JP6209938B2 - Cooling structure of rotating electric machine - Google Patents

Description

  The present invention relates to a cooling structure for a rotating electrical machine.

  2. Description of the Related Art Conventionally, a rotating electrical machine that is provided in a hybrid vehicle and is connected to an engine-side rotating shaft that rotates integrally with an engine, and a motor-side rotating shaft that can be connected to the engine-side rotating shaft; It has been studied to cool a rotating electrical machine having a clutch that changes a connection state between an engine-side rotating shaft and a motor-side rotating shaft with a coolant.

  For example, Patent Document 1 discloses a cooling structure for a rotating electrical machine in which a clutch is disposed on the radially outer side of a motor-side rotating shaft and a rotor is disposed on the radially outer side of the clutch, and is discharged from an oil pump. Oil is supplied to the clutch through the inside of the motor side rotating shaft, and this oil is used to lubricate and cool the clutch, and the oil after lubricating and cooling the clutch is supplied to the rotor to cool the rotor. Yes.

JP 2009-72052 A

  In the structure of Patent Document 1, since oil for cooling is always supplied from the oil pump to the clutch, the motor-side rotating shaft and the engine-side rotating shaft are individually rotated, and a difference in rotational speed is generated between these rotating shafts. Even when the engagement of these rotary shafts is released to cause them, the rotational force is transmitted between the rotary shafts via the cooling oil. For this reason, there is a problem that one rotating shaft becomes the rotational resistance of the other rotating shaft and the rotation efficiency, that is, the energy efficiency is deteriorated. For example, when one of the rotating shafts is stopped and only the other rotating shaft is rotated, the rotating shaft on the stop side becomes the rotational resistance of the rotating shaft on the rotating side, resulting in energy loss.

  This invention is made | formed in view of this point, and it aims at provision of the cooling structure of the rotary electric machine which can cool a rotary electric machine, suppressing rotation resistance small and making energy efficiency high.

In order to solve the above-described problems, the present invention provides an electric rotating machine having an engine-side rotating shaft that rotates integrally with an engine, and a motor-side rotating shaft that is connected to the engine-side rotating shaft and rotates around a predetermined axis. A cooling structure having a motor side connecting portion that rotates integrally with the motor side rotating shaft and an engine side connecting portion that rotates integrally with the engine side rotating shaft, and these connecting portions are engaged with each other. Thus, the connection state between the motor-side rotation shaft and the engine-side rotation shaft is changed to an engagement state in which the rotation shafts engage with each other and rotate together, and the engagement between the connection portions is released and separated from each other. The connection state between the rotation shafts is set to a release state in which a rotational force is not transmitted between the rotation shafts, and the connection state between the rotation shafts is brought into contact with each other without engaging the connection portions. And a clutch that is in a state other than the released state and is in a semi-engaged state in which the rotational force is transmitted between the rotary shafts without rotating integrally with the rotary shafts, and a diameter from the outer peripheral surface of the motor-side rotary shaft. Extending outward in the direction and rotating integrally with the motor-side rotary shaft, and a clutch case having a clutch chamber formed therein for accommodating the clutch, and an outer peripheral surface of the clutch case. A rotor that rotates integrally with the rotating shaft; a stator that is disposed on the radially outer side of the rotor and wound; and an outer peripheral surface of the clutch case, and the shaft of the motor-side rotating shaft of the rotor communicates with through the clutch chamber and the end plate that covers from the axially outward while forming a predetermined space, the interior of the motor side rotation shaft between the end face of the end face, the motor-side Includes a coolant passage for introducing a cooling fluid to the clutch chamber through the interior of the rotating shaft, a passage extending radially outward of the clutch case from the interior of the street the motor side rotating shaft inside of the clutch case, A branch passage that branches off from the coolant passage and leads the coolant in the coolant passage to the radially outer side of the clutch case without passing through the clutch chamber; and an inflow state of the coolant into the clutch chamber. Changeable cooling fluid inflow state changing means, wherein the cooling liquid inflow state changing means is configured so that the connection state between the motor side rotating shaft and the engine side rotating shaft is the engaged state and the released state. restricting the flow of the cooling fluid to the clutch chamber, the when connection state of the half engagement to permit the flow of the cooling fluid to the clutch chamber, the rotor, the The magnet side hole is formed with a magnet hole through which both end surfaces in the axial direction of the motor-side rotating shaft are inserted, and the cooling fluid that has passed through the branch passage passes through the end plate and the rotor. The space between the end plate and the axial end surface of the rotor communicates with the space so as to flow into the magnet hole through the space between the axial end surface of the motor side rotation shaft of the motor. A rotating electrical machine cooling structure is provided.

  According to this structure, when the connection state of the motor side connecting portion that rotates integrally with the motor side rotating shaft and the engine side connecting portion that rotates integrally with the engine side rotating shaft is the half-engaged state, the clutch chamber is brought into the clutch chamber. When the coolant is allowed to flow in and the connected state is in the released state, the coolant is prevented from flowing into the clutch chamber, so that the clutch and thus the rotating electrical machine are properly cooled and applied to the rotating shaft. Energy efficiency can be increased by reducing the rotational resistance.

  Specifically, when the connection state between the motor-side rotation shaft and the engine-side rotation shaft is a semi-engagement state, and the connection portions do not rotate integrally, but are in contact with each other, these connection portions are connected. Frictional heat is generated between the parts. On the other hand, in this structure, since the coolant is introduced into the clutch chamber when the connection state between the motor-side rotation shaft and the engine-side rotation shaft is a half-engaged state, The clutch and the rotating electric machine can be properly cooled. In addition, in this structure, as the coupling state between the motor-side rotating shaft and the engine-side rotating shaft is released, the cooling liquid inflow state changing means regulates the inflow of the cooling liquid into the clutch chamber. . For this reason, even when the rotation shafts are individually rotated with the coupled state of the rotation shafts being released to cause a rotational speed difference between the rotation shafts, the rotation shafts rotate between the rotation shafts via the coolant. It is possible to suppress the transmission of force, and it is possible to increase the energy efficiency by suppressing the rotational resistance generated along with the transmission of this rotational force.

  Further, in this structure, even when the connection state between the motor-side rotation shaft and the engine-side rotation shaft is in the engaged state, frictional heat does not occur in the clutch, and the necessity for cooling the clutch is low, Therefore, the driving energy of a pump or the like for introducing the coolant into the clutch can be kept small.

Further, since the coolant is led out radially outside the clutch case in addition to the clutch chamber, it is possible to cool elements that are located radially outside the clutch case while properly cooling the clutch, and It can cool more effectively.

In the present invention, in the structure in which the cooling liquid is led out radially outside the clutch case by the branch passage , the axial end surface of the motor-side rotating shaft of the rotor is disposed on the outer peripheral surface of the clutch case. An end plate that covers the outer side in the axial direction while forming a predetermined space between the end surface and a magnet is inserted into the rotor through the both end surfaces in the axial direction of the motor-side rotating shaft. A magnet hole is formed, and the branch passage passes through the space between the end plate and the axial end surface of the motor-side rotating shaft of the rotor through which the coolant passes through the branch passage. as it flows into the hole, that have communicates with the space between these end plates and the axial end surface of the rotor.

Therefore , the magnet and the rotor can be effectively cooled while the clutch is properly cooled.

In the above configuration, a housing that accommodates the clutch case, the rotor, and the stator inside, an isolation wall that separates the rotor and the stator and defines a stator chamber that accommodates the stator inside the housing; A stator chamber introduction port that communicates with the stator chamber and introduces coolant into the stator chamber; and the coolant that is introduced into the stator chamber and cools the stator is disposed outside the housing. preferably, the stator chamber outlet is formed to derive the (claim 2).

  In this way, the stator can be cooled by the coolant supplied separately to the stator chamber while the clutch, magnet and rotor are effectively cooled by the coolant supplied via the coolant passage. The entire electric machine can be cooled more reliably.

Further, in the case where the branch passage is provided, the amount of the coolant flowing into the clutch chamber can be changed by changing the amount of the coolant flowing into the branch passage from the coolant passage. . Therefore, when the branch passage is provided, the coolant inflow state changing means is provided in the coolant passage, and the connection state between the motor-side rotating shaft and the engine-side rotating shaft is the engagement state and the engine-side rotating shaft. A coolant passage opening / closing means for closing the coolant passage in the released state and opening the coolant passage when the connected state is the half-engaged state; The branch passage is opened in the engaged state and the disengaged state, and at least one of the branch passage opening and closing means for closing the branch passage when the connected state is the half-engaged state. (Claim 3 ).

In the above-described configuration, the cooling liquid flowing state changing means is driven by a clutch driving means for driving the clutch preferable (claim 4).

  If it does in this way, the distribution state of the cooling fluid to the clutch room changed by the cooling fluid inflow state changing means can be changed more reliably according to the connection state of the rotating shaft.

In the above-described configuration, the cooling liquid flowing state changing means comprises said coolant passage opening and closing means, prior Symbol coolant channel opening and closing means, the cooling fluid first switching means passage of a possible opening and closing each of the second switching means The clutch driving means supplies hydraulic pressure to the clutch, the first opening / closing means, and the second opening / closing means to drive them, and the clutch receives the hydraulic pressure supplied by the clutch driving means. When the pressure is less than the first reference oil pressure, the connection state between the motor-side rotation shaft and the engine-side rotation shaft is set to the released state, and the second reference is greater than the first reference oil pressure and greater than the first reference oil pressure. When the hydraulic pressure is less than the hydraulic pressure, the coupled state is set to the half-engaged state, and when the hydraulic pressure is equal to or higher than the second reference hydraulic pressure, the connected state is set to the engaged state, and the first opening / closing means is controlled by the clutch driving means. Serving The coolant passage is closed only when the hydraulic pressure applied is less than the first reference hydraulic pressure, and the second opening / closing means is configured so that the hydraulic pressure supplied by the clutch driving means is higher than the second reference hydraulic pressure. closing the cooling fluid passage, but not preferred.

  By doing so, the coupling state of the rotating shaft is changed to the released state, the semi-engaged state, and the engaged state as the hydraulic pressure supplied to the clutch by the clutch driving means changes in three stages, and this When the coolant inflow state changing means is driven by hydraulic pressure, the accuracy required for the opening / closing means is kept lower than when the opening / closing state of the coolant passage is changed by one opening / closing means in accordance with three stages of oil pressure. be able to. This is advantageous in terms of cost.

Further, in the case where the branch passage is provided, the cooling liquid inflow state changing means is provided in a branch portion of the cooling fluid passage where the branch passage branches, and the branch portion of the cooling fluid passage is more than the branch portion. Switching means for switching the communication destination of the upstream portion between the downstream portion of the coolant passage and the branch passage, wherein the connection state between the motor side rotation shaft and the engine side rotation shaft is the engagement state and In the released state, the communication destination of the upstream portion of the coolant passage is the branch passage, and in the case of the semi-engaged state, the communication destination of the upstream portion of the coolant passage is this. but it may also be used which the downstream portion of the cooling fluid passage.

  In this way, when the rotating shaft is in a half-engaged state, the clutch can be cooled more reliably by increasing the amount of coolant introduced into the clutch chamber, and the rotating shaft can be In the disengaged state and engaged state, the introduction of the coolant into the clutch chamber is stopped to more reliably suppress the rotational resistance and increase the amount of coolant led out radially outside the clutch case. The element located on the radially outer side of the case can be cooled more reliably.

Also in the configuration, the cooling fluid flowing state changing means is driven not preferred by the clutch driving means for driving the clutch.

  If it does in this way, the distribution state of the cooling fluid to the clutch room changed by the cooling fluid inflow state changing means can be changed more reliably according to the connecting state of the connecting portion.

In the above configuration, when the clutch driving means supplies hydraulic pressure to the clutch and the switching means to drive them, and the clutch has a hydraulic pressure supplied by the clutch driving means that is less than a first reference hydraulic pressure. When the motor-side rotating shaft and the engine-side rotating shaft are connected to each other in the released state, and the hydraulic pressure is equal to or higher than the first reference hydraulic pressure and higher than the first reference hydraulic pressure, the combined state In the half-engaged state, as the switching means, a cylinder in which a space through which the coolant can pass is formed, and the inside of the cylinder according to the hydraulic pressure supplied by the clutch driving means. A sliding portion that slides, and the cylinder is formed at a specific position in the sliding direction of the sliding portion, and communicates with an upstream portion of the coolant passage, A first outlet that communicates with a downstream portion of the reject passage, and a second outlet that communicates with the branch passage, and the sliding portions are arranged in the sliding direction and are supplied by the clutch driving means. A first blocking portion that is located at the specific position and closes the first outlet and communicates the inlet and the second outlet when the hydraulic pressure is less than the first reference hydraulic pressure; and the clutch drive When the hydraulic pressure supplied by the means is equal to or higher than the first reference hydraulic pressure and lower than the second reference hydraulic pressure, the inlet and the first outlet are communicated while being positioned at the specific position and closing the second outlet. A second blocking portion to be closed, and when the hydraulic pressure supplied by the clutch driving means is equal to or higher than the second reference hydraulic pressure, the inlet and the second outlet are positioned at the specific position and block the first outlet. Having a third sealing part that communicates with The recited Ru.

  According to this configuration, the communication destination of the portion upstream of the branch portion of the coolant passage can be appropriately switched by the hydraulic pressure supplied by the clutch driving means with a relatively simple configuration.

Further, as the switching means, a cylinder in which a space through which the coolant can pass is formed, and a sliding portion that slides in the cylinder according to the hydraulic pressure supplied by the clutch driving means, respectively. A first switching means and a second switching means, wherein each of the cylinders of the switching means is formed at a specific position in the sliding direction of the sliding portion, and is an upstream portion of the coolant passage. An inlet that communicates with a downstream portion of the coolant passage, a second outlet that communicates with the branch passage, and the sliding portion of the first switching means includes: When the hydraulic pressure supplied by the clutch driving means is less than the first reference hydraulic pressure, the inlet port and the second outlet port are positioned at the specific position and block the first outlet port. The first switching means side first to communicate with When the hydraulic pressure supplied by the clutch driving means is equal to or higher than the first reference hydraulic pressure, the chain and the first outlet are in communication with each other while the second outlet is closed. A first blocking means side second blocking portion, the sliding portions of the second switching means are arranged in the sliding direction, and the hydraulic pressure supplied by the clutch driving means is less than the second reference hydraulic pressure. In this case, the hydraulic pressure supplied from the second switching means side first blocking portion that is located at the specific position and that connects the inlet and the first outlet while closing the second outlet, and the clutch driving means. A second blocking means-side second sealing portion that is located at the specific position and closes the first outlet and connects the inlet and the second outlet when the pressure is equal to or higher than the second reference hydraulic pressure. what is Ru and the like.

  According to this configuration, the communication destination of the portion upstream of the branch portion of the coolant passage can be appropriately switched by the hydraulic pressure supplied by the clutch driving unit with a relatively simple configuration, and one switching unit Therefore, compared with the case where the open / close state of the coolant passage is changed according to the three stages of hydraulic pressure, the accuracy required for the switching means can be kept low, which is advantageous in terms of cost.

  As described above, according to the present invention, it is possible to cool the rotating electrical machine while keeping the rotational resistance small and increasing the energy efficiency.

It is the schematic which shows the cooling structure of the rotary electric machine which concerns on 1st Embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is a figure for demonstrating operation | movement of a clutch. It is a figure for demonstrating operation | movement of a clutch. It is the VV sectional view taken on the line of FIG. (A) It is a figure for demonstrating operation | movement of a switching valve. (B) It is a figure for demonstrating operation | movement of a switching valve. (C) It is a figure for demonstrating operation | movement of a switching valve. It is a figure which shows the other example of a switching valve. It is a figure which shows the other example of a valve | bulb. It is the schematic which shows the cooling structure of the rotary electric machine which concerns on 2nd Embodiment of this invention. It is the schematic which shows the cooling structure of the rotary electric machine which concerns on other embodiment of this invention. It is the schematic which shows the cooling structure of the rotary electric machine which concerns on other embodiment of this invention. It is the XII-XII sectional view taken on the line of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a schematic diagram illustrating a rotating electrical machine system 100 having a rotating electrical machine cooling structure according to an embodiment of the present invention. FIG. 1 shows a cross section of the rotating electrical machine 1, but in order to simplify the drawing, a part of oblique lines indicating the cross section is omitted.

  As shown in FIG. 1, the rotating electrical machine 1 is disposed on a first shaft (motor-side rotating shaft) 3 and a second shaft (engine-side rotating shaft) 4 that are inserted through the housing 2 and inside the housing 2. The clutch case 10, the rotor 30, the stator 40, and the clutch 20 housed inside the clutch case 10.

  The rotating electrical machine 1 is mounted on a hybrid vehicle together with an engine. The second shaft 4 is connected to an engine (not shown) and rotates integrally with the engine. The second shaft 4 is a cylindrical member extending in a predetermined direction, and rotates about its central axis.

  The first shaft 3 is a substantially columnar member arranged coaxially with the second shaft 4. The first shaft 3 and the second shaft 4 are arranged in a state of being slightly separated in the axial direction. The first shaft 3 rotates around its central axis. That is, the first shaft 3 and the second shaft rotate about the same axis. Hereinafter, the axial direction of the shafts 3 and 4 may be simply referred to as the axial direction, and the radial direction of the shafts 3 and 4 may be simply referred to as the radial direction.

  The clutch case 10 extends radially outward from the outer peripheral surface of the first shaft 3. Specifically, the clutch case 10 extends in the axial direction from the outer peripheral surface of the first shaft 3 in the radial direction and from the radially outer end of the first side wall 12 toward the second shaft 4 side. The peripheral wall 13 has a second side wall 14 that extends radially inward from the axial end of the peripheral wall 13 on the second shaft 3 side. The second side wall 14 faces the outer peripheral surface of the second shaft 4. A clutch 20 is disposed in a space 11 surrounded by the side walls 12 and 14 of the clutch case 10, the peripheral wall 13, and the outer peripheral surface of the second shaft 3, and this space constitutes a clutch chamber 11 in which the clutch 20 is accommodated. ing. The clutch case 10 is connected to the outer peripheral surface of the first shaft 3 so as to rotate integrally with the first shaft 3.

  The rotor 30 has a magnet inside thereof and rotates integrally with the first shaft 3. The rotor 30 is disposed on the radially outer side of the clutch case 10, and is fixed to the outer peripheral surface of the clutch case 10 so as to be rotatable integrally with the clutch case 10 and the first shaft 3. In the present embodiment, the rotor 30 is formed by stacking electromagnetic steel plates in the axial direction and embedding a plurality of magnets in the stacked electromagnetic steel plates. As shown in FIG. 2, which is a cross-sectional view taken along line II-II in FIG. 1, a plurality of magnet holes 32 extending in the axial direction and penetrating the rotor 30 are formed in the rotor 30 side by side in the circumferential direction. These magnet holes 32 are larger than the magnets 33. Each magnet 33 is inserted into the magnet hole 32 while forming a passage 32 a penetrating the rotor 30 in the axial direction between the inner peripheral surface of the magnet hole 32 and the outer peripheral surface of the magnet 33.

  The stator 40 is obtained by winding a stator core with a winding 42. The stator 40 is disposed on the radially outer side of the rotor 30 with a slight gap from the rotor 30. Coil ends 42 a are formed at both axial ends of the stator 40. The stator 40 is formed and arranged so that the coil end 42 a protrudes outward in the axial direction from the rotor 30.

  The clutch 20 is configured such that the first shaft 3 and the second shaft 4 are connected to each other, the shafts 3 and 4 are engaged and rotated integrally, and the shafts 3 and 4 are disengaged. In a state where the rotational force is not transmitted between the shafts 3 and 4, and in a state other than the engaged state and the released state, the shafts 3 and 4 do not rotate integrally, while the rotational force is transmitted between the rotational shafts. Change to the semi-engaged state.

  The detailed structure of the clutch 20 will be described with reference to FIGS. FIG. 3 is a view when the connected state of the shafts 3 and 4 is in the released state, and FIG. 4 is a view when the connected state of the shafts 3 and 4 is in the engaged state.

  The clutch 20 is driven by the hydraulic pressure supplied by the oil pump 9 (clutch driving means), and changes the connection state of the shafts 3 and 4 according to the hydraulic pressure.

  The clutch 20 includes a clutch outer 21, a plurality of clutch plates (motor side coupling portions) 22, a clutch inner 23, a plurality of clutch disks (engine side coupling portions) 24, a spring 26, and a clutch piston 27. .

  The clutch outer 21 extends in the axial direction from the inner surface of the first side wall 12 of the clutch case 10 toward the second shaft 3 side. The clutch outer 21 rotates integrally with the clutch case 10 and the first shaft 3. Each clutch plate 22 is a plate-like member that extends in the radial direction, and is arranged in parallel to the axial direction. The clutch plates 22 are connected to the clutch outer 21 and rotate integrally with the clutch outer 21 and the first shaft 3. A plate 29 to which the clutch plate 22 and the clutch disc 24 are pressed is fixed to the end of the clutch outer 21 on the second shaft 4 side.

  The clutch inner 23 is disposed radially inward of the clutch outer 21 and extends substantially parallel to the clutch outer 21. The clutch inner 23 is coupled to the second shaft 4 via the connection portion 4a. Specifically, a connecting portion 4a extending radially from the outer peripheral surface is fixed to the outer peripheral surface of the axial end of the second shaft 4 on the first shaft 3 side so as to be rotatable integrally with the second shaft 4. The clutch inner 23 extends from the radially outer end of the connecting portion 4a toward the first shaft 3 side. The clutch inner 23 rotates integrally with the second shaft 4.

  Each clutch disk 24 is a plate-like member that extends in the radial direction, and is arranged in parallel to the axial direction. The clutch disks 24 are connected to the clutch inner 23 and rotate integrally with the clutch inner 23 and the second shaft 4. The clutch disks 24 and the clutch plates 22 are alternately arranged facing each other. Specifically, the clutch disks 24 are positioned at both ends in the axial direction, and the clutch plate 22 is disposed between the clutch disks 24.

  The clutch piston 27 slides in the axial direction, presses the clutch disk 24 and the clutch plate 22 against the plate 29, and presses the clutch disk 24 and the clutch plate 22 together. The clutch piston 27 is slidably disposed in the axial direction between the first side wall 12 of the clutch case 10 and a portion where the clutch disk 24 and the clutch plate 22 are arranged. The clutch piston 27 extends radially outward along the first side wall 12 and then protrudes toward the clutch disk 24. A space into which oil pumped by the oil pump 9 is introduced is formed between the clutch piston 27 and the first side wall 12. A portion of the outer peripheral surface of the first shaft 3 that defines the clutch chamber 11 that faces the space between the clutch piston 27 and the first side wall 12 is formed inside the first shaft 3 and communicates with the oil pump 9. The clutch oil passage 62 is opened, and oil is supplied from the oil pump 9 to the space between the clutch piston 27 and the first side wall 12 through the clutch oil passage 62.

  The spring 26 is a spring member that can expand and contract in the axial direction, and biases the clutch piston 27 toward the first side wall 12.

  The oil pump 9 is stopped and no oil is pumped between the first side wall 12 and the clutch piston 27, and the oil pressure in the portion between the first side wall 12 and the clutch piston 27, that is, supplied to the clutch 20. When the hydraulic pressure is lower than the first reference pressure, the clutch piston 27 is disposed at a position that contacts the first side wall 12 by the urging force of the spring 26 and is separated from the clutch disk 24 as shown in FIG. Is done. In this arrangement state, the clutch disk 24 and the clutch plate 22 are separated from each other in the axial direction, and the connection state between the first shaft 3 and the second shaft 4 does not transmit the rotational force between the shafts 3 and 4. Released state.

  On the other hand, when the oil pump 9 is driven and the hydraulic pressure between the first side wall 12 and the clutch piston 27 rises above the first reference pressure, the clutch piston 27 resists the biasing force of the spring 26 and the second shaft 4. Side, that is, in a direction close to the clutch disk 24, presses the clutch disk 24 toward the second shaft 4 to bring the clutch disk 24 and the clutch plate 22 into contact with each other.

  Here, when the hydraulic pressure between the first side wall 12 and the clutch piston 27, that is, the hydraulic pressure supplied to the clutch 20 is less than the second reference pressure and is relatively small, the clutch disk 24 and the clutch plate 22 are Although the rotational forces are transmitted to each other by contact with each other, they do not reach a single rotation. That is, the clutch disk 24 and the clutch plate 22 are slid, and the connection state between the first shaft 3 and the second shaft 4 is that the rotational force is transmitted between the shafts 3 and 4 while the shafts 3 and 4 are connected. Are in a semi-engaged state where they do not rotate together.

  On the other hand, when the hydraulic pressure between the first side wall 12 and the clutch piston 27, that is, the hydraulic pressure supplied to the clutch 20 becomes a sufficiently large pressure equal to or higher than the second reference pressure, as shown in FIG. The clutch plate 22 is pressed against the plate 29 by the clutch piston 27 and is sandwiched between the clutch piston 27 and the plate 29 so as to rotate integrally with each other. And the connection state of the 1st shaft 3 and the 2nd shaft 4 is made into the engagement state which these shafts 3 and 4 rotate integrally.

  As described above, when the connection state between the first shaft 3 and the second shaft 4 is in a half-engaged state, the clutch disk 24 and the clutch plate 22 slide, and frictional heat is generated between them. On the other hand, in the rotating electrical machine system 100 according to the present embodiment, the coolant is supplied into the clutch chamber 11 to cool the clutch 20 to suppress adverse effects due to frictional heat.

  A coolant path of the rotating electrical machine system 100 according to the present embodiment will be described.

  A main coolant passage (coolant passage) 70 for introducing coolant into the clutch chamber 11 is formed inside the first shaft 3 and communicates with the clutch chamber 11 in the shaft, and this shaft coolant. It comprises an external coolant pipe 72 that communicates with the passage 71 and introduces the coolant into the first shaft 3.

  The external cooling liquid pipe 72 is provided outside the housing 2 and the first shaft 3, and includes a cooling liquid pump 79 that discharges the cooling liquid and an in-shaft cooling liquid passage 71 formed on the outer peripheral surface of the first shaft 3. Are communicated with the opening 71a. As shown in FIG. 5 which is a cross-sectional view taken along line VV in FIG. 1, in this embodiment, two in-shaft coolant passages 71 are formed in the first shaft 3 in a state of being separated from each other by 90 degrees. . Accordingly, two openings 71 a of the in-shaft coolant passage 71 are formed on the outer peripheral surface of the first shaft 3. The external coolant pipes 72 communicate with the openings 71a.

  Each of the in-shaft coolant passages 71 extends radially inward from an opening 71a formed on the outer peripheral surface of the first shaft 3, and then extends in the axial direction toward the second shaft 4 side. Each of the in-shaft coolant passages 71 is open to the end surface on the second shaft side of the first shaft 3 in the axial direction. An opening 71 b formed on the axial end surface of each in-shaft coolant passage 71 communicates with the clutch chamber 11. Specifically, the end surface on the second shaft side in the axial direction of the first shaft 3 and the end surface on the first shaft side of the second shaft 4 facing the end surface and the connecting portion 4a are spaced apart in the axial direction. The opening 71b and the clutch chamber 11 communicate with each other through the gap.

  A branch passage 80 is provided in the main coolant passage 70 to guide the coolant to the outside in the radial direction of the clutch case 10 without passing through the clutch chamber 11. The branch passage 80 includes a branch-side external coolant pipe 81, a branch-side shaft coolant passage 82, and a clutch case passage 83 in order from the upstream.

  The branch side external coolant pipe 81 is provided outside the housing 2 and the first shaft 3, and is connected to a branch part 72 a that is an intermediate part of the external coolant pipe 72. The branch-side shaft coolant passage 82 is formed in the first shaft 3. In the present embodiment, as shown in FIG. 5, two branch-side shaft coolant passages 82 are formed in the first shaft 3 so as to be separated from each other by 90 degrees. Along with this, two openings 82 a of the branch-side shaft coolant passage 82 are formed on the outer peripheral surface of the first shaft 3. The branch side external coolant pipe 81 communicates the branch portion 72a with the openings 82a.

  Each branch-side shaft coolant passage 82 extends radially inward from an opening 82 a formed on the outer peripheral surface of the first shaft 3, and then extends in the axial direction toward the second shaft 4. A portion of the case 10 facing the first side wall 12 extends radially outward.

  The clutch case inner passage 83 is formed in the first side wall 12 of the clutch case 10. The clutch case inner passage 83 is a portion of the branch side shaft inner coolant passage 82 that faces the first side wall 12 and communicates with a portion that extends radially outward, and from the inner side of the first shaft 3 in the radial direction. It extends outward. As shown in FIG. 2, eight clutch case inner passages 83 are formed in the first side wall 12 at equal intervals in the circumferential direction. That is, the end of the branch-side shaft coolant passage 82 on the second shaft 4 side in the axial direction is an annular portion extending around the first shaft 3 and a portion extending radially outward from eight locations of the annular portion. Each clutch case passage 83 communicates with a portion extending outward in the radial direction.

  The clutch case inner passage 83 is open to the outer peripheral surface of the first side wall 12, that is, the outer peripheral surface of the clutch case 10. The opening 83 a of the clutch case inner passage 83 is formed on the outer peripheral surface of the clutch case 10 at a position that is axially outer than the rotor 30 and faces the coil end 42 a of the stator 40. That is, the clutch case 10 protrudes outward in the axial direction from the rotor 30, and the clutch case inner passage 83 is an opening at a position that is opposed to the coil end 42 a.

  The first side wall 12 is formed with a communication path 75 that connects the clutch case inner path 83 and the clutch chamber 11. The communication path 75 is provided on the radially outer side than the clutch 20.

  The cooling liquid supplied from the cooling liquid pump 79 to the external cooling liquid pipe 72, which does not branch to the branching-side external cooling liquid pipe 81 in the branching portion 72 a and proceeds directly through the external cooling liquid pipe 72, After flowing into the coolant passage 71 and proceeding through the in-shaft coolant passage 71 toward the second axial shaft 4 side, the first shaft 3, the second shaft 4 and the first shaft 3 are opened from the opening 71 b on the axial end surface of the first shaft 3. It flows into the clutch chamber 11 through a gap with the connecting portion 4a. In the clutch chamber 11, the coolant receives a centrifugal force generated with the rotation of the rotating electrical machine 1, moves to the radially outer side while cooling the clutch 20, and flows into the communication path 75. Here, as shown in FIGS. 3 and 4, the clutch inner 23 and the clutch outer 21 of the clutch 20 are formed with through holes 23 a and 21 a penetrating in the radial direction, respectively. It moves radially outward through the holes 23a, 21a and the like. The coolant that has flowed into the communication passage 75 flows into the clutch case inner passage 83 and moves radially outward in the clutch case passage 83, and then radially outward of the clutch case 10 from the opening 83 a of the clutch case inner passage 83. To be derived. The cooling liquid led out radially outward of the clutch case 10 contacts the rotor 30 and the stator 40 disposed on the radially outer side of the clutch case 10, particularly the coil end 42 a of the stator 40, and cools them. A discharge port 2 a provided in the housing 2 is discharged to the outside of the housing 2.

  On the other hand, the coolant supplied to the external coolant pipe 72 from the coolant pump 79 and branched to the branch-side external coolant pipe 81 flows into the branch-side shaft coolant passage 82 and enters this branch. After the side shaft inner coolant passage 82 has advanced in the axial direction toward the second shaft 4, the portion proceeds to the outer side in the radial direction at a portion facing the first side wall 12. The coolant further passes through the clutch case inner passage 83 and moves outward in the radial direction, and is led out from the opening 83 a of the clutch case inner passage 83 to the outer side in the radial direction of the clutch case 10. The coolant led out radially outward of the clutch case 10 is directed to the rotor 30 and the stator 40 disposed radially outward of the clutch case 10, and after cooling them, the coolant is discharged from a discharge port 2 a provided in the housing 2. It is discharged outside the housing 2. As described above, after contacting and cooling the rotor 30 and the stator 40 arranged on the radially outer side of the clutch case 10 and in particular the coil end 42a of the stator 40, the discharge port 2a provided in the housing 2 is used. It is discharged to the outside of the housing 2.

  The branch part 72 a has a communication destination in a portion upstream of the branch part 72 a in the external coolant pipe 72, a downstream part of the external coolant pipe 72, and a branch side external coolant pipe 81 of the branch passage 80. A switching valve (switching means, cooling liquid inflow state changing means) 50 is provided.

  Details of the switching valve 50 will be described with reference to FIGS. 1 and 6A to 6C. 6A to 6C, the left side view and the right side view are schematic cross-sectional views when the switching valve 50 is cut along planes orthogonal to each other. That is, the diagram on the right side is a cross-sectional view taken along the line AA of the diagram on the left side. FIGS. 6A to 6C are views in a state where valves 52 described later are arranged at different positions.

  The switching valve 50 includes a substantially rectangular cylinder 51 in which a space through which a coolant can pass is formed, and a valve (sliding portion) that is disposed in the cylinder 51 and can slide in the cylinder 51 in a predetermined direction. ) 52 and a spring 56 disposed in the cylinder 51. Here, a case where the valve 52 slides in the vertical direction will be described.

  The outer surface of the cylinder 51 communicates with an inlet 51a that communicates with a portion of the external coolant pipe 72 that is upstream of the branch portion 72a, and with a portion of the external coolant pipe 72 that is downstream of the branch portion 72a. The leading outlet (first outlet) 51b and the branching outlet (second outlet) 51c communicating with the branching external coolant pipe 81 are opened. The inlet 51a, the main outlet 51b, and the branching outlet 51c are formed at substantially the same height. The inlet 51a and the main outlet 51b are opposed to each other, and the branch-side outlet 51c is located between the inlet 51a and the main outlet 51b on the outer surface of the cylinder 51 (for example, the inlet 51a and the main outlet 51b). (Positions 90 degrees apart from each other).

  An oil pressure supply port 51 d for supplying oil pressure for sliding the valve 52 to the inside of the cylinder 51 is opened on the bottom surface of the cylinder 51. In the present embodiment, the oil pump 9 that supplies hydraulic pressure to the clutch 20 supplies hydraulic pressure to the switching valve 50, and the hydraulic supply port 51 d communicates with the oil pump 9. In other words, the oil passage 60 connected to the discharge port of the oil pump 9 branches in the middle of a switching valve oil passage 61 toward the switching valve 50 and a clutch oil passage 62 toward the clutch 20. As described above, in the present embodiment, the switching valve 50 is provided outside the housing 2 and the first shaft 3, and the switching valve oil passage 61 is located outside the oil pump 9 and the switching valve 50. It communicates with the supply port 51d. On the other hand, the clutch oil passage 62 branches from the switching valve oil passage 61 outside the housing 2 and the first shaft 3, and then extends in the axial direction toward the second shaft 4 inside the first shaft 3. It extends radially outward toward the rear clutch chamber 11 and communicates with the clutch chamber 11.

  A stopper 57 is formed on the inner peripheral surface of the cylinder 51 so as to protrude inward and come into contact with the lower surface of the valve 52.

  The valve 52 is arranged in a portion above the stopper 57 in the cylinder 51 in a state of being biased downward by the spring 56. The lower surface of the valve 52 has substantially the same shape as the cross section of the cylinder 51, and oil supplied from the oil pump 9 flows between the lower surface of the valve 52 and the bottom surface of the cylinder 51 through the hydraulic pressure supply port 51d. An oil chamber 51f is formed. The oil pressure in the oil chamber 51 f changes in conjunction with the oil pressure in the clutch chamber 11 to which oil is supplied from the same oil pump 9, specifically, the oil pressure between the first side wall 12 and the clutch piston 27. In the present embodiment, the hydraulic pressure in the oil chamber 51f is set to the same value as the hydraulic pressure in the clutch chamber 11.

  When the oil pressure in the oil chamber 51f is small, the valve 52 is disposed at a position where it abuts against the stopper 57 by the biasing force of the spring 56, and the spring 56 is attached as the oil pressure in the oil chamber 51f increases. Slides up against the forces.

  The valve 52 includes, in order from the top, a seating portion (first blocking portion) 53 whose upper surface functions as a seating surface of the spring 56, a pair of opposing support portions 54a and 54b, and an oil chamber 51f below the oil chamber 51f. And a pressure receiving portion (third sealing portion) 55 for receiving the hydraulic pressure in the chamber 51f. These parts 53, 54a, 54b, and 55 are slidably coupled together.

  The seating portion 53 and the pressure receiving portion 55 are plate-like members having substantially the same cross section as the cylinder 51, and are disposed at positions (specific positions) facing the introduction port 51a, the main outlet 51b, and the branch side outlet port 51c. In this case, the main outlet 51b has a thickness larger than the hole height of the main outlet 51b so that the main outlet 51b can be blocked by the outer surface. When the seating portion 53 and the pressure receiving portion 55 are arranged at positions facing the inlet 51a, the main outlet 51b, and the branching outlet 51c, the outer surface of the seating portion 53 and the pressure receiving portion 55 is branched from the portion facing the inlet 51a. Through holes 53a and 55a penetrating to the portion facing the outlet 51c are formed.

  The support portions 54 a and 54 b are plate-like members that extend along the inner surface of the cylinder 51 across the seating portion 53 and the pressure receiving portion 55. When these support portions 54a and 54b are arranged at positions opposed to the introduction port 51a, the main outlet 51b, and the branch side outlet 51c, the support portions 54a and 54b are led from the introduction port 51a via the space between the support portions 54a and 54b. The outlets 51b are separated from each other so as to communicate with each other. In addition, the support portion 54a disposed on the side where the branch side outlet 51c is formed among the support portions 54a and 54b is disposed at a position facing the introduction port 51a, the main outlet 51b, and the branch side outlet 51c. The inner side surface of the cylinder 51 extends along a portion where the branch side outlet 51c is formed, and the outer side surface closes the branch side outlet 51c. The branch side outlet 51c It functions as a branching path blocking part (second blocking part) that closes.

  As shown in FIG. 6A, when the oil pump 9 is stopped and the hydraulic pressure in the clutch chamber 11 and the oil chamber 51f is set to a low pressure lower than the first reference hydraulic pressure, the connected state of the shafts 3 and 4 Becomes a released state, and the valve 52 comes into contact with the stopper 57. In this state, the seating portion 53 is disposed at a position facing the introduction port 51a, the main exit 51b, and the branch side outlet 51c. And a seating part connects the inlet 51a and the branch side outlet 51c via the through-hole 53a, blocking the main exit 51b by the outer surface. As a result, the communication destination of the upstream portion of the external coolant pipe 72 is the branch-side external coolant pipe 81.

  On the other hand, as shown in FIG. 6 (b), when oil pressure higher than the first reference oil pressure and less than the second reference oil pressure is supplied from the oil pump 9 into the clutch chamber 11 and the oil chamber 51f, the shafts 3, 4 The connection state is set to the half-engaged state, and the valve 52 moves upward from the position where it contacts the stopper 57. In this state, the branch path blocking portion 54a is disposed at a position facing the inlet 51a, the main outlet 51b, and the branch side outlet 51c. At this time, the branch path blocking portion 54a closes the branch side lead-out portion 51c at the outer surface, and the introduction port 51a and the main outlet 51b are located between the branch path blocking portion 54a and the support portion 54b facing the branch path blocking portion 54a. It communicates through the space. Thereby, the communication destination of the upstream portion of the external coolant pipe 72 is the downstream portion of the external coolant pipe 72.

  As shown in FIG. 6C, when a hydraulic pressure higher than the second reference hydraulic pressure is supplied from the oil pump 9 into the clutch chamber 11 and the oil chamber 51f, the coupled state of the shafts 3 and 4 is the engaged state. At the same time, the valve 52 moves further upward. In this state, the pressure receiving portion 55 is disposed at a position facing the inlet 51a, the main outlet 51b, and the branch side outlet 51c. And the pressure receiving part 55 makes the inlet 51a and the branch side outlet 51c communicate with each other through the through hole 55a while closing the main outlet 51b on its outer surface. As a result, the communication destination of the upstream portion of the external coolant pipe 72 is the branch-side external coolant pipe 81.

  As described above, the switching valve 50 is used when the hydraulic pressure supplied from the oil pump 9 to the clutch chamber 11 and the oil chamber 51f is lower than the first reference pressure, and when the connected state of the shafts 3 and 4 is released. When the hydraulic pressure is equal to or higher than the second reference pressure and the connected state of the shafts 3 and 4 is in the engaged state, the communication destination of the upstream portion of the external coolant pipe 72 is connected to the branch-side external coolant pipe 81. To do. Accordingly, when the coupling state of the shafts 3 and 4 is the released state and the engaged state, the coolant discharged from the coolant pump 79 does not flow into the clutch chamber 11, and all of the branch side shaft It is led out to the rotor 30 and the stator 40 from the opening 83 a of the clutch case inner passage 83 through the inner coolant passage 82 and the clutch case inner passage 83.

  In the switching valve 50, when the hydraulic pressure supplied from the oil pump 9 to the clutch chamber 11 and the oil chamber 51f is equal to or higher than the first reference pressure and lower than the second reference pressure, the connection state of the shafts 3 and 4 is half-engaged. In the case of the state, the communication destination of the upstream portion of the external coolant pipe 72 is the downstream portion of the external coolant pipe 72. Accordingly, when the coupling state of the shafts 3 and 4 is in the half-engaged state, the coolant discharged from the coolant pump 79 does not flow into the branch passage 80, but all of the external coolant pipe 72 and It is introduced into the clutch chamber 11 through the in-shaft coolant passage 71. .

  As described above, in the rotating electrical machine system 100, when the connection state of the first shaft 3 and the second shaft 4 is a half-engaged state, frictional heat is generated between the clutch disk 24 and the clutch plate 22. The upstream portion of the external coolant pipe 72 communicates with the branch-side external coolant pipe 81, the main coolant passage 70 is closed, and the branch passage 80 is opened. All of the coolant discharged from the coolant pump 79 is introduced into the clutch chamber 11 without flowing into the branch-side external coolant tube 81, that is, the branch passage 80. Therefore, a large amount of coolant in the clutch chamber 11 can be ensured, the clutch 20 can be effectively cooled, and adverse effects due to frictional heat can be kept small.

  Further, when the connection state between the first shaft 3 and the second shaft 4 is released and it is desired to cause a difference in rotational speed between the shafts 3 and 4, that is, when the shafts 3 and 4 are to be rotated individually. The main coolant passage 70 is opened, the branch passage 80 is closed, and the coolant discharged from the coolant pump 79 is led to the rotor 30 and the stator 40 without flowing into the clutch chamber 11. Therefore, the rotor 30 and the stator 40 can be cooled while increasing the rotation efficiency and thus the energy efficiency. That is, when there is a rotational speed difference between the shafts 3 and 4, that is, the clutch disk 24 and the clutch plate 22, if a coolant is interposed between the clutch disk 24 and the clutch plate 22, these clutch disks are passed through the coolant. Rotational force is transmitted between the clutch plate 22 and the clutch plate 22 and rotational resistance is generated, resulting in a deterioration in rotational efficiency. However, in the present system 100, as described above, the connected state of the shafts 3 and 4 is in the released state. 3, 4, that is, when there is a difference in rotational speed between the clutch disk 24 and the clutch plate 22, the introduction of the coolant into the clutch chamber 11 is prohibited, so that the generation of rotational resistance is avoided and the rotational efficiency is increased. be able to.

  In addition, when the connected state of the shafts 3 and 4 is in the released state, and when the connected state is the engaged state, the clutch disk 24 and the clutch plate 22 rotate integrally, and frictional heat is generated between them. If not, since the branch passage 80 is opened and the coolant is led out toward the rotor 30 and the stator 40, the rotor 30 and the stator 40 are cooled to effectively cool the entire rotating electrical machine 1. can do. In particular, in this embodiment, the opening 83a of the clutch case passage 83 faces the coil end 42a of the stator 40, and the coolant is led out toward the coil end 42a. Can be cooled.

  In the present embodiment, the switching valve 50 is driven by an oil pump 9 that supplies hydraulic pressure to the clutch 20 to drive the clutch 20. Therefore, the open / close state of the branch passage 80 and the main coolant passage 70 can be appropriately opened / closed in conjunction with the operating state of the clutch 20, that is, the connected state of the shafts 3 and 4.

  Here, the specific structure of the switching valve for switching the communication destination of the upstream portion of the external coolant pipe 72 between the downstream portion of the external coolant pipe 72 and the branch side external coolant pipe 81 is not limited to the above. . For example, as shown in FIGS. 7A, 7 </ b> B, and 7 </ b> C, two switching valves 250 and 350 (upstream switching valves (first) are arranged on the external coolant pipe 72 in order from the upstream side. (Switching means) 250 and downstream switching valve (first switching means) 350).

  Similar to the switching valve 50 shown in FIG. 6, the upstream side switching valve 250 includes a cylinder 251, a valve (sliding portion) 252, a spring 256, and a stopper 257. Similarly, the downstream side switching valve 350 includes a cylinder 351, a valve (sliding portion) 352, a spring 356, and a stopper 357. In addition, the cylinders 251 and 351 of the upstream side switching valve 250 and the downstream side switching valve 350 are respectively provided with inlets 251a and 351a that communicate with the portions of the external coolant pipe 72 that are upstream of the switching valves 250 and 350. The main outlets (first outlets) 251b and 351b communicating with the downstream portion of the external coolant pipe 72, and the branch outlets (second outlets) 251c and 351c communicating with the branch-side external coolant pipe 81 Is formed. Further, the valve 252 of the upstream side switching valve 250 includes a seating portion (first switching means side first sealing portion) 253, a branch side sealing portion (first switching means side second sealing portion) 254a, and a pressure receiving portion 255, respectively. The valve 352 of the downstream side switching valve 350 includes a seating portion 353, a branch side blocking portion (second switching means side first blocking portion) 354a, and a pressure receiving portion (second switching means side second sealing block). Part) 355.

  However, the pressure receiving portion 255 of the upstream side switching valve 250 and the seating portion 353 of the downstream side switching valve 350 are not formed with a through hole that allows the introduction port 251a and the branch side external coolant pipe 81 to communicate with each other. Each switching valve 250, 350 does not switch the communication destination of the upstream portion of the external coolant pipe 72 in accordance with the three-stage hydraulic pressure change as in the example shown in FIG. The communication destination is switched according to a change in hydraulic pressure.

  Specifically, the upstream side switching valve 250 closes the main outlet 251b by the seating portion 253 when the hydraulic pressure in the oil chamber 251f is lower than the first reference pressure, and allows the inlet 251a and the branch outlet 251c to communicate with each other. Thus, when the communication destination of the upstream portion of the external coolant pipe 72 is the branch-side external coolant pipe 81, and the hydraulic pressure in the oil chamber 251f is equal to or higher than the first reference pressure, is the hydraulic pressure equal to or higher than the second reference pressure? Regardless, the branch side outlet 251c is closed by the branch side blocking portion 254a, and the inlet 251a and the main outlet 251b are connected to each other, and the communication destination is the downstream portion of the external coolant pipe 72.

  When the hydraulic pressure in the oil chamber 351f is equal to or higher than the second reference pressure, the downstream side switching valve 350 closes the main outlet 351b by the pressure receiving portion 355 and connects the inlet 351a and the branch outlet 351c. In the case where the upstream side of the external coolant pipe 72 is connected to the branch side external coolant pipe 81 and the oil pressure in the oil chamber 351f is lower than the second reference pressure, whether the oil pressure is equal to or higher than the first reference pressure. Regardless, the branch side outlet 351c is blocked by the branch side blocking portion 354a, and the one inlet 351a and the main outlet 351b are communicated with each other so that the communication destination is the downstream portion of the external coolant pipe 72. Here, when the hydraulic pressure is lower than the first reference pressure, the upstream side switching valve 250 causes the communication destination of the portion of the external cooling liquid pipe 72 upstream of the upstream side switching valve 250 to be the branch side external cooling liquid pipe. The external coolant pipe 72 is closed by the upstream side switching valve 250. For this reason, when the hydraulic pressure is less than the first reference pressure, the upstream side switching valve 250 causes the external cooling liquid pipe 72 to be connected to the upstream side switching valve 250 even though the downstream side switching valve 350 of the external cooling liquid pipe 72 is in communication. It is closed and the communication destination is only the branch side external coolant pipe 81.

  In this way, the switching valve is a switching valve that switches the communication destination of the upstream side portion of the external coolant pipe 72 in two patterns according to a two-stage hydraulic pressure change, and the switching patterns for the hydraulic pressure are different from each other. In this case, the switching accuracy, that is, the control accuracy required for the switching valve can be kept low compared to the case where the communication destination is switched in three stages with one switching valve. This is advantageous in terms of cost. In addition, when the switching accuracy is the same, switching can be performed more appropriately than when switching in three stages, and even if an unexpected control error occurs in the switching valve, it is more reliable. In addition, the communication destination can be appropriately switched.

  However, if the switching is performed with one switching valve 50, the structure can be simplified and the number of parts can be reduced.

  Further, as shown in FIG. 8, a valve capable of opening and closing each of the main coolant passage 70 and the branch passage 80 on the downstream side of these branch portions 572a is provided, and each passage 70, 80 may be individually closed. As a valve (coolant passage opening / closing means) for opening and closing the main coolant passage 70, for example, as shown in FIG. 8, a valve 450 excluding the through holes of the seating portion and the pressure receiving portion from the valve shown in FIG. 6 is used. Can do. Further, as a valve (branch passage opening / closing means) for opening and closing the branch passage 80, for example, as shown in FIG. 8, provided on the branch side external coolant pipe 81, the valve shown in FIG. This is a valve provided with a sealing plate 559 located between the portion 553 and the pressure receiving portion 555, and this sealing plate when the hydraulic pressure supplied to the oil chamber 551f is equal to or higher than the first reference hydraulic pressure and lower than the second reference hydraulic pressure. A valve 550 that closes the branch-side external cooling pipe 81 by closing the introduction port 550a that is formed in the cylinder 551 and communicates with the upstream side of the branch-side external coolant pipe 81 and the outlet port 550b that communicates with the downstream side. Can be used. However, the specific configuration of each valve is not limited to this. For example, as a valve for opening and closing the main coolant passage 70, two valves that change the open / close state of the external coolant pipe 72 according to a two-stage hydraulic pressure change and that have different opening / closing patterns with respect to the hydraulic pressure are used. Also good.

  Further, a valve capable of opening and closing the passage may be provided only in one of the main coolant passage 70 and the branch passage 80. That is, a valve capable of opening and closing the main coolant passage 70 may be provided only in the main coolant passage 70. Alternatively, the amount of the coolant flowing into the main coolant passage 70 may be changed by providing a valve capable of opening and closing the branch passage 80 only in the branch passage 80 and changing the amount of the coolant flowing into the branch passage 80.

  Further, the switching valve that switches the communication destination of the upstream portion of the main coolant passage 70 or the valve that can open and close the main coolant passage 70 and the branch passage 80 may be provided inside the rotating electrical machine 1. For example, as shown in FIG. 9, a valve 650 that opens and closes the main coolant passage 70 may be provided in the first shaft 3. In the example shown in FIG. 9, the branch passage 80 is branched at a branch portion 672 a formed in the first shaft 3 and extending in the axial direction in the shaft coolant passage 71, and only a portion extending radially outward is provided. Consists of. The valve 650 is provided in a portion of the in-shaft coolant passage 71 downstream from the branch portion 672a, and hydraulic pressure is supplied from a portion of the oil passage 60 formed in the first shaft 3. It is configured to be driven by this hydraulic pressure. In addition, when providing a valve | bulb inside the member which rotates in this way, it is preferable to provide a valve | bulb at equal intervals in the circumferential direction so that a rotation fluctuation may not arise with providing a valve.

  Further, the structure for cooling the rotor and the stator is not limited to the above, and may be the structure shown in FIG.

  In the rotating electrical machine system 700 shown in FIG. 10, end plates 731 and 732 that cover the axial end surface of the rotor 30 from the axially outer side are provided on the radially outer side of the clutch case 10. The end plates 731 and 732 cover the axial end surface of the rotor 30 over the entire circumference, and cover the axial end surface of the rotor so that a predetermined space is formed between the end plates 731 and 732 and the axial end surface of the rotor 30. Yes.

  A clutch case inner passage 83 formed on the first side wall 12 of the clutch case 10 in the branch passage 80 and extending radially outward from the first shaft 3 side is an end plate 731 disposed on the outer side of the first side wall 12. And the end plate 731 extends to a position communicating with a space between one end face in the axial direction of the rotor 30.

  A main discharge passage 4 b for discharging the coolant to the outside of the housing 2 is formed inside the second shaft 4. Further, the main discharge passage 4b is communicated with the second side wall 14 between a space between the end plate 732 disposed outside the second side wall 14 and the other end surface in the axial direction of the rotor covered by the end plate 732. A clutch case discharge passage 14a is formed.

  In the rotating electrical machine system 700 configured as described above, the coolant is led out to the space between the end plate 731 and one end surface in the axial direction of the rotor 30 through the clutch case passage 83. The derived cooling liquid cools the magnet 33 and the rotor 30, and forms in the magnet hole 32 formed in the rotor 30, specifically, between the inner peripheral surface of the magnet hole 32 and the outer peripheral surface of the magnet 33. The passage 32a is led out to a space between the end surface 732 and the other end surface in the axial direction of the rotor 30, and is discharged from the main discharge passage 4b to the outside of the housing 2 through the discharge passage 14a in the clutch case. The

  In the example shown in FIG. 10, the coolant in the clutch chamber 11 is not led out into the clutch case passage 83 and is discharged to the outside of the clutch case 10 through the communication passage 775 formed in the first side wall 12. The

  Thus, in this rotating electrical machine system 700, the magnet 33 of the rotor 30 is particularly cooled by the coolant in the clutch case inner passage 783, that is, the coolant passing through the branch passage 80.

  Further, the rotating electrical machine system 700 is provided with an isolation wall 790 that isolates the rotor 30 and the stator 40 and defines a stator chamber 790 a that houses the stator 40 inside the housing 2. The outer peripheral wall 2b of the housing 2 is formed with a stator chamber introduction port 2c and a stator chamber outlet port 2d that penetrate the inside and outside of the housing 2 and communicate the interior of the stator chamber 790a with the housing 2. The stator chamber inlet 2c and the stator chamber outlet 2d are formed at positions that are substantially opposite in the axial direction and the circumferential direction. The stator chamber introduction port 2c is for introducing a coolant into the stator chamber 790a, and the coolant introduced into the stator chamber 790a via the stator chamber introduction port 2c cools the stator, It is discharged to the outside from the stator chamber outlet 2d. A cooling liquid is always stored in the stator chamber 790a, and the stator 40 is always cooled by this cooling liquid.

  Thus, in this rotating electrical machine system 700, the stator 40 is cooled separately from the rotor 30, and the rotor 30 and the stator 40 are each effectively cooled.

  In this rotating electrical machine system 700, a passage 2 e is formed in the stator chamber 790 a to connect a portion radially inward of the isolation wall 790 and the outside of the housing 2, and the clutch is passed through the communication passage 775 from the clutch chamber 11. The coolant discharged to the outside of the case 10 is discharged to the outside of the housing 2 through this passage 2e.

  A branch passage 80 is branched from the main coolant passage for introducing the coolant discharged from the coolant pump 79 into the clutch chamber 11, and the coolant is passed through the clutch case 10 in the radial direction without passing through the clutch chamber 11. The branch passage 80 (the branch-side external coolant pipe 81, the branch-side shaft coolant passage 82, and the clutch case passage 83) may be omitted. For example, as shown in FIG. 11, as the rotating electrical machine system 800, the coolant discharged from the coolant pump 79 passes through the external coolant pipe 872 and the in-shaft coolant passage 871 in the main coolant passage 870. It may be configured to be introduced only into the clutch chamber 11. In this case, the valve 450 shown in FIG. 8 may be used as a valve for opening and closing the main coolant passage 870. Instead of the valve 450, a valve in which the through holes 253a and 355a of the seating part and the pressure receiving part are excluded from the valve shown in FIG. Here, in the example shown in FIG. 11, as shown in FIG. 12, which is a cross-sectional view taken along the line XII-XII of FIG. 11, four are formed in the first shaft 3 in a state of being separated from each other by 90 degrees. Therefore, compared with the embodiment in which two in-shaft coolant passages 71 shown in FIGS. 1 and 5 are provided, the coolant can be further diffused in the circumferential direction of the first shaft 3 in the clutch chamber 1. The clutch 20 can be efficiently cooled.

  In the example shown in FIG. 11, similarly to the example shown in FIG. 10, the coolant in the clutch chamber 11 is discharged to the outside of the clutch case 10 through the communication path 775 formed in the first side wall 12. Further, in the example shown in FIG. 11, as in the example shown in FIG. 10, there is an isolation wall 790 that separates the rotor 30 and the stator 40 and partitions the stator chamber 790 a that houses the stator 40 inside the housing 2. The cooling liquid is always stored in the stator chamber 790a, and the stator 40 is always cooled by this cooling liquid.

  The present invention is not limited to the above-described embodiment, and can be substituted without departing from the scope of the claims.

1 Rotating electrical machine 3 1st shaft (motor side rotating shaft)
4 Second shaft (engine-side rotating shaft)
11 Clutch chamber 20 Clutch 22 Clutch plate (motor side connecting part)
24 Clutch disc (engine side connecting part)
50 switching valve (switching means, cooling liquid inflow state changing means)

Claims (4)

A cooling structure for a rotating electrical machine having an engine-side rotating shaft that rotates integrally with an engine, and a motor-side rotating shaft that is connected to the engine-side rotating shaft and rotates around a predetermined axis,
A motor-side connecting portion that rotates integrally with the motor-side rotating shaft; and an engine-side connecting portion that rotates integrally with the engine-side rotating shaft, and the motor-side rotating shaft is engaged by engaging these connecting portions. And the engine-side rotating shaft are connected to each other so that the rotating shafts engage with each other and rotate together, and the connecting portions are disengaged and separated from each other, thereby connecting the rotating shafts to each other. The state is set to a release state in which no rotational force is transmitted between the rotation shafts, and the connection portions of the rotation shafts are brought into contact with each other without engaging the connection portions, and the states other than the engagement state and the release state. A clutch that is in a semi-engaged state in which the rotational force is transmitted between the rotating shafts without rotating the rotating shafts integrally;
A clutch case that extends radially outward from the outer peripheral surface of the motor-side rotary shaft, rotates integrally with the motor-side rotary shaft, and has a clutch chamber that houses the clutch inside;
A rotor that is disposed on an outer peripheral surface of the clutch case and rotates integrally with the motor-side rotation shaft;
A stator that is disposed on the radially outer side of the rotor and wound;
An end plate disposed on an outer peripheral surface of the clutch case and covering an axial end surface of the motor-side rotating shaft of the rotor from the outer side in the axial direction while forming a predetermined space with the end surface;
A coolant passage that communicates with the clutch chamber through the motor-side rotary shaft and introduces coolant into the clutch chamber through the motor-side rotary shaft;
A passage extending from the inside of the motor-side rotary shaft toward the radially outer side of the clutch case through the inside of the clutch case, and branching off from the coolant passage and supplying the coolant in the coolant passage to the clutch chamber A branch passage that leads to the radially outer side of the clutch case without going through,
A coolant inflow state changing means capable of changing the inflow state of the coolant into the clutch chamber,
The cooling liquid inflow state changing means regulates inflow of the cooling liquid into the clutch chamber when the connection state between the motor side rotating shaft and the engine side rotating shaft is the engaged state and the released state. , Allowing the coolant to flow into the clutch chamber when the connected state is the half-engaged state ,
The rotor is formed with a magnet hole through which the magnet is inserted through both end surfaces in the axial direction of the motor-side rotation shaft.
The branch passages are configured so that the coolant that has passed through the branch passage flows into the magnet holes through a space between the end plate and the axial end surface of the motor-side rotation shaft of the rotor. A cooling structure for a rotating electric machine, characterized in that it communicates with a space between an end plate and an axial end surface of a rotor . The cooling structure for a rotating electrical machine according to claim 1 ,
A housing that houses the clutch case, the rotor, and the stator inside;
An isolation wall that separates the rotor and the stator and defines a stator chamber that houses the stator inside the housing;
The housing communicates with the stator chamber and introduces a cooling fluid into the stator chamber and introduces a cooling fluid introduced into the stator chamber and cooling the stator to the outside of the housing. A cooling structure for a rotating electrical machine, wherein a chamber outlet is formed. The cooling structure for a rotating electrical machine according to claim 1 or 2 ,
The cooling liquid inflow state changing means is provided in the cooling liquid passage and closes the cooling liquid passage when the connection state between the motor side rotation shaft and the engine side rotation shaft is the engagement state and the release state. And a coolant passage opening / closing means for opening the coolant passage when the connected state is the half-engaged state, and provided in the branch passage and when the connected state is the engaged state and the released state. And a branch passage opening / closing means for opening the branch passage and closing the branch passage when the connected state is the half-engaged state. The cooling structure for a rotating electrical machine according to claim 3 ,
The cooling liquid inflow state changing means is driven by a clutch driving means for driving the clutch.

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