portion through which the oil to be supplied to the winding end portions flows on both sides in the axial direction.

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